EP1315900B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP1315900B1
EP1315900B1 EP01964937A EP01964937A EP1315900B1 EP 1315900 B1 EP1315900 B1 EP 1315900B1 EP 01964937 A EP01964937 A EP 01964937A EP 01964937 A EP01964937 A EP 01964937A EP 1315900 B1 EP1315900 B1 EP 1315900B1
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EP
European Patent Office
Prior art keywords
armature
fuel injection
valve
valve needle
injection 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.)
Expired - Lifetime
Application number
EP01964937A
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German (de)
French (fr)
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EP1315900A1 (en
Inventor
Martin Mueller
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1315900A1 publication Critical patent/EP1315900A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—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
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/165—Filtering elements specially adapted in fuel inlets to injector

Definitions

  • the invention relates to a fuel injection valve according to the preamble of the main claim.
  • the disadvantage here is in particular the complex design with an additional component. Also, the large-area elastomer ring is unfavorable for the course of the magnetic field and makes it difficult to close the field lines and thus the achievement of high attraction forces in the opening movement of the fuel injection valve.
  • a further cylindrical mass is provided, which is movably clamped by two elastomeric rings in position and held. Upon impact of the valve needle on the valve seat, this second mass can move relative to the armature and valve needle and prevent bouncing of the valve needle.
  • a fuel injection valve which comprises a valve needle which cooperates with a valve seat surface to a sealing seat, and an armature acting on the valve needle, wherein the armature is arranged to be axially movable on the valve needle and of a damping element made of an elastomer is damped.
  • a first intermediate ring is arranged between the armature and the damping element.
  • the intermediate element and / or the flange have radial and / or axial channels which connect an internal volume located between the valve needle and the damping element to a central recess of the fuel injection valve.
  • the drainage channels serve to avoid disadvantageous bouncers of the armature or of the valve needle.
  • the fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that the armature and the valve needle are damped by a liquid damper, which is formed by the interaction of an elastomeric ring and a liquid-filled chamber between the armature and valve needle.
  • a liquid damper which is formed by the interaction of an elastomeric ring and a liquid-filled chamber between the armature and valve needle.
  • the throttle effect of the throttle gap between valve needle and armature wall is advantageous which is pressed during the closing movement of fuel from the annulus.
  • the fuel injection valve 1 is in the form of a fuel injection valve for fuel injection systems of mixture-compression, spark-ignited Internal combustion engine running.
  • the fuel injection valve 1 is suitable in particular for the direct injection of fuel into a combustion chamber, not shown, of an internal combustion engine.
  • the fuel injection valve 1 consists of a nozzle body 2, in which a valve needle 3 is arranged.
  • the valve needle 3 is in operative connection with a valve closing body 4, which cooperates with a arranged on a valve seat body 5 valve seat surface 6 to a sealing seat.
  • the fuel injection valve 1 in the exemplary embodiment is an inwardly opening fuel injection valve 1 which has an injection opening 7.
  • the nozzle body 2 is sealed by a seal 8 against the outer pole 9 of a magnetic coil 10.
  • the magnetic coil 10 is encapsulated in a coil housing 11 and wound on a bobbin 12, which rests against an inner pole 13 of the magnetic coil 10.
  • the inner pole 13 and, the outer pole 9 are separated by a constriction 26 and are connected to each other by a non-ferromagnetic connecting member 29.
  • the magnetic coil 10 is energized via a line 19 from a via an electrical plug contact 17 can be supplied with electric current.
  • the plug contact 17 is surrounded by a plastic casing 18, which may be molded on the
  • valve needle 3 is guided in a valve needle guide 14, which is designed disk-shaped.
  • armature 20 On the other side of the dial 15 is an armature 20. This is frictionally connected via a first flange 21 with the valve needle 3 in connection, which is connected by a weld 22 to the first flange 21.
  • a return spring 23 On the flange 21, a return spring 23 is supported, which is brought in the present design of the fuel injection valve 1 by a sleeve 24 to bias.
  • Fuel channels 30a to 30c which conduct the fuel, which is supplied via a central fuel supply 16 and filtered by a filter element 25, to the ejection opening 7.
  • the fuel injection valve 1 is sealed by a seal 28 against a fuel line, not shown.
  • annular damping element 32 On the discharge side of the armature 20, an annular damping element 32, which consists of an elastomer material, arranged. It rests on a second flange 31 which is non-positively connected to the valve needle 3 via a weld 33.
  • the first flange 21 is welded to the valve needle 3, the armature 20 and the damping element 32 attached and then the second flange 31 pressed under pressure on the damping element 32 and also with the valve needle. 3 welded.
  • the armature 20 has only a slight, strongly damped play between the first flange 21 and the damping element 32nd
  • the armature 20 In the idle state of the fuel injection valve 1, the armature 20 is acted upon by the return spring 23 counter to its stroke direction so that the valve closing body 4 is held on the valve seat 6 in sealing engagement. Upon energization of the magnetic coil 10, this builds up a magnetic field, which moves the armature 20 against the spring force of the return spring 23 in the stroke direction, wherein the stroke is determined by a located in the rest position between the inner pole 13 and the armature 20 working gap 27.
  • the armature 20 takes the flange 21, which is welded to the valve needle 3, also in the stroke direction with.
  • the valve closing body 4 communicating with the valve needle 3 lifts off from the valve seat surface 6 and the fuel guided via the fuel channels 30a to 30c is sprayed through the injection opening 7.
  • the armature 20 drops after sufficient degradation of the magnetic field by the pressure of the return spring 23 from the inner pole 13, whereby the standing with the valve needle 3 in connection flange 21 moves against the stroke direction.
