EP1129287B1 - Injection nozzle for an internal combustion engine with annular groove in said nozzle needle - Google Patents

Injection nozzle for an internal combustion engine with annular groove in said nozzle needle Download PDF

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Publication number
EP1129287B1
EP1129287B1 EP00965779A EP00965779A EP1129287B1 EP 1129287 B1 EP1129287 B1 EP 1129287B1 EP 00965779 A EP00965779 A EP 00965779A EP 00965779 A EP00965779 A EP 00965779A EP 1129287 B1 EP1129287 B1 EP 1129287B1
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EP
European Patent Office
Prior art keywords
nozzle needle
nozzle
injection nozzle
annular groove
injection
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Expired - Lifetime
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EP00965779A
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German (de)
French (fr)
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EP1129287A1 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • 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
    • F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal

Definitions

  • the invention is based on an injection nozzle for internal combustion engines according to the preambles of the independent patent claim 1 and 10.
  • an injection nozzle is known in which both the tip of the nozzle needle and the nozzle needle seat is composed of a plurality of frustoconical sections.
  • an annular groove is provided both in the nozzle needle seat and at the transition between two frusto-conical sections.
  • an injection nozzle is known in the both the tip of the nozzle needle and the nozzle needle seat composed of a plurality of frusto-conical sections.
  • the frusto-conical sections of the nozzle needle act and nozzle needle seat in such a way that to change the Flow resistance of the injector a relatively large stroke the nozzle needle is required.
  • From production engineering Reasons can be between two frustoconical sections of the Nozzle needle be provided an undercut.
  • a seat hole injector is known whose nozzle nozzle tip consists of several frustoconical Sections is composed. At the border of two such Sections an annular groove is provided in the nozzle needle.
  • Injectors of the generic type have because of complicated geometries of nozzle needle tip and nozzle needle seat especially in Generalhub Scheme the nozzle needle a large dispersion the flow resistance and thus also the injected Fuel quantity on. As a result, the emission and Consumption behavior of many of these injectors equipped internal combustion engines not optimal.
  • the invention is based on the object, an injection nozzle in which the dispersion of the injection quantity in Operahub Scheme the nozzle needle in different copies of a Injector of the same type is reduced and thus the Consumption and emission behavior of the inventive Injector equipped internal combustion engine is improved.
  • the cone angle of the nozzle needle seat 60 ° so that a good Sealing effect achieved between the nozzle needle and nozzle needle seat becomes.
  • the cone angle of the nozzle needle to a degree, preferably 15-30 minutes of arc, greater as the cone angle of the nozzle needle seat, so that the Reduced sealing area and in the area of the largest Diameter of the nozzle needle is laid.
  • the annular groove extends parallel to the base of the cone, so that over the entire Scope of the nozzle needle same flow conditions prevail.
  • An embodiment of the invention provides that the width the annular groove 0.1 mm to 0.3 mm, preferably 0.16 mm to 0.24 mm is so that over a sufficiently large Ambihub Scheme the annular groove decisive for the throttle effect of the injector is.
  • the ring groove must in any case be so large that only the The leading edge of the annular groove throttles for a short time.
  • the depth of the annular groove is 0.02 mm to 0.2 mm, preferably 0.08 mm to 0.14 mm, so that the volume of the ring groove is small and thus also the amount of fuel that is at turned off internal combustion engine evaporates, remains small.
  • the blind hole conical allowing the partial load behavior of conical blind hole injectors is improved.
  • the blind hole cylindrical perform so that also the partial load behavior of cylindrical Blind hole injectors is improved.
  • Another embodiment provides that the blind hole a Minisackloch or a micro-blind hole is, so that the invention Benefits are also available with these injectors.
  • The.ege mentioned task is seat hole injectors with the characterizing features of the independent claim 10, so that the advantages of the nozzle needle according to the invention also in seat-hole injection nozzles can be used.
  • seat hole injectors sometimes the problem arises that, due to Magomic centering of the nozzle needle with respect to the nozzle needle seat, the pressure applied to the spray holes distributed over the circumference fuel is not the same, resulting in unfavorable conditions the injection can lead. Through the ring groove can a Pressure equalization between the spray holes done, so that the insufficient centering of the nozzle needle does not adversely affect the Injection conditions affects.
  • the width of the Ring groove larger, preferably one and a half times larger than that Diameter of the or the injection holes, so that the Throttle effect of the injector over a sufficient large Operahub Scheme is influenced by the annular groove.
  • the depth of the annular groove is smaller than the width of the Ring groove is or that the depth of the annular groove 0.02 mm to 0.1 mm, preferably 0.04 mm to 0.07 mm, so that the Volume of the annular groove remains small and still one sufficient influence on the throttling effect of Injection nozzle is through the annular groove.
  • Figure 1 is an injection nozzle 1 with a conical Blind hole 2 shown.
  • the blind hole 2 can also be cylindrical or it may be a mini or Micro blind hole 2 act. In the latter case that is Volume of the blind hole 2 with respect to that in Figure 1 shown reduced type. This evaporates at shut off internal combustion engine less fuel in the Combustion chamber.
  • a spray hole 3 reaches the not shown Fuel from the blind hole 2 in the also not illustrated combustion chamber.
  • a frusto-conical nozzle needle seat 4 To the conical blind hole 2 joins a frusto-conical nozzle needle seat 4.
  • the nozzle needle seat 4 may have a cone angle of 60 °.
  • edge 7 which when grinding of the nozzle needle seat 4 is formed.
  • the edge 7 can be a sharp ridge or a smooth edge.
  • the flow resistance of the edge 7 is significantly influenced by the nature of the same.
  • Ring groove 8 reduces the influence of the edge 7 on the Flow resistance of the injection nozzle 1.
  • the distance of the Ring groove 8 of a bottom 9 of the injection nozzle 1 is about the same size as the distance from the bottom 9 of the Injector 1 and the edge 7. This will, regardless from the stroke of the nozzle needle 5, the throttle effect of Injector 1 not or at least not appreciably the geometry of the edge 7 influenced. This effect is based on that, because of compared to the annular gap between the nozzle needle seat 4 and the cone of the nozzle needle. 5 large hydraulic diameter of the annular gap between Ring groove 8 and edge 7, the flow resistance in the last mentioned annular gap is less than that of first mentioned annular gaps. Since both flow resistances in Are connected for the flow resistance of the series entire injector is essentially the smallest Single resistance decisive.
  • FIG. 2 is the hydraulic diameter 11 of a blind-hole injection nozzle 1 above the nozzle needle stroke 10 qualitatively applied.
  • the hydraulic diameter 11 is a size by means of which any flow-through cross-sections comparable in terms of their flow resistance be made.
  • the reference is the Flow resistance of a pipe with circular Cross-section. A cross section with large hydraulic Diameter has a low flow resistance and vice versa.
  • the nozzle needle stroke 10 has been divided into two areas assigned.
  • a first area extends from zero to "a”
  • the second, hereinafter referred to as Railhub Schemee Range extends from “a” to "b”.
  • At “c” is the full nozzle needle stroke reached.
  • characteristic curves 12 and 13 of an injection nozzle 1 are shown According to the prior art and a characteristic 14 of a blind hole injection nozzle 1 according to the invention shown. at the injection nozzle 1 according to the prior art has the Nozzle needle 5 no annular groove. Because of the above described strains in the geometry of the edge 7, also scatter the characteristics of different specimens identical construction injection nozzles 1, in particular in Partial stroke. This is due to the deviations of Characteristics 12 and 13 from each other in Fig. 2 illustrates.
  • the characteristic curve 14 represents an inventive Injection nozzle, especially in Generalhub Schl the Throttle effect of the edge 7 does not come to fruition, since the Fuel can escape into the annular groove 8.
  • the characteristics scatter 14 different Specimens of the same design according to the invention injectors 1, especially in sectionhub Schl much less, since the Geometry of the annular groove 8 with great repeatability can be made.
  • the characteristic 12 is a measured characteristic is, and that this characteristic 12 in the Control unit of the injection system is stored. Further is assumed that one of the series production taken Injector 1 has the characteristic curve 13. If now the Injector 1 with the characteristic curve 13 with a control unit interacts, in which the characteristic curve 12 is stored, then the actual injection quantity is correct Molhub Scheme the injection nozzle 1 with the curve 13th not with the optimum measured in the test specimens Injection amount according to the characteristic curve 12, so that the Performance and / or emission behavior of Internal combustion engine is deteriorated.
  • the injection nozzles 1 according to the invention scatter the Characteristics 14 only to a very small extent, so that at all equipped with injectors 1 according to the invention Internal combustion engines the correspondence between in the Control device stored characteristic 14 and the characteristics 14 of the built-in injectors 1 significantly improved becomes.
  • the match can be compared to the scatter in injection nozzles 1 according to the prior art, For example, be improved by a factor of 2 to 3.
  • the actual injected Fuel quantity exactly that specified by the controller Injection quantity and the consumption and emission behavior the internal combustion engine is optimal.
  • FIG. 3 an injection nozzle 1 according to the invention with as Seating holes trained spray holes 3 shown.
  • the Reference numerals correspond to those in FIG. 1 related.
  • the Ring groove 8 according to the invention is in seat hole injection nozzles arranged at the height of the spray holes 3, so that the Influence of the transition 15 between nozzle needle seat 4 and Spray holes 3 on the flow resistance of Injector is greatly reduced.
  • the distance of the annular groove 8 of the bottom 9 of the injection nozzle 1 is about the same size as the distance from the bottom 9 of the injection nozzle 1 and a piercing point 16 of the longitudinal axis of the injection hole. 3 and the nozzle needle seat 4. This will, regardless of the stroke the nozzle needle 5, the throttle effect of the injection nozzle. 1 not or at least not appreciably of the geometry of transition 15.
  • Fig. 4 the characteristic curve 12 of an injection nozzle 1 after the prior art and the characteristic 14 of a Seat hole injection nozzle 1 according to the invention shown.

