EP1299638A1 - Fuel injection valve - Google Patents

Fuel injection valve

Info

Publication number
EP1299638A1
EP1299638A1 EP01989419A EP01989419A EP1299638A1 EP 1299638 A1 EP1299638 A1 EP 1299638A1 EP 01989419 A EP01989419 A EP 01989419A EP 01989419 A EP01989419 A EP 01989419A EP 1299638 A1 EP1299638 A1 EP 1299638A1
Authority
EP
European Patent Office
Prior art keywords
swirl
fuel injection
injection valve
fuel
membrane
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
EP01989419A
Other languages
German (de)
French (fr)
Other versions
EP1299638B1 (en
Inventor
Fevzi Yildirim
Guenther Hohl
Michael Huebel
Norbert Keim
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 EP1299638A1 publication Critical patent/EP1299638A1/en
Application granted granted Critical
Publication of EP1299638B1 publication Critical patent/EP1299638B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0671—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
    • 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
    • F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging orifices
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size

Definitions

  • the invention relates to a fuel injector according to the preamble of the main claim.
  • AI is a fuel injection valve for the direct injection of fuel into the combustion chamber of a mixture-compressing, spark-ignited
  • Internal combustion engine which has a guide and seat area at the downstream end of the fuel injection valve, which is formed by three disc-shaped elements.
  • a swirl element is embedded between a guide element and a valve seat element.
  • the guide element serves to guide an axially movable valve needle projecting through it, while a valve closing section of the valve needle interacts with a valve seat surface of the valve seat element.
  • the swirl element has an inner opening area with a plurality of swirl channels which are not connected to the outer circumference of the swirl element. The entire opening area extends completely over the axial thickness of the swirl element.
  • a disadvantage of the fuel injector known from the abovementioned publication is in particular that Fixed swirl angle that cannot be adapted to different operating conditions such as partial and full load operation of an internal combustion engine. As a result, the cone opening angle of the injected mixture cloud cannot be adapted to the different operating states, which leads to inhomogeneities in the combustion, increased fuel consumption and increased exhaust gas emissions.
  • the fuel injector according to the invention with the characterizing features of the main claim has the advantage that the swirl is adjustable depending on the operating state of the internal combustion engine, whereby a spray pattern adapted to the operating state of the internal combustion engine can be generated. This enables the mixture formation and the combustion process to be optimized.
  • the influence on the jet opening angle is advantageously effected via the pressure of the fuel flowing through the fuel injection valve, which causes a change in the cross section of the swirl channels through an elastic membrane in accordance with the operating state and thereby enables a direct influence on the swirl intensity.
  • the formation of the membrane as a disk-shaped membrane, which is arranged between the swirl disk and a guide disk, is particularly advantageous.
  • This embodiment is particularly easy and inexpensive to manufacture and can be used for any shape of swirl disk. It is also advantageous that the disk-shaped membrane is connected to the outside of the guide disk, since leakage losses are thereby avoided.
  • the membrane can also be designed as an elastic layer, which can be arranged on any side surface of the swirl channel.
  • Fig. 1 shows an axial section through a
  • Fig. 2 is a schematic view of an exemplary
  • Fig. 3 is a schematic view of a swirl channel of the swirl disk shown in Fig. 2, and
  • FIGS. 4A-4B show a schematic representation of the functioning of the first and a second exemplary embodiment of a membrane arranged on the swirl disk.
  • FIG. 1 Before exemplary embodiments of a fuel injector 1 according to the invention are described in more detail with reference to FIGS. 2 to 4, the fuel injector 1 according to the invention in an overall view should first be understood with reference to FIG. 1 be briefly explained with regard to its essential components.
  • 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 injection valve 1 comprises a nozzle body 2, in which the valve needle 3 is arranged.
  • the valve needle 3 is operatively connected to a valve closing body 4, which cooperates with a valve seat surface 6 arranged on a valve seat body 5 to form a sealing seat.
  • the fuel injector 1 is an inwardly opening fuel injector 1 which has at least one spray opening 7.
  • the nozzle body 2 is sealed by a seal 8 against the outer pole 9 of a magnetic circuit.
  • a magnetic coil 10 is encapsulated in a coil housing 11 and wound on a coil support 12, which bears against an inner pole 13 of the magnetic circuit.
  • the inner pole 13 and the outer pole 9 are separated from one another by a gap 26 and are supported on a 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.
  • valve needle 3 is guided in a valve needle guide 14, which is disc-shaped.
  • a paired adjusting disk 15 is used for stroke adjustment.
  • An armature 20 is located on the other side of the adjusting disk 15. This armature is non-positively connected to the valve needle 3 via a first flange 21, which is connected to the first flange 21 by a weld seam 22 connected is.
  • a restoring spring 23 is supported on the first flange 21 and, in the present design of the fuel injector 1, is preloaded by a sleeve 24.
  • a second flange 31 which is connected to the valve needle 3 via a weld seam • 33, serves as the lower anchor stop.
  • An elastic intermediate ring 32 which rests on the second flange 31, prevents bouncing when the fuel injector 1 is closed.
  • a guide disk 35 On the inlet side of the sealing seat, a guide disk 35 is formed, which ensures a central alignment of the valve needle 3 and thus closely counteracts tilting of the valve needle 3 and subsequent inaccuracies in the metered fuel.
