EP2521853B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

Info

Publication number
EP2521853B1
EP2521853B1 EP10787447.1A EP10787447A EP2521853B1 EP 2521853 B1 EP2521853 B1 EP 2521853B1 EP 10787447 A EP10787447 A EP 10787447A EP 2521853 B1 EP2521853 B1 EP 2521853B1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
injection valve
valve
regions
throughflow
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.)
Active
Application number
EP10787447.1A
Other languages
German (de)
French (fr)
Other versions
EP2521853A1 (en
Inventor
Martin Buehner
Kai Gartung
Peter Land
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 EP2521853A1 publication Critical patent/EP2521853A1/en
Application granted granted Critical
Publication of EP2521853B1 publication Critical patent/EP2521853B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1886—Details of valve seats not covered by groups F02M61/1866 - F02M61/188
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • 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
    • F02M2200/85—Mounting of fuel injection apparatus
    • F02M2200/858—Mounting of fuel injection apparatus sealing arrangements between injector and engine

Definitions

  • the invention relates to a fuel injection valve according to the preamble of the main claim.
  • FIG. 1 an example of a known from the prior art fuel injection valve is shown, which is installed in a receiving bore of a cylinder head of an internal combustion engine.
  • a fuel injection valve of this type is already out of the DE 10 2006 049 253 A1 known.
  • the fuel injection valve has an excitable actuator in the form of an electromagnetic circuit and a valve element which can be moved along a valve longitudinal axis, wherein a valve closure member sealingly cooperates with a valve seat with a valve seat.
  • a mounted on a nozzle body valve seat body at the discharge end of the fuel injection valve has circumferentially a plurality of flow areas upstream of the valve seat, between which are respective guide portions for the valve element. Downstream of the valve seat several injection openings are provided in the valve seat body.
  • the fuel injector is particularly suitable for use in fuel injection systems of mixture-compression spark-ignition internal combustion engines.
  • a fuel injector for an internal combustion engine in particular of a motor vehicle, known which has a nozzle body and a nozzle body in the axially movable nozzle needle which engages with a nozzle needle tip in a blind hole of the nozzle body, wherein the nozzle needle tip and the blind hole are formed such that the nozzle needle is guided in the blind hole.
  • the fuel injection nozzle has injection openings arranged in the nozzle body, wherein the nozzle needle abuts with a sealing surface on an inner wall of the nozzle body to close the fuel injection nozzle, wherein a pressure space is formed between the nozzle needle and the nozzle body upstream of the sealing surface.
  • the injection openings are formed in a region of the nozzle body, in which the sealing surface is located, wherein the injection openings can be flowed through grooves in the nozzle needle from above and below.
  • a fuel injection valve for fuel injection systems of internal combustion engines wherein the fuel injection valve has at least one excitable actuator and a valve longitudinal axis movable along a spherical valve element which cooperates sealingly with a valve seat.
  • the valve also has a nozzle body at the discharge end of the fuel injection valve, wherein circumferentially a plurality of similar Naturalström Suitee are provided in the form of Einströmlöchern upstream of the valve seat, between which are each guide regions for the valve element.
  • the number of ejection openings downstream of the valve seat differs from the number of injection holes upstream of the valve seat.
  • a fuel injection valve for fuel injection systems of internal combustion engines wherein the fuel injection valve has at least one excitable actuator and a valve longitudinal axis movable along a spherical valve element which cooperates sealingly with a valve seat.
  • the valve also has a nozzle body at the discharge end of the fuel injection valve, wherein circumferentially a plurality of swirl grooves are provided upstream of the valve seat, between which are respective guide portions for the valve element.
  • the spin-loaded fuel is then sprayed downstream of the valve seat surface via a central injection orifice.
  • a fuel injector for an internal combustion engine in particular of a motor vehicle, known which has a nozzle body and a nozzle body in the axially movable nozzle needle which engages with a nozzle needle tip in a blind hole of the nozzle body, wherein the nozzle needle tip and the blind hole are formed such that the nozzle needle is guided in the blind hole.
  • the nozzle needle is designed such that in the region of the valve sealing surface distributed over the circumference a plurality of depressions are formed.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that achieved in a simple manner producible improved flow of spray orifices and as a result, a reduction in dispersion over known solutions in which the number of injection ports does not match the number of Anströmpfaden upstream of the valve seat , is achieved in the jet and flow characteristics.
  • the flow of the spray orifices is, above all things, evened out and more stable over time. Flow fluctuations in the spray orifices can be reduced, leaving the overall spray pattern a quieter impression. As a result, a cleaner and better combustion of the fuel in the combustion chamber is achieved. Combustion misfires, which could occur in the case of certain jet patterns or interpretations of the injection orifices in known cases in extreme cases, can be excluded according to the invention here.
  • the inventive design of the fuel injector is also suitable for spray-guided combustion.
  • At least two flow-through regions upstream of the valve seat differ in size, such as circumferential width and / or radial depth, and / or contour.
  • the flow-through areas are advantageously changed in width and depth so that wider and at the same time deeper or on the other hand deeper flow-through areas are designed so that they reliably and reliably cover the quantity required for two spray openings, while the narrower and at the same time having a low depth or on the one hand narrower and on the other hand flat flow areas are reduced so that a sufficient amount of fuel for exactly one spray opening is provided.
  • FIG. 1 a valve in the form of an injection valve 1 for fuel injection systems of mixture-compression spark-ignited internal combustion engines in a side view.
  • the fuel injection valve 1 which is designed in the form of a direct-injection injector for injecting fuel directly into a combustion chamber 25 of the internal combustion engine, is installed in a receiving bore 20 of a cylinder head 9.
  • the discharge end 17 of the fuel injection valve 1 according to FIG. 1 which is marked with II, is in the FIG. 2 shown in an enlarged view, since it characterizes the invention essential part of the fuel injection valve 1.
  • a sealing ring 2, in particular of Teflon®, ensures optimum sealing of the fuel injection valve 1 with respect to the wall of the receiving bore 20 of the cylinder head 9.
  • a flat intermediate element 24 is inserted, which is designed in the form of a washer.
  • the fuel injection valve 1 has at its inlet-side end 3 a plug connection to a fuel distributor line (fuel rail) 4, which is sealed by a sealing ring 5 between a connection piece 6 of the fuel distributor line 4, which is shown in section, and an inlet connection 7 of the fuel injection valve 1.
  • the fuel injection valve 1 is inserted into a receiving opening 12 of the connection piece 6 of the fuel distribution line 4.
  • the connecting piece 6 is in this case e.g. in one piece from the actual fuel distributor line 4 and has upstream of the receiving opening 12 a smaller diameter flow opening 15 through which the flow of the fuel injection valve 1 takes place.
  • the fuel injection valve 1 has an electrical connection plug 8 for the electrical contacting for actuating the fuel injection valve 1.
  • a holding-down device 10 is provided between the fuel injection valve 1 and the connecting piece 6.
  • the hold-down 10 is as a bow-shaped component executed, eg as a punching-bending part.
  • the hold-down device 10 has a part-ring-shaped base element 11, from which a hold-down bar 13 extends, which abuts against a downstream end face 14 of the connecting piece 6 on the fuel distributor line 4 in the installed state.
  • FIG. 2 is the discharge-side end 17 of the fuel injection valve 1 according to FIG. 1 is shown with a plurality of fürström Suiteen 26 in the nozzle body 18 in an enlarged view.
  • the fuel injection valve 1 has at least one excitable actuator (not shown), such as an electromagnetic circuit, a piezoelectric or magnetostrictive actuator, and a valve element movable along a valve longitudinal axis 27.
  • the valve element, not shown (valve needle, valve closing body) cooperates sealingly with a valve seat 28 which is formed, for example, at the downstream end of a blind hole 29 in the nozzle body 18 itself. Upstream of the valve seat 28, a plurality of through-flow regions 26 are formed in the wall of the blind bore 29 of the nozzle body 18.
  • flow-through regions 26 are formed in the form of flow-through pockets which allow the fuel to flow unimpeded to the valve seat 28 when the valve element is installed.
  • reference numeral 18 is intended in particular a fixed to a nozzle body valve seat body, as in eg FIG. 2 the DE 10 2006 049 253 A1 is meant to be meant.
  • FIG. 3 shows a sectional view taken along the line III-III of in FIG. 2 From this view, it is clear that the naturalström Societye 26 form leksnutähnliche flow pockets, which are spaced from each other.
  • a guide region 30 for the axially movable valve element lies between the flow-through regions 26.
  • five flow areas 26 are provided in the nozzle body 18.
  • Downstream of the valve seat 28 are in a bottom portion 31 of the nozzle body 18 or in an alternative spray perforated disk, which is fastened to the nozzle body 18, a plurality of ejection openings 32 is formed by the fuel atomized finely atomized into the combustion chamber 25 is discharged.
  • the spray-discharge openings 32 are, for example, oriented in such a way that they extend obliquely inclined radially outward beyond the thickness of the bottom section 31 or the spray-perforated pane.
  • the fürström Schemee 26 are thus at a regular average distance of 72 ° to each other and are incorporated with the same circumferential width and radial depth in the nozzle body 18. Due to the different number of fürström Schemeen 26 and spray openings 32 arise depending on the valve design instabilities in the flow of the spray openings 32. This can ultimately lead to a large divergence of the jet and flow characteristics disadvantageously. Due to the ambiguous and temporally not necessarily stable quantity allocation, it can also lead to a restless "fluttering" spray pattern.
  • FIG. 4 is a first embodiment of a fuel injection valve 1 according to the invention in the region of its nozzle body 18 in a representation analogous to FIG. 3 shown.
  • at least two flow areas 26 differ in their circumferential width.
  • the flow-through regions 26 are now changed in width so that, for example, wider flow-through regions 26 are designed so that they safely and reliably cover the quantity required for two spray-discharge openings 32, while the narrow flow-through regions 26 are reduced in size compared with the known ones Solution according to FIG. 3 are that a sufficient amount of fuel for exactly one ejection opening 32 is provided.
  • FIG. 5 is a second embodiment of a fuel injection valve 1 according to the invention in the region of its nozzle body 18 in a representation analogous to FIG. 3 shown.
  • at least two flow areas 26 differ in their radial depth.
  • the flow-through regions 26 are now changed in their depth so that, for example, deeper flow-through regions 26 are designed such that they reliably and reliably cover the quantity required for two spray-discharge openings 32, while the flow-through regions 26 having a small depth thus become smaller compared to the known solution according to FIG. 3 are that a sufficient amount of fuel for exactly one ejection opening 32 is provided.
  • the maximum depth of the fürström Schemee 26 is determined inter alia by the compressive strength of the nozzle body 18 at its downstream end 17.
  • FIG. 6 is a third embodiment of a fuel injection valve 1 according to the invention in the region of its nozzle body 18 in a representation analogous to FIG. 3 shown.
  • at least two flow areas 26 differ in their circumferential width and their radial depth.
  • this variant represents a combination of the two embodiments described above.
  • the flow areas 26 are now changed in width and depth so that, for example, wider and at the same time deeper or, on the one hand, wider and, on the other hand, lower flow-through areas 26 are designed in that they reliably and reliably cover the quantity required for two ejection openings 32, while the narrower and at the same time having a shallower depth or, on the one hand, narrow and, on the other hand, flat flow-through regions 26 are thus reduced in comparison with the known solution according to FIG. 3 are that sufficient Amount of fuel for exactly one spray opening 32 is provided. In this way, a uniform and temporally stable flow of the ejection openings 32 can be optimized and thus a reduction in the scattering of the jet and flow characteristics can be achieved.
  • an asymmetrical distribution of the flow-through regions 26 can be generated over the circumference, so that a uniform distribution of the fürström Schemee 26 is abandoned, the geometry and the dimensions of the fürström Schemee 26 remain the same, the widths of the guide surfaces of the guide portions 30, however, vary.