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  • 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 einer Einspritzdüse für Brennkraftmaschinen nach dem Oberbegriffen der nebengeordneten Patentanspürche 1 und 10.
Aus der nachveröffentlichten WO99/58844 ist eine Einspritzdüse bekannt bei der sowohl die Spitze der Düsennadel als auch der Düsennadelsitz aus mehreren kegelstumpfförmigen Abschnitten zusammengesetzt ist. Dabei ist sowohl im Düsennadelsitz als auch an dem Übergang zwischen zwei kegelstumpfförmigen Abschnitten eine Ringnut vorgesehen.The invention is based on an injection nozzle for internal combustion engines according to the preambles of the independent patent claim 1 and 10.
From the post-published WO99 / 58844 an injection nozzle is known in which both the tip of the nozzle needle and the nozzle needle seat is composed of a plurality of frustoconical sections. In this case, an annular groove is provided both in the nozzle needle seat and at the transition between two frusto-conical sections.

Aus der EP 0 283 154 A1 ist eine Einspritzdüse bekannt bei der sowohl die Spitze der Düsennadel als auch der Düsennadelsitz aus mehreren kegelstumpfförmigen Abschnitten zusammengesetzt ist. Dabei wirken die kegelstumpfförmigen Abschnitte von Düsennadel und Düsennadelsitz dergestalt zusammen, dass zur Änderung des Strömungswiderstands der Einspritzdüse ein relativ großer Hub der Düsennadel erforderlich ist. Aus fertigungstechnischen Gründen kann zwischen zwei kegelstumpfförmigen Abschnitten der Düsennadel ein Freistich vorgesehen sein.From EP 0 283 154 A1 an injection nozzle is known in the both the tip of the nozzle needle and the nozzle needle seat composed of a plurality of frusto-conical sections. The frusto-conical sections of the nozzle needle act and nozzle needle seat in such a way that to change the Flow resistance of the injector a relatively large stroke the nozzle needle is required. From production engineering Reasons can be between two frustoconical sections of the Nozzle needle be provided an undercut.

Aus der US 5,890,660 ist eine Sitzloch-Einspritzdüse bekannt, deren Düsenndaelspitze aus mehreren kegelstumpfförmigen Abschnitten zusammengesetzt ist. An der Grenze zweier solcher Abschnitte ist eine Ringnut in der Düsennadel vorgesehen.From US 5,890,660 a seat hole injector is known whose nozzle nozzle tip consists of several frustoconical Sections is composed. At the border of two such Sections an annular groove is provided in the nozzle needle.