  • a swirl disk 34 which has swirl channels 36, is arranged between the guide disk 35 and the valve seat body 5.
  • a membrane 37 is provided, which preferably consists of an elastic material and which is deformable under the influence of the system pressure prevailing in the fuel injection valve 1. A detailed representation of the membrane 37 and its mode of operation can be seen in FIGS. 3 and 4.
  • Fuel channels 30a to 30c run in the valve needle guide 14, in the armature 20 and in the guide disk 35.
  • the fuel is supplied via a central fuel supply 16 and filtered by a filter element 25.
  • the fuel injector 1 is sealed by a seal 28 against a fuel line, not shown.
  • 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 magnet coil 10 When the magnet coil 10 is excited, it builds up a magnetic field which the armature 20 counteracts the spring force of the Return spring 23 moves in the stroke direction, the stroke being predetermined by a working gap 27 in the rest position between the inner pole 12 and the armature 20.
  • the armature 20 also carries the flange 21, which is welded to the valve needle 3, in the lifting direction.
  • the valve closing body 4, which is operatively connected to the valve needle 3, lifts off the valve seat surface 6 and the fuel is sprayed 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 flange 21 which is operatively 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.
  • the swirl disk 34 has four swirl channels 36 which are offset tangentially to a center of the swirl disk 34.
  • the offset of the swirl channels 36 and their radial length, their number and arrangement are arbitrary.
  • the cross section of the swirl channels 36 depends on the fuel pressure and the requirements for
  • Swirl disk 34 and the membrane 37 according to the invention are adapted.
  • FIG. 3 shows an excerpt from a sectional view of a section of the swirl disk 34 shown in FIG. 2 of the fuel injection valve 1 according to the invention in area III in FIG. 2.
  • The, for example, cuboidal swirl channel 36 shown in FIG. 3 has, similar to a cover plate, the membrane 37, which covers the swirl channel 36.
  • the membrane 37 can be arranged as a disk-shaped membrane 37a between the swirl disk 34 and the guide disk 35 or in the form of an elastic layer 37b on an end face of the guide disk 35 facing the swirl disk 34.
  • the arrow indicates the direction of flow of the fuel.
  • the arrangement of the membrane 37 is not limited to the position between the guide disk 35 and the swirl disk 34, but can in principle take place on each of the radially extending side surfaces 41.
  • the disk-shaped design and the arrangement between the swirl disk 34 and the guide disk 35 is represented as a preferred exemplary embodiment by the particularly simple shape and type of arrangement.
  • FIGS. 4A and 4B illustrate the mode of operation of the disk-shaped membrane 37a and the elastic layer 37b.
  • the membrane 37a or the layer 37b is shown in each case at the top in FIGS. 4A and 4B.
  • FIG. 4A The operation of the disk-shaped membrane 37a is shown schematically in FIG. 4A.
  • the swirl channel 36 is in a lateral sectional view along the in Fig.
  • Membrane 37a is between the swirl disk 34 and the
  • the swirl flow caused in the swirl chamber 39 is only weakly pronounced, as a result of which a mixture cloud injected into the combustion chamber of the internal combustion engine has a small jet opening angle.
  • the penetration of the mixture cloud is correspondingly high, which corresponds to the requirements for the shape and stoichiometry of the mixture cloud in part-load operation.
  • the disk-shaped membrane 37a experiences a deformation due to a shift in the acting force ratio, which allows the axial expansion of the swirl channel 36 to decrease. Accordingly, the speed of the fuel flowing through the swirl channels 36 continues to increase, as a result of which the swirl is also increased. This causes the mixture cloud injected into the combustion chamber to expand, which therefore has a larger jet opening angle and homogeneously fills the combustion chamber with an ignitable mixture.
  • FIG. 4B shows, in the same view as FIG. 4A, the membrane 37 designed as an elastic layer 37b.
  • the elastic layer 37b shown in FIG. 4B is not arranged as a loose disk between the swirl disk 34 and the guide disk 35, but in shape an elastic layer 37b formed on the outlet-side end face 38 of the guide disk 35, which is connected in its entire extent to the guide disk 35.
  • the mode of operation is accordingly the reverse of that of the exemplary embodiment shown in FIG. 4A. If the fuel pressure in the fuel injection valve 1 increases during operation, the elastic layer 37b is deformed against the flow direction with subsequently larger cross sections of the swirl channels 36. This is due to the fact that the elastic layer 37b which is firmly connected to the outflow-side end face 38 is displaced or compressed when the fuel pressure increases.
  • the invention is not restricted to the exemplary embodiments shown and can also be used in particular in the case of fuel injection valves 1 with piezoelectric or magnetostrictive actuators 10 and in any shape of swirl discs 34 with any swirl channels 36 of any shape.

Landscapes

  • 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)

Abstract

The invention relates to a fuel injection valve (1), especially for the direct injection of fuel into the combustion chamber of a mixture-compressing, spark-ignited internal combustion engine. Said valve comprises an actuator (10), a valve needle (3), actuated by the actuator (10), for actuating a valve closing body (4) that forms a sealing seat together with a valve face (6), and a swirl plate (34) that has at least one swirl duct (36). An elastic membrane (37) is disposed on the inlet side of the swirl plate (34) in such a manner that a metering cross-section of the at least one swirl duct (36) can be varied depending on the fuel pressure prevailing in the fuel injection valve (1) during operation.