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.

In der Figur 1 ist beispielhaft ein aus dem Stand der Technik bekanntes Brennstoffeinspritzventil gezeigt, das in einer Aufnahmebohrung eines Zylinderkopfes einer Brennkraftmaschine eingebaut ist. Ein solches Brennstoffeinspritzventil dieser Bauart ist bereits aus der DE 10 2006 049 253 A1 bekannt. Das Brennstoffeinspritzventil weist einen erregbaren Aktuator in Form eines elektromagnetischen Kreises sowie ein entlang einer Ventillängsachse bewegbares Ventilelement auf, wobei ein Ventilschließkörper an einer Ventilnadel mit einem Ventilsitz dichtend zusammenwirkt. Ein an einem Düsenkörper befestigter Ventilsitzkörper am abspritzseitigen Ende des Brennstoffeinspritzventils besitzt umfangsmäßig mehrere Durchströmbereiche stromaufwärts des Ventilsitzes, zwischen denen jeweils Führungsbereiche für das Ventilelement liegen. Stromabwärts des Ventilsitzes sind im Ventilsitzkörper mehrere Abspritzöffnungen vorgesehen. Das Brennstoffeinspritzventil eignet sich besonders für den Einsatz in Brennstoffeinspritzanlagen von gemischverdichtenden fremdgezündeten Brennkraftmaschinen.In the FIG. 1 an example of a known from the prior art fuel injection valve is shown, which is installed in a receiving bore of a cylinder head of an internal combustion engine. Such a fuel injection valve of this type is already out of the DE 10 2006 049 253 A1 known. The fuel injection valve has an excitable actuator in the form of an electromagnetic circuit and a valve element which can be moved along a valve longitudinal axis, wherein a valve closure member sealingly cooperates with a valve seat with a valve seat. A mounted on a nozzle body valve seat body at the discharge end of the fuel injection valve has circumferentially a plurality of flow areas upstream of the valve seat, between which are respective guide portions for the valve element. Downstream of the valve seat several injection openings are provided in the valve seat body. The fuel injector is particularly suitable for use in fuel injection systems of mixture-compression spark-ignition internal combustion engines.