Einspritzdüsen der gattungsgemäßen Art weisen wegen der komplizierten Geometrien von Düsennadelspitze und Düsennadelsitz vor allem im Teilhubbereich der Düsennadel eine große Streuung des Strömungswiderstands und damit auch der eingespritzten Kraftstoffmenge auf. In Folge dessen ist das Emissions- und Verbrauchsverhalten vieler der mit diesen Einspritzdüsen ausgerüsteten Brennkraftmaschinen nicht optimal.Injectors of the generic type have because of complicated geometries of nozzle needle tip and nozzle needle seat especially in Teilhubbereich the nozzle needle a large dispersion the flow resistance and thus also the injected Fuel quantity on. As a result, the emission and Consumption behavior of many of these injectors equipped internal combustion engines not optimal.

Der Erfindung liegt die Aufgabe zugrunde, eine Einspritzdüse bereitzustellen, bei der die Streuung der Einspritzmenge im Teilhubbereich der Düsennadel bei verschiedenen Exemplaren einer Einspritzdüse gleicher Bauart verringert wird und somit das Verbrauchs- und Emissionsverhalten der mit der erfindungsgemäßen Einspritzdüse ausgerüsteten Brennkraftmaschinen verbessert wird.The invention is based on the object, an injection nozzle in which the dispersion of the injection quantity in Teilhubbereich the nozzle needle in different copies of a Injector of the same type is reduced and thus the Consumption and emission behavior of the inventive Injector equipped internal combustion engine is improved.

Diese Aufgabe wird gelöst durch eine Einspritzdüse für Brennkraftmaschinen mit den kennzeichnenden Merkmalen von Anspruch 1.This object is achieved by an injection nozzle for Internal combustion engines with the characterizing features of Claim 1.

Die Ringnut in dem dem Düsennadelsitz zugewandten Ende der Düsennadel ist im Teilhubbereich der Düsennadel maßgeblich für die Drosselwirkung der Einspritzdüse, da sie auf Höhe der Kante zwischen Düsennadelsitz und Sackloch angeordnet ist, so dass im Teilhubbereich der Düsennadel die Ringnut anstelle des Übergangs die Drosselwirkung der Einspritzdüse bestimmt. Da es möglich ist, Ringnuten mit großer wiederholgenauigkeit zu fertigen, und die Geometrie der erfindungsgemäßen Einspritzdüse sehr einfach ist, streut das Betriebsverhalten zwischen verschiedenen Exemplaren erfindungsgemäßer Einspritzdüsen gleicher Bauart nur noch in sehr geringem Umfang. Aus diesem Grund kann durch Messen des Betriebsverhaltens einer erfindungsgemäßen Einspritzdüse das Betriebsverhalten aller anderen bauartgleichen Einspritzdüsen mit wesentlich größerer Genauigkeit vorhergesagt werden und die Steuerung des Einspritzvorgangs entsprechend optimiert werden. Gleichzeitig werden die Herstellungskosten wegen der einfachen Geometrie gegenüber den aus dem Stand der Technik bekannten Einspritzdüsen deutlich reduziert.The annular groove in the nozzle needle seat facing the end of the Nozzle needle is in the Teilhubbereich the nozzle needle authoritative for the throttle effect of the injector, as it is at the level of the edge between nozzle needle seat and blind hole is arranged so that in Teilhubbereich the nozzle needle, the annular groove instead of the transition determines the throttle effect of the injector. As it is possible is to manufacture ring grooves with great repeatability, and the geometry of the injector according to the invention very simple is, the operating behavior scatters between different Exemplary injectors according to the invention of the same type only still to a very limited extent. For this reason, by measuring the operating behavior of an injection nozzle according to the invention Operating behavior of all other identical injection nozzles be predicted with much greater accuracy and the Control of the injection process can be optimized accordingly. At the same time, the manufacturing cost is because of the simple Geometry over those known from the prior art Injectors significantly reduced.

Bei einer Variante der erfindungsgemäßen Einspritzdüse beträgt der Kegelwinkel des Düsennadelsitzes 60°, so dass eine gute Dichtwirkung zwischen Düsennadel und Düsennadelsitz erzielt wird.In a variant of the injection nozzle according to the invention the cone angle of the nozzle needle seat 60 °, so that a good Sealing effect achieved between the nozzle needle and nozzle needle seat becomes.

In Ergänzung der Erfindung ist der Kegelwinkel der Düsennadel bis zu einem Grad, vorzugsweise 15 - 30 Winkelminuten, größer als der Kegelwinkel des Düsennadelsitzes, so dass die Dichtfläche verkleinert und in den Bereich des größten Durchmessers der Düsennadel verlegt wird.In addition to the invention, the cone angle of the nozzle needle to a degree, preferably 15-30 minutes of arc, greater as the cone angle of the nozzle needle seat, so that the Reduced sealing area and in the area of the largest Diameter of the nozzle needle is laid.

Bei einer Ausführungsform der Erfindung verläuft die Ringnut parallel zur Grundfläche des Kegels, so dass über den gesamten Umfang der Düsennadel gleiche Strömungsbedingungen herrschen.In one embodiment of the invention, the annular groove extends parallel to the base of the cone, so that over the entire Scope of the nozzle needle same flow conditions prevail.

Eine Ausführungsform der Erfindung sieht vor, dass die Breite der Ringnut 0,1 mm bis 0,3 mm, vorzugsweise 0,16 mm bis 0,24 mm beträgt, so dass über einen ausreichend großen Teilhubbereich die Ringnut maßgeblich für die Drosselwirkung der Einspritzdüse ist. Die Ringnut muss in jedem Fall so groß sein, dass nur die Vorderkante der Ringnut kurzzeitig drosselt.An embodiment of the invention provides that the width the annular groove 0.1 mm to 0.3 mm, preferably 0.16 mm to 0.24 mm is so that over a sufficiently large Teilhubbereich the annular groove decisive for the throttle effect of the injector is. The ring groove must in any case be so large that only the The leading edge of the annular groove throttles for a short time.

Bei einer anderen Ausgestaltung der Erfindung ist vorgesehen, dass die Tiefe der Ringnut 0,02 mm bis 0,2 mm, vorzugsweise 0,08 mm bis 0,14 mm beträgt, so dass das Volumen der Ringut klein bleibt und somit auch die Menge des Kraftstoffs, die bei abgestellter Brennkraftmaschine verdunstet, klein bleibt. In another embodiment of the invention is provided the depth of the annular groove is 0.02 mm to 0.2 mm, preferably 0.08 mm to 0.14 mm, so that the volume of the ring groove is small and thus also the amount of fuel that is at turned off internal combustion engine evaporates, remains small.

