EP3014104B1 - Nozzle assembly for a fuel injector, and fuel injector - Google Patents

Nozzle assembly for a fuel injector, and fuel injector Download PDF

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Publication number
EP3014104B1
EP3014104B1 EP14720622.1A EP14720622A EP3014104B1 EP 3014104 B1 EP3014104 B1 EP 3014104B1 EP 14720622 A EP14720622 A EP 14720622A EP 3014104 B1 EP3014104 B1 EP 3014104B1
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EP
European Patent Office
Prior art keywords
nozzle
valve seat
nozzle needle
pressure bore
blind
Prior art date
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Application number
EP14720622.1A
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German (de)
French (fr)
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EP3014104A1 (en
Inventor
Christian Wehr
Gerhard Suenderhauf
Andreas Koeninger
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP3014104A1 publication Critical patent/EP3014104A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—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
    • F02M61/1813—Discharge orifices having different orientations with respect to valve member direction of movement, e.g. orientations being such that fuel jets emerging from discharge orifices collide with each other
    • 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
    • F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
    • 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
    • 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
    • F02M61/1893—Details of valve member ends 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
    • F02M2200/02—Fuel-injection apparatus having means for reducing wear
    • 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
    • F02M2200/06—Fuel-injection apparatus having means for preventing coking, e.g. of fuel injector discharge orifices or valve needles
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • the invention relates to a nozzle assembly for a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine with the features of the preamble of claim 1. Furthermore, the invention relates to a fuel injector with such a nozzle assembly.
  • a nozzle assembly for a fuel injector comprising a nozzle body having a bore which opens via a conical nozzle needle seat for a conical sealing surface of a received in the bore nozzle needle in a blind hole.
  • a conical nozzle needle seat for a conical sealing surface of a received in the bore nozzle needle in a blind hole.
  • the nozzle needle has a nozzle needle tip with a pin which dips into the blind hole and in this way reduces the dead volume remaining in the blind hole in the closed position of the nozzle needle.
  • the peg-like nozzle needle tip can be lifted completely out of the blind hole, so that there is a risk of the nozzle needle striking the nozzle body during re-immersion.
  • the result is increased wear in the transition region from the nozzle needle seat into the blind hole, in particular in the area of an intersecting edge. The wear in turn leads to a changed switching behavior of the nozzle needle.
  • a nozzle needle fuel injectors for diesel engines is known with an injector, wherein the nozzle needle cooperates with a formed in the Injektorgeophuse conical seat for opening and closing at least one injection port.
  • the nozzle needle has a cylindrical end portion, which is arranged in a cylindrical portion of the injector and this has a distance of two to three hundredths of a millimeter.
  • the invention is therefore based on the object to provide a nozzle assembly for a fuel injector, comprising a nozzle needle with a submersible in a blind hole pin, which is less subject to wear.
  • the proposed nozzle assembly comprises a nozzle body and a nozzle needle, which is accommodated for releasing and closing at least one injection port in a high-pressure bore of the nozzle body, wherein a in a blind hole-like end portion overflowing conical portion of the high-pressure bore for forming a valve seat with a conical sealing surface of the nozzle needle, to which is a plunged into the blind hole-like end portion pin is attached, sealingly cooperates.
  • a valve seat near guide region upstream of the valve seat between the nozzle needle and the nozzle body is formed for permanent guidance of the nozzle needle in the high pressure bore, whose radial guide clearance smaller than a radial gap between a cylindrical part of the blind hole-like end portion of the high-pressure bore and a cylindrical part of the pin of the nozzle needle.
  • the permanent guidance of the nozzle needle via the at least one valve seat near the guide region upstream of the valve seat prevents a radial deflection of the nozzle needle and thus the risk of striking the nozzle needle on the nozzle body. In this way, the wear in the transition region from the valve seat in the blind hole-like end portion is significantly reduced.
  • the pin of the nozzle needle is designed so that he a cylindrical part of the blind hole-like end portion cooperating throttle forming.
  • the throttle formation is dependent on the stroke of the nozzle needle, so that over this the inflow to at least one injection port is controllable.
  • the radial gap is greater than the radial guide clearance of the valve seat near the guide region upstream of the valve seat selected. Because the radial gap is not suitable for permanent guidance of the nozzle needle in the high-pressure bore, since its formation is dependent on the stroke of the nozzle needle. A guiding function could take over the radial gap therefore only temporarily.
  • a radial gap of less than 20 microns, preferably less than 10 microns is proposed.
  • the leadership function of the valve seat near guide area is maintained, its radial guide clearance is to be chosen correspondingly smaller.
  • the at least two injection openings are arranged at an axial distance from one another. This allows the formation of at least two axially spaced spray hole rows. The arrangement of the axially spaced injection openings is preferably carried out in such a way that the inflow of fuel through the throttle-forming radial gap in dependence on the stroke of the nozzle needle is controllable.
  • the at least two axially spaced injection openings can for example be arranged such that at least one injection opening in the region of the blind-hole-like end portion and at least one further injection opening in the region of the conical portion downstream of the valve seat open into the high-pressure bore.
