EP1308618B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP1308618B1
EP1308618B1 EP02022008A EP02022008A EP1308618B1 EP 1308618 B1 EP1308618 B1 EP 1308618B1 EP 02022008 A EP02022008 A EP 02022008A EP 02022008 A EP02022008 A EP 02022008A EP 1308618 B1 EP1308618 B1 EP 1308618B1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel injection
closing body
tapered portion
swirl
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
EP02022008A
Other languages
German (de)
French (fr)
Other versions
EP1308618A1 (en
Inventor
Wolfgang-Manfred Ruehle
Tadeusz Glazewski
Matthias Boee
Norbert Keim
Joerg Schlerfer
Martin Mueller
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 EP1308618A1 publication Critical patent/EP1308618A1/en
Application granted granted Critical
Publication of EP1308618B1 publication Critical patent/EP1308618B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M61/16—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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • F02M2200/505—Adjusting spring tension by sliding spring seats
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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 injector according to the preamble of the main claim.
  • a fuel injector which is characterized in that a guide and seat area is provided at the downstream end of the 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 which projects 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 above-mentioned document is, in particular, that the starting flow of the fuel flowing through the fuel injector is particularly low in the partial load range Injection quantities lead to vibrations both in the mass flow and in the jet angle. As a result, neither the spray behavior of an individual fuel injector nor that of a whole of fuel injectors of an internal combustion engine is reproducible.
  • the fuel injector according to the invention with the characterizing features of the main claim has the advantage that a tapering of the valve closing body formed on the valve needle in the region of a swirl element creates an additional volume that increases the swirl chamber, which dampens the vibrations when the flow starts, inhomogeneities in the flow reduced and thus enables a more accurate metering in the partial load range and better reproducibility of mass flow and jet angle.
  • the tapering of the valve closing body advantageously extends in the region of the swirl element or on the inflow side beyond it in order to achieve optimal damping behavior.
  • taper can be produced in a simple manner by turning or grinding the valve closing body and the shape of the other components can remain unchanged.
  • the damping behavior is adapted to the taper by a cylindrical or concave shape can be. This can also be at least partially in the form of a groove on the valve closing body.
  • FIG. 1 An exemplary embodiment of a fuel injection valve 1 according to the invention shown in FIG. 1 is in the form of a fuel injection valve 1 for fuel injection systems of mixture-compressing, spark-ignited internal combustion engines.
  • the 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 consists of a nozzle body 2, in which a 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 injection valve 1 is a fuel injection valve 1 that opens inwards and has a spray opening 7.
  • the nozzle body 2 is sealed by a seal 8 against an outer pole 9 of a solenoid 10 sealed.
  • the magnet coil 10 is encapsulated in a coil housing 11 and wound on a coil carrier 12, which bears against an inner pole 13 of the magnet coil 10.
  • the inner pole 13 and the outer pole 9 are separated from one another by a constriction 26 and are connected to one another by a non-ferromagnetic connecting component 29.
  • the magnet coil 10 is excited via a line 19 by an electrical current that can be supplied via an electrical plug contact 17.
  • the plug contact 17 is surrounded by a plastic sheath 18, which can be molded onto the inner pole 13.
  • the valve needle 3 is guided in a valve needle guide 14, which is disc-shaped.
  • a paired adjusting disk 15 is used for stroke adjustment.
  • the armature 20 is located on the other side of the adjusting disk 15. This armature is non-positively connected via a first flange 21 to the valve needle 3, which is connected to the first flange 21 by a weld seam 22.
  • a restoring spring 23 is supported on the first flange 21 and, in the present design of the fuel injector 1, is preloaded by a sleeve 24.
  • Fuel channels 30a to 30c run in the valve needle guide 14, in the armature 20 and on the valve seat body 5.
  • 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.
  • An annular damping element 32 which consists of an elastomer material, is arranged on the spray-side side of the armature 20. It rests on a second flange 31, which is non-positively connected to the valve needle 3 via a weld seam 33.
  • a swirl element 34 is arranged on the valve seat body 5, which is penetrated by the valve closing body 4 through a swirl chamber 35.