Trotzdem erfolgt eine ausreichende Beeinflussung der Drosselwirkung der Einspritzdüse durch die Ringnut.Nevertheless, there is a sufficient influence on the throttle effect the injection nozzle through the annular groove.

Bei einer weiteren Ausführungsform der Erfindung ist das Sackloch konisch, so dass das Teillastverhalten von konischen Sackloch-Einspritzdüsen verbessert wird.In a further embodiment of the invention, the blind hole conical, allowing the partial load behavior of conical blind hole injectors is improved.

In Ergänzung der Erfindung ist vorgesehen, das Sackloch zylindrisch auszuführen, so dass auch das Teillastverhalten von zylindrischen Sackloch-Einspritzdüsen verbessert wird.In addition to the invention is provided, the blind hole cylindrical perform so that also the partial load behavior of cylindrical Blind hole injectors is improved.

Eine andere Ausführungsform sieht vor, dass das Sackloch ein Minisackloch oder ein Mikrosackloch ist, so dass die erfindungsgemäßen Vorteile auch bei diesen Einspritzdüsen nutzbar sind.Another embodiment provides that the blind hole a Minisackloch or a micro-blind hole is, so that the invention Benefits are also available with these injectors.

Die.eingangs genannte Aufgabe wird bei sitzloch-Einspritzdüsen mit den kennzeichnenden Merkmalen des nebengeordneten Anspruchs 10 gelöst, so dass die Vorteile der erfindungsgemäßen Düsennadel auch bei Sitzloch-Einspritzdüsen genutzt werden können. Bei Sitzloch-Einspritzdüsen tritt darüber hinaus bisweilen auch das Problem auf, dass, aufgrund magelhafter Zentrierung der Düsennadel bezüglich des Düsennadelsitzes, der an den über den Umfang verteilten Spritzlöchern anliegende Druck des Kraftstoffs nicht gleich ist, was zu ungünstigen Bedingungen bei der Einspritzung führen kann. Durch die Ringnut kann ein Druckausgleich zwischen den Spritzlöchern erfolgen, so dass sich die mangelhafte Zentrierung der Düsennadel nicht negativ auf die Einspritzbedungungen auswirkt.The.ege mentioned task is seat hole injectors with the characterizing features of the independent claim 10, so that the advantages of the nozzle needle according to the invention also in seat-hole injection nozzles can be used. For seat hole injectors In addition, sometimes the problem arises that, due to Magomic centering of the nozzle needle with respect to the nozzle needle seat, the pressure applied to the spray holes distributed over the circumference fuel is not the same, resulting in unfavorable conditions the injection can lead. Through the ring groove can a Pressure equalization between the spray holes done, so that the insufficient centering of the nozzle needle does not adversely affect the Injection conditions affects.

Dadurch, dass bei geschlossener Einspritzdüse der Abstand des Durchstoßpunkts der Längsachse des oder der Spritzlöcher durch den Düsennadelsitz vom Grund der Einspritzdüse und der Abstand der Ringnut vom Grund der Einspritzdüse im Wesentlichen gleich sind, bestimmt im Teilhubbereich der Düsennadel die Ringnut anstelle des Übergangs vom Düsennadelsitz in das Spritzloch die Drosselwirkung und damit das Betriebsverhalten der Einspritzdüse. Due to the fact that when the injection nozzle is closed, the distance of the Piercing point of the longitudinal axis of the or the injection holes through the Nozzle needle seat from the bottom of the injector and the distance of the annular groove are essentially the same from the bottom of the injector, determined in Teilhubbereich the nozzle needle, the annular groove instead of the transition from Düsennadelsitz in the spray hole the Throttling action and thus the performance of the injector.

Bei einer Ausführungsform der Erfindung ist die Breite der Ringnut größer, vorzugsweise eineinhalb mal größer als der Durchmesser des oder der Spritzlöcher, so dass die Drosselwirkung der Einspritzdüse über einen ausreichend großen Teilhubbereich von der Ringnut beeinflusst wird.In one embodiment of the invention, the width of the Ring groove larger, preferably one and a half times larger than that Diameter of the or the injection holes, so that the Throttle effect of the injector over a sufficient large Teilhubbereich is influenced by the annular groove.

Bei anderen Ausgestaltungen der Erfindung ist vorgesehen, dass die Tiefe der Ringnut kleiner als die Breite der Ringnut ist oder dass die Tiefe der Ringnut 0,02 mm bis 0,1 mm, vorzugsweise 0,04 mm bis 0,07 mm beträgt, so dass das Volumen der Ringnut klein bleibt und trotzdem eine ausreichende Beeinflussung der Drosselwirkung der Einspritzdüse durch die Ringnut erfolgt.In other embodiments of the invention is provided that the depth of the annular groove is smaller than the width of the Ring groove is or that the depth of the annular groove 0.02 mm to 0.1 mm, preferably 0.04 mm to 0.07 mm, so that the Volume of the annular groove remains small and still one sufficient influence on the throttling effect of Injection nozzle is through the annular groove.

Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of Invention are the following description, the Drawing and claims removed.

Ein Ausführungsbeispiel des Gegenstands der Erfindung ist in der Zeichnung dargestellt und im Folgenden näher beschrieben. Es zeigen:

Figur 1:
einen Querschnitt durch eine erfindungsgemäße Sackloch-Einspritzdüse;
Figur 2:
eine Kennlinie des hydraulischen Durchmessers einer erfindungsgemäßen Sackloch-Einspritzdüse über dem Hub der Düsennadel;
Figur 3:
einen Querschnitt durch eine erfindungsgemäße Sitzloch-Einspritzdüse und
Figur 4:
eine Kennlinie des hydraulischen Durchmessers einer erfindungsgemäßen Sitzloch-Einspritzdüse über dem Hub der Düsennadel.
An embodiment of the object of the invention is illustrated in the drawing and described in more detail below. Show it:
FIG. 1:
a cross section through a blind hole injection nozzle according to the invention;
FIG. 2:
a characteristic of the hydraulic diameter of a blind hole injection nozzle according to the invention over the stroke of the nozzle needle;
FIG. 3:
a cross section through a seat hole injection nozzle according to the invention and
FIG. 4:
a characteristic of the hydraulic diameter of a seat hole injection nozzle according to the invention over the stroke of the nozzle needle.