  • the at least one injection opening opening into the blind-hole-like end section is then controllable via the throttle-forming radial gap.
  • a guide region near the valve seat does not preclude that an additional guide region for permanent guidance of the nozzle needle is formed at an axial distance therefrom, ie in a region of the high-pressure bore remote from the valve seat, as is conventionally the case with known nozzle assemblies for fuel injectors.
  • the permanent guidance of the nozzle needle via the at least one valve seat near guide region not only has a wear-reducing effect, but also prevents an asymmetrical spray pattern caused by a disalignment of the nozzle needle. This has an advantageous effect on the pollutant emissions of the internal combustion engine when using the nozzle assembly in a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine.
  • the nozzle body or the nozzle needle to form the valve seat near the guide region upstream of the valve seat at least two axially extending guide ribs, between which flow channels are formed.
  • the flow channels ensure the inflow of fuel to the at least one injection port during operation of the fuel injector.
  • the guide ribs are formed on the nozzle body, they preferably cooperate with a cylindrical shaft portion of the nozzle needle gap-forming.
  • the guide ribs are preferably on a radial wall defining the high-pressure bore cylindrical wall surface of the nozzle body arranged and protrude into the high pressure bore.
  • the guide ribs may be formed on the nozzle needle and cooperate with a high pressure bore radially bounding cylindrical wall surface of the nozzle body gap-forming.
  • the guide ribs can be arranged in this case on a cylindrical shaft portion of the nozzle needle, so that they protrude into the high-pressure bore.
  • the axially extending guide ribs for forming the valve seat near guide region upstream of the valve seat are arranged at the same angular distance from each other.
  • at least three guide ribs are provided at an angular distance of 120 °.
  • the angular distance is 90 °, with five guide ribs 72 ° and with six guide ribs 60 °.
  • more than six guide ribs can be provided, wherein it must be ensured that sufficiently large flow channels remain between the guide ribs.
  • the same angular distance of the guide ribs to each other ensures optimal guidance of the nozzle needle in the high-pressure bore.
  • a plurality of injection openings are provided for forming at least one spray hole row.
  • the plurality of injection openings of a spray hole row are preferably arranged at equal angular distance from each other to produce a symmetrical spray pattern.
  • a fuel injector is proposed with a nozzle assembly according to the invention further.
  • the less wear-prone nozzle assembly increases the life of the fuel injector:
  • the pollutant emissions can also be reduced because the permanent guide prevents radial deflection of the nozzle needle and thus an asymmetric spray pattern.
  • the fuel injector may in particular be a fuel injector for a common-rail injection system.
  • FIG. 1 shows a longitudinal section through a nozzle assembly according to the invention in the region of a valve seat.
  • the nozzle assembly shown comprises a nozzle body 1 with a high-pressure bore 4, in which a nozzle needle 2 is received in a liftable manner.
  • the high-pressure bore 4 has, to form a valve seat 7, a conical section 6, which merges into a blind-hole-like end section 5, into which at least one injection opening 3 opens.
  • a further injection opening 3 opens into the conical section 5 into the high-pressure bore 4.
  • the nozzle needle 2 has a conical sealing surface 8 sealingly cooperating with the valve seat 7 a pin 9 is attached.
  • the pin 9 has a directly adjacent to the conical sealing surface 8 cylindrical part which cooperates with a cylindrical portion of the blind hole-like end portion 5 - in response to the stroke of the nozzle needle 2 - forming a radial gap 11.
  • the radial gap 11 has a throttle function to control the inflow of fuel to the injection port 3, which opens into the blind-hole-like end portion 5 of the high-pressure bore 4. This has the consequence that in a first phase of the opening stroke of the nozzle needle 2, the injection takes place primarily via the injection port 3, which opens into the conical portion 6 of the high-pressure bore 4.
  • the nozzle assembly shown has a valve seat near guide portion 10 upstream of the valve seat 7.
  • the guide region 10 is formed by a plurality of axially extending guide ribs 12 of the nozzle body 1, which cooperate with a cylindrical shaft portion of the nozzle needle 2 forming a gap.
  • the guide ribs 12 protrude from a cylindrical wall surface of the nozzle body 1 to the radial boundary of the high-pressure bore 4 into the high-pressure bore 4.
  • the guide ribs 12 are provided at an angular distance of 90 °, wherein between the guide ribs 12 axially extending flow channels are formed, which ensure the inflow of fuel to the injection openings 3.
  • the guide region 10 ensures a permanent guidance of the nozzle needle 2 in the high-pressure bore 4 independently of the stroke of the nozzle needle 2. This ensures that the nozzle needle 2 undergoes no radial deflection, which could lead to the striking of the pin 9 on the nozzle body 1.
  • the Radial gap 11 greater than the radial guide clearance of the valve seat near the guide region 10 is selected.
  • Another advantage of the permanent guidance of the nozzle needle 2 via the valve seat near guide region 10 is the fact that an asymmetric spray pattern associated with a desalination of the nozzle needle 2 is prevented. This has a favorable effect on the pollutant emissions when using the nozzle assembly in a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine. This means that pollutant emissions are reduced.
  • the invention is not limited to the illustrated preferred embodiment. Modifications are possible, which relate in particular to the number, arrangement and specific design of the guide ribs 12 for forming the guide region 10.
  • the guide ribs 12 may also be formed on the nozzle needle 2.
  • the number, the arrangement and the specific configuration of preferably a plurality of injection openings 3 are freely selectable.