  • the valve needle 3 is thereby moved in the same direction, whereby the valve closing body 4 touches on the valve seat surface 6 and the fuel injection valve is 1. founded.
  • Fig. 2 shows an excerpted sectional view of the designated in Fig. 1 with II section of the fuel injector 1. Matching components are provided with matching reference numerals.
  • the present first embodiment of a fuel injection valve 1 according to the invention on a discharge side 42 of the armature 20 an inner annular projection 34 and a funnel-shaped recess 35.
  • the fuel channel 30a opens into the funnel-shaped recess 35.
  • the annular projection 34 which is penetrated by the valve needle 3 in a central recess 38 of the armature 20, is supported on the damping element 32 and thus on the second flange 31, which is materially connected via the weld 33 with the valve needle 3.
  • the second flange 31 has an annular recess 36, in which the damping element 32 is arranged and which is covered cover-like by the annular projection 34.
  • the annular projection 34 lies here on the damping element 32.
  • the annular recess 36 has an inner edge 43 facing the valve needle 3 and a radially outer edge 44 which is axially higher than the inner edge 43.
  • the annular projection 34 closes the annular recess 36 to the outside, while in the idle state of the fuel injection valve 1 between the edge 43 and the projection 34, an axial gap 45 remains.
  • a radially through the valve needle 3 and the damping element 32 limited annular space 37 is formed in the annular recess 36 a radially through the valve needle 3 and the damping element 32 limited annular space 37 is formed.
  • the annular space 37 is filled with fuel, which flows via the acting as a throttle central recess 38 of the armature 20 into the annular space 37.
  • the fuel in the annular space 37 is compressed by the initially opposing movements of the armature 20 and the valve needle 3.
  • the armature 20 can swing through only to the point at which the gap 45 between the edge 43 and the projection 34 of the armature 20 is closed. Due to the closed shape of the annular space 37, the fuel can leave the annular space 37 only through the throttle gap 39 acting as a throttle between an inner wall 40 of the armature 20 and the valve needle 3.
  • the movement of the armature 20 and on the other hand the remindschwingterrorism the valve needle 3 is attenuated.
  • FIG. 3 shows in the same view as FIG. 2 a second exemplary embodiment of the fuel injection valve 1 according to the invention.
  • the second flange 31 is provided with a deeper annular recess 36 than in the previous embodiment.
  • the outer edge 44 of the second flange 31 is increased while the inner edge 43 is absent.
  • a lower end 46 of the supernatant 34 of the armature 20 is formed so that the damping element 32 is disposed radially between the thin end 46 of the supernatant 34 and the edge 44 of the second flange 31, wherein between the lower end 46 of the supernatant 34 and the second flange 45 is formed an axial gap.
  • the second embodiment of the fuel injection valve 1 according to the invention is not so much to an accurate and accurate production or obstruction of the individual components, whereby the production and installation of the components can be made cheaper.
  • the second embodiment of the fuel injection valve 1 is similar to the first embodiment shown in FIG.
  • the armature 20 swings through, whereby the damping element 32 and the fuel in the annular space 37 are compressed by the projection 34 of the armature 20.
  • the armature 20 can only so far swing through until the lower end 46 of the projection 34 impinges on the second flange 31.
  • the damping element 32 absorbs most of the kinetic energy of the armature 20, while the fuel displaced from the annular space 37 exits through the throttle gap 39 between the valve needle 3 and the inner wall 40 of the armature 20, whereby the swinging of the valve needle 3 is decelerated and the valve closing body 4 is prevented from again briefly withdraw from the valve seat surface 6.
  • the illustrated in Fig. 4 third embodiment of the fuel injection valve 1 according to the invention differs slightly in construction from the two previous embodiments.
  • the annular projection 34 of the armature 20 forms a cap-shaped cover sleeve 41, on which the projection 34 of the armature 20 is supported, the annular recess 36.
  • the annular recess 36 is open in the third embodiment in the outflow direction of the fuel.
  • the second flange 31 is formed flat here and closes the annular recess 36 in the form of a cover in the outflow direction.
  • the cover sleeve 41 has the particular advantage that it can be produced particularly easily as a separate component independently of the armature 20.
  • the damping element 32 is arranged, the annular space 37 is as in the previous embodiments with the throttle gap 39 between the inner wall 40 of the armature 20 and the valve needle 3 in connection.
  • the components of the third embodiment have the advantage that on the one hand they are particularly easy to produce and on the other hand, the armature 20 can be designed so that the introduced in the armature 20 fuel passage 30a can be easily processed and deburred on its downstream side.
  • the armature 20 When closing the fuel injection valve 1, the armature 20 in turn oscillates in Abspritzutter, whereby the cap-shaped cover sleeve 41 via the second flange 31st is pushed, since the outer diameter of the flange 31 corresponds to the inner diameter of the jacket portion of the cover sleeve 41 and is minimally smaller.
  • the gap 45 need not be limited by a particular geometric arrangement as in the embodiments described above, but in this case is equal to the height of the annulus 37.
  • the invention is not limited to the illustrated embodiments and e.g. also suitable for flat anchors or for any designs of fuel injection valves.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Hauptanspruchs.The invention relates to 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 Ventilschließkörper, der mit einer an einem Ventilsitzkörper ausgebildeten Ventilsitzfläche zu einem Dichtsitz zusammenwirkt, aufweist. Zur elektromagnetischen Betätigung des 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.It is already known from US 4,766,405 a fuel injection valve having a connected to a valve needle valve closing body which cooperates with a formed on a valve seat body valve seat surface to a sealing seat has. For electromagnetic actuation of the fuel injection valve, a magnetic coil is provided, which cooperates with an armature which is non-positively connected to the valve needle. To the armature and the valve needle, an additional mass is provided in a cylindrical shape, which is connected via an elastomer layer to the armature.