Vorteile der ErfindungAdvantages of the invention

Aus der DE 10 2007 026 122 A1 ist bereits eine Kraftstoffeinspritzdüse für eine Brennkraftmaschine, insbesondere eines Kraftfahrzeugs, bekannt, die einen Düsenkörper und eine in dem Düsenkörper axial beweglich angeordnete Düsennadel aufweist, welche mit einer Düsennadelspitze in ein Sackloch des Düsenkörpers eingreift, wobei die Düsennadelspitze und das Sackloch derart ausgebildet sind, dass die Düsennadel in dem Sackloch geführt ist. Außerdem besitzt die Kraftstoffeinspritzdüse in dem Düsenkörper angeordnete Einspritzöffnungen, wobei die Düsennadel mit einer Dichtfläche an einer Innenwandung des Düsenkörpers anschlägt, um die Kraftstoffeinspritzdüse zu verschließen, wobei zwischen der Düsennadel und dem Düsenkörper stromauf der Dichtfläche ein Druckraum ausgebildet ist. Hierbei sind die Einspritzöffnungen in einem Bereich des Düsenkörpers ausgebildet, in dem sich die Dichtfläche befindet, wobei die Einspritzöffnungen über Rillen in der Düsennadel von oben und unten her angeströmt werden können.From the DE 10 2007 026 122 A1 is already a fuel injector for an internal combustion engine, in particular of a motor vehicle, known which has a nozzle body and a nozzle body in the axially movable nozzle needle which engages with a nozzle needle tip in a blind hole of the nozzle body, wherein the nozzle needle tip and the blind hole are formed such that the nozzle needle is guided in the blind hole. In addition, the fuel injection nozzle has injection openings arranged in the nozzle body, wherein the nozzle needle abuts with a sealing surface on an inner wall of the nozzle body to close the fuel injection nozzle, wherein a pressure space is formed between the nozzle needle and the nozzle body upstream of the sealing surface. Here, the injection openings are formed in a region of the nozzle body, in which the sealing surface is located, wherein the injection openings can be flowed through grooves in the nozzle needle from above and below.

Aus der EP 2 108 810 A2 ist bereits ein Brennstoffeinspritzventil für Brennstoffeinspritzanlagen von Brennkraftmaschinen bekannt, wobei das Brennstoffeinspritzventil wenigstens einen erregbaren Aktuator sowie ein entlang einer Ventillängsachse bewegbares kugelförmiges Ventilelement aufweist, das mit einem Ventilsitz dichtend zusammenwirkt. Das Ventil besitzt zudem einen Düsenkörper am abspritzseitigen Ende des Brennstoffeinspritzventils, wobei umfangsmäßig mehrere gleichartige Durchströmbereiche in Form von Einströmlöchern stromaufwärts des Ventilsitzes vorgesehen sind, zwischen denen jeweils Führungsbereiche für das Ventilelement liegen. Die Anzahl von Abspritzöffnungen stromabwärts des Ventilsitzes weicht von der Anzahl der Einströmlöcher stromaufwärts des Ventilsitzes ab.From the EP 2 108 810 A2 a fuel injection valve for fuel injection systems of internal combustion engines is already known, wherein the fuel injection valve has at least one excitable actuator and a valve longitudinal axis movable along a spherical valve element which cooperates sealingly with a valve seat. The valve also has a nozzle body at the discharge end of the fuel injection valve, wherein circumferentially a plurality of similar Durchströmbereiche are provided in the form of Einströmlöchern upstream of the valve seat, between which are each guide regions for the valve element. The number of ejection openings downstream of the valve seat differs from the number of injection holes upstream of the valve seat.

Aus der WO 02/25101 A1 ist bereits ein Brennstoffeinspritzventil für Brennstoffeinspritzanlagen von Brennkraftmaschinen bekannt, wobei das Brennstoffeinspritzventil wenigstens einen erregbaren Aktuator sowie ein entlang einer Ventillängsachse bewegbares kugelförmiges Ventilelement aufweist, das mit einem Ventilsitz dichtend zusammenwirkt. Das Ventil besitzt zudem einen Düsenkörper am abspritzseitigen Ende des Brennstoffeinspritzventils, wobei umfangsmäßig mehrere Drallnuten stromaufwärts des Ventilsitzes vorgesehen sind, zwischen denen jeweils Führungsbereiche für das Ventilelement liegen. Der drallbeaufschlagte Brennstoff wird dann stromabwärts der Ventilsitzfläche über eine zentrale Abspritzöffnung abgespritzt.From the WO 02/25101 A1 a fuel injection valve for fuel injection systems of internal combustion engines is already known, wherein the fuel injection valve has at least one excitable actuator and a valve longitudinal axis movable along a spherical valve element which cooperates sealingly with a valve seat. The valve also has a nozzle body at the discharge end of the fuel injection valve, wherein circumferentially a plurality of swirl grooves are provided upstream of the valve seat, between which are respective guide portions for the valve element. The spin-loaded fuel is then sprayed downstream of the valve seat surface via a central injection orifice.

Aus der DE 102 40 827 A1 ist bereits eine Kraftstoffeinspritzdüse für eine Brennkraftmaschine, insbesondere eines Kraftfahrzeugs, bekannt, die einen Düsenkörper und eine in dem Düsenkörper axial beweglich angeordnete Düsennadel aufweist, welche mit einer Düsennadelspitze in ein Sackloch des Düsenkörpers eingreift, wobei die Düsennadelspitze und das Sackloch derart ausgebildet sind, dass die Düsennadel in dem Sackloch geführt ist. Die Düsennadel ist derart ausgeführt, dass im Bereich der Ventildichtfläche über den Umfang verteilt eine Vielzahl von Vertiefungen eingeformt sind.From the DE 102 40 827 A1 is already a fuel injector for an internal combustion engine, in particular of a motor vehicle, known which has a nozzle body and a nozzle body in the axially movable nozzle needle which engages with a nozzle needle tip in a blind hole of the nozzle body, wherein the nozzle needle tip and the blind hole are formed such that the nozzle needle is guided in the blind hole. The nozzle needle is designed such that in the region of the valve sealing surface distributed over the circumference a plurality of depressions are formed.

Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Anspruchs 1 hat den Vorteil, dass in einfach herstellbarer Weise eine verbesserte Anströmung von Abspritzöffnungen erzielt und als Resultat eine Streuungsreduzierung gegenüber bekannten Lösungen, bei denen die Anzahl der Abspritzöffnungen nicht mit der Anzahl von Anströmpfaden stromaufwärts des Ventilsitzes übereinstimmt, bei den Strahl- und Durchflusskenngrößen erreicht wird.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that achieved in a simple manner producible improved flow of spray orifices and as a result, a reduction in dispersion over known solutions in which the number of injection ports does not match the number of Anströmpfaden upstream of the valve seat , is achieved in the jet and flow characteristics.