Description

Die Erfindung betrifft eine Düsenbaugruppe für einen Kraftstoffinjektor zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine mit den Merkmalen des Oberbegriffs des Anspruchs 1. Ferner betrifft die Erfindung einen Kraftstoffinjektor mit einer solchen Düsenbaugruppe.The invention relates to a nozzle assembly for a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine with the features of the preamble of claim 1. Furthermore, the invention relates to a fuel injector with such a nozzle assembly.

Stand der TechnikState of the art

Aus der Offenlegungsschrift DE 10 2008 039 920 A1 geht eine Düsenbaugruppe für einen Kraftstoffinjektor hervor, umfassend einen Düsenkörper mit einer Bohrung, die über einen kegelförmigen Düsennadelsitz für eine kegelförmige Dichtfläche einer in der Bohrung aufgenommenen Düsennadel in einem Sackloch mündet. Im Bereich des Sacklochs sind mehrere Einspritzöffnung in einer Lochreihe angeordnet. Die Düsennadel weist eine Düsennadelspitze mit einem Zapfen auf, der in das Sackloch eintaucht und auf diese Weise das im Sackloch verbleibende Schadvolumen in Schließstellung der Düsennadel verringert. Um Streuungen bei den Einspritzungen durch Fertigungstoleranzen im Bereich eines hydraulischen Durchmessers der die Düsennadel aufnehmenden Bohrung stromabwärts des Düsennadelsitzes zu vermeiden, wird vorgeschlagen, einen Absatz im Übergangsbereich vom Düsennadelsitz zum Sackloch vorzusehen. Ferner wird vorgeschlagen, dass der Absatz innen in einer Wandung des Düsenkörpers eine im Wesentlichen hohlzylindrische Kontur aufweist. Im Verschneidungsbereich der hohlzylindrischen Kontur mit dem kegelförmigen Düsennadelsitz stromaufwärts des Absatzes sowie im Verschneidungsbereich des Absatzes mit einem sich stromabwärts anschließenden kegelförmigen Abschnitt des Sacklochs wird jeweils eine ringförmige Verschneidungskante ausgebildet.From the publication DE 10 2008 039 920 A1 shows a nozzle assembly for a fuel injector, comprising a nozzle body having a bore which opens via a conical nozzle needle seat for a conical sealing surface of a received in the bore nozzle needle in a blind hole. In the area of the blind hole several injection openings are arranged in a row of holes. The nozzle needle has a nozzle needle tip with a pin which dips into the blind hole and in this way reduces the dead volume remaining in the blind hole in the closed position of the nozzle needle. In order to avoid scattering in the injections by manufacturing tolerances in the range of a hydraulic diameter of the nozzle needle receiving bore downstream of the nozzle needle seat, it is proposed to provide a shoulder in the transition region from the nozzle needle seat to the blind hole. It is also proposed that the shoulder inside a wall of the nozzle body has a substantially hollow cylindrical contour. In the intersection region of the hollow cylindrical contour with the conical nozzle needle seat upstream of the shoulder and in the intersection of the shoulder with a downstream adjoining conical portion of the blind hole an annular intersection edge is formed in each case.