  • the swirl element 34 is held in contact with the valve seat body 5 by a guide element 36 mated on the inlet side.
  • the valve needle 3 of the fuel injection valve 1 and / or the valve closing body 4 connected to the valve needle 3 has a taper 37 in the region of the swirl element 34, which taper extends from an inlet side 38 of the swirl element 34 to the sealing seat.
  • the swirl chamber 35 is widened radially by the taper 37, which results in a damping of the fuel flow during the opening process of the fuel injector 1, as a result of which vibrations or inhomogeneities in the mass flow and in the jet angle can be reduced.
  • the armature 20 In the idle state of the fuel injection valve 1, the armature 20 is acted upon by the return spring 23 against its stroke direction in such a way that the valve closing body 4 is held in sealing contact with the valve seat 6.
  • the magnetic coil 10 When the magnetic coil 10 is excited, it builds up a magnetic field which moves the armature 20 in the stroke direction against the spring force of the return spring 23, the stroke being predetermined by a working gap 27 which is in the rest position between the inner pole 12 and the armature 20.
  • the armature 20 also takes the first flange 21, which is welded to the valve needle 3, in the lifting direction.
  • the valve closing body 4, which is connected to the valve needle 3, lifts off from the valve seat surface 6, and the fuel is sprayed off through the spray opening 7.
  • the armature 20 drops from the inner pole 13 after the magnetic field has been sufficiently reduced by the pressure of the return spring 23, as a result of which the first flange 21, which is connected to the valve needle 3, moves counter to the stroke direction.
  • the valve needle 3 will thereby moved in the same direction, whereby the valve closing body 4 rests on the valve seat surface 6 and the fuel injector 1 is closed.
  • FIG. 2 shows an excerpted sectional view of a section designated II in FIG. 1 from the exemplary embodiment of a fuel injector 1 designed according to the invention shown in FIG. 1. Corresponding components are provided with the same reference numerals.
  • the valve closing body 4 has a taper 37 in the area of the swirl element 34, by means of which the radial expansion of the vertical closing body 4 is reduced.
  • the taper 37 extends between the sealing seat, wherein it already starts at a contact surface 40 of the valve closing body 4 bearing against the valve seat surface 6, at least up to an inlet-side end face 38 of the swirl element 34.
  • the valve closing body 4 therefore completely penetrates the swirl element 34 with its tapered end or at least partially.
  • the taper 37 widens the swirl chamber 35 formed between the swirl element 34 and the valve closing body 4 radially inwards.
  • the increase in the volume of the swirl chamber 35 can be, for example, 80% compared to the conventional arrangement.
  • the increased volume dampens and homogenizes the flow start. This means that when the fuel injector 1 is opened, fluctuations which occur both in the metered amount of fuel and in the spray angle, in particular in the case of small amounts of fuel in the partial load range, are reduced.
  • the quantity deviations occurring in this regard both in terms of the reproducibility of individual fuel injection valves 1 and between the fuel iris injection valves 1 of an internal combustion engine are intolerable. The reason for this is in particular in the transition from Search fuel injector 1 in the ballistic operation with small quantity metering.
  • the taper 37 of the valve closing body 4 and the resulting increase in the volume of the swirl chamber 35 can reduce the vibrations in the mass flow and in the jet angle and thus the reproducibility of the quantities mentioned within the scope of the metering accuracy during operation of the internal combustion engine based on a single fuel injector 1 and on the entirety of all fuel injection valves 1 of the internal combustion engine can be improved.
  • the taper 37 of the valve closing body 4 can be cylindrical or concave, as seen in the axial direction, or else as a groove 41, which is indicated by a broken line in FIG. 2.
  • the taper 37 must not adversely affect the contact surface 40 which is appropriately dimensioned for reliable sealing against the combustion chamber pressure and is formed on the valve closing body 4 and corresponds to the valve seat surface 6 of the valve seat body.
  • the taper 37 formed on the valve closing body 4 in FIG. 2 is concave and continues axially in the feed direction on the valve closing body 4, as a result of which a further improvement in the steady, calm flow behavior when the fuel injector 1 is opened can be achieved.
  • the groove 41 indicated by the dashed line represents a further possibility for enlarging the swirl chamber 35, which does not further impair the other functional values of the fuel injection valve 1.
  • the invention is not restricted to the exemplary embodiment shown and is suitable for any construction of fuel injection valves 1.