Die Anströmung der Abspritzöffnungen wird vor allen Dingen vergleichmäßigt und über einen Zeitverlauf stabiler. Durchflussschwankungen in den Abspritzöffnungen können reduziert werden, wodurch das Gesamtstrahlbild einen ruhigeren Eindruck hinterlässt. In der Folge wird eine sauberere und bessere Verbrennung des Brennstoffs im Brennraum erzielt. Verbrennungsaussetzer, die im Extremfall bei bestimmten Strahlbildern bzw. Auslegungen der Abspritzöffnungen bei bekannten Lösungen auftreten könnten, können erfindungsgemäß hier ausgeschlossen werden. In vorteilhafter Weise eignet sich die erfindungsgemäße Ausbildung des Brennstoffeinspritzventils auch für strahlgeführte Brennverfahren.The flow of the spray orifices is, above all things, evened out and more stable over time. Flow fluctuations in the spray orifices can be reduced, leaving the overall spray pattern a quieter impression. As a result, a cleaner and better combustion of the fuel in the combustion chamber is achieved. Combustion misfires, which could occur in the case of certain jet patterns or interpretations of the injection orifices in known cases in extreme cases, can be excluded according to the invention here. Advantageously, the inventive design of the fuel injector is also suitable for spray-guided combustion.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous refinements and improvements of the claim 1 fuel injector are possible.

Besonders vorteilhaft ist es, wenn sich wenigstens zwei Durchströmbereiche stromaufwärts des Ventilsitzes in Größe, wie umfängliche Breite und/oder radiale Tiefe, und/oder Kontur unterscheiden. In Abhängigkeit der Anzahl der Abspritzöffnungen sind die Durchströmbereiche in ihrer Breite und Tiefe vorteilhafterweise so verändert, dass breitere und zugleich tiefere oder einerseits breitere sowie andererseits tiefere Durchströmbereiche so ausgelegt sind, dass sie sicher und zuverlässig den Mengenbedarf für zwei Abspritzöffnungen abdecken, während die schmaleren und zugleich eine geringe Tiefe aufweisenden oder einerseits schmaleren sowie andererseits flachen Durchströmbereiche so verkleinert sind, dass eine ausreichende Brennstoffmenge für genau eine Abspritzöffnung bereitgestellt wird.It is particularly advantageous if at least two flow-through regions upstream of the valve seat differ in size, such as circumferential width and / or radial depth, and / or contour. Depending on the number of spray-discharge openings, the flow-through areas are advantageously changed in width and depth so that wider and at the same time deeper or on the other hand deeper flow-through areas are designed so that they reliably and reliably cover the quantity required for two spray openings, while the narrower and at the same time having a low depth or on the one hand narrower and on the other hand flat flow areas are reduced so that a sufficient amount of fuel for exactly one spray opening is provided.

Zeichnungdrawing

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

Figur 1
ein teilweise dargestelltes Brennstoffeinspritzventil in einer bekannten Ausführung,
Figur 2
das abspritzseitige Ende II des Brennstoffeinspritzventils gemäß Figur 1 mit einer Vielzahl von Durchströmbereichen in einem Düsenkörper in einer vergrößerten Ansicht,
Figur 3
eine Schnittdarstellung entlang der Linie III-III des in Figur 2 gezeigten bekannten Düsenkörpers,
Figur 4
ein erstes Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils im Bereich seines Düsenkörpers in einer Darstellung analog zur Figur 3,
Figur 5
ein zweites Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils im Bereich seines Düsenkörpers in einer Darstellung analog zur Figur 3 und
Figur 6
ein drittes Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils im Bereich seines Düsenkörpers in einer Darstellung analog zur Figur 3.
Embodiments of the invention are shown in simplified form in the drawing and explained in more detail in the following description. Show it
FIG. 1
a partially illustrated fuel injection valve in a known embodiment,
FIG. 2
the discharge-side end II of the fuel injection valve according to FIG. 1 with a plurality of flow areas in a nozzle body in an enlarged view,
FIG. 3
a sectional view taken along the line III-III of in FIG. 2 shown known nozzle body,
FIG. 4
a first embodiment of a fuel injection valve according to the invention in the region of its nozzle body in a representation analogous to FIG. 3 .
FIG. 5
A second embodiment of a fuel injection valve according to the invention in the region of its nozzle body in a representation analogous to FIG. 3 and
FIG. 6
A third embodiment of a fuel injection valve according to the invention in the region of its nozzle body in a representation analogous to FIG. 3 ,

Beschreibung der AusführungsbeispieleDescription of the embodiments

Anhand der Figur 1 wird ein bekanntes Brennstoffeinspritzventil in seinem grundsätzlichen Aufbau kurz beschrieben. In der Figur 1 ist als ein Ausführungsbeispiel ein Ventil in der Form eines Einspritzventils 1 für Brennstoffeinspritzanlagen von gemischverdichtenden fremdgezündeten Brennkraftmaschinen in einer Seitenansicht dargestellt. Mit einem stromabwärtigen Ende 17 ist das Brennstoffeinspritzventil 1, das in Form eines direkt einspritzenden Einspritzventils zum direkten Einspritzen von Brennstoff in einen Brennraum 25 der Brennkraftmaschine ausgeführt ist, in eine Aufnahmebohrung 20 eines Zylinderkopfes 9 eingebaut. Das abspritzseitige Ende 17 des Brennstoffeinspritzventils 1 gemäß Figur 1, das mit II gekennzeichnet ist, ist in der Figur 2 in einer vergrößerten Ansicht dargestellt, da es den erfindungswesentlichen Teil des Brennstoffeinspritzventils 1 charakterisiert. Ein Dichtring 2, insbesondere aus Teflon ®, sorgt für eine optimale Abdichtung des Brennstoffeinspritzventils 1 gegenüber der Wandung der Aufnahmebohrung 20 des Zylinderkopfes 9.Based on FIG. 1 a known fuel injection valve will be briefly described in its basic structure. In the FIG. 1 is shown as an embodiment, a valve in the form of an injection valve 1 for fuel injection systems of mixture-compression spark-ignited internal combustion engines in a side view. With a downstream end 17, the fuel injection valve 1, which is designed in the form of a direct-injection injector for injecting fuel directly into a combustion chamber 25 of the internal combustion engine, is installed in a receiving bore 20 of a cylinder head 9. The discharge end 17 of the fuel injection valve 1 according to FIG. 1 , which is marked with II, is in the FIG. 2 shown in an enlarged view, since it characterizes the invention essential part of the fuel injection valve 1. A sealing ring 2, in particular of Teflon®, ensures optimum sealing of the fuel injection valve 1 with respect to the wall of the receiving bore 20 of the cylinder head 9.

Zwischen einem Absatz 21 eines Ventilgehäuses 22, dessen stromabwärtiges Ende als Düsenkörper 18 ausgeführt ist, oder einer unteren Stirnseite 21 eines Abstützelements 19 und einer z.B. rechtwinklig zur Längserstreckung der Aufnahmebohrung 20 verlaufenden Schulter 23 der Aufnahmebohrung 20 ist ein flaches Zwischenelement 24 eingelegt, das in Form einer Unterlegscheibe ausgeführt ist.Between a shoulder 21 of a valve housing 22, whose downstream end is designed as a nozzle body 18, or a lower end face 21 of a support element 19 and a e.g. perpendicular to the longitudinal extent of the receiving bore 20 extending shoulder 23 of the receiving bore 20, a flat intermediate element 24 is inserted, which is designed in the form of a washer.