In Abhängigkeit vom Hub der Düsennadel kann die zapfenartige Düsennadelspitze vollständig aus dem Sackloch gehoben werden, so dass beim Wiedereintauchen die Gefahr eines Anschlagen der Düsennadel am Düsenkörper besteht. Die Folge ist ein erhöhter Verschleiß im Übergangsbereich vom Düsennadelsitz in das Sackloch, insbesondere im Bereich einer Verschneidungskante. Der Verschleiß führt wiederum zu einem veränderten Schaltverhalten der Düsennadel.Depending on the stroke of the nozzle needle, the peg-like nozzle needle tip can be lifted completely out of the blind hole, so that there is a risk of the nozzle needle striking the nozzle body during re-immersion. The result is increased wear in the transition region from the nozzle needle seat into the blind hole, in particular in the area of an intersecting edge. The wear in turn leads to a changed switching behavior of the nozzle needle.

Aus der GB 2 138 073 A ist eine Düsennadel aus Kraftstoffinjektoren für Dieselmotoren mit einem Injektorgehäuse bekannt, wobei die Düsennadel mit einem in dem Injektorgehäuse ausgebildeten konischen Sitz zum Öffnen und Schließen wenigstens einer Einspritzöffnung zusammenwirkt. Dabei weist die Düsennadel einen zylindrischen Endabschnitt auf, welcher in einem zylindrischen Abschnitt des Injektorgehäuses angeordnet ist und zu diesem einen Abstand von zwei bis drei Hundertstel eines Millimeters aufweist.From the GB 2 138 073 A a nozzle needle fuel injectors for diesel engines is known with an injector, wherein the nozzle needle cooperates with a formed in the Injektorgehäuse conical seat for opening and closing at least one injection port. In this case, the nozzle needle has a cylindrical end portion, which is arranged in a cylindrical portion of the injector and this has a distance of two to three hundredths of a millimeter.

Der Erfindung liegt daher die Aufgabe zu Grunde, eine Düsenbaugruppe für einen Kraftstoffinjektor, umfassend eine Düsennadel mit einem in ein Sackloch eintauchbaren Zapfen anzugeben, die weniger verschleißbehaftet ist.The invention is therefore based on the object to provide a nozzle assembly for a fuel injector, comprising a nozzle needle with a submersible in a blind hole pin, which is less subject to wear.

Die Aufgabe wird gelöst durch eine Düsenbaugruppe mit den Merkmalen des Anspruchs 1. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben.The object is achieved by a nozzle assembly having the features of claim 1. Advantageous developments of the invention are specified in the subclaims.