In Figur 1 ist eine Einspritzdüse 1 mit einem konischen Sackloch 2 dargestellt. Das Sackloch 2 kann auch zylindrisch sein oder es kann sich um eine Mini- oder Mikro-Sackloch 2 handeln. Bei letztgenannten ist das Volumen des Sacklochs 2 gegenüber der in Figur 1 dargestellten Bauart verringert. Dadurch verdunstet bei abgestellter Brennkraftmaschine weniger Kraftstoff in den Brennraum.In Figure 1 is an injection nozzle 1 with a conical Blind hole 2 shown. The blind hole 2 can also be cylindrical or it may be a mini or Micro blind hole 2 act. In the latter case that is Volume of the blind hole 2 with respect to that in Figure 1 shown reduced type. This evaporates at shut off internal combustion engine less fuel in the Combustion chamber.

Über ein Spritzloch 3 gelangt der nicht dargestellte Kraftstoff aus dem Sackloch 2 in den ebenfalls nicht dargestellten Brennraum. An das konische Sackloch 2 schließt sich ein kegelstumpfförmiger Düsennadelsitz 4 an. Der Düsennadelsitz 4 kann einen Kegelwinkel von 60° haben.About a spray hole 3 reaches the not shown Fuel from the blind hole 2 in the also not illustrated combustion chamber. To the conical blind hole 2 joins a frusto-conical nozzle needle seat 4. The nozzle needle seat 4 may have a cone angle of 60 °.

An dem Düsennadelsitz 4 liegt eine Düsennadel 5 auf. In Figur 1 ist deutlich zu erkennen, dass der Kegelwinkel der Düsennadel 5 größer als der Kegelwinkel des Düsennadelsitzes 4 ist. Dadurch liegt die Kontaktzone 6 zwischen Düsennadel 5 und Düsennadelsitz 4 im Bereich des größten Durchmessers der Düsennadel 5 und die Flächenpressung zwischen Düsennadel 5 und Düsennadelsitz 4 wird erhöht. Die Differenz der Kegelwinkel von Düsennadel 5 und Düsennadelsitz 4 ist in Figur 1 übertrieben dargestellt. In der Regel ist die o. g. Differenz kleiner als 1 Grad und bewegt sich im Bereich von wenigen Winkelminuten.At the nozzle needle seat 4 is a nozzle needle 5. In Figure 1 is clearly seen that the cone angle of Nozzle needle 5 larger than the cone angle of the Nozzle needle seat 4 is. As a result, the contact zone 6 between the nozzle needle 5 and nozzle needle seat 4 in the region of largest diameter of the nozzle needle 5 and the Surface pressure between the nozzle needle 5 and nozzle needle seat 4th will be raised. The difference of the cone angle of the nozzle needle 5 and nozzle needle seat 4 is exaggerated in FIG shown. As a rule, the o. G. Difference smaller than 1 degree and ranges in the range of a few Angular minutes.

Der Übergang zwischen Sackloch 2 und Düsennadelsitz 4 nach dem Stand der Technik ist eine Kante 7, die beim Schleifen des Düsennadelsitzes 4 entsteht. Je nach Art der Bearbeitung kann die Kante 7 ein scharfer Grat oder eine glatte Kante sein. Der Strömungswiderstand der Kante 7 wird wesentlich von der Beschaffenheit derselben beeinflusst.The transition between blind hole 2 and nozzle needle seat 4 after In the prior art is an edge 7, which when grinding of the nozzle needle seat 4 is formed. Depending on the type of Editing, the edge 7 can be a sharp ridge or a smooth edge. The flow resistance of the edge 7 is significantly influenced by the nature of the same.

Eine in die Düsennadel 5 eingestochene oder geschliffene Ringnut 8 verringert den Einfluss der Kante 7 auf den Strömungswiderstand der Einspritzdüse 1. Der Abstand der Ringnut 8 von einem Grund 9 der Einspritzdüse 1 ist etwa gleich groß wie der Abstand von dem Grund 9 der Einspritzdüse 1 und der Kante 7. Dadurch wird, unabhängig vom Hub der Düsennadel 5, die Drosselwirkung der Einspritzdüse 1 nicht oder zumindest nicht nennenswert von der Geometrie der Kante 7 beeinflusst. Dieser Effekt beruht darauf, dass, wegen des im Vergleich zu dem Ringspalt zwischen Düsennadelsitz 4 und dem Kegel der Düsennadel 5 großen hydraulischen Durchmessers des Ringspalts zwischen Ringnut 8 und Kante 7, der Stömungswiderstand in dem letzgenannten Ringspalt geringer ist als der des erstgenannten Ringspalts. Da beide Strömungswiderstände in Reihe geschaltet sind, ist für den Strömungswiderstand der gesamten Einspritzdüse im Wesentlichen der kleinste Einzelwiderstand maßgeblich.A pierced or ground into the nozzle needle 5 Ring groove 8 reduces the influence of the edge 7 on the Flow resistance of the injection nozzle 1. The distance of the Ring groove 8 of a bottom 9 of the injection nozzle 1 is about the same size as the distance from the bottom 9 of the Injector 1 and the edge 7. This will, regardless from the stroke of the nozzle needle 5, the throttle effect of Injector 1 not or at least not appreciably the geometry of the edge 7 influenced. This effect is based on that, because of compared to the annular gap between the nozzle needle seat 4 and the cone of the nozzle needle. 5 large hydraulic diameter of the annular gap between Ring groove 8 and edge 7, the flow resistance in the last mentioned annular gap is less than that of first mentioned annular gaps. Since both flow resistances in Are connected for the flow resistance of the series entire injector is essentially the smallest Single resistance decisive.

