EP1481159B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

Info

Publication number
EP1481159B1
EP1481159B1 EP02795038A EP02795038A EP1481159B1 EP 1481159 B1 EP1481159 B1 EP 1481159B1 EP 02795038 A EP02795038 A EP 02795038A EP 02795038 A EP02795038 A EP 02795038A EP 1481159 B1 EP1481159 B1 EP 1481159B1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
valve
injection valve
ground surface
closing body
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
EP02795038A
Other languages
German (de)
French (fr)
Other versions
EP1481159A1 (en
Inventor
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 EP1481159A1 publication Critical patent/EP1481159A1/en
Application granted granted Critical
Publication of EP1481159B1 publication Critical patent/EP1481159B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure
    • 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
    • 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
    • F02M61/042—The valves being provided with fuel passages
    • 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
    • F02M61/08—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 the valves opening in direction of fuel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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

Definitions

  • the invention relates to a fuel injection valve according to the preamble of the main claim.
  • an ignitable fuel / air mixture can be formed by injecting fuel into each combustion chamber delimited by a piston by releasing a nozzle orifice by lifting a valve member from a valve seat comprising the nozzle orifice.
  • the opening stroke of the valve member and the injection time are variably adjustable.
  • the Fuel injection device includes a fuel injection valve, which is arranged in the cylinder wall at a distance from the cylinder head and with respect to the outlet opening, and an outlet opening, wherein the beam axis of the fuel injection valve is directed to the region around the cylinder head arranged in the spark plug.
  • the fuel injection valve has a solenoid-operated valve needle with helical swirl grooves for generating a swirl flow of the injection jet.
  • the fuel injection valve is directed with its beam axis on the arranged in the cylinder head center ignition point.
  • a device for injecting fuel into the combustion chamber of a mixture-compression, spark-ignited internal combustion engine in which fuel is injected in a cone-shaped manner into the combustion chamber at a certain initial angle.
  • the injected fuel fills the combustion chamber in the form of a cone, wherein effects of wall wetting are largely suppressed.
  • a relatively flat formed piston spherically deforms the injected fuel cloud during the compression phase.
  • the spherical mixture cloud mixes only insignificantly with the supplied air and is passed on further compression to the spark gap of the spark plug.
  • combustion chamber geometries are difficult to produce; on the other hand, combustion can not be optimized with respect to the emission of nitrogen oxides and the consumption of fuel.
  • a fuel injector for an internal combustion engine which has a valve body accommodated in a housing, wherein the valve body comprises a valve seat surrounded by a valve opening.
  • a valve needle which is provided with a closing body, extends through the valve opening, so that the closing body cooperates with the valve seat to open and close the valve.
  • the valve needle is provided at its downstream end with a shoulder at which annular cylindrical guide surfaces and flattened surfaces are alternately formed around the outer circumferential surface thereof, which form outlet openings or gaps for the fuel stream. The exit gaps together form the narrowest flow passage of the injector, where the fuel flow is accelerated for proper atomization in the combustion chamber.
  • the fuel injector according to the invention with the characterizing features of the main claim has the advantage that the injected into the combustion chamber of the engine mixture cloud can be influenced by a corresponding shaping of the valve closing body of the fuel injector by a targeted throttling in front of the sealing seat so that the mixture cloud the spark plug only at the end reached the injection process.
  • the valve needle or the valve closing body in this case hasprofitnanschliffe, which throttle the flow of fuel depending on the radial depth ofassinanschliffe more or less, so that the fuel injection valve leaving mixture cloud depending on the stroke position of the valve needle has a larger or smaller opening angle ⁇ .
  • the throttling effect is adjustable either by recessed arranged legislativenanschliffe or via a raised guide ring.
  • Fig. 1 shows in an excerpt, schematic sectional view of an embodiment of a fuel injection system 1 for a mixture-compression spark-ignition internal combustion engine.
  • the fuel injection system 1 comprises a combustion chamber 2 which is delimited by cylinder walls 3, a cylinder head 4 which has ridge slopes 5, and a piston 6.
  • a spark plug 7 is z. B. arranged laterally projecting into the combustion chamber 2.
  • a fuel injection valve 10 according to the invention is arranged between the ridge bevels 5 in such a way that fuel is injected into the combustion chamber 2 in the form of, for example, a conical mixture cloud 8, 9.
  • the fuel injector 10 is inventively designed so that the prevailing fuel flow is throttled to varying degrees so that depending on the Hubbert a valve needle of the fuel injection valve 10, a mixture cloud 8, 9 can be generated with a variable opening angle ⁇ in the combustion chamber 2.
  • valve needle or a valve-closing body operatively connected therewith has at least one, preferably a plurality of surface contours or a guide ring for this purpose.
  • Illustrated by the inventive measure in Fig.1 can first be a mixture cloud 8 are generated in the combustion chamber 2, which has a large penetration and a small opening angle ⁇ , while the closing of the fuel injection valve 10 briefly the mixture cloud 9 is generated with a larger opening angle ⁇ , which touches the spark plug 7 in the electrodes and thus inflammable mixture transported to the spark gap of the spark plug 7.
  • FIG Fig. 2 An embodiment of a fuel injection valve 10 designed according to the invention, which is suitable for this operating mode, is shown in FIG Fig. 2 shown and described below.
  • Fig. 2 shows a schematic sectional view of an embodiment of an inventively designed fuel injector 10, which in particular for use in the in Fig. 1 illustrated fuel injection system 1 is suitable.
  • the fuel injection valve 10 is designed in the form of a direct-injection fuel injection valve 10, which serves for the direct injection of fuel into the combustion chamber 2 of the mixture-compressing, spark-ignited internal combustion engine. In the exemplary embodiment, this is an outwardly opening fuel injection valve 10.
  • the fuel injection valve 10 includes an actuator 11, which is formed in the present embodiment as a piezoelectric actuator 11.
  • the actuator 11 is encapsulated in an actuator housing 12 for stabilization and is supported at the end in the inlet direction at an abutment 13 and downstream on a shoulder 14 from.
  • the shoulder 14 is in frictional connection with a two-part valve needle 15.
  • An inflow-side first part 16 of the valve needle 15 is supported on the shoulder 14, while a second part 17 downstream of the first part 16 is arranged separately from this.
  • the first part 16 of the valve needle 15 is acted upon by a first return spring 18, which is arranged between the shoulder 14 and a sealing housing 19.
  • the second part 17 of the valve needle 15 is acted upon by a second return spring 20 whose spring force is lower than that of the first return spring 18, so that the second part 17 of the valve needle 15 can swing through relative to the first part 16.
  • the fuel injection valve 10 further comprises a corrugated tube seal 21 which protects the actuator 11 from the fuel flowing through the fuel injection valve 10.
  • the fuel is supplied via a central fuel supply 22 and flows through a fuel channel 23 in a housing body 24. It is thereby past the sealing housing 19 into a recess 25 of a nozzle body 26 inserted into the housing body 24, in which also the second part 17 the valve needle 15 is arranged, passed.
  • the second part 17 of the valve needle 15 has an integral with the valve needle 15 or in frictional connection with this standing valve closing body 27, which forms a sealing seat with a formed on the nozzle body 26 valve seat surface 28.
  • FIGS. 3A to 3B the measures according to the invention are in Fig. 4 shown in detail and explained in detail in the following description.
  • an exciter voltage is applied to the actuator 11, for example via an electrical line, not shown.
  • the first part 16 of the valve needle 15 is moved in a stroke direction.
  • the second part 17 of the valve needle 15 with the valve closing body 27 formed thereon is also moved counter to the force of the second return spring 20 in the stroke direction, so that the valve closing body 27 lifts from the valve seat surface 28 and fuel is sprayed.
  • the first part 16 of the valve needle 15 returns to its original position against the stroke direction by the force of the first return spring 18.
  • the second part 17 of the valve needle 15 is also relieved, as a result of which the valve closing body 27 rests again on the valve seat surface 28 and the fuel injection valve 10 is closed.
  • FIGS. 3A and 3B show a partial enlargement of the in Fig. 2 With III designated section of the fuel injection valve 10 in two different stroke positions of the valve needle 15. It provides Fig. 3A a stroke position, which corresponds for example to an open position of the fuel injection valve 10, while Fig. 3B shows a stroke position, which occurs at a lower stroke of the valve needle 15, for example when closing the fuel injection valve 10.
  • Matching components are provided in all figures with corresponding reference numerals.
  • the second part 17 of the valve needle 15 on the integrally formed with her valve closing body 27 or directly on the second part 17 of the valve needle 15 at least one clergynanschliff 29.
  • a plurality of clergynanschliffe 29 are regularly or irregularly distributed over the circumference of the valve closing body 27 formed on this.
  • the ceremoniesnanschliffe 29 are formed, for example, longitudinally oval and alternate with guide surfaces 30 which abut against a formed on the nozzle body 26 mating surface 31.
  • the guide surfaces 30 and the counter surface 31 guide the second part 17 of the valve needle 15 during the lifting movement. This malfunction of the fuel injection valve 10 can be prevented by offsets of the valve needle 15 with subsequent jamming.
  • the change in an opening angle ⁇ of the mixture cloud 8, 9 injected into the combustion chamber 2 is to be designed such that a mixture cloud 9 is produced at the end of the injection cycle whose opening angle ⁇ 2 is greater than the opening angle ⁇ 1 at the beginning of the injection cycle is.
  • the foundednanschliffe 29 on the valve closing body 27 are accordingly formed in their radial extent so that they define the width of a between the professionnanschliffen 29 and the mating surface 31 released throttle gap 32.
  • the width of the opening cross-section at the sealing seat in the fully open state of the fuel injection valve 10 is in any case greater than the width of the defined by the professionnanschliffe 29 throttle gap 32 so that the ceremoniesnanschliffe 29 serve as a choke.
  • the flow lamella formed in the narrow gap at the surface poles is thinner than the gap at the seal seat.
  • the fuel lamella can thereby flow with little deflection to the outside through the sealing seat.
  • the fuel lamella does not flow parallel to the walls through the sealing seat area, but obliquely directed downward.
  • the conical mixture cloud thus has a small opening angle.
  • valve closing body 27 When the valve closing body 27 is moved in a closing direction because the actuator 11 of the fuel injection valve 10 is supplied with a smaller excitation voltage, the distance of the valve closing body 27 from the valve seat surface 28 narrows. When the distance becomes smaller than the gap at the surfaces, the flow flows through the seat gap inevitably parallel to the walls. This forms a larger opening angle of the conical mixture cloud than in the first case.
  • Fig. 4 shows an embodiment of an inventively designed fuel injection valve 10 in the same representation as FIGS. 3A and 3B ,
  • the throttling function of the throttle gap 32 is independent of the tenunanschliffen 29th
  • a guide portion 33 is formed on the valve closing body, which defines a throttle gap 34, which is always the same distance over the circumference of the valve closing body 27.
  • the throttling effect and the subsequent widening of the opening angle ⁇ of the mixture cloud 8, 9 can be intensified, for example, by the activation of two discrete stroke positions via the actuator 11 or a slowing down of the closing operation of the fuel injection valve 10.
  • the invention is not limited to the illustrated embodiments and for any designs of fuel injectors 10 different arrangements of spark plugs 7 and fuel injectors 10 in the cylinder head 4 of an internal combustion engine and magnetic drive valve needle movement applicable.