Offenbarung der ErfindungDisclosure of the invention

Die vorgeschlagene Düsenbaugruppe umfasst einen Düsenkörper und eine Düsennadel, die zum Freigeben und Verschließen wenigstens einer Einspritzöffnung in einer Hochdruckbohrung des Düsenkörpers hubbeweglich aufgenommen ist, wobei ein in einen sacklochartigen Endabschnitt übergehender kegelförmiger Abschnitt der Hochdruckbohrung zur Ausbildung eines Ventilsitzes mit einer kegelförmigen Dichtfläche der Düsennadel, an welcher ein in den sacklochartigen Endabschnitt eintauchbarer Zapfen angesetzt ist, dichtend zusammenwirkt. Erfindungsgemäß ist zur permanenten Führung der Düsennadel in der Hochdruckbohrung ein ventilsitznaher Führungsbereich stromaufwärts des Ventilsitzes zwischen der Düsennadel und dem Düsenkörper ausgebildet, dessen radiales Führungsspiel kleiner als ein Radialspalt zwischen einem zylinderförmigen Teil des sacklochartigen Endabschnitt der Hochdruckbohrung und einem zylinderförmigen Teil des Zapfens der Düsennadel ist. Die permanente Führung der Düsennadel über den wenigstens einen ventilsitznahen Führungsbereich stromaufwärts des Ventilsitzes verhindert eine radiale Auslenkung der Düsennadel und damit die Gefahr des Anschlagens der Düsennadel am Düsenkörper. Auf diese Weise wird der Verschleiß im Übergangsbereich vom Ventilsitz in den sacklochartigen Endabschnitt deutlich gemindert. Zugleich ist der Zapfen der Düsennadel derart ausgebildet dass er mit einem zylinderförmigen Teil des sacklochartigen Endabschnitts drosselbildend zusammenwirkt. Die Drosselbildung ist dabei vom Hub der Düsennadel abhängig, so dass hierüber die Zuströmung zu wenigstens einer Einspritzöffnung steuerbar ist. Zur Sicherstellung, dass die Führung der Düsennadel über den ventilsitznahen Führungsbereich und nicht über den drosselbildenden Radialspalt erfolgt, ist der Radialspalt größer als das radiale Führungsspiel des ventilsitznahen Führungsbereichs stromaufwärts des Ventilsitzes gewählt. Denn der Radialspalt ist zur permanenten Führung der Düsennadel in der Hochdruckbohrung nicht geeignet, da dessen Ausbildung vom Hub der Düsennadel abhängig ist. Eine Führungsfunktion könnte der Radialspalt demnach nur temporär übernehmen. Außerdem wird zur Ausbildung der Drossel zwischen dem zylinderförmigen Teil des sacklochartigen Endabschnitts und dem zylinderförmigen Teil des Zapfens ein Radialspalt kleiner 20 µm, vorzugsweise kleiner 10 µm vorgeschlagen. Damit die Führungsfunktion des ventilsitznahen Führungsbereichs erhalten bleibt, ist dessen radiales Führungsspiel entsprechend kleiner zu wählen. Darüber hinaus sind die wenigstens zwei Einspritzöffnungen in einem axialen Abstand zueinander angeordnet. Das ermöglicht die Ausbildung von wenigstens zwei axial beabstandeten Spritzlochreihen. Die Anordnung der axial beabstandeten Einspritzöffnungen erfolgt bevorzugt in der Weise, dass die Zuströmung von Kraftstoff über den drosselbildenden Radialspalt in Abhängigkeit vom Hub der Düsennadel steuerbar ist. Hierzu können die wenigstens zwei axial beabstandeten Einspritzöffnungen beispielsweise derart angeordnet werden, dass wenigstens eine Einspritzöffnung im Bereich des sacklochartigen Endabschnitts und wenigstens eine weitere Einspritzöffnung im Bereich des kegelförmigen Abschnitts stromabwärts des Ventilsitzes in die Hochdruckbohrung münden. Die wenigstens eine in den sacklochartigen Endabschnitt mündende Einspritzöffnung ist dann über den drosselbildenden Radialspalt steuerbar.The proposed nozzle assembly comprises a nozzle body and a nozzle needle, which is accommodated for releasing and closing at least one injection port in a high-pressure bore of the nozzle body, wherein a in a blind hole-like end portion overflowing conical portion of the high-pressure bore for forming a valve seat with a conical sealing surface of the nozzle needle, to which is a plunged into the blind hole-like end portion pin is attached, sealingly cooperates. According to the invention, a valve seat near guide region upstream of the valve seat between the nozzle needle and the nozzle body is formed for permanent guidance of the nozzle needle in the high pressure bore, whose radial guide clearance smaller than a radial gap between a cylindrical part of the blind hole-like end portion of the high-pressure bore and a cylindrical part of the pin of the nozzle needle. The permanent guidance of the nozzle needle via the at least one valve seat near the guide region upstream of the valve seat prevents a radial deflection of the nozzle needle and thus the risk of striking the nozzle needle on the nozzle body. In this way, the wear in the transition region from the valve seat in the blind hole-like end portion is significantly reduced. At the same time the pin of the nozzle needle is designed so that he a cylindrical part of the blind hole-like end portion cooperating throttle forming. The throttle formation is dependent on the stroke of the nozzle needle, so that over this the inflow to at least one injection port is controllable. To ensure that the leadership of the nozzle needle on the valve seat near the guide area and not via the throttle-forming radial gap, the radial gap is greater than the radial guide clearance of the valve seat near the guide region upstream of the valve seat selected. Because the radial gap is not suitable for permanent guidance of the nozzle needle in the high-pressure bore, since its formation is dependent on the stroke of the nozzle needle. A guiding function could take over the radial gap therefore only temporarily. In addition, to form the throttle between the cylindrical part of the blind-hole-like end portion and the cylindrical part of the pin, a radial gap of less than 20 microns, preferably less than 10 microns is proposed. Thus, the leadership function of the valve seat near guide area is maintained, its radial guide clearance is to be chosen correspondingly smaller. In addition, the at least two injection openings are arranged at an axial distance from one another. This allows the formation of at least two axially spaced spray hole rows. The arrangement of the axially spaced injection openings is preferably carried out in such a way that the inflow of fuel through the throttle-forming radial gap in dependence on the stroke of the nozzle needle is controllable. For this purpose, the at least two axially spaced injection openings can for example be arranged such that at least one injection opening in the region of the blind-hole-like end portion and at least one further injection opening in the region of the conical portion downstream of the valve seat open into the high-pressure bore. The at least one injection opening opening into the blind-hole-like end section is then controllable via the throttle-forming radial gap.