Description

Brennstoffeinspritzventil Fuel injector
Stand der TechnikState of the art
Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Hauptanspruchs.The invention relates to a fuel injector according to the preamble of the main claim.
Aus der DE 197 36 682 AI ist ein Brennstoffeinspritzventil zum direkten Einspritzen von Brennstoff in den Brennraum einer gemischverdichtenden, fremdgezündetenFrom DE 197 36 682 AI is a fuel injection valve for the direct injection of fuel into the combustion chamber of a mixture-compressing, spark-ignited
Brennkraftmaschine bekannt, welches am stromabwärtigen Ende des Brennstoffeinspritzventils einen Führungs- und Sitzbereich aufweist, der von drei scheibenförmigen Elementen gebildet wird. Dabei ist ein Drallelement zwischen einem Führungselement und einem Ventilsitzelement eingebettet. Das Führungselement dient der Führung einer es durchragenden, axial beweglichen Ventilnadel, während ein Ventilschließabschnitt der Ventilnadel mit einer Ventilsitzfläche des Ventilsitzelements zusammenwirkt. Das Drallelement weist einen inneren Öffnungsbereich mit mehreren Drallkanälen auf, die nicht mit dem äußeren Umfang des Drallelements in Verbindung stehen. Der gesamte Öffnungsbereich erstreckt sich vollständig über die axiale Dicke des Drallelements.Internal combustion engine is known, which has a guide and seat area at the downstream end of the fuel injection valve, which is formed by three disc-shaped elements. A swirl element is embedded between a guide element and a valve seat element. The guide element serves to guide an axially movable valve needle projecting through it, while a valve closing section of the valve needle interacts with a valve seat surface of the valve seat element. The swirl element has an inner opening area with a plurality of swirl channels which are not connected to the outer circumference of the swirl element. The entire opening area extends completely over the axial thickness of the swirl element.
Nachteilig bei dem aus der obengenannten Druckschrift bekannten Brennstoffeinspritzventil ist insbesondere der festeingestellte Drallwinkel, der nicht den unterschiedlichen Betriebszuständen wie Teil- und Vollastbetrieb einer Brennkraftmaschine angepaßt werden kann. Dadurch kann auch der Kegelöffnungswinkel der eingespritzten Gemischwolke nicht an die verschiedenen Betriebszustände angepaßt werden, was zu Inhomogenitäten bei der Verbrennung, erhöhtem Brennstoffverbrauch sowie erhöhter Abgasemission führt.A disadvantage of the fuel injector known from the abovementioned publication is in particular that Fixed swirl angle that cannot be adapted to different operating conditions such as partial and full load operation of an internal combustion engine. As a result, the cone opening angle of the injected mixture cloud cannot be adapted to the different operating states, which leads to inhomogeneities in the combustion, increased fuel consumption and increased exhaust gas emissions.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß der Drall abhängig vom Betriebszustand der Brennkraftmaschine einstellbar ist, wodurch ein dem Betriebszustand der Brennkraftmaschine angepaßtes Strahlbild erzeugt werden kann. Dadurch können die Gemischbildung sowie das Brennverfahren optimiert werden.The fuel injector according to the invention with the characterizing features of the main claim has the advantage that the swirl is adjustable depending on the operating state of the internal combustion engine, whereby a spray pattern adapted to the operating state of the internal combustion engine can be generated. This enables the mixture formation and the combustion process to be optimized.
Die Einflußnahme auf den Strahlöffnungswinkel erfolgt dabei vorteilhafterweise über den Druck des das Brennstoffeinspritzventil durchströmenden Brennstoffs, der eine Querschnittsänderung der Drallkanäle durch eine elastische Membran gemäß dem Betriebszustand bewirkt und dadurch eine direkte Einflußnahme auf die Drallintensität ermöglicht .The influence on the jet opening angle is advantageously effected via the pressure of the fuel flowing through the fuel injection valve, which causes a change in the cross section of the swirl channels through an elastic membrane in accordance with the operating state and thereby enables a direct influence on the swirl intensity.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Hauptanspruch angegebenen Brennstoffeinspritzventils möglich.The measures listed in the subclaims allow advantageous developments and improvements of the fuel injector specified in the main claim.
Von Vorteil ist dabei insbesondere die Ausbildung der Membran als scheibenförmige Membran, die zwischen der Drallscheibe und einer Führungsseheibe angeordnet ist. Diese Ausführungsform ist besonders leicht und kostengünstig herstellbar und für beliebige Formen von Drallscheiben anwendbar. Weiterhin ist von Vorteil, daß die scheibenförmige Membran mit der Außenseite der Führungsscheibe verbunden ist, da dadurch Leckverluste vermieden werden.The formation of the membrane as a disk-shaped membrane, which is arranged between the swirl disk and a guide disk, is particularly advantageous. This embodiment is particularly easy and inexpensive to manufacture and can be used for any shape of swirl disk. It is also advantageous that the disk-shaped membrane is connected to the outside of the guide disk, since leakage losses are thereby avoided.
Vorteilhafterweise kann die Membran auch als elastische Schicht ausgeführt sein, die an einer beliebigen Seitenfläche des Drallkanals angeordnet sein kann.Advantageously, the membrane can also be designed as an elastic layer, which can be arranged on any side surface of the swirl channel.
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 axialen Schnitt durch einFig. 1 shows an axial section through a
Ausführungsbeispiel eines erfindungsgemäßenEmbodiment of an inventive
Brennstoffeinspritzventils,Fuel injector,