Landscapes

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

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Hauptanspruchs.The invention relates to a fuel injection valve according to the preamble of the main claim.

Aus der DE 196 42 653 C1 ist bereits ein Verfahren zur Bildung eines zündfähigen Brennstoff-/Luftgemisches bekannt. In den Zylindern von direkteinspritzenden Brennkraftmaschinen ist ein zündfähiges Brennstoff-/ Luftgemisch bildbar, indem in jedem von einem Kolben begrenzten Brennraum mittels eines Injektors bei Freigabe einer Düsenöffnung durch Abheben eines Ventilgliedes von einem die Düsenöffnung umfassenden Ventilsitz Brennstoff eingespritzt wird. Um unter allen Betriebsbedingungen der Brennkraftmaschine, insbesondere im Schichtladungsbetrieb, eine verbrauchs- und emissionsoptimierte innere Gemischbildung in jedem Betriebspunkt des gesamten Kennfeldes zu ermöglichen, ist vorgesehen, daß der Öffnungshub des Ventilgliedes und die Einspritzzeit variabel einstellbar sind.From the DE 196 42 653 C1 A method for forming an ignitable fuel / air mixture is already known. In the cylinders of direct injection internal combustion engines, an ignitable fuel / air mixture can be formed by injecting fuel into each combustion chamber delimited by a piston by releasing a nozzle orifice by lifting a valve member from a valve seat comprising the nozzle orifice. In order to allow under all operating conditions of the internal combustion engine, especially in stratified charge mode, a fuel consumption and emission optimized internal mixture formation at each operating point of the entire map, it is provided that the opening stroke of the valve member and the injection time are variably adjustable.