Der Ausbildung eines ventilsitznahen Führungsbereichs steht nicht entgegen, dass in einem axialen Abstand hierzu, d. h. in einem ventilsitzferneren Bereich der Hochdruckbohrung, ein weiterer Führungsbereich zur permanenten Führung der Düsennadel ausgebildet ist, wie dies regelmäßig bei bekannten Düsenbaugruppen für Kraftstoffinjektoren der Fall ist. Durch die Ausbildung eines weiteren ventilsitzfernen Führungsbereichs stromaufwärts des Ventilsitzes kann die Führung der Düsennadel weiter optimiert werden.The formation of a guide region near the valve seat does not preclude that an additional guide region for permanent guidance of the nozzle needle is formed at an axial distance therefrom, ie in a region of the high-pressure bore remote from the valve seat, as is conventionally the case with known nozzle assemblies for fuel injectors. By forming a further valve seat remote guide region upstream of the valve seat, the leadership of the nozzle needle can be further optimized.

Die permanente Führung der Düsennadel über den wenigstens einen ventilsitznahen Führungsbereich wirkt sich nicht nur verschleißverringernd aus, sondern verhindert ferner ein durch eine Desachsierung der Düsennadel bedingtes asymmetrisches Spritzbild. Dies wirkt sich bei Einsatz der Düsenbaugruppe in einem Kraftstoffinjektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine vorteilhaft auf die Schadstoffemissionen der Brennkraftmaschine aus.The permanent guidance of the nozzle needle via the at least one valve seat near guide region not only has a wear-reducing effect, but also prevents an asymmetrical spray pattern caused by a disalignment of the nozzle needle. This has an advantageous effect on the pollutant emissions of the internal combustion engine when using the nozzle assembly in a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine.

Bevorzugt besitzt der Düsenkörper oder die Düsennadel zur Ausbildung des ventilsitznahen Führungsbereichs stromaufwärts des Ventilsitzes wenigstens zwei sich axial erstreckende Führungsrippen, zwischen denen Strömungskanäle ausgebildet werden. Die Strömungskanäle stellen die Zuströmung von Kraftstoff zu der wenigstens einen Einspritzöffnung im Betrieb des Kraftstoffinjektors sicher. Sofern die Führungsrippen am Düsenkörper ausgebildet sind, wirken sie vorzugsweise mit einem zylinderförmigen Schaftabschnitt der Düsennadel spaltbildend zusammen. Die Führungsrippen sind vorzugsweise auf einer die Hochdruckbohrung radial begrenzenden zylinderförmigen Wandungsfläche des Düsenkörpers angeordnet und ragen in die Hochdruckbohrung hinein. Alternativ können die Führungsrippen an der Düsennadel ausgebildet sein und mit einer die Hochdruckbohrung radial begrenzenden zylinderförmigen Wandungsfläche des Düsenkörpers spaltbildend zusammenwirken. Die Führungsrippen können in diesem Fall an einem zylinderförmigen Schaftabschnitt der Düsennadel angeordnet sein, so dass sie in die Hochdruckbohrung hinein ragen.Preferably, the nozzle body or the nozzle needle to form the valve seat near the guide region upstream of the valve seat at least two axially extending guide ribs, between which flow channels are formed. The flow channels ensure the inflow of fuel to the at least one injection port during operation of the fuel injector. If the guide ribs are formed on the nozzle body, they preferably cooperate with a cylindrical shaft portion of the nozzle needle gap-forming. The guide ribs are preferably on a radial wall defining the high-pressure bore cylindrical wall surface of the nozzle body arranged and protrude into the high pressure bore. Alternatively, the guide ribs may be formed on the nozzle needle and cooperate with a high pressure bore radially bounding cylindrical wall surface of the nozzle body gap-forming. The guide ribs can be arranged in this case on a cylindrical shaft portion of the nozzle needle, so that they protrude into the high-pressure bore.