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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 injector according to the preamble of the main claim.

Aus der DE 197 36 682 A1 ist ein Brennstoffeinspritzventil bekannt, welches sich dadurch auszeichnet, daß am stromabwärtigen Ende des Ventils ein Führungs- und Sitzbereich vorgesehen ist, 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.From DE 197 36 682 A1 a fuel injector is known, which is characterized in that a guide and seat area is provided at the downstream end of the 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 which projects 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, daß die Anlaufströmung des das Brennstoffeinspritzventil durchströmenden Brennstoffs vor allem im Teillastbereich beiminimalen Einspritzmengen zu Schwingungen sowohl im Massenstrom als auch im Strahlwinkel führt. Dadurch ist weder das Abspritzverhalten eines einzelnen Brennstoffeinspritzventils noch dasjenige einer Gesamtheit von Brennstoffeinspritzventilen einer Brennkraftmaschine reproduzierbar.A disadvantage of the fuel injector known from the above-mentioned document is, in particular, that the starting flow of the fuel flowing through the fuel injector is particularly low in the partial load range Injection quantities lead to vibrations both in the mass flow and in the jet angle. As a result, neither the spray behavior of an individual fuel injector nor that of a whole of fuel injectors of an internal combustion engine is reproducible.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß durch eine Verjüngung des an der Ventilnadel ausgebildeten Ventilschließkörpers im Bereich eines Drallelements ein zusätzliches, die Drallkammer vergrößerndes Volumen geschaffen wird, welches die Schwingungen beim Anlaufen der Strömung dämpft, Inhomogenitäten der Strömung reduziert und somit eine genauere Zumessung im Teillastbereich und eine bessere Reproduzierbarkeit von Massenfluß und Strahlwinkel ermöglicht.The fuel injector according to the invention with the characterizing features of the main claim has the advantage that a tapering of the valve closing body formed on the valve needle in the region of a swirl element creates an additional volume that increases the swirl chamber, which dampens the vibrations when the flow starts, inhomogeneities in the flow reduced and thus enables a more accurate metering in the partial load range and better reproducibility of mass flow and jet angle.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterentwicklungen des im Hauptanspruch angegebenen Brennstoffeinspritzventils möglich.The measures listed in the subclaims allow advantageous further developments of the fuel injector specified in the main claim.

Vorteilhafterweise erstreckt sich die Verjüngung des Ventilschließkörpers im Bereich des Drallelements oder zuströmseitig darüber hinaus, um ein optimales Dämpfungsverhalten zu erzielen.The tapering of the valve closing body advantageously extends in the region of the swirl element or on the inflow side beyond it in order to achieve optimal damping behavior.

Weiterhin ist von Vorteil, daß die Verjüngung in einfacher Weise durch Drehen oder Schleifen am Ventilschließkörper herstellbar ist und die Form der übrigen Bauteile unverändert bleiben kann.Another advantage is that the taper can be produced in a simple manner by turning or grinding the valve closing body and the shape of the other components can remain unchanged.