Fig. 2 eine schematische Ansicht einer beispielhaftenFig. 2 is a schematic view of an exemplary
Drallscheibe des in Fig. 1 dargestellten erfindungsgemäß ausgestalteten Brennstoff- einspritzventils ,Swirl disk of the fuel injector designed according to the invention shown in FIG. 1,
Fig. 3 eine schematische Ansicht eines Drallkanals der in Fig. 2 dargestellten Drallscheibe, undFig. 3 is a schematic view of a swirl channel of the swirl disk shown in Fig. 2, and
Fig. 4A-4B eine schematische Darstellung der Funktionsweise des ersten und eines zweiten Ausführungsbeispiels einer an der Drallscheibe angeordneten Membran.4A-4B show a schematic representation of the functioning of the first and a second exemplary embodiment of a membrane arranged on the swirl disk.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Bevor anhand der Figuren 2 bis 4 Ausführungsbeispiele eines erfindungsgemäßen Brennstoffeinspritzventils 1 näher beschrieben werden, soll zum besseren Verständnis der Erfindung zunächst anhand von Fig. 1 das erfindungsgemäße Brennstoffeinspritzventil 1 in einer Gesamtdarstellung 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. 2 to 4, the fuel injector 1 according to the invention in an overall view should first be understood with reference to FIG. 1 be briefly explained with regard to its essential components.
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 ausgeführ . DasInternal combustion engines executed. 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 umfaßt einen Düsenkörper 2, in welchem die Ventilnadel 3 angeordnet ist. Die Ventilnadel 3 steht mit einem Ventilschließkörper 4 in Wirkverbindung, 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 mindestens eine Abspritzöffnung 7 verfügt. Der Düsenkörper 2 ist durch eine Dichtung 8 gegen den Außenpol 9 eines Magnetkreises abgedichtet. Eine Magnetspule 10 ist in einem Spulengehäuse 11 gekapselt und auf einen Spulenträger 12 gewickelt, welcher an einem Innenpol 13 des Magnetkreises anliegt. Der Innenpol 13 und der Außenpol 9 sind durch einen Spalt 26 voneinander getrennt und stützen sich auf einem Verbindungsbauteil 29 ab. 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 comprises a nozzle body 2, in which the valve needle 3 is arranged. The valve needle 3 is operatively connected to a 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, the fuel injector 1 is an inwardly opening fuel injector 1 which has at least one spray opening 7. The nozzle body 2 is sealed by a seal 8 against the outer pole 9 of a magnetic circuit. A magnetic coil 10 is encapsulated in a coil housing 11 and wound on a coil support 12, which bears against an inner pole 13 of the magnetic circuit. The inner pole 13 and the outer pole 9 are separated from one another by a gap 26 and are supported on a 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 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 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.The valve needle 3 is guided in a valve needle guide 14, which is disc-shaped. A paired adjusting disk 15 is used for stroke adjustment. An armature 20 is located on the other side of the adjusting disk 15. This armature is non-positively connected to the valve needle 3 via a first flange 21, which is connected to the first flange 21 by a weld seam 22 connected is. A restoring spring 23 is supported on the first flange 21 and, in the present design of the fuel injector 1, is preloaded by a sleeve 24.
Ein zweiter Flansch 31, welcher mit der Ventilnadel 3 über eine Schweißnaht • 33 verbunden ist, dient als unterer Ankeranschlag. Ein elastischer Zwischenring 32, welcher auf dem zweiten Flansch 31 aufliegt, vermeidet Prellen beim Schließen des Brennstoffeinspritzventils 1.A second flange 31, which is connected to the valve needle 3 via a weld seam • 33, serves as the lower anchor stop. An elastic intermediate ring 32, which rests on the second flange 31, prevents bouncing when the fuel injector 1 is closed.
Zulaufseitig des Dichtsitzes ist eine FührungsScheibe 35 ausgebildet, die für eine mittige Ausrichtung der Ventilnadel 3 sorgt und somit einem Verkanten der Ventilnadel 3 und nachfolgenden Ungenauigkeiten in der zugemessenen Brennstoff enge entgegenwirkt . Zwischen der FührungsScheibe 35 und dem Ventilsitzkörper 5 ist eine Drallscheibe 34 angeordnet, welche Drallkanäle 36 aufweist. Zwischen der FührungsScheibe 35 und der Drallscheibe 34 ist eine Membran 37 vorgesehen, die vorzugsweise aus einem elastischen Material besteht und die unter dem Einfluß des im Brennstoffeinspritzventil 1 herrschenden Systemdrucks verformbar ist. Eine detaillierte Darstellung der Membran 37 und ihrer Funktionsweise ist den Fig. 3 und 4 zu entnehmen.On the inlet side of the sealing seat, a guide disk 35 is formed, which ensures a central alignment of the valve needle 3 and thus closely counteracts tilting of the valve needle 3 and subsequent inaccuracies in the metered fuel. A swirl disk 34, which has swirl channels 36, is arranged between the guide disk 35 and the valve seat body 5. Between the guide disk 35 and the swirl disk 34, a membrane 37 is provided, which preferably consists of an elastic material and which is deformable under the influence of the system pressure prevailing in the fuel injection valve 1. A detailed representation of the membrane 37 and its mode of operation can be seen in FIGS. 3 and 4.
In der Ventilnadelführung 14, im Anker 20 sowie in der FührungsScheibe 35 verlaufen Brennstoffkanäle 30a bis 30c. Der Brennstoff wird über eine zentrale Brennstoffzufuhr 16 zugeführt und durch ein Filterelement 25 gefiltert. Das Brennstoffeinspritzventil 1 ist durch eine Dichtung 28 gegen eine nicht weiter dargestellte Brennstoffleitung abgedichtet .Fuel channels 30a to 30c run in the valve needle guide 14, in the armature 20 and in the guide disk 35. The fuel is supplied via a central fuel supply 16 and filtered by a filter element 25. The fuel injector 1 is sealed by a seal 28 against a fuel line, not shown.