Das Brennstoffeinspritzventil 1 weist an seinem zulaufseitigen Ende 3 eine Steckverbindung zu einer Brennstoffverteilerleitung (Fuel Rail) 4 auf, die durch einen Dichtring 5 zwischen einem Anschlussstutzen 6 der Brennstoffverteilerleitung 4, der im Schnitt dargestellt ist, und einem Zulaufstutzen 7 des Brennstoffeinspritzventils 1 abgedichtet ist. Das Brennstoffeinspritzventil 1 ist in eine Aufnahmeöffnung 12 des Anschlussstutzens 6 der Brennstoffverteilerleitung 4 eingeschoben. Der Anschlussstutzen 6 geht dabei z.B. einteilig aus der eigentlichen Brennstoffverteilerleitung 4 hervor und besitzt stromaufwärts der Aufnahmeöffnung 12 eine durchmesserkleinere Strömungsöffnung 15, über die die Anströmung des Brennstoffeinspritzventils 1 erfolgt. Das Brennstoffeinspritzventil 1 verfügt über einen elektrischen Anschlussstecker 8 für die elektrische Kontaktierung zur Betätigung des Brennstoffeinspritzventils 1.The fuel injection valve 1 has at its inlet-side end 3 a plug connection to a fuel distributor line (fuel rail) 4, which is sealed by a sealing ring 5 between a connection piece 6 of the fuel distributor line 4, which is shown in section, and an inlet connection 7 of the fuel injection valve 1. The fuel injection valve 1 is inserted into a receiving opening 12 of the connection piece 6 of the fuel distribution line 4. The connecting piece 6 is in this case e.g. in one piece from the actual fuel distributor line 4 and has upstream of the receiving opening 12 a smaller diameter flow opening 15 through which the flow of the fuel injection valve 1 takes place. The fuel injection valve 1 has an electrical connection plug 8 for the electrical contacting for actuating the fuel injection valve 1.

Um das Brennstoffeinspritzventil 1 und die Brennstoffverteilerleitung 4 weitgehend radialkraftfrei voneinander zu beabstanden und das Brennstoffeinspritzventil 1 sicher in der Aufnahmebohrung des Zylinderkopfes niederzuhalten, ist ein Niederhalter 10 zwischen dem Brennstoffeinspritzventil 1 und dem Anschlussstutzen 6 vorgesehen. Der Niederhalter 10 ist als bügelförmiges Bauteil ausgeführt, z.B. als Stanz-Biege-Teil. Der Niederhalter 10 weist ein teilringförmiges Grundelement 11 auf, von dem aus abgebogen ein Niederhaltebügel 13 verläuft, der an einer stromabwärtigen Endfläche 14 des Anschlussstutzens 6 an der Brennstoffverteilerleitung 4 im eingebauten Zustand anliegt.In order to space the fuel injection valve 1 and the fuel distributor line 4 substantially free of radial force from one another and to hold down the fuel injection valve 1 securely in the receiving bore of the cylinder head, a holding-down device 10 is provided between the fuel injection valve 1 and the connecting piece 6. The hold-down 10 is as a bow-shaped component executed, eg as a punching-bending part. The hold-down device 10 has a part-ring-shaped base element 11, from which a hold-down bar 13 extends, which abuts against a downstream end face 14 of the connecting piece 6 on the fuel distributor line 4 in the installed state.

In der Figur 2 ist das abspritzseitige Ende 17 des Brennstoffeinspritzventils 1 gemäß Figur 1 mit einer Vielzahl von Durchströmbereichen 26 in dem Düsenkörper 18 in einer vergrößerten Ansicht dargestellt. Das Brennstoffeinspritzventil 1 weist wenigstens einen (nicht dargestellten) erregbaren Aktuator, wie z.B. einen elektromagnetischen Kreis, einen piezoelektrischen oder magnetostriktiven Aktor, sowie ein entlang einer Ventillängsachse 27 bewegbares Ventilelement auf. Das nicht dargestellte Ventilelement (Ventilnadel, Ventilschließkörper) wirkt dichtend mit einem Ventilsitz 28 zusammen, der beispielsweise am stromabwärtigen Ende einer Sacklochbohrung 29 im Düsenkörper 18 selbst ausgebildet ist. Stromaufwärts des Ventilsitzes 28 sind in der Wandung der Sacklochbohrung 29 des Düsenkörpers 18 umfangsmäßig mehrere Durchströmbereiche 26 ausgebildet. Diese Durchströmbereiche 26 sind in der Form von Durchflusstaschen ausgeformt, die dem Brennstoff bei eingebautem Ventilelement ein ungehindertes Anströmen bis zum Ventilsitz 28 erlauben. Mit dem Bezugszeichen 18 soll insbesondere auch ein an einem Düsenkörper befestigter Ventilsitzkörper, wie er z.B. in Figur 2 der DE 10 2006 049 253 A1 gezeigt ist, gemeint sein.In the FIG. 2 is the discharge-side end 17 of the fuel injection valve 1 according to FIG. 1 is shown with a plurality of Durchströmbereichen 26 in the nozzle body 18 in an enlarged view. The fuel injection valve 1 has at least one excitable actuator (not shown), such as an electromagnetic circuit, a piezoelectric or magnetostrictive actuator, and a valve element movable along a valve longitudinal axis 27. The valve element, not shown (valve needle, valve closing body) cooperates sealingly with a valve seat 28 which is formed, for example, at the downstream end of a blind hole 29 in the nozzle body 18 itself. Upstream of the valve seat 28, a plurality of through-flow regions 26 are formed in the wall of the blind bore 29 of the nozzle body 18. These flow-through regions 26 are formed in the form of flow-through pockets which allow the fuel to flow unimpeded to the valve seat 28 when the valve element is installed. By the reference numeral 18 is intended in particular a fixed to a nozzle body valve seat body, as in eg FIG. 2 the DE 10 2006 049 253 A1 is meant to be meant.

Figur 3 zeigt eine Schnittdarstellung entlang der Linie III-III des in Figur 2 gezeigten bekannten Düsenkörpers 18. Aus dieser Ansicht wird deutlich, dass die Durchströmbereiche 26 längsnutähnliche Durchflusstaschen bilden, die voneinander beabstandet sind. Zwischen den Durchströmbereichen 26 liegt dabei jeweils ein Führungsbereich 30 für das axial bewegliche Ventilelement. In einer bekannten Ausführung sind z.B. fünf Durchströmbereiche 26 in dem Düsenkörper 18 vorgesehen. Stromabwärts des Ventilsitzes 28 sind in einem Bodenabschnitt 31 des Düsenkörpers 18 oder in einer alternativen Spritzlochscheibe, die am Düsenkörper 18 befestigbar ist, mehrere Abspritzöffnungen 32 ausgebildet, durch die der Brennstoff fein zerstäubt in den Brennraum 25 abgegeben wird. Die Abspritzöffnungen 32 sind beispielsweise derart ausgerichtet, dass sie schräg geneigt nach radial außen über die Dicke des Bodenabschnitts 31 bzw. der Spritzlochscheibe verlaufen. FIG. 3 shows a sectional view taken along the line III-III of in FIG. 2 From this view, it is clear that the Durchströmbereiche 26 form längsnutähnliche flow pockets, which are spaced from each other. In each case, a guide region 30 for the axially movable valve element lies between the flow-through regions 26. In a known embodiment, for example, five flow areas 26 are provided in the nozzle body 18. Downstream of the valve seat 28 are in a bottom portion 31 of the nozzle body 18 or in an alternative spray perforated disk, which is fastened to the nozzle body 18, a plurality of ejection openings 32 is formed by the fuel atomized finely atomized into the combustion chamber 25 is discharged. The spray-discharge openings 32 are, for example, oriented in such a way that they extend obliquely inclined radially outward beyond the thickness of the bottom section 31 or the spray-perforated pane.