Von Vorteil ist außerdem, daß je nach Bauweise des Brennstoffeinspritzventils das Dämpfungsverhalten durch eine zylindrische oder konkave Ausformung der Verjüngung angepaßt werden kann. Diese kann auch zumindest teilweise in Form einer Nut am Ventilschließkörper ausgebildet sein.It is also advantageous that, depending on the design of the fuel injector, the damping behavior is adapted to the taper by a cylindrical or concave shape can be. This can also be at least partially in the form of a groove on the valve closing body.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
einen schematischen Schnitt durch ein Ausführungsbeispiel eines erfindungsgemäß ausgestalteten Brennstoffeinspritzventils, und
Fig. 2
einen schematischen Ausschnitt aus dem in Fig. 1 dargestellten Ausführungsbeispiel des erfindungsgemäßen Brennstoffeinspritzventils im Bereich II in Fig. 1.
An embodiment of the invention is shown in simplified form in the drawing and explained in more detail in the following description. Show it:
Fig. 1
a schematic section through an embodiment of a fuel injector designed according to the invention, and
Fig. 2
2 shows a schematic section of the exemplary embodiment of the fuel injector according to the invention shown in FIG. 1 in area II in FIG. 1.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Ein in Fig. 1 dargestelltes Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils 1 ist in der Form eines Brennstoffeinspritzventils 1 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.An exemplary embodiment of a fuel injection valve 1 according to the invention shown in FIG. 1 is in the form of a fuel injection valve 1 for fuel injection systems of mixture-compressing, spark-ignited internal combustion engines. The fuel injection valve 1 is particularly suitable for injecting fuel directly into a combustion chamber (not shown) of an internal combustion engine.

Das Brennstoffeinspritzventil 1 besteht aus einem Düsenkörper 2, in welchem eine Ventilnadel 3 angeordnet ist. Die Ventilnadel 3 steht in Wirkverbindung mit einem Ventilschließkörper 4, der mit einer auf einem Ventilsitzkörper 5 angeordneten Ventilsitzfläche 6 zu einem Dichtsitz zusammenwirkt. Bei dem Brennstoffeinspritzventil 1 handelt es sich im Ausführungsbeispiel um ein nach innen öffnendes Brennstoffeinspritzventil 1, welches über eine Abspritzöffnung 7 verfügt. Der Düsenkörper 2 ist durch eine Dichtung 8 gegen einen Außenpol 9 einer Magnetspule 10 abgedichtet. Die Magnetspule 10 ist in einem Spulengehäuse 11 gekapselt und auf einen Spulenträger 12 gewickelt, welcher an einem Innenpol 13 der Magnetspule 10 anliegt. Der Innenpol 13 und der Außenpol 9 sind durch eine Verengung 26 voneinander getrennt und miteinander durch ein nicht ferromagnetisches Verbindungsbauteil 29 verbunden. Die Magnetspule 10 wird über eine Leitung 19 von einem über einen elektrischen Steckkontakt 17 zuführbaren elektrischen Strom erregt. Der Steckkontakt 17 ist von einer Kunststoffummantelung 18 umgeben, die am Innenpol 13 angespritzt sein kann.The fuel injection valve 1 consists of a nozzle body 2, in which a 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 injection valve 1 is a fuel injection valve 1 that opens inwards and has a spray opening 7. The nozzle body 2 is sealed by a seal 8 against an outer pole 9 of a solenoid 10 sealed. The magnet coil 10 is encapsulated in a coil housing 11 and wound on a coil carrier 12, which bears against an inner pole 13 of the magnet coil 10. The inner pole 13 and the outer pole 9 are separated from one another by a constriction 26 and are connected to one another by a non-ferromagnetic connecting component 29. The magnet coil 10 is excited via a line 19 by an electrical current that can be supplied via an electrical plug contact 17. The plug contact 17 is surrounded by a plastic sheath 18, which can be molded onto the inner pole 13.

Die Ventilnadel 3 ist in einer Ventilnadelführung 14 geführt, welche scheibenförmig ausgeführt ist. Zur Hubeinstellung dient eine zugepaarte Einstellscheibe 15. An der anderen Seite der Einstellscheibe 15 befindet sich der Anker 20. Dieser steht über einen ersten Flansch 21 kraftschlüssig mit der Ventilnadel 3 in Verbindung, welche durch eine Schweißnaht 22 mit dem ersten Flansch 21 verbunden ist. Auf dem ersten Flansch 21 stützt sich eine Rückstellfeder 23 ab, welche in der vorliegenden Bauform des Brennstoffeinspritzventils 1 durch eine Hülse 24 auf Vorspannung gebracht wird. In der Ventilnadelführung 14, im Anker 20 und am Ventilsitzkörper 5 verlaufen Brennstoffkanäle 30a bis 30c. 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.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. The armature 20 is located on the other side of the adjusting disk 15. This armature is non-positively connected via a first flange 21 to the valve needle 3, which is connected to the first flange 21 by a weld seam 22. A restoring spring 23 is supported on the first flange 21 and, in the present design of the fuel injector 1, is preloaded by a sleeve 24. Fuel channels 30a to 30c run in the valve needle guide 14, in the armature 20 and on the valve seat body 5. 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.