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 Flansch 21, welcher mit der Ventilnadel 3 verschweißt ist, ebenfalls in Hubrichtung mit. Der mit der Ventilnadel 3 in Wirkverbindung stehende Ventilschließkörper 4 hebt von der Ventilsitzfläche 6 ab und der Brennstoff wird 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 magnet coil 10 is excited, it builds up a magnetic field which the armature 20 counteracts the spring force of the Return spring 23 moves in the stroke direction, the stroke being predetermined by a working gap 27 in the rest position between the inner pole 12 and the armature 20. The armature 20 also carries the flange 21, which is welded to the valve needle 3, in the lifting direction. The valve closing body 4, which is operatively connected to the valve needle 3, lifts off the valve seat surface 6 and the fuel is sprayed off.
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 Wirkverbindung 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 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 flange 21 which is operatively 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. 2 zeigt in einer schematischen Darstellung eine beispielhafte Drallscheibe 34, die die weiter unten beschriebene erfindungsgemäße Membran 37 besonders einfach und effektiv unterstützt. Die Drallscheibe 34 weist dabei im vorliegenden Ausführungsbeispiel vier Drallkanäle 36 auf, die tangential zu einem Mittelpunkt der Drallscheibe 34 versetzt sind. Der Versatz der Drallkanäle 36 sowie ihre radiale Länge, ihre Anzahl und Anordnung sind dabei beliebig. Der Querschnitt der Drallkanäle 36 richtet sich nach dem Brennstoffdruck und den Anforderungen an die2 shows a schematic illustration of an exemplary swirl disk 34 which supports the membrane 37 according to the invention described below in a particularly simple and effective manner. In the present exemplary embodiment, the swirl disk 34 has four swirl channels 36 which are offset tangentially to a center of the swirl disk 34. The offset of the swirl channels 36 and their radial length, their number and arrangement are arbitrary. The cross section of the swirl channels 36 depends on the fuel pressure and the requirements for
Drallintensität und kann durch einfache Veränderungen in der Breite der Drallkanäle 36 bzw. der axialen Dicke derSwirl intensity and can be achieved by simple changes in the width of the swirl channels 36 or the axial thickness of the
Drallscheibe 34 sowie durch die erfindungsgemäße Membran 37 angepaßt werden.Swirl disk 34 and the membrane 37 according to the invention are adapted.
Die Drallkanäle 36 münden in eine Drallkammer 39 ein, die von der Ventilnadel 3 durchgriffen wird. Die Drallkammer 39 sollte so dimensioniert sein, daß die Drallströmung möglichst homogen bleibt und das Totvolumen so klein wie möglich gehalten wird. Fig. 3 zeigt in einer auszugsweisen Schnittdarstellung einen Ausschnitt aus der in Fig. 2 dargestellten Drallscheibe 34 des erfindungsgemäßen Brennstoffeinspritzventils 1 im Bereich III in Fig. 2.The swirl channels 36 open into a swirl chamber 39 which is penetrated by the valve needle 3. The swirl chamber 39 should be dimensioned so that the swirl flow remains as homogeneous as possible and the dead volume is kept as small as possible. FIG. 3 shows an excerpt from a sectional view of a section of the swirl disk 34 shown in FIG. 2 of the fuel injection valve 1 according to the invention in area III in FIG. 2.
Der in Fig. 3 dargestellte, beispielsweise quaderförmige Drallkanal 36 weist ähnlich einer Deckelplatte als Abschluß die Membran 37 auf, die den Drallkanal 36 abdeckt. Die Membran 37 kann dabei als scheibenförmige Membran 37a zwischen der Drallscheibe 34 und der Führungsscheibe 35 angeordnet sein oder in Form einer elastischen Schicht 37b an einer der Drallscheibe 34 zugewandten Stirnseite der FührungsScheibe 35 ausgebildet sein. Der Pfeil bezeichnet die Strömungsrichtung des Brennstoffs . Die Anordnung der Membran 37 ist dabei nicht auf die Position zwischen der Führungsscheibe 35 und der Drallscheibe 34 beschränkt, sondern kann im Prinzip an jeder der radial verlaufenden Seitenflächen 41 erfolgen. Die scheibenförmige Ausbildung und die Anordnung zwischen der Drallscheibe 34 und der Führungsscheibe 35 ist durch die besonders einfache Form und Anordnungsart als bevorzugtes Ausführungsbeispiel dargestellt .The, for example, cuboidal swirl channel 36 shown in FIG. 3 has, similar to a cover plate, the membrane 37, which covers the swirl channel 36. The membrane 37 can be arranged as a disk-shaped membrane 37a between the swirl disk 34 and the guide disk 35 or in the form of an elastic layer 37b on an end face of the guide disk 35 facing the swirl disk 34. The arrow indicates the direction of flow of the fuel. The arrangement of the membrane 37 is not limited to the position between the guide disk 35 and the swirl disk 34, but can in principle take place on each of the radially extending side surfaces 41. The disk-shaped design and the arrangement between the swirl disk 34 and the guide disk 35 is represented as a preferred exemplary embodiment by the particularly simple shape and type of arrangement.
Fig. 4A und 4B verdeutlichen die Funktionsweise der scheibenförmigen Membran 37a bzw. der elastischen Schicht 37b. Die Membran 37a bzw. die Schicht 37b ist dabei in der Fig. 4A bzw. 4B jeweils oben dargestellt.4A and 4B illustrate the mode of operation of the disk-shaped membrane 37a and the elastic layer 37b. The membrane 37a or the layer 37b is shown in each case at the top in FIGS. 4A and 4B.
In Fig. 4A ist die Funktionsweise der scheibenförmigen Membran 37a schematisch dargestellt. Der Drallkanal 36 ist dabei in einer seitlichen Schnittansicht entlang der in Fig.The operation of the disk-shaped membrane 37a is shown schematically in FIG. 4A. The swirl channel 36 is in a lateral sectional view along the in Fig.
2 angedeuteten Linie IV-IV dargestellt. Die scheibenförmige2 indicated line IV-IV shown. The disc-shaped