Nachteilig ist hierbei 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.The disadvantage here is in particular the complex design with an additional component. Also, the large-area elastomer ring is unfavorable for the course of the magnetic field and makes it difficult to close the field lines and thus the achievement of high attraction forces in the opening movement of the fuel injection valve.

Ebenfalls aus der oben genannten Druckschrift ist eine 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 den Ventilsitz kann sich diese zweite Masse relativ zu Anker und Ventilnadel bewegen und ein Prellen der Ventilnadel verhindern.Also from the above document an embodiment of a fuel injection valve is known in which for damping and Entprellung to the armature and the valve needle, a further cylindrical mass is provided, which is movably clamped by two elastomeric rings in position and held. Upon impact of the valve needle on the valve seat, this second mass can move relative to the armature and valve needle and prevent bouncing of the valve needle.

Nachteilig an dieser Ausführungsform ist der zusätzliche Aufwand und Platzbedarf. Auch ist der Anker nicht entkoppelt, wodurch sein Impuls bei der Ventilnadel die Neigung zu Prellern vergrößert.A disadvantage of this embodiment, the additional effort and space. Also, the armature is not decoupled, whereby its pulse at the valve needle increases the tendency 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 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 vollkommen undefiniert ist, werden Preller nur in beschränktem Maße vermieden. Insbesondere wird bei der aus der oben genannten Druckschrift bekannten Bauweise des Brennstoffeinspritzventils nicht vermieden, daß der Anker bei der Schließbewegung des Brennstoffeinspritzventils auf den dem Ventilschließkörper zugewandten Anschlag auftrifft und seinen Impuls auf die Ventilnadel überträgt. Diese schlagartige Impulsübertragung kann zusätzliche Preller des Ventilschließkörpers verursachen.From US 5,299,776 a fuel injection valve with a valve needle and an armature is known, which is movably guided on the valve needle and whose movement is limited in the stroke direction of the valve needle by a first stop and against the stroke direction by a second stop. The fixed by the two attacks axial movement of the armature 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 rebound of the valve needle from the valve seat surface during closing of the fuel injection valve within certain limits. However, since the axial position of the armature with respect to the valve needle by the free movement of the armature is completely undefined, Preller be avoided only to a limited extent. In particular, in the known from the above-mentioned document construction of the fuel injection valve is not avoided that the armature impinges on the valve closing body facing the stop during the closing movement of the fuel injection valve and transmits its pulse to the valve needle. This sudden pulse transmission can cause additional bumps of the valve closing body.

Es ist weiter aus der Praxis bekannt, den auf der Ventilnadel geführten Anker durch einen Elastomerring in seiner Position beweglich eingespannt zu befestigen. Hierzu wird der Anker zwischen zwei mit der Ventilnadel verschweißten Flanschen gehalten, wobei zwischen Anker und unterem Flansch ein Elastomerring liegt. Dabei tritt jedoch das Problem auf, daß zur Zuführung des Brennstoffs zum Dichtsitz eine Bohrung durch den Anker nötig ist. Die Bohrung durch den Anker ist nahe der Ventilnadel ausgeführt, wobei die dem Ventilsitz zugewandte Ausmündung der Bohrung teilweise durch den Elastomerring verdeckt wird. Dadurch kommt es zu einer ungleichmäßigen Pressung des Elastomerrings, die Bohrungskanten führen schließlich durch Kantenpressung zu einer Zerstörung des Elastomerrings. Daneben kommt es zu Schwingungsanregungen des nicht gestützten Elastomerrings, die ebenfalls zur Störung durch die Bohrungskanten beitragen. Dies tritt besonders bei niedrigen Temperaturen auf, wenn das Elastomer in einen steifen Zustand übergeht.It is further known from practice to fasten the armature guided on the valve needle by an elastomeric ring in its position movable clamped. For this purpose, the armature is held between two welded to the valve needle flanges, wherein between the armature and lower flange is an elastomeric ring. However, the problem arises that a bore through the armature is necessary to supply the fuel to the sealing seat. The bore through the armature is carried out near the valve needle, wherein the valve seat facing the mouth of the bore is partially covered by the elastomeric ring. This leads to an uneven pressing of the elastomer ring, the bore edges eventually lead by edge pressure to a destruction of the elastomer ring. In addition, it comes to vibrational excitations of the non-supported elastomeric ring, which also contribute to the disturbance by the bore edges. This occurs especially at low temperatures when the elastomer goes into a stiff state.

Aus der nicht vorveröffentlichten WO 02/12709 A 1 ist bereits ein Brennstoffeinspritzventil bekannt, das eine Ventilnadel, die mit einer Ventilsitzfläche zu einem Dichtsitz zusammenwirkt, und einen an der Ventilnadel angreifenden Anker umfasst, wobei der Anker an der Ventilnadel axial beweglich angeordnet ist und von einem aus einem Elastomer bestehenden Dämpfungselement gedämpft wird. Zwischen dem Anker und dem Dämpfungselement ist dabei ein erster Zwischenring angeordnet. Das Dämpfungselement liegt auf einem mit der Ventilnadel kraftschlüssig verbundenen Flansch auf Der Zwischenring und/oder der Flansch weisen radiale und/oder axiale Kanäle auf, welche ein zwischen der Ventilnadel und dem Dämpfungselement befindliches Innenvolumen mit einer zentralen Ausnehmung des Brennstoffeinspritzventils verbinden. Die Drainagekanäle dienen der Vermeidung von nachteiligen Prellern des Ankers bzw. der Ventilnadel.From the unpublished WO 02/12709 A 1, a fuel injection valve is already known, which comprises a valve needle which cooperates with a valve seat surface to a sealing seat, and an armature acting on the valve needle, wherein the armature is arranged to be axially movable on the valve needle and of a damping element made of an elastomer is damped. Between the armature and the damping element, a first intermediate ring is arranged. The intermediate element and / or the flange have radial and / or axial channels which connect an internal volume located between the valve needle and the damping element to a central recess of the fuel injection valve. The drainage channels serve to avoid disadvantageous bouncers of the armature or of the valve needle.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß der Anker und die Ventilnadel durch einen Flüssigkeitsdämpfer gedämpft werden, welcher durch das Zusammenwirken eines Elastomerrings und einer flüssigkeitsgefüllten Kammer zwischen Anker und Ventilnadel gebildet wird. Dadurch werden einerseits Ankerpreller vom unteren Ankeranschlag und andererseits Ventilnadelpreller vom Dichtsitz wirkungsvoll gedämpft.The fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that the armature and the valve needle are damped by a liquid damper, which is formed by the interaction of an elastomeric ring and a liquid-filled chamber between the armature and valve needle. As a result, on the one hand anchor bouncers from the lower anchor stopper and the other hand valve needle bouncers are effectively damped from the sealing seat.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterentwicklungen des im Hauptanspruch angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous developments of the fuel injection valve specified in the main claim are possible.

Von Vorteil ist insbesondere die Drosselwirkung des Drosselspalts zwischen Ventilnadel und Ankerwandung, in welchen bei der Schließbewegung Brennstoff aus dem Ringraum gedrückt wird.The throttle effect of the throttle gap between valve needle and armature wall, in particular, is advantageous which is pressed during the closing movement of fuel from the annulus.