Aus der DE 38 08 635 C2 ist eine Brennstoffeinspritzvorrichtung zum direkten Einspritzen von Brennstoff in den Zylinder einer gemischverdichtenden Brennkraftmaschine- bekannt. Die Brennstoffeinspritzvorrichtung beinhaltet ein Brennstoffeinspritzventil, das in der Zylinderwandung mit Abstand zum Zylinderkopf und gegenüber der Auslaßöffnung angeordnet ist, und eine Ausgangsöffnung, wobei die Strahlachse des Brennstoffeinspritzventils auf den Bereich um die im Zylinderkopf angeordnete Zündkerze gerichtet ist. Das Brennstoffeinspritzventil weist eine magnetbetätigte Ventilnadel mit schraubenförmigen Drallnuten zum Erzeugen einer Drallströmung des Einspritzstrahls auf. Das Brennstoffeinspritzventil ist mit seiner Strahlachse auf den in der Zylinderkopfmitte angeordneten Zündpunkt gerichtet.From the DE 38 08 635 C2 there is known a fuel injector for injecting fuel directly into the cylinder of a mixture-compression internal combustion engine. The Fuel injection device includes a fuel injection valve, which is arranged in the cylinder wall at a distance from the cylinder head and with respect to the outlet opening, and an outlet opening, wherein the beam axis of the fuel injection valve is directed to the region around the cylinder head arranged in the spark plug. The fuel injection valve has a solenoid-operated valve needle with helical swirl grooves for generating a swirl flow of the injection jet. The fuel injection valve is directed with its beam axis on the arranged in the cylinder head center ignition point.

Weiterhin ist aus der US 5, 941, 207 eine Vorrichtung zum Einspritzen von Brennstoff in den Brennraum einer gemischverdichtenden, fremdgezündeten Brennkraftmaschine bekannt, bei der Brennstoff unter einem bestimmten Anfangswinkel kegelförmig in den Brennraum eingespritzt wird. Der eingespritzte Brennstoff füllt dabei die Brennkammer kegelförmig aus, wobei Effekte der Wandbenetzung weitgehend unterdrückt werden. Ein relativ flach ausgebildeter Kolben verformt die eingespritzte Brennstoffwolke während der Verdichtungsphase kugelförmig. Die kugelförmige Gemischwolke vermischt sich nur unwesentlich mit der zugeführten Luft und wird bei weiterer Verdichtung zur Funkenstrecke der Zündkerze geführt.Furthermore, from the US 5,941,207 a device for injecting fuel into the combustion chamber of a mixture-compression, spark-ignited internal combustion engine, in which fuel is injected in a cone-shaped manner into the combustion chamber at a certain initial angle. The injected fuel fills the combustion chamber in the form of a cone, wherein effects of wall wetting are largely suppressed. A relatively flat formed piston spherically deforms the injected fuel cloud during the compression phase. The spherical mixture cloud mixes only insignificantly with the supplied air and is passed on further compression to the spark gap of the spark plug.

Nachteilig an den aus den obengenannten Druckschriften bekannten Verfahren bzw. Vorrichtungen zum Einspritzen von Brennstoff in den Brennraum einer gemischverdichtenden fremdgezündeten Brennkraftmaschine sind insbesondere die komplizierten Brennraumgeometrien, welche nötig sind, den eingespritzten Brennstoff mit der zugeführten Luft zu vermischen, ein zündfähiges Brennstoff-/Luftgemisch zu bilden und dieses zur Zündung in die Nähe der Funkenstrecke der Zündkerze zu transportieren. Derartige Brennraumgeometrien sind zum einen schwer herstellbar, zum anderen kann die Verbrennung in Bezug auf die Emission von Stickoxyden und den Verbrauch von Brennstoff nicht optimiert werden.A disadvantage of the methods and devices for injecting fuel into the combustion chamber of a mixture-compressing spark-ignited internal combustion engine known from the above-mentioned publications, in particular the complicated combustion chamber geometries, which are necessary to mix the injected fuel with the supplied air, an ignitable fuel / air mixture and to transport this to the ignition in the vicinity of the spark gap of the spark plug. On the one hand, such combustion chamber geometries are difficult to produce; on the other hand, combustion can not be optimized with respect to the emission of nitrogen oxides and the consumption of fuel.

Weiterhin ist von Nachteil, dass in den meisten Fällen die Zündkerze direkt durch das Brennstoffeinspritzventil angespritzt wird. Dadurch ist die Zündkerze einerseits starken thermischen Schockbelastungen ausgesetzt, andererseits lagert sich Russ auf den Zündkerzenelektroden ab, wodurch die Lebensdauer der Zündkerze erheblich beschränkt wird.Furthermore, it is disadvantageous that in most cases the spark plug is injected directly through the fuel injection valve. As a result, the spark plug on the one hand exposed to severe thermal shock loads, on the other hand, soot deposits on the spark plug electrodes, whereby the life of the spark plug is considerably limited.

Insbesondere ist an dem aus der DE 198 27 219 A1 bekannten Brennstoffeinspritzventil von Nachteil, dass der durch die unterschiedlichen Einspritzwinkel in den Brennraum eingespritzte Brennstoff größtenteils auf die Wände des Brennraums bzw. den Kolben auftrifft, dort abkühlt und somit nur unter hoher Schadstoffemission bzw. Russentwicklung verbrannt werden kann.In particular, is on the from the DE 198 27 219 A1 known fuel injection valve of disadvantage that the fuel injected by the different injection angle into the combustion chamber largely impinges on the walls of the combustion chamber or the piston, where it cools and thus can only be burned under high pollutant emission or soot.

In US-A-5 829 688 ist eine Brennstoffeinspritzvorrichtung für eine Brennkraftmaschine beschrieben, welche einen in einem Gehäuse aufgenommenen Ventilkörper aufweist, wobei der Ventilkörper eine von einem Ventilsitz umgebene Ventilöffnung umfasst. Eine Ventilnadel, welche mit einem Schließkörper versehen ist, erstreckt sich durch die Ventilöffnung, so dass der Schließkörper mit dem Ventilsitz zusammenwirkt, um das Ventil zu öffnen und zu schließen. Die Ventilnadel ist an ihrem stromabwärtigen Ende mit einem Absatz versehen, an dem abwechselnd um dessen äußere Umfangsoberfläche ringförmig zylindrische Führungsoberflächen und abgeflachte Oberflächen vorgesehen sind, welche Austrittsöffnungen bzw. -spalte für den Brennstoffstrom bilden. Die Austrittsspalte bilden gemeinsam den engsten Strömungsdurchgang des Einspritzventils, wo der Brennstoffstrom zur richtigen Zerstäubung in dem Verbrennungsraum beschleunigt wird.In US-A-5,829,688 a fuel injector for an internal combustion engine is described, which has a valve body accommodated in a housing, wherein the valve body comprises a valve seat surrounded by a valve opening. A valve needle, which is provided with a closing body, extends through the valve opening, so that the closing body cooperates with the valve seat to open and close the valve. The valve needle is provided at its downstream end with a shoulder at which annular cylindrical guide surfaces and flattened surfaces are alternately formed around the outer circumferential surface thereof, which form outlet openings or gaps for the fuel stream. The exit gaps together form the narrowest flow passage of the injector, where the fuel flow is accelerated for proper atomization in the combustion chamber.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, dass die in den Brennraum der Brennkraftmaschine eingespritzte Gemischwolke durch eine entsprechende Formung des Ventilschließkörpers des Brennstoffeinspritzventils durch eine gezielte Drosselung vor dem Dichtsitz so beeinflussbar ist, dass die Gemischwolke die Zündkerze nur am Ende des Einspritzvorgangs erreicht.The fuel injector according to the invention with the characterizing features of the main claim has the advantage that the injected into the combustion chamber of the engine mixture cloud can be influenced by a corresponding shaping of the valve closing body of the fuel injector by a targeted throttling in front of the sealing seat so that the mixture cloud the spark plug only at the end reached the injection process.