Membran 37a ist zwischen der Drallscheibe 34 und derMembrane 37a is between the swirl disk 34 and the
Führungsscheibe 35 angeordnet und zur Vermeidung von Leckverlusten mit der Führungsscheibe 35 an einem radial äußeren Rand 40 der Führungsscheibe 35 verklebt oder verschweißt . Während des Betriebs des Brennstoffeinspritzventils 1 durchströmt Brennstoff den Drallkanal 36 von radial außen nach radial innen. Dabei wird je nach Strömungsgeschwindigkeit des Brennstoffs ein unterschiedlich starker hydrodynamischer Druck auf die scheibenförmige Membran 37a erzeugt, der dazu führt, daß diese nach unten gezogen wird und dadurch der Querschnitt des Drallkanals 36 verkleinert wird. Dies wiederum führt zu einer Erhöhung der Strömungsgeschwindigkeit des Brennstoffs . Der Zustand stabilisiert sich, sobald ein Kräftegleichgewicht erreicht ist .Guide disk 35 arranged and glued or welded to the guide disk 35 on a radially outer edge 40 of the guide disk 35 to avoid leakage losses. During the operation of the fuel injection valve 1, fuel flows through the swirl channel 36 from radially outside to radially inside. Depending on the flow rate of the fuel, a differently strong hydrodynamic pressure is generated on the disk-shaped membrane 37a, which leads to the latter being pulled downward and thereby reducing the cross section of the swirl channel 36. This in turn leads to an increase in the flow rate of the fuel. The state stabilizes as soon as a balance of forces is reached.
Strömt der Brennstoff langsam durch einen großen Querschnitt, ist die in der Drallkammer 39 hervorgerufene Drallströmung nur schwach ausgeprägt, wodurch eine in den Brennraum der Brennkraftmaschine eingespritzte Gemischwolke einen geringen Strahlöffnungswinkel aufweist. Dementsprechend hoch ist die Penetration der Gemischwolke, was den Anforderungen an die Form und Stöchio etrie der Gemischwolke im Teillastbetrieb entspricht.If the fuel flows slowly through a large cross section, the swirl flow caused in the swirl chamber 39 is only weakly pronounced, as a result of which a mixture cloud injected into the combustion chamber of the internal combustion engine has a small jet opening angle. The penetration of the mixture cloud is correspondingly high, which corresponds to the requirements for the shape and stoichiometry of the mixture cloud in part-load operation.
Wird die Strömungsgeschwindigkeit erhöht, was dem Vollastbetrieb des Brennstoffeinspritzventils 1 entspricht, erfährt die scheibenförmige Membran 37a bedingt durch eine Verschiebung des wirkenden Kräfteverhältnisses eine Verformung, die die axiale Ausdehnung des Drallkanals 36 abnehmen läßt. Entsprechend nimmt in der Folge die Geschwindigkeit des die Drallkanäle 36 durchströmenden Brennstoffs weiter zu, wodurch auch der Drall verstärkt wird. Dadurch kommt es zu einer AufWeitung der in den Brennraum eingespritzten Gemischwolke, die somit einen größeren Strahlöffnungswinkel aufweist und den Brennraum homogen mit einem zündfähigen Gemisch ausfüllt.If the flow rate is increased, which corresponds to the full-load operation of the fuel injection valve 1, the disk-shaped membrane 37a experiences a deformation due to a shift in the acting force ratio, which allows the axial expansion of the swirl channel 36 to decrease. Accordingly, the speed of the fuel flowing through the swirl channels 36 continues to increase, as a result of which the swirl is also increased. This causes the mixture cloud injected into the combustion chamber to expand, which therefore has a larger jet opening angle and homogeneously fills the combustion chamber with an ignitable mixture.
Fig. 4B zeigt in gleicher Ansicht wie Fig. 4A die als elastische Schicht 37b ausgeführte Membran 37. Im Gegensatz zu Fig. 4A ist die in Fig. 4B dargestellte elastische Schicht 37b nicht als lose Scheibe zwischen der Drallscheibe 34 und der Führungsscheibe 35 angeordnet, sondern in Form einer an der ablaufseitigen Stirnseite 38 der Führungsscheibe 35 ausgebildeten elastischen Schicht 37b, die in ihrer gesamten Ausdehnung mit der Führungsscheibe 35 verbunden ist, ausgeführt.4B shows, in the same view as FIG. 4A, the membrane 37 designed as an elastic layer 37b. In contrast to FIG. 4A, the elastic layer 37b shown in FIG. 4B is not arranged as a loose disk between the swirl disk 34 and the guide disk 35, but in shape an elastic layer 37b formed on the outlet-side end face 38 of the guide disk 35, which is connected in its entire extent to the guide disk 35.
Die Funktionsweise ist dementsprechend umgekehrt zu derjenigen des in Fig. 4A dargestellten Ausführungsbeispiels . Steigt nämlich der Brennstoffdruck im Brennstoffeinspritzventil 1 während des Betriebs an, wird die elastische Schicht 37b entgegen der Strömungsrichtung mit in der Folge größeren Querschnitten der Drallkanäle 36 verformt. Dies ist dadurch bedingt, daß die mit der abströmseitigen Stirnseite 38 fest verbundene elastische Schicht 37b bei einer Erhöhung des Brennstoffdrucks verdrängt bzw. zusammengedrückt wird.The mode of operation is accordingly the reverse of that of the exemplary embodiment shown in FIG. 4A. If the fuel pressure in the fuel injection valve 1 increases during operation, the elastic layer 37b is deformed against the flow direction with subsequently larger cross sections of the swirl channels 36. This is due to the fact that the elastic layer 37b which is firmly connected to the outflow-side end face 38 is displaced or compressed when the fuel pressure increases.
Die Erfindung ist nicht auf die dargestellten Ausführungsbeispiele beschränkt und insbesondere auch bei Brennstoffeinspritzventilen 1 mit piezoelektrischen oder magnetostriktiven Aktoren 10 und bei beliebigen Formen von Drallscheiben 34 mit beliebig geformten Drallkanälen 36 anwendbar . The invention is not restricted to the exemplary embodiments shown and can also be used in particular in the case of fuel injection valves 1 with piezoelectric or magnetostrictive actuators 10 and in any shape of swirl discs 34 with any swirl channels 36 of any shape.