Zeichnungdrawing

Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
einen schematischen Schnitt durch ein Beispiel eines Brennstoffeinspritzventils mit Ankerentprellung gemäß dem Stand der Technik,
Fig. 2
eine vergrößerte Ansicht eines ersten Ausführungsbeispiels des erfindungsgemäßen Brennstoffeinspritzventils im Bereich II in Fig. 1,
Fig. 3
eine Ansicht eines zweiten Ausführungsbeispiels des erfindungsgemäßen Brennstoffeinspritzventils im gleichen Bereich wie in Fig. 2, und
Fig. 4
eine Ansicht eines dritten Ausführungsbeispiels des erfindungsgemäßen Brennstoffeinspritzventils im gleichen Bereich wie in Fig. 2 und 3.
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
FIG. 2 is a schematic section through an example of a prior art armature debounce fuel injector; FIG.
Fig. 2
an enlarged view of a first embodiment of the fuel injection valve according to the invention in the area II in Fig. 1,
Fig. 3
a view of a second embodiment of the fuel injection valve according to the invention in the same area as in Fig. 2, and
Fig. 4
a view of a third embodiment of the fuel injection valve according to the invention in the same area as in Fig. 2 and 3.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Bevor anhand der Fig. 2 bis 4 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 Brennstoffeinspritzventil gemäß dem Stand der Technik bezüglich seiner wesentlichen Bauteile kurz erläutert werden.2 to 4 embodiments of a fuel injection valve 1 according to the invention will be briefly explained for better understanding of the invention with reference to FIG. 1, apart from the inventive measures identical fuel injector according to the prior art with respect to its essential components.

Das Brennstoffeinspritzventil 1 ist in der Form eines Brennstoffeinspritzventils für Brennstoffeinspritzanlagen von gemischverdichtenden, fremdgezündeten Brennkraftmaschinen ausgeführt. Das Brennstoffeinspritzventil 1 eignet sich insbesondere zum direkten Einspritzen von Brennstoff in einen nicht dargestellten Brennraum einer Brennkraftmaschine.The fuel injection valve 1 is in the form of a fuel injection valve for fuel injection systems of mixture-compression, spark-ignited Internal combustion engine running. The fuel injection valve 1 is suitable in particular for the direct injection of fuel 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 einem Ventilschließkörper 4, der mit einer an 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 sind 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 injection valve 1 consists of a nozzle body 2, in which a valve needle 3 is arranged. The valve needle 3 is in operative connection with a valve closing body 4, which cooperates with a arranged on a valve seat body 5 valve seat surface 6 to a sealing seat. The fuel injection valve 1 in the exemplary embodiment is an inwardly opening fuel injection valve 1 which has an injection opening 7. The nozzle body 2 is sealed by a seal 8 against the outer pole 9 of a magnetic coil 10. The magnetic coil 10 is encapsulated in a coil housing 11 and wound on a bobbin 12, which rests against an inner pole 13 of the magnetic coil 10. The inner pole 13 and, the outer pole 9 are separated by a constriction 26 and are connected to each other by a non-ferromagnetic connecting member 29. The magnetic coil 10 is energized via a line 19 from a via an electrical plug contact 17 can be supplied with electric current. The plug contact 17 is surrounded by a plastic casing 18, which may be molded on 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 ein 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 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 designed disk-shaped. On the other side of the dial 15 is an armature 20. This is frictionally connected via a first flange 21 with the valve needle 3 in connection, which is connected by a weld 22 to the first flange 21. On the flange 21, a return spring 23 is supported, which is brought in the present design of the fuel injection valve 1 by a sleeve 24 to bias. Run in the valve needle guide 14, the armature 20 and the valve seat body 5 Fuel channels 30a to 30c, which conduct the fuel, which is supplied via a central fuel supply 16 and filtered by a filter element 25, to the ejection opening 7. The fuel injection valve 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.On the discharge side of the armature 20, an annular damping element 32, which consists of an elastomer material, arranged. It rests on a second flange 31 which is non-positively connected to the valve needle 3 via a weld 33.

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 Dämpfungselement 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 Dämpfungselement 32.In the manufacture of the consisting of armature 20 and valve needle 3 component, the first flange 21 is welded to the valve needle 3, the armature 20 and the damping element 32 attached and then the second flange 31 pressed under pressure on the damping element 32 and also with the valve needle. 3 welded. In this way, the armature 20 has only a slight, strongly damped play between the first flange 21 and the damping element 32nd

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 13 und dem Anker 20 befindlichen Arbeitsspalt 27 vorgegeben ist. Der Anker 20 nimmt den 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 counter to its stroke direction so that the valve closing body 4 is held on the valve seat 6 in sealing engagement. Upon energization of the magnetic coil 10, this builds up a magnetic field, which moves the armature 20 against the spring force of the return spring 23 in the stroke direction, wherein the stroke is determined by a located in the rest position between the inner pole 13 and the armature 20 working gap 27. The armature 20 takes the flange 21, which is welded to the valve needle 3, also in the stroke direction with. The valve closing body 4 communicating with the valve needle 3 lifts off from the valve seat surface 6 and the fuel guided via the fuel channels 30a to 30c is sprayed through the injection 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 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 turned off, the armature 20 drops after sufficient degradation of the magnetic field by the pressure of the return spring 23 from the inner pole 13, whereby the standing with the valve needle 3 in connection flange 21 moves against the stroke direction. The valve needle 3 is thereby moved in the same direction, whereby the valve closing body 4 touches on the valve seat surface 6 and the fuel injection valve is 1.geschlossen.

In dieser Phase treten die Preller auf, welche zum einen durch den Anker 20, welcher beim Schließvorgang des Brennstoffeinspritzventils 1 in Abspritzrichtung vom Innenpol 13 abfällt, und zum anderen durch die Ventilnadel 3 bzw. den am Dichtsitz aufsetzenden Ventilschließkörper 4 hervorgerufen werden.In this phase, the bouncers occur, which on the one hand by the armature 20, which falls off in the Abspritzrichtung of the fuel injection valve 1 from the inner pole 13, and on the other by the valve needle 3 and the sealing seat placed on the valve closing body 4 are caused.

Fig. 2 zeigt in einer auszugsweisen Schnittdarstellung den in Fig. 1 mit II bezeichneten Ausschnitt des Brennstoffeinspritzventils 1. Übereinstimmende Bauteile sind mit übereinstimmenden Bezugszeichen versehen.Fig. 2 shows an excerpted sectional view of the designated in Fig. 1 with II section of the fuel injector 1. Matching components are provided with matching reference numerals.