Die Folgen der Streuung des Strömungswiderstands von Einspritzdüsen 1 im Bereich der Kante 7 werden anhand des in Figur 2 dargestellten Diagramms veranschaulicht. In Figur 2 ist der hydraulische Durchmesser 11 einer Sackloch-Einspritzdüse 1 über dem Düsennadelhub 10 qualitativ aufgetragen. Der hydraulische Durchmesser 11 ist eine Größe mittels derer beliebige durchströmte Querschnitte hinsichtlich ihres Strömungswiderstands vergleichbar gemacht werden. Als Bezugsgröße dient der Strömungswiderstand eines Rohrs mit kreisförmigem Querschnitt. Ein Querschnitt mit großem hydraulischen Durchmesser hat einen geringen Strömungswiderstand und umgekehrt.The consequences of the dispersion of the flow resistance of Injectors 1 in the region of the edge 7 are based on the illustrated in Figure 2 diagram. In FIG. 2 is the hydraulic diameter 11 of a blind-hole injection nozzle 1 above the nozzle needle stroke 10 qualitatively applied. The hydraulic diameter 11 is a size by means of which any flow-through cross-sections comparable in terms of their flow resistance be made. The reference is the Flow resistance of a pipe with circular Cross-section. A cross section with large hydraulic Diameter has a low flow resistance and vice versa.

In Figur 2 wurde der Düsennadelhub 10 in zwei Bereiche eingeteilt. Ein erster Bereich erstreckt sich von Null bis "a", der zweite, nachfolgend als Teilhubbereich bezeichnete Bereich erstreckt sich von "a" bis "b". Bei "c" ist der volle Düsennadelhub erreicht. In FIG. 2, the nozzle needle stroke 10 has been divided into two areas assigned. A first area extends from zero to "a", the second, hereinafter referred to as Teilhubbereiche Range extends from "a" to "b". At "c" is the full nozzle needle stroke reached.

Wenn eine geschlossene Einspritzdüse 1, bei der die Düsennadel 5 auf dem Düsennadelsitz 4 aufliegt, geöffnet wird, ergibt sich bei sehr kleinem Düsennadelhub 10 im Bereich der Kontaktzone 6 ein sehr schmaler Spalt, durch den der unter Druck stehende Kraftstoff in das Sackloch 2 strömen kann. Dieser sehr schmale Spalt bestimmt den Strömungswiderstand der Einspritzdüse 1 maßgeblich und legt damit auch den hydraulischen Durchmesser 11 fest. Da der Strömungswiderstand dieses sehr schmalen Spalts groß ist, ist der hydraulische Durchmesser 11 der Einspritzdüse 1 bei sehr kleinem Düsennadelhub 10 sehr klein.If a closed injection nozzle 1, in which the Nozzle needle 5 rests on the nozzle needle seat 4, opened is, results in very small Düsennadelhub 10 in Area of the contact zone 6 a very narrow gap, through the pressurized fuel in the blind hole. 2 can flow. This very narrow gap determines the Flow resistance of the injector 1 authoritative and sets thus also the hydraulic diameter 11 firmly. Since the Flow resistance of this very narrow gap is large, the hydraulic diameter 11 of the injection nozzle 1 is at very small Düsennadelhub 10 very small.

Im Teilhubbereich zwischen "a" und "b" wird der Strömungswiderstand von Einspritzdüsen 1 nach dem Stand der Technik maßgeblich von der Kante 7 zwischen Düsennadelsitz 4 und Sackloch 2 bestimmt. Damit ist die Kante 7 im Teilhubbereich auch für den hydraulischen Durchmesser der Einspritzdüse 1 von großer Bedeutung. Das bedeutet, dass Änderungen in der Geometrie der Kante 7 Änderungen des hydraulischen Durchmessers 11 zur Folge haben. Im Bereich des vollen Düsennadelhubs "c" ist das Spritzloch 3 der Einspritzdüse 1 maßgeblich für den hydraulischen Durchmesser der Einspritzdüse 1.In Teilhubbereich between "a" and "b" is the Flow resistance of injectors 1 according to the state of Technique significantly from the edge 7 between nozzle needle seat 4 and blind hole 2 determined. This is the edge 7 in Teilhubbereich also for the hydraulic diameter of the Injector 1 of great importance. It means that Changes in the geometry of the edge 7 Changes in the hydraulic diameter 11 result. In the area of the full nozzle needle stroke "c" is the injection hole 3 of the Injector 1 decisive for the hydraulic Diameter of the injection nozzle 1.

Gemäß dem vorstehend Gesagten führen Streuungen in der Geometrie der Kante 7 zu einer Änderung der Kennlinie 12 der Einspritzdüse 1 vor allem im Teilhubbereich zwischen "a" und "b".According to the above, variations in the Geometry of the edge 7 to a change of the characteristic 12 the injection nozzle 1, especially in Teilhubbereich between "a" and "b".

In Figur 2 sind Kennlinien 12 und 13 einer Einspritzdüse 1 nach dem Stand der Technik und eine Kennlinie 14 einer erfindungsgemäßen Sackloch-Einspritzdüse 1 dargestellt. Bei der Einspritzdüse 1 nach dem Stand der Technik weist die Düsennadel 5 keine Ringnut auf. Wegen der oben beschriebenen Streungen in der Geometrie der Kante 7, streuen auch die Kennlinien verschiedener Exemplare bauartgleicher Einspritzdüsen 1, insbesondere im Teilhubbereich. Dies ist durch die Abweichungen der Kennlinien 12 und 13 voneinander in Fig. 2 veranschaulicht.In FIG. 2, characteristic curves 12 and 13 of an injection nozzle 1 are shown According to the prior art and a characteristic 14 of a blind hole injection nozzle 1 according to the invention shown. at the injection nozzle 1 according to the prior art has the Nozzle needle 5 no annular groove. Because of the above described strains in the geometry of the edge 7, also scatter the characteristics of different specimens identical construction injection nozzles 1, in particular in Partial stroke. This is due to the deviations of Characteristics 12 and 13 from each other in Fig. 2 illustrates.