Claims

Ansprüche Expectations
1. Brennstoffeinspritzventil (1), insbesondere zum direkten Einspritzen von Brennstoff in einen Brennraum einer gemischverdichtenden, fremdgezündeten Brennkraftmaschine, mit einem Aktor (10) , einer durch den Aktor (10) betätigbaren Ventilnadel (3) zur Betätigung eines Ventilschließkörpers (4) , der zusammen mit einer Ventilsitzfläche (6) einen Dichtsitz bildet, und einer Drallscheibe (34) , die über mindestens einen Drallkanal (36) verfügt, dadurch gekennzeichnet, daß eine elastische Membran (37) so an der Drallscheibe (34) angeordnet ist, daß ein Zumeßquerschnitt des zumindest einen Drallkanals (36) abhängig von einem im Brennstoffeinspritzventil (1) während des Betriebs herrschenden Brennstoffdruck veränderbar ist .1. Fuel injection valve (1), in particular for direct injection of fuel into a combustion chamber of a mixture-compressing, spark-ignited internal combustion engine, with an actuator (10), a valve needle (3) which can be actuated by the actuator (10) for actuating a valve closing body (4) forms a sealing seat together with a valve seat surface (6), and a swirl disk (34) which has at least one swirl channel (36), characterized in that an elastic membrane (37) is arranged on the swirl disk (34) in such a way that a The metering cross section of the at least one swirl channel (36) can be changed as a function of a fuel pressure prevailing in the fuel injection valve (1) during operation.
2. Brennstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß die Membran (37) zumindest eine Seitenfläche (41) des zumindest einen Drallkanals (36) bildet.2. Fuel injection valve according to claim 1, characterized in that the membrane (37) forms at least one side surface (41) of the at least one swirl channel (36).
3. Brennstoffeinspritzventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die elastische Membran (37) in Form einer scheibenförmigen Membran (37a) ausgeführt ist. 3. Fuel injection valve according to claim 1 or 2, characterized in that the elastic membrane (37) is designed in the form of a disc-shaped membrane (37a).
4. Brennstoffeinspritzventil nach Anspruch 3, dadurch gekennzeichnet, daß die scheibenförmige Membran (37a) zwischen der Drallscheibe (34) und einer zulaufseitig der Drallscheibe (34) angeordneten Führungsscheibe (35) angeordnet ist.4. Fuel injection valve according to claim 3, characterized in that the disc-shaped membrane (37a) between the swirl disc (34) and an inlet side of the swirl disc (34) arranged guide disc (35) is arranged.
5. Brennstoffeinspritzventil nach Anspruch 4, dadurch gekennzeichnet, daß die scheibenförmige Membran (37a) zumindest an einem radial äußeren Rand (40) mit der Führungsscheibe (35) verbunden is . •5. Fuel injection valve according to claim 4, characterized in that the disc-shaped membrane (37a) is connected at least on a radially outer edge (40) with the guide disc (35). •
6. Brennstoffeinspritzventil nach Anspruch 4 oder 5, dadurch gekennzeichnet, daß ein Querschnitt des zumindest einen Drallkanals (36) bei zunehmendem Brennstoffdruck durch die scheibenförmige Membran (37a) abnimmt.6. Fuel injection valve according to claim 4 or 5, characterized in that a cross section of the at least one swirl channel (36) decreases with increasing fuel pressure through the disc-shaped membrane (37a).
7. Brennstoffeinspritzventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Membran (37) in Form einer elastischen Schicht (37b) ausgebildet ist.7. Fuel injection valve according to claim 1 or 2, characterized in that the membrane (37) is designed in the form of an elastic layer (37b).
8. Brennstoffeinspritzventil nach Anspruch 7, dadurch gekennzeichnet, daß ein Querschnitt des zumindest einen Drallkanals (36) bei zunehmendem Brennstoffdruck durch die elastische Schicht8. Fuel injection valve according to claim 7, characterized in that a cross section of the at least one swirl channel (36) with increasing fuel pressure through the elastic layer
(37a) zunimmt. (37a) increases.
EP01989419A 2000-12-19 2001-12-15 Fuel injection valve Expired - Lifetime EP1299638B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10063259 2000-12-19
DE10063259A DE10063259A1 (en) 2000-12-19 2000-12-19 Fuel injector
PCT/DE2001/004751 WO2002050427A1 (en) 2000-12-19 2001-12-15 Fuel injection valve