Gegenüber dem in Fig. 1 beschriebenen Brennstoffeinspritzventil 1 gemäß dem Stand der Technik weist das vorliegende erste Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils 1 an einer abspritzseitigen Seite 42 des Ankers 20 einen inneren kreisringförmigen Überstand 34 und eine trichterförmige Ausnehmung 35 auf. Der Brennstoffkanal 30a mündet in der trichterförmigen Ausnehmung 35 aus. Der kreisringförmige Überstand 34, der von der Ventilnadel 3 in einer zentralen Ausnehmung 38 des Ankers 20 durchgriffen wird, stützt sich auf dem Dämpfungselement 32 und somit auf dem zweiten Flansch 31 ab, welcher über die Schweißnaht 33 mit der Ventilnadel 3 stoffschlüssig verbunden ist.Compared with the fuel injection valve 1 according to the prior art described in Fig. 1, the present first embodiment of a fuel injection valve 1 according to the invention on a discharge side 42 of the armature 20 an inner annular projection 34 and a funnel-shaped recess 35. The fuel channel 30a opens into the funnel-shaped recess 35. The annular projection 34, which is penetrated by the valve needle 3 in a central recess 38 of the armature 20, is supported on the damping element 32 and thus on the second flange 31, which is materially connected via the weld 33 with the valve needle 3.

Der zweite Flansch 31 weist eine ringförmige Vertiefung 36 auf, in welcher das Dämpfungselement 32 angeordnet ist und die durch den kreisringförmigen Überstand 34 deckelähnlich abgedeckt ist. Der kreisringförmige Überstand 34 liegt dabei auf dem Dämpfungselement 32 auf. Die ringförmige Vertiefung 36 weist eine der Ventilnadel 3 zugewandte innere Kante 43 und eine radial äußere Kante 44 auf, welche axial höher als die innere Kante 43 ist. Dadurch schließt der kreisringförmige Überstand 34 die ringförmige Vertiefung 36 nach außen ab, während im Ruhezustand des Brennstoffeinspritzventils 1 zwischen der Kante 43 und dem Überstand 34 ein axialer Spalt 45 verbleibt. In der ringförmigen Vertiefung 36 ist ein radial durch die Ventilnadel 3 und das Dämpfungselement 32 begrenzter Ringraum 37 ausgebildet. Der Ringraum 37 ist mit Brennstoff gefüllt, welcher über die wie eine Drossel wirkende zentrale Ausnehmung 38 des Ankers 20 in den Ringraum 37 einfließt.The second flange 31 has an annular recess 36, in which the damping element 32 is arranged and which is covered cover-like by the annular projection 34. The annular projection 34 lies here on the damping element 32. The annular recess 36 has an inner edge 43 facing the valve needle 3 and a radially outer edge 44 which is axially higher than the inner edge 43. As a result, the annular projection 34 closes the annular recess 36 to the outside, while in the idle state of the fuel injection valve 1 between the edge 43 and the projection 34, an axial gap 45 remains. In the annular recess 36 a radially through the valve needle 3 and the damping element 32 limited annular space 37 is formed. The annular space 37 is filled with fuel, which flows via the acting as a throttle central recess 38 of the armature 20 into the annular space 37.

Sobald beim Schließen des Brennstoffeinspritzventils 1 der Ventilschließkörper 4 auf der Ventilsitzfläche 6 aufsetzt, schwingt der Anker 20, welcher beweglich an der Ventilnadel 3 angeordnet ist, durch. Gewöhnlich führt dieses Durchschwingen zu einer erneuten Bewegung des Ankers 20 in Hubrichtung, wodurch es zu einem kurzzeitigen, unerwünschten weiteren Öffnungsvorgang des Brennstoffeinspritzventils 1 kommen kann, da dadurch auch die Ventilnadel 3 nochmals in Hubrichtung bewegt wird. Dies wird durch den in dem Ringraum 37 enthaltenen Brennstoff sowie das Dämpfungselement 32 auf zweierlei Weise verhindert.As soon as the valve closing body 4 touches down on the valve seat surface 6 when closing the fuel injection valve 1, the armature 20, which is arranged movably on the valve needle 3, oscillates. Usually, this swinging leads to a renewed movement of the armature 20 in the stroke direction, which can lead to a brief, undesirable further opening operation of the fuel injection valve 1, as this also the valve needle 3 is moved again in the stroke direction. This is prevented by the fuel contained in the annular space 37 and the damping element 32 in two ways.

Einerseits wird der Brennstoff im Ringraum 37 durch die zunächst gegenläufigen Bewegungen des Ankers 20 und der Ventilnadel 3 komprimiert. Der Anker 20 kann nur noch bis zu dem Punkt, an welchem der Spalt 45 zwischen der Kante 43 und dem Überstand 34 des Ankers 20 geschlossen ist, durchschwingen. Durch die abgeschlossene Form des Ringraums 37 kann der Brennstoff nur durch den wie eine Drossel wirkenden Drosselspalt 39 zwischen einer inneren Wandung 40 des Ankers 20 und der Ventilnadel 3 den Ringraum 37 verlassen. Dadurch wird einerseits die Bewegung des Ankers 20 und andererseits die Rückschwingbewegung der Ventilnadel 3 gedämpft. Andererseits wird insbesondere die Rückschwingbewegung des Ankers 20 durch das Dämpfungselement 32, welches in der ringförmigen Vertiefung 36 angeordnet ist, wirkungsvoll gedämpft, da das Dämpfungselement 32 den größten Teil der Bewegungsenergie des Ankers 20 in Verformungsenergie des Dämpfungselements 32 umwandelt und weil bei der Rückschwingbewegung ein Unterdruck im Ringraum 37 entsteht.On the one hand, the fuel in the annular space 37 is compressed by the initially opposing movements of the armature 20 and the valve needle 3. The armature 20 can swing through only to the point at which the gap 45 between the edge 43 and the projection 34 of the armature 20 is closed. Due to the closed shape of the annular space 37, the fuel can leave the annular space 37 only through the throttle gap 39 acting as a throttle between an inner wall 40 of the armature 20 and the valve needle 3. As a result, on the one hand, the movement of the armature 20 and on the other hand, the Rückschwingbewegung the valve needle 3 is attenuated. On the other hand, in particular the Rückschwingbewegung of the armature 20 by the damping element 32, which is arranged in the annular recess 36, effectively damped, since the damping element 32 converts most of the kinetic energy of the armature 20 in the deformation energy of the damping element 32 and because in the Rückschwingbewegung a negative pressure in the annular space 37 is formed.