An der abspritzseitigen Seite des Ankers 20 ist ein ringförmiges Dämpfungselement 32, welches aus einem Elastomerwerkstoff besteht, angeordnet. Es liegt auf einem zweiten Flansch 31 auf, welcher über eine Schweißnaht 33 kraftschlüssig mit der Ventilnadel 3 verbunden ist.An annular damping element 32, which consists of an elastomer material, is arranged on the spray-side side of the armature 20. It rests on a second flange 31, which is non-positively connected to the valve needle 3 via a weld seam 33.

Ein Drallelement 34 ist am Ventilsitzkörper 5 angeordnet, welches durch eine Drallkammer 35 von dem Ventilschließkörper 4 durchgriffen wird. Das Drallelement 34 wird durch ein zulaufseitig zugepaartes Führungselement 36 am Ventilsitzkörper 5 in Anlage gehalten.A swirl element 34 is arranged on the valve seat body 5, which is penetrated by the valve closing body 4 through a swirl chamber 35. The swirl element 34 is held in contact with the valve seat body 5 by a guide element 36 mated on the inlet side.

Erfindungsgemäß weis die Ventilnadel 3 des Brennstoffeinspritzventils 1 und/oder der mit der Ventilnadel 3 verbundene Ventilschließkörper 4 im Bereich des Drallelements 34 eine Verjüngung 37 auf, die sich von einer zulaufseitigen Seite 38 des Drallelements 34 bis zum Dichtsitz erstreckt. Durch die Verjüngung 37 ist die Drallkammer 35 radial erweitert, was in einer Dämpfung der Brennstoffströmung beim Öffnungsvorgang des Brennstoffeinspritzventils 1 resultiert, wodurch Schwingungen bzw. Inhomogenitäten im Massestrom und im Strahlwinkel reduziert werden können. Eine detaillierte Darstellung der erfindungsgemäßen Maßnahmen sowie der Funktion des Brennstoffeinspritzventils 1 ist der Fig. 2 sowie der nachfolgenden Beschreibung zu entnehmen.According to the invention, the valve needle 3 of the fuel injection valve 1 and / or the valve closing body 4 connected to the valve needle 3 has a taper 37 in the region of the swirl element 34, which taper extends from an inlet side 38 of the swirl element 34 to the sealing seat. The swirl chamber 35 is widened radially by the taper 37, which results in a damping of the fuel flow during the opening process of the fuel injector 1, as a result of which vibrations or inhomogeneities in the mass flow and in the jet angle can be reduced. A detailed illustration of the measures according to the invention and the function of the fuel injection valve 1 can be found in FIG. 2 and in the description below.