Üblicherweise weicht bei sogenannten Mehrlochventilen die Anzahl der Abspritzöffnungen 32 von der Anzahl der Durchströmbereiche 26 im Düsenkörper 18 ab. Im in der Figur 3 gezeigten bekannten Beispiel sind fünf Durchströmbereiche 26 vorgesehen, während stromabwärts des Ventilsitzes 28 sieben Abspritzöffnungen 32 folgen. Die Durchströmbereiche 26 befinden sich damit in einem regelmäßigen mittleren Abstand von 72° zueinander und sind mit gleicher umfänglicher Breite und radialer Tiefe im Düsenkörper 18 eingearbeitet. Aufgrund der unterschiedlichen Anzahl von Durchströmbereichen 26 und Abspritzöffnungen 32 ergeben sich abhängig von der Ventilauslegung Instabilitäten in der Anströmung der Abspritzöffnungen 32. Dies kann in nachteiliger Weise letztlich zu einer großen Streuung der Strahl- und Durchflusskenngrößen führen. Durch die nicht eindeutige und zeitlich nicht unbedingt stabile Mengenzuordnung kann es zudem zu einem unruhigen "flatternden" Strahlbild kommen.Usually deviates in so-called multi-hole valves, the number of spray openings 32 from the number of Durchströmbereiche 26 in the nozzle body 18 from. I'm in the FIG. 3 shown in the known example five Durchströmbereiche 26 are provided, while downstream of the valve seat 28 follow seven spray openings 32. The Durchströmbereiche 26 are thus at a regular average distance of 72 ° to each other and are incorporated with the same circumferential width and radial depth in the nozzle body 18. Due to the different number of Durchströmbereichen 26 and spray openings 32 arise depending on the valve design instabilities in the flow of the spray openings 32. This can ultimately lead to a large divergence of the jet and flow characteristics disadvantageously. Due to the ambiguous and temporally not necessarily stable quantity allocation, it can also lead to a restless "fluttering" spray pattern.

In der Figur 4 ist ein erstes Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils 1 im Bereich seines Düsenkörpers 18 in einer Darstellung analog zur Figur 3 dargestellt. In dieser Ausführung unterscheiden sich wenigstens zwei Durchströmbereiche 26 in ihrer umfänglichen Breite. In Abhängigkeit der Anzahl der Abspritzöffnungen 32 sind die Durchströmbereiche 26 in ihrer Breite nun so verändert, dass z.B. breitere Durchströmbereiche 26 so ausgelegt sind, dass sie sicher und zuverlässig den Mengenbedarf für zwei Abspritzöffnungen 32 abdecken, während die schmaleren Durchströmbereiche 26 so verkleinert gegenüber der bekannten Lösung gemäß Figur 3 sind, dass eine ausreichende Brennstoffmenge für genau eine Abspritzöffnung 32 bereitgestellt wird. Auf diese Weise wird eine gleichmäßige und zeitlich stabile Anströmung der Abspritzöffnungen 32 gewährleistet und somit eine Streuungsreduzierung bei den Strahl- und Durchflusskenngrößen erzielt. Für die Dauerlaufstabilität ist es jedoch wichtig, dass die Breiten der Führungsflächen der Führungsbereiche 30 hinreichend groß ausgebildet bleiben.In the FIG. 4 is a first embodiment of a fuel injection valve 1 according to the invention in the region of its nozzle body 18 in a representation analogous to FIG. 3 shown. In this embodiment, at least two flow areas 26 differ in their circumferential width. Depending on the number of ejection openings 32, the flow-through regions 26 are now changed in width so that, for example, wider flow-through regions 26 are designed so that they safely and reliably cover the quantity required for two spray-discharge openings 32, while the narrow flow-through regions 26 are reduced in size compared with the known ones Solution according to FIG. 3 are that a sufficient amount of fuel for exactly one ejection opening 32 is provided. In this way, a uniform and temporally stable flow of the ejection openings 32 is ensured, thus achieving a reduction in the scattering of jet and flow characteristics. However, for the endurance stability, it is important that the widths of the guide surfaces of the guide portions 30 remain sufficiently large.

In der Figur 5 ist ein zweites Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils 1 im Bereich seines Düsenkörpers 18 in einer Darstellung analog zur Figur 3 dargestellt. In dieser Ausführung unterscheiden sich wenigstens zwei Durchströmbereiche 26 in ihrer radialen Tiefe. In Abhängigkeit der Anzahl der Abspritzöffnungen 32 sind die Durchströmbereiche 26 in ihrer Tiefe nun so verändert, dass z.B. tiefere Durchströmbereiche 26 so ausgelegt sind, dass sie sicher und zuverlässig den Mengenbedarf für zwei Abspritzöffnungen 32 abdecken, während die eine geringe Tiefe aufweisenden Durchströmbereiche 26 so verkleinert gegenüber der bekannten Lösung gemäß Figur 3 sind, dass eine ausreichende Brennstoffmenge für genau eine Abspritzöffnung 32 bereitgestellt wird. Auf diese Weise wird eine gleichmäßige und zeitlich stabile Anströmung der Abspritzöffnungen 32 gewährleistet und somit eine Streuungsreduzierung bei den Strahl- und Durchflusskenngrößen erzielt. Die maximale Tiefe der Durchströmbereiche 26 wird dabei jedoch u.a. von der Druckfestigkeit des Düsenkörpers 18 an seinem stromabwärtigen Ende 17 bestimmt.In the FIG. 5 is a second embodiment of a fuel injection valve 1 according to the invention in the region of its nozzle body 18 in a representation analogous to FIG. 3 shown. In this embodiment, at least two flow areas 26 differ in their radial depth. Depending on the number of spray-discharge orifices 32, the flow-through regions 26 are now changed in their depth so that, for example, deeper flow-through regions 26 are designed such that they reliably and reliably cover the quantity required for two spray-discharge openings 32, while the flow-through regions 26 having a small depth thus become smaller compared to the known solution according to FIG. 3 are that a sufficient amount of fuel for exactly one ejection opening 32 is provided. In this way, a uniform and temporally stable flow of the ejection openings 32 is ensured, thus achieving a reduction in the scattering of jet and flow characteristics. However, the maximum depth of the Durchströmbereiche 26 is determined inter alia by the compressive strength of the nozzle body 18 at its downstream end 17.