Die Kennlinie 14 repräsentiert eine erfindungsgemäße Einspritzdüse bei der vor allem im Teilhubbereich die Drosselwirkung der Kante 7 nicht zum Tragen kommt, da der Kraftstoff in die Ringnut 8 ausweichen kann. In Folge dessen ist der hydraulische Durchmesser 11 der erfindungsgemäßen Einspritzdüse 1 im Teilhubbereich größer als der von Einspritzdüsen 1 nach dem Stand der Technik. Vor allem aber streuen die Kennlinien 14 verschiedener Exemplare bauartgleicher erfindungsgemäßer Einspritzdüsen 1, insbesondere im Teilhubbereich sehr viel weniger, da die Geometrie der Ringnut 8 mit großer Wiederholgenauigkeit gefertigt werden kann.The characteristic curve 14 represents an inventive Injection nozzle, especially in Teilhubbereich the Throttle effect of the edge 7 does not come to fruition, since the Fuel can escape into the annular groove 8. As a result whose is the hydraulic diameter 11 of the Injector 1 according to the invention in the Teilhubbereich larger as that of injection nozzles 1 according to the prior art. Above all, the characteristics scatter 14 different Specimens of the same design according to the invention injectors 1, especially in Teilhubbereich much less, since the Geometry of the annular groove 8 with great repeatability can be made.

Bei in Serie gefertigten Brennkraftmaschinen wird das Kennfeld der Brennkraftmaschine und des zugehörigen Einspritzsystems anhand eines oder mehrerer ausgewählter Testexemplare durch Messungen ermittelt. Die solcherart ermittelten Kennfelder werden allen bauartgleichen Einspritzsystemen zugrundegelegt.In mass produced internal combustion engines is the Characteristic map of the internal combustion engine and the associated Injection system based on one or more selected Test copies determined by measurements. The kind Determined maps are all same type Based on injection systems.

Im Folgenden wird angenommen, dass die Kennlinie 12 eine gemessene Kennlinie ist, und dass diese Kennlinie 12 in dem Steuergerät des Einspritzsystems abgespeichert ist. Weiter wird unterstellt, dass eine der Serienfertigung entnommene Einspritzdüse 1 die Kennlinie 13 hat. Wenn nun die Einspritzdüse 1 mit der Kennlinie 13 mit einem Steuergerät zusammenwirkt, in dem die Kennlinie 12 abgespeichert ist, dann stimmt die tatsächliche Einspritzmenge im Teilhubbereich der Einspritzdüse 1 mit der Kennlinie 13 nicht mit der bei den Testexemplaren gemessenen optimalen Einspritzmenge gemäß der Kennlinie 12 überein, so dass die Leistung und/oder das Emissionsverhalten der Brennkraftmaschine verschlechtert wird.In the following, it is assumed that the characteristic 12 is a measured characteristic is, and that this characteristic 12 in the Control unit of the injection system is stored. Further is assumed that one of the series production taken Injector 1 has the characteristic curve 13. If now the Injector 1 with the characteristic curve 13 with a control unit interacts, in which the characteristic curve 12 is stored, then the actual injection quantity is correct Teilhubbereich the injection nozzle 1 with the curve 13th not with the optimum measured in the test specimens Injection amount according to the characteristic curve 12, so that the Performance and / or emission behavior of Internal combustion engine is deteriorated.

Bei den erfindungsgemäßen Einspritzdüsen 1 streuen die Kennlinien 14 nur in sehr geringen Maße, so dass bei allen mit erfindungsgemäßen Einspritzdüsen 1 ausgerüsteten Brennkraftmaschinen die Übereinstimmung zwischen der im Steuergerät abgespeicherten Kennlinie 14 und den Kennlinien 14 der eingebauten Einspritzdüsen 1 deutlich verbesssert wird. Die Übereinstimmung kann, verglichen mit der Streuung bei Einspritzdüsen 1 nach dem Stand der Technik, beispielsweise um den Faktor 2 bis 3 verbessert werden. In Folge dessen entspricht die tatsächlich eingespritzte Kraftstoffmenge genau der von dem Steuergerät vorgegebenen Einspritzmenge und das Verbrauchs- und Emissionsverhalten der Brennkraftmaschine ist optimal.In the injection nozzles 1 according to the invention scatter the Characteristics 14 only to a very small extent, so that at all equipped with injectors 1 according to the invention Internal combustion engines the correspondence between in the Control device stored characteristic 14 and the characteristics 14 of the built-in injectors 1 significantly improved becomes. The match can be compared to the scatter in injection nozzles 1 according to the prior art, For example, be improved by a factor of 2 to 3. In As a result, the actual injected Fuel quantity exactly that specified by the controller Injection quantity and the consumption and emission behavior the internal combustion engine is optimal.

In Fig. 3 ist eine erfindungsgemäße Einspritzdüse 1 mit als Sitzlöchern ausgebildeten Spritzlöchern 3 dargestellt. Die Bezugszahlen entsprechen den in Fig. 1 verwandten. Der wesentliche Unterschied besteht darin, dass im Teilhubbereich anstelle der Kante 7 der Übergang 15 zwischen Düsennadelsitz 4 und Spritzlöchern 3 maßgeblich für den Strömungswiderstand der Einspritzdüse 1 ist. Die erfindungsgemäße Ringnut 8 ist bei Sitzloch-Einspritzdüsen auf Höhe der Spritzlöcher 3 angeordnet, so dass der Einfluss des Übergangs 15 zwischen Düsennadelsitz 4 und Spritzlöchern 3 auf den Strömungswiderstand der Einspritzdüse stark reduziert wird. Der Abstand der Ringnut 8 von dem Grund 9 der Einspritzdüse 1 ist etwa gleich groß wie der Abstand von dem Grund 9 der Einspritzdüse 1 und einem Durchstoßpunkt 16 der Längsachse des Spritzlochs 3 und dem Düsennadelsitz 4. Dadurch wird, unabhängig vom Hub der Düsennadel 5, die Drosselwirkung der Einspritzdüse 1 nicht oder zumindest nicht nennenswert von der Geometrie des Übergangs 15 beeinflusst. In Fig. 3, an injection nozzle 1 according to the invention with as Seating holes trained spray holes 3 shown. The Reference numerals correspond to those in FIG. 1 related. Of the main difference is that in the Teilhubbereich instead of the edge 7 of the transition 15th between nozzle needle seat 4 and spray holes 3 authoritative for the flow resistance of the injection nozzle 1 is. The Ring groove 8 according to the invention is in seat hole injection nozzles arranged at the height of the spray holes 3, so that the Influence of the transition 15 between nozzle needle seat 4 and Spray holes 3 on the flow resistance of Injector is greatly reduced. The distance of the annular groove 8 of the bottom 9 of the injection nozzle 1 is about the same size as the distance from the bottom 9 of the injection nozzle 1 and a piercing point 16 of the longitudinal axis of the injection hole. 3 and the nozzle needle seat 4. This will, regardless of the stroke the nozzle needle 5, the throttle effect of the injection nozzle. 1 not or at least not appreciably of the geometry of transition 15.