Die Ventilnadel oder der Ventilschließkörper weist hierbei Flächenanschliffe auf, welche die Brennstoffströmung je nach der radialen Tiefe der Flächenanschliffe mehr oder weniger stark drosseln, so dass die das Brennstoffeinspritzventil verlassende Gemischwolke je nach der Hubstellung der Ventilnadel einen größeren oder kleineren Öffnungswinkel α aufweist.The valve needle or the valve closing body in this case has Flächenanschliffe, which throttle the flow of fuel depending on the radial depth of Flächenanschliffe more or less, so that the fuel injection valve leaving mixture cloud depending on the stroke position of the valve needle has a larger or smaller opening angle α.

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

Von Vorteil ist insbesondere, daß die Anzahl der Flächenanschliffe beliebig ist, so daß die gewünschte Drosselwirkung frei wählbar ist.Of particular advantage is that the number of surface contours is arbitrary, so that the desired throttle effect is freely selectable.

Vorteilhafterweise wirken zwischen den Flächenanschliffen angeordnete erhabene Führungsflächen mit einer am Düsenkörper ausgebildeten Gegenfläche so zusammen, daß die Führung der Ventilnadel jederzeit gewährleistet ist. Dadurch kann Fehlfunktionen durch Versätze der Ventilnadel vorgebeugt werden.Advantageously, between the Flächenanschliffen arranged raised guide surfaces cooperate with a mating surface formed on the nozzle body together so that the leadership of the valve needle is guaranteed at all times. As a result, malfunctions can be prevented by offsetting the valve needle.

Weiterhin ist vorteilhaft, daß die Drosselwirkung entweder durch vertieft angeordnete Flächenanschliffe oder über einen erhabenen Führungsring regulierbar ist.Furthermore, it is advantageous that the throttling effect is adjustable either by recessed arranged Flächenanschliffe or via a raised guide ring.

Zeichnungdrawing

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

Fig. 1
einen Längsschnitt durch ein Ausführungsbeispiel eines Brennstoffeinspritzsystems mit einer Gemischwolke, welche durch ein erfindungsgemäßes Brennstoffeinspritzventil im Brennraum erzeugt wird,
Fig. 2
eine teilweise geschnittene Ansicht eines Ausführungsbeispiels eines erfindungsgemäßen Brennstoffeinspritzventils,
Fig. 3A-B
einen Schnitt durch den abspritzseitigen Teil des in Fig. 2 dargestellten nicht erfindungsgemäßen Beispiels eines erfindungsgemäßen Brennstoffeinspritzventils in zwei verschiedenen Hubstellungen, und
Fig. 4
ein Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils in gleicher Darstellung wie in Fig. 3A und 3B.
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
a longitudinal section through an embodiment of a fuel injection system with a mixture cloud, which is generated by a fuel injection valve according to the invention in the combustion chamber,
Fig. 2
a partially sectioned view of an embodiment of a fuel injection valve according to the invention,
Fig. 3A-B
a section through the discharge-side part of in Fig. 2 illustrated non-inventive example of a fuel injection valve according to the invention in two different stroke positions, and
Fig. 4
an embodiment of a fuel injection valve according to the invention in the same representation as in FIGS. 3A and 3B ,

Beschreibung der AusführungsbeispieleDescription of the embodiments

Fig. 1 zeigt in einer auszugsweisen, schematisierten Schnittdarstellung ein Ausführungsbeispiel eines Brennstoffeinspritzsystems 1 für eine gemischverdichtende fremdgezündete Brennkraftmaschine. Fig. 1 shows in an excerpt, schematic sectional view of an embodiment of a fuel injection system 1 for a mixture-compression spark-ignition internal combustion engine.

Das Brennstoffeinspritzsystem 1 umfaßt einen Brennraum 2, welcher durch Zylinderwandungen 3, einen Zylinderkopf 4, welcher Firstschrägen 5 aufweist, und einen Kolben 6 begrenzt ist. Eine Zündkerze 7 ist z. B. seitlich in den Brennraum 2 hineinragend angeordnet. Ein erfindungsgemäßes Brennstoffeinspritzventil 10 ist zwischen den Firstschrägen 5 so angeordnet, daß Brennstoff in Form einer beispielsweise kegelförmigen Gemischwolke 8, 9 in den Brennraum 2 eingespritzt wird.The fuel injection system 1 comprises a combustion chamber 2 which is delimited by cylinder walls 3, a cylinder head 4 which has ridge slopes 5, and a piston 6. A spark plug 7 is z. B. arranged laterally projecting into the combustion chamber 2. A fuel injection valve 10 according to the invention is arranged between the ridge bevels 5 in such a way that fuel is injected into the combustion chamber 2 in the form of, for example, a conical mixture cloud 8, 9.

Um die oben angesprochenen Mängel in Bezug auf die Stöchiometrie der Gemischwolke 8, 9 sowie des direkten Anspritzens der Zündkerze 7 zu beheben, ist das Brennstoffeinspritzventil 10 erfindungsgemäß so ausgelegt, daß die darin herrschende Brennstoffströmung in unterschiedlich starkem Maß so gedrosselt wird, daß abhängig von der Hubstellung einer Ventilnadel des Brennstoffeinspritzventils 10 eine Gemischwolke 8, 9 mit einem variablen Öffnungswinkel α im Brennraum 2 erzeugt werden kann.In order to remedy the above-mentioned deficiencies with respect to the stoichiometry of the mixture cloud 8, 9 and the direct injection of the spark plug 7, the fuel injector 10 is inventively designed so that the prevailing fuel flow is throttled to varying degrees so that depending on the Hubstellung a valve needle of the fuel injection valve 10, a mixture cloud 8, 9 can be generated with a variable opening angle α in the combustion chamber 2.

Wie in den Fig. 3A und 3B sowie 4 dargestellt und in der nachfolgenden Beschreibung näher erläutert, weist die Ventilnadel oder ein mit dieser in Wirkverbindung stehender Ventilschließkörper zu diesem Zweck zumindest einen, vorzugsweise mehrere Flächenanschliffe oder einen Führungsring auf.As in the FIGS. 3A and 3B 4 and explained in more detail in the following description, the valve needle or a valve-closing body operatively connected therewith has at least one, preferably a plurality of surface contours or a guide ring for this purpose.