In der Figur 6 ist ein drittes Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils 1 im Bereich seines Düsenkörpers 18 in einer Darstellung analog zur Figur 3 dargestellt. In dieser Ausführung unterscheiden sich wenigstens zwei Durchströmbereiche 26 in ihrer umfänglichen Breite und ihrer radialen Tiefe. Insofern stellt diese Variante eine Kombination der beiden zuvor beschriebenen Ausführungsbeispiele dar. In Abhängigkeit der Anzahl der Abspritzöffnungen 32 sind die Durchströmbereiche 26 in ihrer Breite und Tiefe nun so verändert, dass z.B. breitere und zugleich tiefere oder einerseits breitere sowie andererseits tiefere Durchströmbereiche 26 so ausgelegt sind, dass sie sicher und zuverlässig den Mengenbedarf für zwei Abspritzöffnungen 32 abdecken, während die schmaleren und zugleich eine geringe Tiefe aufweisenden oder einerseits schmaleren sowie andererseits flachen Durchströmbereiche 26 so verkleinert gegenüber der bekannten Lösung gemäß Figur 3 sind, dass eine ausreichende Brennstoffmenge für genau eine Abspritzöffnung 32 bereitgestellt wird. Auf diese Weise kann eine gleichmäßige und zeitlich stabile Anströmung der Abspritzöffnungen 32 optimiert erzeugt und somit eine Streuungsreduzierung bei den Strahl- und Durchflusskenngrößen erzielt werden.In the FIG. 6 is a third embodiment of a fuel injection valve 1 according to the invention in the region of its nozzle body 18 in a representation analogous to FIG. 3 shown. In this embodiment, at least two flow areas 26 differ in their circumferential width and their radial depth. In this respect, this variant represents a combination of the two embodiments described above. Depending on the number of spray openings 32, the flow areas 26 are now changed in width and depth so that, for example, wider and at the same time deeper or, on the one hand, wider and, on the other hand, lower flow-through areas 26 are designed in that they reliably and reliably cover the quantity required for two ejection openings 32, while the narrower and at the same time having a shallower depth or, on the one hand, narrow and, on the other hand, flat flow-through regions 26 are thus reduced in comparison with the known solution according to FIG FIG. 3 are that sufficient Amount of fuel for exactly one spray opening 32 is provided. In this way, a uniform and temporally stable flow of the ejection openings 32 can be optimized and thus a reduction in the scattering of the jet and flow characteristics can be achieved.

Alternativ kann auch eine asymmetrische Verteilung der Durchströmbereiche 26 über den Umfang erzeugt werden, so dass damit eine gleichmäßige Verteilung der Durchströmbereiche 26 aufgegeben ist, wobei die Geometrie und die Abmessungen der Durchströmbereiche 26 gleich bleiben, die Breiten der Führungsflächen der Führungsbereiche 30 jedoch variieren.Alternatively, an asymmetrical distribution of the flow-through regions 26 can be generated over the circumference, so that a uniform distribution of the Durchströmbereiche 26 is abandoned, the geometry and the dimensions of the Durchströmbereiche 26 remain the same, the widths of the guide surfaces of the guide portions 30, however, vary.

Claims (5)

  1. Fuel injection valve (1) for fuel injection systems of internal combustion engines, in particular for the direct injection of fuel into a combustion chamber, wherein the fuel injection valve (1) has at least one excitable actuator and a valve element which is movable along a valve longitudinal axis (27) and which interacts sealingly with a valve seat (28), and having a nozzle body (18) at the ejection-side end (17) of the fuel injection valve (1), wherein multiple throughflow regions (26) are provided circumferentially upstream of the valve seat (28), between which throughflow regions there are situated in each case guide regions (30) for the valve element, and having ejection openings (32) downstream of the valve seat (28), the number of which differs from the number of throughflow regions (26),
    wherein at least two throughflow regions (26) differ in size, such as circumferential width and/or radial depth,
    and/or contour,
    characterized
    in that the throughflow regions (26) are formed circumferentially, in the form of throughflow pockets, on the wall of a blind bore (29) of the nozzle body (18), and the throughflow pockets run in the manner of longitudinal grooves and so as to be spaced apart from one another.
  2. Fuel injection valve according to Claim 1,
    characterized
    in that the number of ejection openings (32) is greater than the number of throughflow regions (26).
  3. Fuel injection valve according to Claim 2,
    characterized
    in that five throughflow regions (26) and more than five ejection openings (32) are provided.
  4. Fuel injection valve according to one of the preceding claims,
    characterized
    in that the ejection openings (32) are formed in a base section (31) of the nozzle body (18) or in a separate spray hole disc which is fastenable to the nozzle body (18) .
  5. Fuel injection valve according to one of the preceding claims,
    characterized
    in that the ejection openings (32) are oriented so as to run radially outward in an obliquely inclined manner.
EP10787447.1A 2010-01-08 2010-12-06 Fuel injection valve Active EP2521853B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010000754A DE102010000754A1 (en) 2010-01-08 2010-01-08 Fuel injector
PCT/EP2010/068957 WO2011082916A1 (en) 2010-01-08 2010-12-06 Fuel injection valve

Publications (2)

Publication Number Publication Date
EP2521853A1 EP2521853A1 (en) 2012-11-14
EP2521853B1 true EP2521853B1 (en) 2019-02-20

Family

ID=43570911

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10787447.1A Active EP2521853B1 (en) 2010-01-08 2010-12-06 Fuel injection valve

Country Status (8)

Country Link
US (1) US9133803B2 (en)
EP (1) EP2521853B1 (en)
JP (1) JP5808340B2 (en)
KR (1) KR101815841B1 (en)
CN (1) CN102713245B (en)
BR (1) BR112012016282A2 (en)
DE (1) DE102010000754A1 (en)
WO (1) WO2011082916A1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014101308B4 (en) 2014-02-03 2022-01-27 Stoba Holding Gmbh & Co. Kg Fuel injector, fuel injector, tool for manufacturing a fuel injector and method for manufacturing a fuel injector
DE102015226769A1 (en) * 2015-12-29 2017-06-29 Robert Bosch Gmbh Fuel injector
GB2553838B (en) * 2016-09-16 2020-01-29 Perkins Engines Co Ltd Fuel injector and piston bowl
DE102017205483A1 (en) * 2017-03-31 2018-10-04 Robert Bosch Gmbh Valve sleeve of an injector and manufacturing method therefor
DE102017219866A1 (en) 2017-11-08 2019-05-09 Robert Bosch Gmbh Suspension for injection systems, in particular fuel injection systems, with a fluid-carrying component and a metering valve and injection system
DE102018216970A1 (en) * 2018-10-04 2020-04-09 Robert Bosch Gmbh Fuel injector
US20230064203A1 (en) * 2021-08-25 2023-03-02 Caterpillar Inc. Fuel injector having controlled nozzle tip protrusion in cylinder head and cylinder head assembly with same

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002025101A1 (en) * 2000-09-19 2002-03-28 Robert Bosch Gmbh Method for producing a valve seat body of a fuel injection valve
DE10240827A1 (en) * 2002-09-04 2004-03-18 Robert Bosch Gmbh Fuel injection valve for IC engine has recesses in the tapering head of the flow control needle t provide a cushioning effect when closing off the fuel flow