In Fig. 4 sind die Kennlinie 12 einer Einspritzdüse 1 nach dem Stand der Technik und die Kennlinie 14 einer erfindungsgemäßen Sitzloch-Einspritzdüse 1 dargestellt.In Fig. 4, the characteristic curve 12 of an injection nozzle 1 after the prior art and the characteristic 14 of a Seat hole injection nozzle 1 according to the invention shown.

Für die erfindungsgemäßen Sitzloch-Einspritzdüsen gilt das bezüglich der Sackloch-Einspritzdüsen oben gesagte mit den erwähnten Unterschieden entsprechend.This applies to the seat hole injection nozzles according to the invention with respect to the blind hole injectors said above mentioned differences accordingly.

Alle in der Beschreibung, den nachfolgenden Ansprüchen und der Zeichnung dargestellten Merkmale können sowohl einzeln als auch in beliebiger Kombination miteinander erfindungswesentlich sein.All in the description, the following claims and The features shown in the drawing can both individually as well as in any combination with each other be essential to the invention.

Claims (13)

  1. Injection nozzle having a frustum-shaped nozzle needle seat having a blind hole (2) adjoining it, at least one spray hole (3) being present in the blind hole (2), the end of the nozzle needle (5) which faces the nozzle needle seat (4) being frustum shaped and an annular groove (8) being present in the frustum-shaped end of the nozzle needle (5), characterized in that the nozzle needle seat (4) is embodied simply in the shape of a frustum, in that the end of the nozzle needle (5) which faces the nozzle needle seat (4) is embodied simply in the shape of a frustum, in that the junction between the nozzle needle seat (4) and the blind hole (2) is formed by an edge (7), and in that when the injection nozzle (1) is closed, the distance between the edge (7) and the base (9) of the injection nozzle (1) and the distance between the annular groove (8) and the base (9) of the injection nozzle (1) are essentially the same.
  2. Injection nozzle (1) according to Claim 1, characterized in that the cone angle of the nozzle needle seat (4) is approximately 60°.
  3. Injection nozzle (1) according to one of Claims 1 or 2, characterized in that the cone angle of the nozzle needle (5) is up to approximately one degree, preferably 15 to 30 angular minutes, greater than the cone angle of the nozzle needle seat (4).
  4. Injection nozzle (1) according to one of the preceding claims, characterized in that the annular groove (8) extends parallel to the base surface of the cone.
  5. Injection nozzle (1) according to one of the preceding claims, characterized in that the width of the annular groove (8) is approximately 0.1 mm to 0.3 mm, preferably approximately 0.16 mm to 0.24 mm.
  6. Injection nozzle (1) according to one of the preceding claims, characterized in that the depth of the annular groove (8) is approximately 0.02 mm to 0.2 mm, preferably approximately 0.08 mm to 0.14 mm.
  7. Injection nozzle (1) according to one of the preceding claims, characterized in that the blind hole (2) is conical.
  8. Injection nozzle (1) according to one of Claims 1 to 6, characterized in that the blind hole (2) is cylindrical.
  9. Injection nozzle (1) according to one of the preceding claims, characterized in that the blind hole (2) is a mini blind hole or a micro blind hole.
  10. Injection nozzle having a frustum-shaped nozzle needle seat (4), at least one spray hole (3) being present in the nozzle needle seat (4), the end of the nozzle needle (5) which faces the nozzle needle seat (4) being of frustum-shaped design and an annular groove (8) being present in the frustum-shaped end of the nozzle needle (5), characterized in that the end of the nozzle needle (5) which faces the nozzle needle seat (4) is embodied simply in the shape of a frustum, and in that, when the injection nozzle (1) is closed, the distance between the penetration point (16) of the longitudinal axis of the spray hole or holes (3) through the nozzle needle seat (4) from the base (9) of the injection nozzle (1) and the distance of the annular groove (8) from the base (9) of the injection nozzle (1) are essentially the same.
  11. Injection nozzle (1) according to Claim 10, characterized in that the width of the annular groove (8) is larger, preferably one and a half times larger, than the diameter of the spray hole or holes (3).
  12. Injection nozzle (1) according to one of Claims 10 or 11, characterized in that the depth of the annular groove (8) is smaller than the width of the annular groove (8).
  13. Injection nozzle (1) according to one of Claims 10 to 12, characterized in that the depth of the annular groove (8) is approximately 0.02 mm to 0.1 mm, preferably approximately 0.04 mm to 0.07 mm.
EP00965779A 1999-09-04 2000-08-18 Injection nozzle for an internal combustion engine with annular groove in said nozzle needle Expired - Lifetime EP1129287B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19942370A DE19942370A1 (en) 1999-09-04 1999-09-04 Injection nozzle for internal combustion engines with an annular groove in the nozzle needle
DE19942370 1999-09-04
PCT/DE2000/002814 WO2001018387A1 (en) 1999-09-04 2000-08-18 Injection nozzle for an internal combustion engine with annular groove in said nozzle needle

Publications (2)

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EP1129287A1 EP1129287A1 (en) 2001-09-05
EP1129287B1 true EP1129287B1 (en) 2005-05-18

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US (1) US7128280B1 (en)
EP (1) EP1129287B1 (en)
JP (1) JP4709451B2 (en)
KR (1) KR100737712B1 (en)
DE (2) DE19942370A1 (en)
WO (1) WO2001018387A1 (en)

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US8720802B2 (en) 2005-06-01 2014-05-13 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
CN105492757A (en) * 2013-08-30 2016-04-13 罗伯特·博世有限公司 Fuel injector
CN105492757B (en) * 2013-08-30 2018-10-23 罗伯特·博世有限公司 Fuel injector

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EP1129287A1 (en) 2001-09-05
DE19942370A1 (en) 2001-03-22
DE50010346D1 (en) 2005-06-23
JP4709451B2 (en) 2011-06-22
KR100737712B1 (en) 2007-07-11
KR20010092436A (en) 2001-10-24
JP2003508684A (en) 2003-03-04
US7128280B1 (en) 2006-10-31
WO2001018387A1 (en) 2001-03-15

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