Durch die erfindungsgemäße Maßnahme dargestellt in Fig.1 kann zunächst eine Gemischwolke 8 im Brennraum 2 erzeugt werden, die eine große Penetration und einen geringen Öffnungswinkel α aufweist, während beim Schließvorgang des Brennstoffeinspritzventils 10 kurzzeitig die Gemischwolke 9 mit einem größeren Öffnungswinkel α erzeugt wird, welche die Zündkerze 7 im Bereich der Elektroden streift und somit zündfähiges Gemisch zur Funkenstrecke der Zündkerze 7 transportiert.Illustrated by the inventive measure in Fig.1 can first be a mixture cloud 8 are generated in the combustion chamber 2, which has a large penetration and a small opening angle α, while the closing of the fuel injection valve 10 briefly the mixture cloud 9 is generated with a larger opening angle α, which touches the spark plug 7 in the electrodes and thus inflammable mixture transported to the spark gap of the spark plug 7.

Ein Ausführungsbeispiel eines erfindungsgemäß ausgestalteten Brennstoffeinspritzventils 10, welches sich für diese Betriebsart eignet, ist in Fig. 2 dargestellt und im folgenden beschrieben.An embodiment of a fuel injection valve 10 designed according to the invention, which is suitable for this operating mode, is shown in FIG Fig. 2 shown and described below.

Fig. 2 zeigt eine schematisierte geschnittene Ansicht eines Ausführungsbeispiels eines erfindungsgemäß ausgestalteten Brennstoffeinspritzventils 10, welches insbesondere zur Verwendung in dem in Fig. 1 dargestellten Brennstoffeinspritzsystem 1 geeignet ist. Fig. 2 shows a schematic sectional view of an embodiment of an inventively designed fuel injector 10, which in particular for use in the in Fig. 1 illustrated fuel injection system 1 is suitable.

Das Brennstoffeinspritzventil 10 ist dabei in Form eines direkt einspritzenden Brennstoffeinspritzventils 10 ausgeführt, das zum direkten Einspritzen von Brennstoff in den Brennraum 2 der gemischverdichtenden, fremdgezündeten Brennkraftmaschine dient. Im Ausführungsbeispiel handelt es sich dabei um ein nach außen öffnendes Brennstoffeinspritzventil 10.The fuel injection valve 10 is designed in the form of a direct-injection fuel injection valve 10, which serves for the direct injection of fuel into the combustion chamber 2 of the mixture-compressing, spark-ignited internal combustion engine. In the exemplary embodiment, this is an outwardly opening fuel injection valve 10.

Das Brennstoffeinspritzventil 10 umfaßt einen Aktor 11, der im vorliegenden Ausführungsbeispiel als piezoelektrischer Aktor 11 ausgebildet ist. Der Aktor 11 ist in einem Aktorgehäuse 12 zur Stabilisierung gekapselt und stützt sich endseitig in Zulaufrichtung an einem Widerlager 13 und abströmseitig an einer Schulter 14 ab. Die Schulter 14 steht mit einer zweiteiligen Ventilnadel 15 in kraftschlüssiger Verbindung.The fuel injection valve 10 includes an actuator 11, which is formed in the present embodiment as a piezoelectric actuator 11. The actuator 11 is encapsulated in an actuator housing 12 for stabilization and is supported at the end in the inlet direction at an abutment 13 and downstream on a shoulder 14 from. The shoulder 14 is in frictional connection with a two-part valve needle 15.

Ein zuströmseitiger erster Teil 16 der Ventilnadel 15 stützt sich an der Schulter 14 ab, während ein zweiter Teil 17 abströmseitig des ersten Teils 16 von diesem getrennt angeordnet ist. Der erste Teil 16 der Ventilnadel 15 wird durch eine erste Rückstellfeder 18 beaufschlagt, welche zwischen der Schulter 14 und einem Dichtgehäuse 19 angeordnet ist. Der zweite Teil 17 der Ventilnadel 15 wird durch eine zweite Rückstellfeder 20 beaufschlagt, deren Federkraft geringer ist als diejenige der ersten Rückstellfeder 18, so daß der zweite Teil 17 der Ventilnadel 15 gegenüber dem ersten Teil 16 durchschwingen kann. Dies ist bei schnellschaltenden Brennstoffeinspritzventilen 10 mit piezoelektrischen Aktoren 11 zur Dämpfung und Entprellung der Schließbewegung zweckmäßig.An inflow-side first part 16 of the valve needle 15 is supported on the shoulder 14, while a second part 17 downstream of the first part 16 is arranged separately from this. The first part 16 of the valve needle 15 is acted upon by a first return spring 18, which is arranged between the shoulder 14 and a sealing housing 19. The second part 17 of the valve needle 15 is acted upon by a second return spring 20 whose spring force is lower than that of the first return spring 18, so that the second part 17 of the valve needle 15 can swing through relative to the first part 16. This is useful in fast-switching fuel injection valves 10 with piezoelectric actuators 11 for damping and Entprellung the closing movement.

Das Brennstoffeinspritzventil 10 umfaßt weiterhin eine Wellrohrdichtung 21, welche den Aktor 11 vor dem das Brennstoffeinspritzventil 10 durchströmenden Brennstoff schützt. Der Brennstoff wird im Ausführungsbeispiel über eine zentrale Brennstoffzufuhr 22 zugeführt und strömt durch einen Brennstoffkanal 23 in einem Gehäusekörper 24. Er wird dabei an dem Dichtgehäuse 19 vorbei in eine Ausnehmung 25 eines in den Gehäusekörper 24 eingeschobenen Düsenkörpers 26, in welcher auch der zweite Teil 17 der Ventilnadel 15 angeordnet ist, geleitet.The fuel injection valve 10 further comprises a corrugated tube seal 21 which protects the actuator 11 from the fuel flowing through the fuel injection valve 10. In the exemplary embodiment, the fuel is supplied via a central fuel supply 22 and flows through a fuel channel 23 in a housing body 24. It is thereby past the sealing housing 19 into a recess 25 of a nozzle body 26 inserted into the housing body 24, in which also the second part 17 the valve needle 15 is arranged, passed.

Der zweite Teil 17 der Ventilnadel 15 weist einen mit der Ventilnadel 15 einstückig ausgebildeten oder in kraftschlüssiger Verbindung mit dieser stehenden Ventilschließkörper 27 auf, welcher mit einer an dem Düsenkörper 26 ausgebildeten Ventilsitzfläche 28 einen Dichtsitz bildet.The second part 17 of the valve needle 15 has an integral with the valve needle 15 or in frictional connection with this standing valve closing body 27, which forms a sealing seat with a formed on the nozzle body 26 valve seat surface 28.

An dem Ventilschließkörper 27 und/oder dem zweiten Teil 17 der Ventilnadel 15 sind erfindungsgemäß Flächenanschliffe 29 ausgebildet, welche so angebracht sind, daß eine Drosselwirkung auf den das Brennstoffeinspritzventil 10 durchströmenden Brennstoff ausgeübt wird. Ausführungsbeispiele, die zwar nicht Teil der Erfindung sind, aber zum besseren Verständnis der Erfindung beitragen sind in Fig. 3A bis 3B, die erfindungsgemäßen Maßnahmen sind in Fig. 4 näher dargestellt und in der nachfolgenden Beschreibung eingehend erläutert.At the valve closing body 27 and / or the second part 17 of the valve needle 15 Flächenanschliffe 29 are formed according to the invention, which are mounted so that a throttling action is exerted on the fuel injection valve 10 flowing through the fuel. Embodiments, which are not part of the invention, but contribute to a better understanding of the invention are in FIGS. 3A to 3B , the measures according to the invention are in Fig. 4 shown in detail and explained in detail in the following description.