Im Ruhezustand des Brennstoffeinspritzventils 1 wird der Anker 20 von der Rückstellfeder 23 entgegen seiner Hubrichtung so beaufschlagt, daß der Ventilschließkörper 4 am Ventilsitz 6 in dichtender Anlage gehalten wird. Bei Erregung der Magnetspule 10 baut diese ein Magnetfeld auf, welches den Anker 20 entgegen der Federkraft der Rückstellfeder 23 in Hubrichtung bewegt, wobei der Hub durch einen in der Ruhestellung zwischen dem Innenpol 12 und dem Anker 20 befindlichen Arbeitsspalt 27 vorgegeben ist. Der Anker 20 nimmt den ersten Flansch 21, welcher mit der Ventilnadel 3 verschweißt ist, ebenfalls in Hubrichtung mit. Der mit der Ventilnadel 3 in Verbindung stehende Ventilschließkörper 4 hebt von der Ventilsitzfläche 6 ab, und der Brennstoff wird durch die Abspritzöffnung 7 abgespritzt.In the idle state of the fuel injection valve 1, the armature 20 is acted upon by the return spring 23 against its stroke direction in such a way that the valve closing body 4 is held in sealing contact with the valve seat 6. When the magnetic coil 10 is excited, it builds up a magnetic field which moves the armature 20 in the stroke direction against the spring force of the return spring 23, the stroke being predetermined by a working gap 27 which is in the rest position between the inner pole 12 and the armature 20. The armature 20 also takes the first flange 21, which is welded to the valve needle 3, in the lifting direction. The valve closing body 4, which is connected to the valve needle 3, lifts off from the valve seat surface 6, and the fuel is sprayed off through the spray opening 7.

Wird der Spulenstrom abgeschaltet, fällt der Anker 20 nach genügendem Abbau des Magnetfeldes durch den Druck der Rückstellfeder 23 vom Innenpol 13 ab, wodurch sich der mit der Ventilnadel 3 in Verbindung stehende erste Flansch 21 entgegen der Hubrichtung bewegt. Die Ventilnadel 3 wird dadurch in die gleiche Richtung bewegt, wodurch der Ventilschließkörper 4 auf der Ventilsitzfläche 6 aufsetzt und das Brennstoffeinspritzventil 1 geschlossen wird.If the coil current is switched off, the armature 20 drops from the inner pole 13 after the magnetic field has been sufficiently reduced by the pressure of the return spring 23, as a result of which the first flange 21, which is connected to the valve needle 3, moves counter to the stroke direction. The valve needle 3 will thereby moved in the same direction, whereby the valve closing body 4 rests on the valve seat surface 6 and the fuel injector 1 is closed.

Fig. 2 zeigt in einer auszugsweisen Schnittdarstellung einen in Fig. 1 mit II bezeichneten Ausschnitt aus dem in Fig. 1 dargestellten Ausführungsbeispiel eines erfindungsgemäß ausgestalteten Brennstoffeinspritzventils 1. Übereinstimmende Bauteile sind mit übereinstimmenden Bezugszeichen versehen.FIG. 2 shows an excerpted sectional view of a section designated II in FIG. 1 from the exemplary embodiment of a fuel injector 1 designed according to the invention shown in FIG. 1. Corresponding components are provided with the same reference numerals.

Wie bereits in der Beschreibung zu Fig. 1 erwähnt, weist der Ventilschließkörper 4 im Bereich des Drallelements 34 eine Verjüngung 37 auf, durch welche die radiale Ausdehnung des Veritilschließkörpers 4 reduziert wird. Die Verjüngung 37 erstreckt sich zwischen dem Dichtsitz, wobei sie bereits an einer an der Ventilsitzfläche 6 anliegenden Anlagefläche 40 des Ventilschließkörpers 4 beginnt, zumindest bis zu einer zulaufseitigen Stirnseite 38 des Drallelements 34. Der Ventilschließkörper 4 durchgreift demnach das Drallelement 34 mit seinem verjüngten Ende ganz oder zumindest teilweise.As already mentioned in the description of FIG. 1, the valve closing body 4 has a taper 37 in the area of the swirl element 34, by means of which the radial expansion of the vertical closing body 4 is reduced. The taper 37 extends between the sealing seat, wherein it already starts at a contact surface 40 of the valve closing body 4 bearing against the valve seat surface 6, at least up to an inlet-side end face 38 of the swirl element 34. The valve closing body 4 therefore completely penetrates the swirl element 34 with its tapered end or at least partially.