Fig. 3 zeigt in derselben Ansicht wie Fig. 2 ein zweites Ausführungsbeispiel des erfindungsgemäßen Brennstoffeinspritzventils 1.FIG. 3 shows in the same view as FIG. 2 a second exemplary embodiment of the fuel injection valve 1 according to the invention.

Bei diesem Ausführungsbeispiel ist der zweite Flansch 31 mit einer tieferen ringförmigen Vertiefung 36 versehen als im vorigen Ausführungsbeispiel. Die äußere Kante 44 des zweiten Flansches 31.ist erhöht, während die innere Kante 43 fehlt. Ein unteres Ende 46 des Überstandes 34 des Ankers 20 ist dabei so ausgebildet, daß das Dämpfungselement 32 radial zwischen dem dünnen Ende 46 des Überstandes 34 und der Kante 44 des zweiten Flansches 31 angeordnet ist, wobei zwischen dem unteren Ende 46 des Überstands 34 und dem zweiten Flansch ein axialer Spalt 45 ausgebildet ist. Bei gleichem Außendurchmesser des zweiten Flansches 31 wie in Fig. 2 wird dadurch das wirksame Dämpfungsvolumen, welches in diesem Fall unterhalb des Dämpfungselements 32 angeordnet ist, vergrößert.In this embodiment, the second flange 31 is provided with a deeper annular recess 36 than in the previous embodiment. The outer edge 44 of the second flange 31 is increased while the inner edge 43 is absent. A lower end 46 of the supernatant 34 of the armature 20 is formed so that the damping element 32 is disposed radially between the thin end 46 of the supernatant 34 and the edge 44 of the second flange 31, wherein between the lower end 46 of the supernatant 34 and the second flange 45 is formed an axial gap. With the same outside diameter of the second flange 31 as in FIG. 2, the effective damping volume, which in this case is arranged below the damping element 32, is thereby increased.

Insbesondere kommt es beim zweiten Ausführungsbeispiel des erfindungsgemäßen Brennstoffeinspritzventils 1 nicht so sehr auf eine paßgenaue und exakte Fertigung bzw. Verbauung der einzelnen Bauteile an, wodurch die Herstellung und Verbauung der Bauteile kostengünstiger gestaltet werden kann.In particular, it comes in the second embodiment of the fuel injection valve 1 according to the invention is not so much to an accurate and accurate production or obstruction of the individual components, whereby the production and installation of the components can be made cheaper.

In der Wirkungsweise gleicht das zweite Ausführungsbeispiel des erfindungsgemäßen Brennstoffeinspritzventils 1 dem in Fig. 2 dargestellten ersten Ausführungsbeispiel. Beim Schließen des Brennstoffeinspritzventils 1 schwingt der Anker 20 durch, wodurch das Dämpfungselement 32 sowie der Brennstoff in dem Ringraum 37 durch den Überstand 34 des Ankers 20 komprimiert werden. Der Anker 20 kann nur soweit durchschwingen, bis das untere Ende 46 des Überstands 34 auf dem zweiten Flansch 31 auftrifft. Das Dämpfungselement 32 nimmt den größten Teil der Bewegungsenergie des Ankers 20 auf, während der aus dem Ringraum 37 verdrängte Brennstoff über den Drosselspalt 39 zwischen der Ventilnadel 3 und der inneren Wandung 40 des Ankers 20 austritt, wodurch das Durchschwingen der Ventilnadel 3 abgebremst und der Ventilschließkörper 4 daran gehindert wird, nochmals kurzzeitig von der Ventilsitzfläche 6 abzuheben.In the mode of operation, the second embodiment of the fuel injection valve 1 according to the invention is similar to the first embodiment shown in FIG. When closing the fuel injection valve 1, the armature 20 swings through, whereby the damping element 32 and the fuel in the annular space 37 are compressed by the projection 34 of the armature 20. The armature 20 can only so far swing through until the lower end 46 of the projection 34 impinges on the second flange 31. The damping element 32 absorbs most of the kinetic energy of the armature 20, while the fuel displaced from the annular space 37 exits through the throttle gap 39 between the valve needle 3 and the inner wall 40 of the armature 20, whereby the swinging of the valve needle 3 is decelerated and the valve closing body 4 is prevented from again briefly withdraw from the valve seat surface 6.

Das in Fig. 4 dargestellte dritte Ausführungsbeispiel des erfindungsgemäßen Brennstoffeinspritzventils 1 unterscheidet sich in der Konstruktion geringfügig von den beiden vorhergehenden Ausführungsbeispielen. Statt des kreisringförmigen Überstands 34 des Ankers 20 bildet eine kappenförmige Abdeckhülse 41, auf der sich der Überstand 34 des Ankers 20 abstützt, die ringförmige Vertiefung 36. Die ringförmige Vertiefung 36 ist im dritten Ausführungsbeispiel in Abströmrichtung des Brennstoffs geöffnet. Der zweite Flansch 31 ist hier flach ausgebildet und schließt die ringförmige Vertiefung 36 deckelförmig in Abströmrichtung ab. Die Abdeckhülse 41 hat den besonderen Vorteil, daß sie als gesondertes Bauteil unabhängig vom Anker 20 besonders leicht herstellbar ist.The illustrated in Fig. 4 third embodiment of the fuel injection valve 1 according to the invention differs slightly in construction from the two previous embodiments. Instead of the annular projection 34 of the armature 20 forms a cap-shaped cover sleeve 41, on which the projection 34 of the armature 20 is supported, the annular recess 36. The annular recess 36 is open in the third embodiment in the outflow direction of the fuel. The second flange 31 is formed flat here and closes the annular recess 36 in the form of a cover in the outflow direction. The cover sleeve 41 has the particular advantage that it can be produced particularly easily as a separate component independently of the armature 20.