Zur Betätigung des Brennstoffeinspritzventils 10 wird an den Aktor 11 eine Erregerspannung beispielsweise über eine nicht weiter dargestellte elektrische Leitung angelegt. Der Aktor 11, welcher als piezoelektrischer Aktor 11 ausgeführt ist, dehnt sich daraufhin entgegen der Kraft der ersten Rückstellfeder 18 aus. Dadurch wird der erste Teil 16 der Ventilnadel 15 in einer Hubrichtung bewegt. Der zweite Teil 17 der Ventilnadel 15 mit dem daran ausgebildeten Ventilschließkörper 27 wird ebenfalls entgegen der Kraft der zweiten Rückstellfeder 20 in Hubrichtung bewegt, so daß der Ventilschließkörper 27 von der Ventilsitzfläche 28 abhebt und Brennstoff abgespritzt wird.For actuating the fuel injection valve 10, an exciter voltage is applied to the actuator 11, for example via an electrical line, not shown. The actuator 11, which is designed as a piezoelectric actuator 11, then expands against the force of the first return spring 18. As a result, the first part 16 of the valve needle 15 is moved in a stroke direction. The second part 17 of the valve needle 15 with the valve closing body 27 formed thereon is also moved counter to the force of the second return spring 20 in the stroke direction, so that the valve closing body 27 lifts from the valve seat surface 28 and fuel is sprayed.

Wird der Aktor 11 entladen, kehrt der erste Teil 16 der Ventilnadel 15 durch die Kraft der ersten Rückstellfeder 18 entgegen der Hubrichtung in seine Ausgangsposition zurück. Dadurch wird auch der zweite Teil 17 der Ventilnadel 15 entlastet, wodurch der Ventilschließkörper 27 wieder auf der Ventilsitzfläche 28 aufsetzt und das Brennstoffeinspritzventil 10 geschlossen wird.When the actuator 11 is unloaded, the first part 16 of the valve needle 15 returns to its original position against the stroke direction by the force of the first return spring 18. As a result, the second part 17 of the valve needle 15 is also relieved, as a result of which the valve closing body 27 rests again on the valve seat surface 28 and the fuel injection valve 10 is closed.

Die Fig. 3A und 3B zeigen eine auszugsweise Vergrößerung des in Fig. 2 mit III bezeichneten Ausschnitts des Brennstoffeinspritzventils 10 in zwei verschiedenen Hubstellungen der Ventilnadel 15. Dabei stellt Fig. 3A eine Hubstellung dar, welche beispielsweise einer Offenstellung des Brennstoffeinspritzventils 10 entspricht, während Fig. 3B eine Hubstellung zeigt, welche bei einem geringeren Hub der Ventilnadel 15 beispielsweise beim Schließen des Brennstoffeinspritzventils 10 auftritt. Übereinstimmende Bauteile sind in allen Figuren mit übereinstimmenden Bezugszeichen versehen.The FIGS. 3A and 3B show a partial enlargement of the in Fig. 2 With III designated section of the fuel injection valve 10 in two different stroke positions of the valve needle 15. It provides Fig. 3A a stroke position, which corresponds for example to an open position of the fuel injection valve 10, while Fig. 3B shows a stroke position, which occurs at a lower stroke of the valve needle 15, for example when closing the fuel injection valve 10. Matching components are provided in all figures with corresponding reference numerals.

Wie bereits weiter oben angesprochen, weist der zweite Teil 17 der Ventilnadel 15 an dem mit ihr einstückig ausgebildeten Ventilschließkörper 27 oder direkt an dem zweiten Teil 17 der Ventilnadel 15 zumindest einen Flächenanschliff 29 auf. Vorzugsweise sind mehrere Flächenanschliffe 29 regelmäßig oder unregelmäßig über den Umfang des Ventilschließkörpers 27 verteilt an diesem ausgebildet.As already mentioned above, the second part 17 of the valve needle 15 on the integrally formed with her valve closing body 27 or directly on the second part 17 of the valve needle 15 at least one Flächenanschliff 29. Preferably, a plurality of Flächenanschliffe 29 are regularly or irregularly distributed over the circumference of the valve closing body 27 formed on this.

Die Flächenanschliffe 29 sind beispielsweise längsoval ausgebildet und wechseln mit Führungsflächen 30 ab, welche an einer an dem Düsenkörper 26 ausgebildeten Gegenfläche 31 anliegen. Die Führungsflächen 30 und die Gegenfläche 31 führen den zweiten Teil 17 der Ventilnadel 15 während der Hubbewegung. Dadurch kann Fehlfunktionen des Brennstoffeinspritzventils 10 durch Versätze der Ventilnadel 15 mit nachfolgendem Verklemmen vorgebeugt werden.The Flächenanschliffe 29 are formed, for example, longitudinally oval and alternate with guide surfaces 30 which abut against a formed on the nozzle body 26 mating surface 31. The guide surfaces 30 and the counter surface 31 guide the second part 17 of the valve needle 15 during the lifting movement. This malfunction of the fuel injection valve 10 can be prevented by offsets of the valve needle 15 with subsequent jamming.

Wie bereits oben ausgeführt, ist die Veränderung eines Öffnungswinkels α der in den Brennraum 2 eingespritzten Gemischwolke 8, 9 so zu gestalten, daß zum Ende des Einspritztaktes eine Gemischwolke 9 erzeugt wird, deren Öffnungswinkel α2 größer als der Öffnungswinkel α1 zum Beginn des Einspritztaktes ist. Die Flächenanschliffe 29 am Ventilschließkörper 27 sind dementsprechend in ihrer radialen Ausdehnung so ausgebildet, daß sie die Weite eines zwischen den Flächenanschliffen 29 und der Gegenfläche 31 freiwerdenden Drosselspalts 32 definieren. Die Weite des Öffnungsquerschnitts am Dichtsitz im voll geöffneten Zustand des Brennstoffeinspritzventils 10 ist dabei in jedem Fall größer als die Weite des durch die Flächenanschliffe 29 definierten Drosselspaltes 32, so daß die Flächenanschliffe 29 als Vordrossel dienen.As already stated above, the change in an opening angle α of the mixture cloud 8, 9 injected into the combustion chamber 2 is to be designed such that a mixture cloud 9 is produced at the end of the injection cycle whose opening angle α 2 is greater than the opening angle α 1 at the beginning of the injection cycle is. The Flächenanschliffe 29 on the valve closing body 27 are accordingly formed in their radial extent so that they define the width of a between the Flächenanschliffen 29 and the mating surface 31 released throttle gap 32. The width of the opening cross-section at the sealing seat in the fully open state of the fuel injection valve 10 is in any case greater than the width of the defined by the Flächenanschliffe 29 throttle gap 32 so that the Flächenanschliffe 29 serve as a choke.