Durch die Verjüngung 37 wird die zwischen dem Drallelement 34 und dem Ventilschließkörper 4 ausgebildete Drallkammer 35 radial nach innen erweitert. Dabei kann die Erhöhung des Volumens der Drallkammer 35 beispielsweise 80% gegenüber der herkömmlichen Anordnung betragen. In der Folge wird durch das erweiterte Volumen eine Dämpfung und Homogenisierung des Strömungsanlaufs erzielt. Dies bedeutet, daß beim Öffnen des Brennstoffeinspritzventils 1 Schwankungen, die sowohl in der zugemessenen Brennstoffmenge als auch im Strahlwinkel insbesondere bei geringen Brennstoffmengen im Teillastbereich auftreten, reduziert werden. Die dabei auftretenden Mengenabweichungen sowohl bei der Reproduzierbarkeit einzelner Brennstoffeinspritzventile 1 als auch zwischen den Brennstoffeirispritzventilen 1 einer Brennkraftmaschine sind nicht tolerierbar. Die Begründung hierfür ist in insbesondere im Übergang des Brennstoffeinspritzventils 1 in den ballistischen Betrieb bei Kleinmengenzumessung zu suchen.The taper 37 widens the swirl chamber 35 formed between the swirl element 34 and the valve closing body 4 radially inwards. The increase in the volume of the swirl chamber 35 can be, for example, 80% compared to the conventional arrangement. As a result, the increased volume dampens and homogenizes the flow start. This means that when the fuel injector 1 is opened, fluctuations which occur both in the metered amount of fuel and in the spray angle, in particular in the case of small amounts of fuel in the partial load range, are reduced. The quantity deviations occurring in this regard both in terms of the reproducibility of individual fuel injection valves 1 and between the fuel iris injection valves 1 of an internal combustion engine are intolerable. The reason for this is in particular in the transition from Search fuel injector 1 in the ballistic operation with small quantity metering.

Durch die Verjüngung 37 des Ventilschließkörpers 4 und die daraus resultierende Vergrößerung des Volumens der Drallkammer 35 können die Schwingungen im Massenstrom und im Strahlwinkel verringert und damit die Reproduzierbarkeit der genannten Größen im Rahmen der Zumeßgenauigkeit während des Betriebes der Brennkraftmaschine bezogen auf ein einzelnes Brennstoffeinspritzventil 1 und auf die Gesamtheit aller Brennstoffeinspritzventile 1 der Brennkraftmaschine verbessert werden.The taper 37 of the valve closing body 4 and the resulting increase in the volume of the swirl chamber 35 can reduce the vibrations in the mass flow and in the jet angle and thus the reproducibility of the quantities mentioned within the scope of the metering accuracy during operation of the internal combustion engine based on a single fuel injector 1 and on the entirety of all fuel injection valves 1 of the internal combustion engine can be improved.

Die Verjüngung 37 des Ventilschließkörper 4 kann dabei in axialer Richtung gesehen zylindrisch oder konkav oder auch als Nut 41, die mit einer strichlinie in Fig. 2 angedeutet ist, ausgeführt sein. Die Verjüngung 37 darf dabei die zum sicheren Abdichten gegen den Brennraumdruck entsprechend dimensionierte Anlagefläche 40, welche am Ventilschließkörper 4 ausgebildet ist und mit der Ventilsitzfläche 6 des Ventilsitzkörpers korrespondiert, nicht beeinträchtigen.The taper 37 of the valve closing body 4 can be cylindrical or concave, as seen in the axial direction, or else as a groove 41, which is indicated by a broken line in FIG. 2. The taper 37 must not adversely affect the contact surface 40 which is appropriately dimensioned for reliable sealing against the combustion chamber pressure and is formed on the valve closing body 4 and corresponds to the valve seat surface 6 of the valve seat body.

Die in Fig. 2 am Ventilschließkörper 4 ausgebildete Verjüngung 37 ist konkav ausgebildet und setzt axial weiter in Zulaufrichtung am Ventilschließkörper 4 an, wodurch eine weitere Verbesserung des stationären, beruhigten Strömungsverhaltens beim Öffnen des Brennstoffeinspritzventils 1 erzielt werden kann.The taper 37 formed on the valve closing body 4 in FIG. 2 is concave and continues axially in the feed direction on the valve closing body 4, as a result of which a further improvement in the steady, calm flow behavior when the fuel injector 1 is opened can be achieved.