Weiterhin bevorzugt sind die sich axial erstreckenden Führungsrippen zur Ausbildung des ventilsitznahen Führungsbereichs stromaufwärts des Ventilsitzes in gleichem Winkelabstand zueinander angeordnet. Vorzugsweise sind wenigstens drei Führungsrippen in einem Winkelabstand von 120° vorgesehen. Bei vier Führungsrippen beträgt der Winkelabstand 90°, bei fünf Führungsrippen 72° und bei sechs Führungsrippen 60°. Ferner können mehr als sechs Führungsrippen vorgesehen werden, wobei sichergestellt sein muss, dass ausreichend große Strömungskanäle zwischen den Führungsrippen verbleiben. Der gleiche Winkelabstand der Führungsrippen zueinander gewährleistet eine optimale Führung der Düsennadel in der Hochdruckbohrung.Further preferably, the axially extending guide ribs for forming the valve seat near guide region upstream of the valve seat are arranged at the same angular distance from each other. Preferably, at least three guide ribs are provided at an angular distance of 120 °. With four guide ribs the angular distance is 90 °, with five guide ribs 72 ° and with six guide ribs 60 °. Furthermore, more than six guide ribs can be provided, wherein it must be ensured that sufficiently large flow channels remain between the guide ribs. The same angular distance of the guide ribs to each other ensures optimal guidance of the nozzle needle in the high-pressure bore.

Vorteilhafterweise sind mehrere Einspritzöffnungen zur Ausbildung wenigstens einer Spritzlochreihe vorgesehen. Die mehreren Einspritzöffnungen einer Spritzlochreihe sind vorzugsweise in gleichem Winkelabstand zueinander angeordnet, um ein symmetrisches Spritzbild zu erzeugen.Advantageously, a plurality of injection openings are provided for forming at least one spray hole row. The plurality of injection openings of a spray hole row are preferably arranged at equal angular distance from each other to produce a symmetrical spray pattern.

Als weiterbildende Maßnahme wird vorgeschlagen, dass wenigstens zwei Einspritzöffnungen vorgesehen sind, deren Längsachsen gegenüber einer Längsachse A der Hochdruckbohrung unterschiedlich geneigt sind. Durch diese Maßnahme kann das Spritzbild verbessert werden.As a further development measure, it is proposed that at least two injection openings are provided whose longitudinal axes are inclined differently with respect to a longitudinal axis A of the high-pressure bore. By this measure, the spray pattern can be improved.

Zur Lösung der eingangs genannten Aufgabe wird ferner ein Kraftstoffinjektor mit einer erfindungsgemäßen Düsenbaugruppe vorgeschlagen. Die weniger verschleißbehaftete Düsenbaugruppe erhöht die Lebensdauer des Kraftstoffinjektors: Bei Einsatz des Kraftstoffinjektors zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine können zudem die Schadstoffemissionen verringert werden, da die permanente Führung eine radiale Auslenkung der Düsennadel und damit ein asymmetrisches Spritzbild verhindert. Bei dem Kraftstoffinjektor kann es sich insbesondere um einen Kraftstoffinjektor für ein Common-Rail-Einspritzsystem handeln.To solve the above object, a fuel injector is proposed with a nozzle assembly according to the invention further. The less wear-prone nozzle assembly increases the life of the fuel injector: When using the fuel injector for injecting fuel into the combustion chamber of an internal combustion engine, the pollutant emissions can also be reduced because the permanent guide prevents radial deflection of the nozzle needle and thus an asymmetric spray pattern. The fuel injector may in particular be a fuel injector for a common-rail injection system.