Ist, wie in Fig. 3A dargestellt, der Hub des Ventilschließkörpers 27 groß, beispielsweise in einer Maximalstellung, kann durch die in dem Drosselspalt 32 erzielte Vordrosselung eine kegelförmige Gemischwolke 8 mit einem kleinen Öffnungswinkel α1 in den Brennraum 2 eingespritzt werden.Is, as in Fig. 3A shown, the stroke of the valve closing body 27 large, for example in a maximum position, a conical mixture cloud can be injected 8 with a small aperture angle α 1 in the combustion chamber 2 by the scored in the throttle gap 32 Vordrosselung.

Die Strömungslamelle, die in dem engen Spalt an den Flächenanschliffen gebildet wird, ist dünner als der Spalt am Dichtsitz. Die Kraftstofflamelle kann dadurch mit geringer Umlenkung nach außen durch den Dichtsitz fließen. Die Kraftstofflamelle fließt nicht parallel zu den Wandungen durch den Dichtsitzbereich, sondern schräg dazu nach unten gerichtet. Die kegelförmige Gemischwolke hat dadurch einen kleinen Öffnungswinkel.The flow lamella formed in the narrow gap at the surface poles is thinner than the gap at the seal seat. The fuel lamella can thereby flow with little deflection to the outside through the sealing seat. The fuel lamella does not flow parallel to the walls through the sealing seat area, but obliquely directed downward. The conical mixture cloud thus has a small opening angle.

Wird der Ventilschließkörper 27 in einer Schließrichtung bewegt, weil der Aktor 11 des Brennstoffeinspritzventils 10 mit einer kleineren Erregerspannung versorgt wird, verengt sich die Entfernung des Ventilschließkörpers 27 von der Ventilsitzfläche 28. Wenn die Entfernung kleiner als der Spalt an den Flächenanschliffen wird, fließt die Strömung durch den Sitzspalt zwangsläufig parallel der Wandungen. Damit bildet sich ein größerer Öffnungswinkel der kegeligen Gemischwolke als im ersten Fall aus.When the valve closing body 27 is moved in a closing direction because the actuator 11 of the fuel injection valve 10 is supplied with a smaller excitation voltage, the distance of the valve closing body 27 from the valve seat surface 28 narrows. When the distance becomes smaller than the gap at the surfaces, the flow flows through the seat gap inevitably parallel to the walls. This forms a larger opening angle of the conical mixture cloud than in the first case.

Fig. 4 zeigt ein Ausführungsbeispiel für ein erfindungsgemäß ausgestaltetes Brennstoffeinspritzventil 10 in gleicher Darstellung wie Fig. 3A und 3B. Fig. 4 shows an embodiment of an inventively designed fuel injection valve 10 in the same representation as FIGS. 3A and 3B ,

In diesem Ausführungsbeispiel ist die Drosselungsfunktion des Drosselspalts 32 unabhängig von den Flächenanschliffen 29.In this embodiment, the throttling function of the throttle gap 32 is independent of the Flächenanschliffen 29th

Abströmseitig der Flächenanschliffe 29 ist am Ventilschließkörper 27 ein Führungsbereich 33 ausgebildet, welcher einen Drosselspalt 34 definiert, welcher über den Umfang des Ventilschließkörpers 27 immer gleich weit ist. Beim Schließen des Brennstoffeinspritzventils 10 verschiebt sich wiederum das Verhältnis der Drosslung durch den Drosselspalt 34 zur Drosselung durch den Dichtsitz zugunsten der Drosselung im Dichtsitz, wodurch ebenfalls eine Aufweitung der in den Brennraum 2 eingespritzten Gemischwolke erfolgt.Downstream of Flächenanschliffe 29 27, a guide portion 33 is formed on the valve closing body, which defines a throttle gap 34, which is always the same distance over the circumference of the valve closing body 27. When the fuel injection valve 10 is closed, the ratio of the throttling through the throttle gap 34 for throttling through the sealing seat in turn shifts in favor of the throttling in the sealing seat, which likewise causes a widening of the mixture cloud injected into the combustion chamber 2.

Der Drosseleffekt und die nachfolgende Aufweitung des Öffnungswinkels α der Gemischwolke 8, 9 kann beispielsweise auch durch das Ansteuern zweier diskreter Hubstellungen über den Aktor 11 oder eine Verlangsamung des Schließvorgangs des Brennstoffeinspritzventils 10 verstärkt werden.The throttling effect and the subsequent widening of the opening angle α of the mixture cloud 8, 9 can be intensified, for example, by the activation of two discrete stroke positions via the actuator 11 or a slowing down of the closing operation of the fuel injection valve 10.

Die Erfindung ist nicht auf die dargestellten Ausführungsbeispiele beschränkt und für beliebige Bauformen von Brennstoffeinspritzventilen 10 unterschiedliche Anordnungen von Zündkerzen 7 und Brennstoffeinspritzventilen 10 im Zylinderkopf 4 einer Brennkraftmaschine und Magnetantrieb der Ventilnadelbewegung anwendbar.The invention is not limited to the illustrated embodiments and for any designs of fuel injectors 10 different arrangements of spark plugs 7 and fuel injectors 10 in the cylinder head 4 of an internal combustion engine and magnetic drive valve needle movement applicable.

Claims (7)

  1. Fuel injection valve (10) for internal combustion engines, having an actuator (10) which is operatively connected to a valve needle (15) which is guided in a nozzle body (26), and having a valve closing body (27) which is connected in a non-positively locking fashion to the valve needle (15) and forms a sealing seat together with a valve seat surface (28) which is formed on the nozzle body (26),
    the valve needle (15) and/or the valve closing body (27) having at least one ground surface portion (29) which is formed on the circumference of the valve needle (15) and/or of the valve closing body (27), and a throttling gap (32) being formed between the at least one ground surface portion (29) and a counterpart surface (31) which is formed on the nozzle body (26), the cross section of which throttling gap (32) is smaller than the opening cross section at the sealing seat in the open state of the fuel injection valve (10),
    characterized
    in that a guide region (33) in the form of a raised guide ring is formed at the outflow side of the at least one ground surface portion (29), which guide ring defines a throttling gap (34), the guide region (33) forming a throttling gap (34) of constant width together with the counterpart surface (31), and the guide region (33) being formed in one piece with the valve closing body (27).
  2. Fuel injection valve according to Claim 1,
    characterized
    in that the at least one ground surface portion (29) is provided in the region of the guide in the nozzle body (26).
  3. Fuel injection valve according to Claim 2,
    characterized
    in that a plurality of ground surface portions (29) are provided which are arranged on the valve closing body (27) at regular or irregular intervals around the circumference.
  4. Fuel injection valve according to Claim 3,
    characterized
    in that guide surfaces (30) are formed between the ground surface portions (29).
  5. Fuel injection valve according to Claim 4,
    characterized
    in that the guide surfaces (30) interact with the counterpart surface (31), which is formed on the nozzle body (26), to provide guidance of the valve closing body (27).
  6. Fuel injection valve according to one of Claims 1 to 5, characterized
    in that the throttling action of the ground surface portions (29) exceeds the throttling action at the sealing seat in the open state of the fuel injection valve (10).
  7. Fuel injection valve according to one of Claims 1 to 6,
    characterized
    in that, as the fuel injection valve (10) closes, the opening cross section at the sealing seat becomes ever closer in size.to the cross section of the throttling gap (32) in the region of the ground surface portions (29).
EP02795038A 2002-02-26 2002-12-23 Fuel injection valve Expired - Lifetime EP1481159B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10208222 2002-02-26
DE10208222A DE10208222A1 (en) 2002-02-26 2002-02-26 Fuel injector
PCT/DE2002/004730 WO2003072929A1 (en) 2002-02-26 2002-12-23 Fuel injection valve