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4408722A (en) * 1981-05-29 1983-10-11 General Motors Corporation Fuel injection nozzle with grooved poppet valve
DE3911910A1 (en) * 1989-04-12 1990-10-18 Bosch Gmbh Robert IC engine fuel injection nozzle - has needle guided in nozzle housing incorporating two or more longitudinal grooves in its bore
JP2726705B2 (en) 1989-07-12 1998-03-11 三井東圧化学株式会社 Method for producing polyamide solution
DE4025945C2 (en) * 1990-08-16 1998-10-08 Bosch Gmbh Robert Method of adjusting a fuel injector and fuel injector
JP3134813B2 (en) * 1997-06-20 2001-02-13 トヨタ自動車株式会社 Fuel injection valve for internal combustion engine
JP2000274328A (en) * 1999-03-25 2000-10-03 Hitachi Ltd Fuel injection valve for cylinder injection
JP3915347B2 (en) * 1999-11-05 2007-05-16 株式会社日立製作所 Fuel injection valve
DE10055483B4 (en) * 2000-11-09 2007-11-29 Robert Bosch Gmbh Fuel injector
JP2006214292A (en) * 2005-02-01 2006-08-17 Hitachi Ltd Fuel injection valve
US7828232B2 (en) * 2005-04-18 2010-11-09 Denso Corporation Injection valve having nozzle hole
DE102006049253A1 (en) 2006-10-19 2008-04-30 Robert Bosch Gmbh Fuel injection valve for mixture-compressed, foreign-ignited internal-combustion engine, involves pressing needle against seat surface in unexcited condition of magnetic coil, and forming shoulder as stop for reset spring at inner pole
DE102007026122A1 (en) * 2007-06-05 2008-12-11 Volkswagen Ag Fuel injection nozzle for internal combustion engine of motor vehicle, has body, injection opening arranged in body and needle attached with sealing surface at inner wall of body, in order to close nozzle
US20090255998A1 (en) * 2008-04-10 2009-10-15 Sudhakar Das Fuel injection tip

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002025101A1 (en) * 2000-09-19 2002-03-28 Robert Bosch Gmbh Method for producing a valve seat body of a fuel injection valve
DE10240827A1 (en) * 2002-09-04 2004-03-18 Robert Bosch Gmbh Fuel injection valve for IC engine has recesses in the tapering head of the flow control needle t provide a cushioning effect when closing off the fuel flow

Also Published As

Publication number Publication date
CN102713245B (en) 2019-08-27
DE102010000754A1 (en) 2011-07-14
US20130062441A1 (en) 2013-03-14
WO2011082916A1 (en) 2011-07-14
BR112012016282A2 (en) 2017-03-07
KR20120101528A (en) 2012-09-13
EP2521853A1 (en) 2012-11-14
US9133803B2 (en) 2015-09-15
JP2013516569A (en) 2013-05-13
KR101815841B1 (en) 2018-01-08
JP5808340B2 (en) 2015-11-10
CN102713245A (en) 2012-10-03

Similar Documents

Publication Publication Date Title
EP2521853B1 (en) Fuel injection valve
DE3841142C2 (en) Injector
EP1379773B1 (en) Fuel injection valve
EP1599669B1 (en) Fuel injection valve
EP2087228B1 (en) Fuel injection valve
EP1076772A1 (en) Fuel injection nozzle for an internal combustion engine
DE102010064268A1 (en) Injector
WO2003031806A1 (en) Fuel injection valve
DE102006041475A1 (en) Fuel injector
EP1402175B1 (en) Fuel injection valve
DE102013209272A1 (en) Valve for metering fluid
EP1312796B1 (en) Fuel injection valve
DE102009041028A1 (en) Nozzle assembly for injection valve, has nozzle body, in which nozzle body cutout and injection opening are disposed, where nozzle body cutout is hydraulically coupled to high-pressure circuit of fluid
DE102017218224A1 (en) Valve for metering a fluid, in particular fuel injection valve
DE10050751A1 (en) Fuel injection valve for IC engines has swirl-generating device formed by swirl channels in upstream side of valve seat body
EP1702156B1 (en) Fuel injection valve
EP1481159B1 (en) Fuel injection valve
DE102004044820A1 (en) Fuel injection valve for direct injection of fuel into combustion chamber of internal combustion engine, has nozzle body with castellated structure around its periphery
DE10354467A1 (en) Fuel injector
DE60320235T2 (en) Injection nozzle with improved injection and method for its production
EP1598550B1 (en) Fuel injector
DE102012221713A1 (en) Injector
DE102010063307A1 (en) Valve i.e. injection valve, for injecting e.g. fuel into fuel injection system of internal combustion engine, has inflow channel with output directly lying at hole inlet, where channel comprises smaller cross-section against spray hole
EP3397851A1 (en) Fuel injection valve
DE102018221833A1 (en) Valve for metering a fluid, in particular a 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: 20120808

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
17Q First examination report despatched

Effective date: 20160406

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20180718

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502010015798

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1098514

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190315

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

Ref country code: NL

Ref legal event code: MP

Effective date: 20190220

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

Ref country code: FI

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

Effective date: 20190220

Ref country code: SE

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

Effective date: 20190220

Ref country code: LT

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

Effective date: 20190220

Ref country code: NO

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

Effective date: 20190520

Ref country code: PT

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

Effective date: 20190620

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

Ref country code: NL

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

Effective date: 20190220

Ref country code: RS

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

Effective date: 20190220

Ref country code: LV

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

Effective date: 20190220

Ref country code: IS

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

Effective date: 20190620

Ref country code: HR

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

Effective date: 20190220

Ref country code: GR

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

Effective date: 20190521

Ref country code: BG

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

Effective date: 20190520

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

Ref country code: EE

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

Effective date: 20190220

Ref country code: RO

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

Effective date: 20190220

Ref country code: CZ

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

Effective date: 20190220

Ref country code: ES

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

Effective date: 20190220

Ref country code: AL

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

Effective date: 20190220

Ref country code: DK

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

Effective date: 20190220

Ref country code: SK

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

Effective date: 20190220

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502010015798

Country of ref document: DE

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

Ref country code: PL

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

Effective date: 20190220

Ref country code: SM

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

Effective date: 20190220

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: 20191121

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

Ref country code: SI

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

Effective date: 20190220

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

Ref country code: TR

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

Effective date: 20190220

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20191231

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

Ref country code: MC

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

Effective date: 20190220

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

Effective date: 20191206

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: 20191206

Ref country code: LU

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

Effective date: 20191206

Ref country code: FR

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

Effective date: 20191231

Ref country code: IE

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

Effective date: 20191206

Ref country code: GB

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

Effective date: 20191206

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

Ref country code: BE

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

Effective date: 20191231

Ref country code: CH

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

Effective date: 20191231

Ref country code: LI

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

Effective date: 20191231

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1098514

Country of ref document: AT

Kind code of ref document: T

Effective date: 20191206

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

Ref country code: AT

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

Effective date: 20191206

Ref country code: CY

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

Effective date: 20190220

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

Ref country code: HU

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

Effective date: 20101206

Ref country code: MT

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

Effective date: 20190220

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

Ref country code: MK

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

Effective date: 20190220

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

Ref country code: DE

Payment date: 20240227

Year of fee payment: 14