In der ringförmigen Vertiefung 36 der Abdeckhülse 41 ist das Dämpfungselement 32 angeordnet, der Ringraum 37 steht wie in den vorherigen Ausführungsbeispielen mit dem Drosselspalt 39 zwischen der inneren Wandung 40 des Ankers 20 und der Ventilnadel 3 in Verbindung. Die Bauteile des dritten Ausführungsbeispiels haben den Vorteil, daß sie einerseits besonders leicht herstellbar sind und andererseits der Anker 20 so gestaltet werden kann, daß der im Anker 20 eingebrachte Brennstoffkanal 30a an seiner stromabwärtigen Seite leichter bearbeitet und entgratet werden kann.In the annular recess 36 of the cover 41, the damping element 32 is arranged, the annular space 37 is as in the previous embodiments with the throttle gap 39 between the inner wall 40 of the armature 20 and the valve needle 3 in connection. The components of the third embodiment have the advantage that on the one hand they are particularly easy to produce and on the other hand, the armature 20 can be designed so that the introduced in the armature 20 fuel passage 30a can be easily processed and deburred on its downstream side.

Beim Schließen des Brennstoff einspritzventils 1 schwingt der Anker 20 wiederum in Abspritzrichtung durch, wodurch die kappenförmige Abdeckhülse 41 über den zweiten Flansch 31 geschoben wird, da der Außendurchmesser des Flansches 31 dem Innendurchmesser des Mantelbereichs der Abdeckhülse 41 entspricht bzw. minimal kleiner ist. Im vorliegenden Ausführungsbeispiel braucht vorteilhafterweise der Spalt 45 nicht durch eine besondere geometrische Anordnung begrenzt zu werden wie in den oben beschriebenen Ausführungsbeispielen, sondern ist in diesem Fall gleich der Höhe des Ringraums 37. Das zwischen der Abdeckhülse 41 und dem zweiten Flansch 31 liegende Dämpfungselement 32 sowie der im Ringraum 37 vorhandene Brennstoff werden durch die Bewegung komprimiert, das Dämpfungselement 32 nimmt dabei die Bewegungsenergie des Ankers 20 auf, während der Brennstoff aus dem Ringraum 37 in den Drosselspalt 39 zwischen der Ventilnadel 3 und der inneren Wandung 40 des Ankers 20 verdrängt wird. Durch die Viskosität des Brennstoffs bzw. die Drosselwirkung des Drosselspalts 39 wird das Durchschwingen der Ventilnadel 3 gedämpft.When closing the fuel injection valve 1, the armature 20 in turn oscillates in Abspritzrichtung, whereby the cap-shaped cover sleeve 41 via the second flange 31st is pushed, since the outer diameter of the flange 31 corresponds to the inner diameter of the jacket portion of the cover sleeve 41 and is minimally smaller. In the present embodiment, advantageously, the gap 45 need not be limited by a particular geometric arrangement as in the embodiments described above, but in this case is equal to the height of the annulus 37. The lying between the cover 41 and the second flange 31 damping element 32 and the existing fuel in the annular space 37 are compressed by the movement, the damping element 32 absorbs the kinetic energy of the armature 20, while the fuel from the annular space 37 in the throttle gap 39 between the valve needle 3 and the inner wall 40 of the armature 20 is displaced. Due to the viscosity of the fuel or the throttling action of the throttle gap 39, the swinging through of the valve needle 3 is damped.

Die Erfindung ist nicht auf die dargestellten Ausführungsbeispiele beschränkt und z.B. auch für Flachanker bzw. für beliebige Bauformen von Brennstoffeinspritzventilen geeignet.The invention is not limited to the illustrated embodiments and e.g. also suitable for flat anchors or for any designs of fuel injection valves.

Claims (12)

  1. Fuel injection valve (1), in particular fuel injection valve for fuel injection systems of internal combustion engines, with a valve needle (3), the valve-closing body (4) of which co-operates with a valve-seat surface (6) to form a sealing seat, and with an armature (20) acting on the valve needle (3), the armature (20) being arranged axially movably on the valve needle (3) and being damped by a damping element (32) which consists of an elastomer and which is arranged between a flange (31) connected non-positively to the valve needle (3) and the armature (20), characterized in that the flange (31) has formed on it an annular depression (36) in which the damping element (32) is arranged, and in that an annular space (37), which is filled with fuel, is formed between the valve needle (3) and the damping element (32), the annular space (37) being connected to a throttle gap (39) of the valve needle (3).
  2. Fuel injection valve according to Claim 1, characterized in that the throttle gap (39) is formed between the valve needle (3) and an inner wall (40) of the armature (20).
  3. Fuel injection valve according to Claim 1 or 2, characterized in that a circularly annular projection (34) of the armature (20) covers the annular depression (36).
  4. Fuel injection valve according to Claim 3, characterized in that the projection (34) of the armature (20) lies on the damping element (32) arranged in the annular depression (36).
  5. Fuel injection valve according to one of Claims 1 to 4, characterized in that the armature (20) has, on an outflow side (42), a funnel-shaped recess (35), into which issues a fuel duct (30a) penetrating through the armature (20).
  6. Fuel injection valve according to one of Claims 1 to 5, characterized in that an inner edge (43), facing the valve needle (3), of the flange (31) is lower than an outer edge (44) of the flange (32).
  7. Fuel injection valve according to Claim 6, characterized in that a gap (45) is formed between the inner edge (43) and a projection (34) of the armature (20).
  8. Fuel injection valve according to Claim 7, characterized in that the gap (45) is connected to the throttle gap (39).
  9. Fuel injection valve according to one of Claims 4, 7 or 8, characterized in that the projection (34) has a lower end (46), the diameter of which is smaller than the diameter of the flange (31).
  10. Fuel injection valve according to Claim 9, characterized in that the damping element (32) is tension-mounted radially between the lower end (46) of the projection (34) and the flange (31).
  11. Fuel injection valve (1), in particular fuel injection valve for fuel injection systems of internal combustion engines, with a valve needle (3), the valve-closing body (4) of which co-operates with a valve-seat surface (6) to form a sealing seat, and with an armature (20) acting on the valve needle (3), the armature (20) being axially movably arranged on the valve needle (3) and being damped by a damping element (32) which consists of an elastomer and which is arranged between a flange (31) connected non-positively to the valve needle (3) and the armature (20), characterized in that a circularly annular projection (34) is provided on the armature (20), and the projection (34) is supported on a covering sleeve (41) which is designed in the form of a cap with an annular depression (36) and is penetrated by the valve needle (3), and the flange (31) has a flat disc-shaped design, the damping element (32) being arranged in the annular depression (36), and in that an annular space (37), which is filled with fuel, is formed between the valve needle (3) and the damping element (32), the annular space (37) being connected to a throttle gap (39) at the valve needle (3).
  12. Fuel injection valve according to Claim 11, characterized in that the flange (31) has an outside diameter which corresponds to the inside diameter of the covering sleeve (41).
EP01964937A 2000-09-01 2001-08-25 Fuel injection valve Expired - Lifetime EP1315900B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10043085A DE10043085A1 (en) 2000-09-01 2000-09-01 Fuel injector
DE10043085 2000-09-01
PCT/DE2001/003266 WO2002018776A1 (en) 2000-09-01 2001-08-25 Fuel injection valve