Publications (2)

Publication Number Publication Date
EP1481159A1 EP1481159A1 (en) 2004-12-01
EP1481159B1 true EP1481159B1 (en) 2009-10-28

Family

ID=27762450

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02795038A Expired - Lifetime EP1481159B1 (en) 2002-02-26 2002-12-23 Fuel injection valve

Country Status (5)

Country Link
EP (1) EP1481159B1 (en)
JP (1) JP4593927B2 (en)
KR (1) KR100972523B1 (en)
DE (2) DE10208222A1 (en)
WO (1) WO2003072929A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2651925C1 (en) * 2017-07-19 2018-04-24 Федеральное государственное бюджетное образовательное учреждение высшего образования "Ярославский государственный технический университет" ФГБОУВО "ЯГТУ" Atomizer of valve injector for internal combustion engine and method of its assembly

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009138614A (en) * 2007-12-05 2009-06-25 Mitsubishi Heavy Ind Ltd Fuel injection valve of pressure accumulation-type fuel injection device
ITNA20110032A1 (en) * 2011-07-29 2011-10-28 Antonio Potignano HOLE FUEL PULVERIZER AND VARIABLE INJECTION SECTION
ITNA20110035A1 (en) * 2011-08-09 2011-11-08 Antonio Potignano HOLE FUEL PULVERIZER AND VARIABLE INJECTION SECTION
EP2927473B1 (en) * 2014-04-03 2017-09-20 Continental Automotive GmbH Fuel injection valve for an internal combustion engine

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5829688A (en) * 1996-01-13 1998-11-03 Robert Bosch Gmbh Injection valve for directly injecting fuel into an internal combustion engine

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9008403D0 (en) * 1990-04-12 1990-06-13 Lucas Ind Plc Fuel injection nozzle
DE19623713B4 (en) 1996-06-14 2008-06-19 Robert Bosch Gmbh Injection valve, in particular for the direct injection of fuel into a combustion chamber of an internal combustion engine
DE19633260A1 (en) * 1996-08-17 1998-02-19 Bosch Gmbh Robert Injection valve, in particular for injecting fuel directly into a combustion chamber of an internal combustion engine
US20060155499A1 (en) * 2005-01-11 2006-07-13 Wei-Kuo Shih Method for calibration of digital image-captured devices

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5829688A (en) * 1996-01-13 1998-11-03 Robert Bosch Gmbh Injection valve for directly injecting fuel into an internal combustion engine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2651925C1 (en) * 2017-07-19 2018-04-24 Федеральное государственное бюджетное образовательное учреждение высшего образования "Ярославский государственный технический университет" ФГБОУВО "ЯГТУ" Atomizer of valve injector for internal combustion engine and method of its assembly

Also Published As

Publication number Publication date
KR20040083459A (en) 2004-10-01
EP1481159A1 (en) 2004-12-01
KR100972523B1 (en) 2010-07-28
DE10208222A1 (en) 2003-10-30
JP2005518498A (en) 2005-06-23
DE50213972D1 (en) 2009-12-10
WO2003072929A1 (en) 2003-09-04
JP4593927B2 (en) 2010-12-08

Similar Documents

Publication Publication Date Title
EP1045136B1 (en) Method for operating a reciprocating internal combustion engine and injection nozzle for carrying out the method
EP0846225B1 (en) Injection valve, in particular for directly injecting fuel into the combustion chamber of an internal combustion engine
EP1440239B1 (en) Fuel injection valve
EP0975870B1 (en) Fuel injection valve or fuel injection nozzle
EP2480783B1 (en) Fuel injection valve for an internal combustion engine
DE10012969B4 (en) Injection nozzle and a method for forming a fuel-air mixture
DE10329524A1 (en) Auto-ignition internal combustion engine
EP1119703B1 (en) Fuel injection valve
DE10334347B4 (en) Fuel injection valve and internal combustion engine with fuel injection valve
WO2002095201A1 (en) Fuel injection system
DE19812092A1 (en) Fuel injection unit for IC engine with nozzle body
WO2004076851A1 (en) Fuel injection valve
DE10210976A1 (en) Fuel injection valve for internal combustion engine has injection jets converging from at least one outer and one inner injection channel
DE602004001580T2 (en) FUEL INJECTION VALVE FOR INTERNAL COMBUSTION ENGINE
EP2521853B1 (en) Fuel injection valve
EP1290322B1 (en) Fuel injection system
DE10012970B4 (en) Method for forming an ignitable fuel-air mixture
EP1481159B1 (en) Fuel injection valve
EP1312796B1 (en) Fuel injection valve
EP1573192A1 (en) Internal combustion engine having auto-ignition
EP1137880B1 (en) Method for dosing fuel with a fuel injection valve
DE102017218224A1 (en) Valve for metering a fluid, in particular fuel injection valve
EP1702156B1 (en) Fuel injection valve
DE102007013244A1 (en) Combustion method for e.g. diesel engine, involves producing rotary spraying jets by eccentric arrangement of injecting openings at combustion chamber-sided end of nozzle body or at combustion chamber-sided end of injection valve element
EP1346149A1 (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: 20040927

AK Designated contracting states

Kind code of ref document: A1

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

17Q First examination report despatched

Effective date: 20050803

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

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 50213972

Country of ref document: DE

Date of ref document: 20091210

Kind code of ref document: P

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: 20100729

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20131217

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20131219

Year of fee payment: 12

Ref country code: FR

Payment date: 20131213

Year of fee payment: 12

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20141223

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20150831

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 NON-PAYMENT OF DUE FEES

Effective date: 20141223

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

Ref country code: FR

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

Effective date: 20141231

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: 20141223

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20190221

Year of fee payment: 17

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50213972

Country of ref document: DE

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: 20200701