Die durch die gestrichelte Linie angedeutete Nut 41 stellt eine weitere Möglichkeit zur Vergrößerung der Drallkammer 35 dar, welche keine weiter Beeinträchtigung der übrigen Funktionswerte des Brennstoffeinspritzventils 1 nach sich zieht.The groove 41 indicated by the dashed line represents a further possibility for enlarging the swirl chamber 35, which does not further impair the other functional values of the fuel injection valve 1.

Die Erfindung ist nicht auf das dargestellte Ausführungsbeispiel beschränkt und für beliebige Bauweisen von Brennstoffeinspritzventilen 1 geeignet.The invention is not restricted to the exemplary embodiment shown and is suitable for any construction of fuel injection valves 1.

Claims (7)

  1. Fuel injection valve (1), in particular for the direct injection of fuel into a combustion chamber of an internal combustion engine, having an actuator (10) which is operatively connected to a valve needle (3), the valve needle (3) having, at its ejection end, a valve closing body (4) which interacts with a valve seat face (6) on a valve seat body (5) to form a sealing seat, and the valve closing body (4) reaching through a swirl element (34) which is arranged on an inlet-side end face (39) of the valve seat body (5), the valve needle (3) and/or the valve closing body (4) having, in the region of the swirl element (34), a tapered portion (37) which reduces the radial extent of the valve needle (3), the tapered portion (37) extending in the axial direction at least between the sealing seat and an inlet-side end side (38) of the swirl element (34), characterized in that the tapered portion (37) is configured in the shape of a groove (41) at least in sections.
  2. Fuel injection valve according to Claim 1, characterized in that the swirl element (34) and the valve needle (3) and/or the valve closing body (4) delimit a swirl chamber (35).
  3. Fuel injection valve according to Claim 2, characterized in that the tapered portion (37) is formed in the region of the swirl chamber (35) of the swirl element (34).
  4. Fuel injection valve according to one of Claims 1 to 3, characterized in that the tapered portion (37) increases the volume of the swirl chamber (35) radially.
  5. Fuel injection valve according to one of Claims 1 to 4, characterized in that the tapered portion (37) is manufactured by turning or grinding the valve needle (3) and/or the valve closing body (4).
  6. Fuel injection valve according to one of Claims 1 to 5, characterized in that the tapered portion (37) is shaped cylindrically at least in sections.
  7. Fuel injection valve according to one of Claims 1 to 5, characterized in that the tapered portion (37) is shaped concavely at least in sections.
EP02022008A 2001-10-31 2002-10-01 Fuel injection valve Expired - Lifetime EP1308618B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10153627 2001-10-31
DE10153627A DE10153627A1 (en) 2001-10-31 2001-10-31 Fuel injector

Publications (2)

Publication Number Publication Date
EP1308618A1 EP1308618A1 (en) 2003-05-07
EP1308618B1 true EP1308618B1 (en) 2004-12-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP02022008A Expired - Lifetime EP1308618B1 (en) 2001-10-31 2002-10-01 Fuel injection valve

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Country Link
EP (1) EP1308618B1 (en)
JP (1) JP2003148281A (en)
DE (2) DE10153627A1 (en)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE365752C (en) * 1920-04-15 1922-12-21 Samuel White & Company Ltd J Liquid fuel atomizers
US5288025A (en) * 1992-12-18 1994-02-22 Chrysler Corporation Fuel injector with a hydraulically cushioned valve
DE19625059A1 (en) * 1996-06-22 1998-01-02 Bosch Gmbh Robert Injection valve, in particular for injecting fuel directly into a combustion chamber of an internal combustion engine
DE19736682A1 (en) * 1997-08-22 1999-02-25 Bosch Gmbh Robert Fuel injector for internal combustion engine

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JP2003148281A (en) 2003-05-21
EP1308618A1 (en) 2003-05-07
DE10153627A1 (en) 2003-11-06
DE50201879D1 (en) 2005-02-03

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