Publications (2)

Publication Number Publication Date
EP1299638A1 true EP1299638A1 (en) 2003-04-09
EP1299638B1 EP1299638B1 (en) 2004-05-26

Family

ID=7667764

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01989419A Expired - Lifetime EP1299638B1 (en) 2000-12-19 2001-12-15 Fuel injection valve

Country Status (5)

Country Link
US (1) US20050072864A1 (en)
EP (1) EP1299638B1 (en)
JP (1) JP2004516409A (en)
DE (2) DE10063259A1 (en)
WO (1) WO2002050427A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5880872B2 (en) * 2013-01-14 2016-03-09 株式会社デンソー Fuel injection valve and fuel injection device

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4647013A (en) * 1985-02-21 1987-03-03 Ford Motor Company Silicon valve
US4756508A (en) * 1985-02-21 1988-07-12 Ford Motor Company Silicon valve
DE19736682A1 (en) * 1997-08-22 1999-02-25 Bosch Gmbh Robert Fuel injector for internal combustion engine
US5996912A (en) * 1997-12-23 1999-12-07 Siemens Automotive Corporation Flat needle for pressurized swirl fuel injector
US6145496A (en) * 1998-04-07 2000-11-14 Siemens Automotive Corporation Fuel injector with porous element for atomizing fuel under air pressure
JP2000055226A (en) * 1998-08-03 2000-02-22 Zexel Corp Fluid injection valve
US6296199B1 (en) * 1998-08-27 2001-10-02 Robert Bosch Gmbh Fuel injection valve
US6168098B1 (en) * 1999-06-09 2001-01-02 Siemens Automotive Corporation Fuel injector with tubular lower needle guide
DE10034445A1 (en) * 2000-07-15 2002-01-24 Bosch Gmbh Robert Fuel injector

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0250427A1 *

Also Published As

Publication number Publication date
JP2004516409A (en) 2004-06-03
DE10063259A1 (en) 2002-07-11
WO2002050427A1 (en) 2002-06-27
US20050072864A1 (en) 2005-04-07
EP1299638B1 (en) 2004-05-26
DE50102422D1 (en) 2004-07-01

Similar Documents

Publication Publication Date Title
EP1364117B1 (en) Fuel injection valve
WO1999010648A1 (en) Fuel injection valve
EP1309793A1 (en) Fuel injection valve
EP1370765B1 (en) Fuel injection valve
EP0937203B1 (en) Fuel injection valve
DE10055483B4 (en) Fuel injector
EP1303695A1 (en) Fuel injection valve
EP1322858A1 (en) Fuel injection valve
DE10063261B4 (en) Fuel injector
EP1346147A1 (en) Fuel-injection valve
EP1327070B1 (en) Fuel-injection valve
EP1299638B1 (en) Fuel injection valve
EP1209353B1 (en) Fuel injection valve
WO2002033247A2 (en) Fuel injection valve
EP1346148A1 (en) Fuel injection valve
EP1342064A1 (en) Fuel injection valve
EP1308618B1 (en) Fuel injection valve
WO2002031351A2 (en) Fuel injection valve

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20020706

AK Designated contracting states

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

RIN1 Information on inventor provided before grant (corrected)

Inventor name: HUEBEL, MICHAEL

Inventor name: YILDIRIM, FEVZI

Inventor name: HOHL, GUENTHER

Inventor name: KEIM, NORBERT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20040526

Ref country code: FR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20040526

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

REF Corresponds to:

Ref document number: 50102422

Country of ref document: DE

Date of ref document: 20040701

Kind code of ref document: P

GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]

Effective date: 20040526

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20050301

EN Fr: translation not filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050701

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20051215