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EP1315900A1 EP1315900A1 (en) 2003-06-04
EP1315900B1 true EP1315900B1 (en) 2006-05-03

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US (1) US6745993B2 (en)
EP (1) EP1315900B1 (en)
JP (1) JP2004507661A (en)
KR (1) KR20020044177A (en)
CN (1) CN1255627C (en)
CZ (1) CZ20021505A3 (en)
DE (2) DE10043085A1 (en)
WO (1) WO2002018776A1 (en)

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19950761A1 (en) * 1999-10-21 2001-04-26 Bosch Gmbh Robert Fuel injection valve has supporting ring between elastomeric ring and armature that supports elastomeric ring axially near opening of fuel channel in armature and radially on shoulder
DE10140795A1 (en) 2001-08-20 2003-03-06 Bosch Gmbh Robert Fuel injector
DE10256948A1 (en) * 2002-12-05 2004-06-24 Robert Bosch Gmbh Fuel injector
JP4038462B2 (en) * 2003-09-11 2008-01-23 三菱電機株式会社 Fuel injection valve
JP4064934B2 (en) * 2004-02-27 2008-03-19 三菱重工業株式会社 Solenoid valve device
DE102004024533A1 (en) * 2004-05-18 2005-12-15 Robert Bosch Gmbh Fuel injector
CN100389258C (en) * 2004-06-02 2008-05-21 株式会社电装 Fuel injection valve
DE102004037250B4 (en) * 2004-07-31 2014-01-09 Robert Bosch Gmbh Fuel injector
US7900604B2 (en) * 2005-06-16 2011-03-08 Siemens Diesel Systems Technology Dampening stop pin
JP4428357B2 (en) * 2006-04-03 2010-03-10 株式会社デンソー Fuel injection valve
EP2067982B1 (en) * 2006-09-25 2013-01-16 Hitachi Ltd. Fuel injection valve
DE102006052817A1 (en) * 2006-11-09 2008-05-15 Robert Bosch Gmbh Fuel injection valve for e.g. direct injection of fuel into combustion chamber of internal combustion engine, has valve seat body and closing body provided with rigidity-reducing element that is designed as recess i.e. circulating groove
US8556194B2 (en) * 2010-06-23 2013-10-15 Delphi Technologies, Inc. Fuel injector
US9346074B2 (en) 2010-09-13 2016-05-24 Nordson Corporation Conformal coating applicator and method
US8534639B1 (en) * 2012-04-18 2013-09-17 HUSCO Automotive Holdings, Inc. Solenoid valve with a digressively damped armature
EP3076004B1 (en) * 2015-04-02 2018-09-12 Continental Automotive GmbH Valve assembly with a particle retainer element and fluid injection valve
DE102015213216A1 (en) * 2015-07-15 2017-01-19 Robert Bosch Gmbh Valve for metering a fluid
US10731614B2 (en) 2015-10-15 2020-08-04 Continental Automotive Gmbh Fuel injection valve with an anti bounce device
DE102017207845A1 (en) * 2017-05-10 2018-11-15 Robert Bosch Gmbh Valve for metering a fluid
US20190093038A1 (en) * 2017-09-22 2019-03-28 Leonard Ortiz System for Gasification on Demand
CN209164045U (en) * 2018-11-19 2019-07-26 浙江锐韦机电科技有限公司 Integrated pump valve mechanism

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002012709A1 (en) * 2000-08-10 2002-02-14 Robert Bosch Gmbh Fuel injection valve

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2114961A (en) * 1934-08-20 1938-04-19 Honeywell Regulator Co Electromagnetic valve
US2392741A (en) * 1943-10-21 1946-01-08 Wilbur F Hurlburt Dispensing valve
DE3521040A1 (en) * 1985-06-12 1986-12-18 Vdo Adolf Schindling Ag, 6000 Frankfurt INJECTION VALVE
US4766405A (en) 1987-04-14 1988-08-23 Allied Corporation Dynamic energy absorber
GB8729087D0 (en) * 1987-12-12 1988-01-27 Lucas Ind Plc Control valve
US4878650A (en) * 1988-04-29 1989-11-07 Allied-Signal Inc. Armature with shear stress damper
JP2997751B2 (en) 1990-10-31 2000-01-11 ヤマハ発動機株式会社 Solenoid valve device
US5288025A (en) * 1992-12-18 1994-02-22 Chrysler Corporation Fuel injector with a hydraulically cushioned valve
US5299776A (en) 1993-03-26 1994-04-05 Siemens Automotive L.P. Impact dampened armature and needle valve assembly
DE19707666C2 (en) * 1997-02-26 1999-12-02 Ford Global Tech Inc Solenoid valve, in particular for heating systems in motor vehicles
DE19816315A1 (en) * 1998-04-11 1999-10-14 Bosch Gmbh Robert Fuel injector
DE19855547A1 (en) * 1998-12-02 2000-06-08 Bosch Gmbh Robert Electromagnetically actuated valve
US6318646B1 (en) * 1999-03-26 2001-11-20 MAGNETI MARELLI S.p.A. Fuel injector
JP2002168160A (en) * 2000-12-01 2002-06-14 Mitsubishi Electric Corp Fuel injection valve

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002012709A1 (en) * 2000-08-10 2002-02-14 Robert Bosch Gmbh Fuel injection valve

Also Published As

Publication number Publication date
EP1315900A1 (en) 2003-06-04
KR20020044177A (en) 2002-06-14
DE10043085A1 (en) 2002-03-14
US20030146400A1 (en) 2003-08-07
CN1388862A (en) 2003-01-01
US6745993B2 (en) 2004-06-08
CZ20021505A3 (en) 2003-10-15
WO2002018776A1 (en) 2002-03-07
CN1255627C (en) 2006-05-10
DE50109710D1 (en) 2006-06-08
JP2004507661A (en) 2004-03-11

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