Eine bevorzugte Ausführungsform der Erfindung wird nachfolgend anhand der beigefügten Figur näher erläutert. Diese zeigt einen Längsschnitt durch eine erfindungsgemäße Düsenbaugruppe im Bereich eines Ventilsitzes.A preferred embodiment of the invention will be explained in more detail with reference to the accompanying figure. This shows a longitudinal section through a nozzle assembly according to the invention in the region of a valve seat.

Ausführliche Beschreibung der FigurDetailed description of the figure

Die dargestellte Düsenbaugruppe umfasst einen Düsenkörper 1 mit einer Hochdruckbohrung 4, in der eine Düsennadel 2 hubbeweglich aufgenommen ist. Die Hochdruckbohrung 4 weist zur Ausbildung eines Ventilsitzes 7 einen kegelförmigen Abschnitt 6 auf, der in einen sacklochartigen Endabschnitt 5 übergeht, in den wenigstens eine Einspritzöffnung 3 mündet. Eine weitere Einspritzöffnung 3 mündet im kegelförmigen Abschnitt 5 in die Hochdruckbohrung 4. Zum Freigeben und Verschließen der Einspritzöffnungen 3 weist die Düsennadel 2 eine mit dem Ventilsitz 7 dichtend zusammenwirkende kegelförmige Dichtfläche 8 auf, an welche ein Zapfen 9 angesetzt ist. Der Zapfen 9 besitzt einen unmittelbar an die kegelförmige Dichtfläche 8 anschließenden zylinderförmigen Teil, der mit einem zylinderförmigen Teil des sacklochartigen Endabschnitts 5 - in Abhängigkeit vom Hub der Düsennadel 2 - einen Radialspalt 11 ausbildend zusammenwirkt. Der Radialspalt 11 besitzt eine Drosselfunktion, um die Zuströmung von Kraftstoff zu der Einspritzöffnung 3 zu steuern, die in den sacklochartigen Endabschnitt 5 der Hochdruckbohrung 4 mündet. Dies hat zur Folge, das in einer ersten Phase des Öffnungshubes der Düsennadel 2 die Einspritzung vorrangig über die Einspritzöffnung 3 erfolgt, die in den kegelförmigen Abschnitt 6 der Hochdruckbohrung 4 mündet. Erst in einer zweiten Phase des Öffnungshubes wird die Drosselfunktion des Radialspalts 11 aufgehoben, da der zylinderförmige Teil des Zapfens 9 oberhalb des zylinderförmigen Teils des sacklochartigen Endabschnitts 5 der Hochdruckbohrung 4 zu liegen kommt. Dem zylinderförmigen Teil des sacklochartigen Endabschnitts 5 liegt dann ein kegelstumpfförmiger Teil des Zapfens 9 gegenüber, dessen Aufgabe es ist, das im sacklochartigen Endabschnitt 5 verbleibende Schadvolumen in Schließstellung der Düsennadel 2 zu verringern.The nozzle assembly shown comprises a nozzle body 1 with a high-pressure bore 4, in which a nozzle needle 2 is received in a liftable manner. The high-pressure bore 4 has, to form a valve seat 7, a conical section 6, which merges into a blind-hole-like end section 5, into which at least one injection opening 3 opens. A further injection opening 3 opens into the conical section 5 into the high-pressure bore 4. In order to release and close the injection openings 3, the nozzle needle 2 has a conical sealing surface 8 sealingly cooperating with the valve seat 7 a pin 9 is attached. The pin 9 has a directly adjacent to the conical sealing surface 8 cylindrical part which cooperates with a cylindrical portion of the blind hole-like end portion 5 - in response to the stroke of the nozzle needle 2 - forming a radial gap 11. The radial gap 11 has a throttle function to control the inflow of fuel to the injection port 3, which opens into the blind-hole-like end portion 5 of the high-pressure bore 4. This has the consequence that in a first phase of the opening stroke of the nozzle needle 2, the injection takes place primarily via the injection port 3, which opens into the conical portion 6 of the high-pressure bore 4. Only in a second phase of the opening stroke, the throttle function of the radial gap 11 is repealed, since the cylindrical part of the pin 9 above the cylindrical portion of the blind-hole-like end portion 5 of the high-pressure bore 4 comes to rest. The cylindrical part of the blind-hole-like end portion 5 is then opposite to a frustoconical part of the pin 9, the object of which is to reduce the dead volume remaining in the blind hole-like end portion 5 in the closed position of the nozzle needle 2.

Um beim Schließen der Düsennadel 2, d. h. beim vollständigen Wiedereintauchen des Zapfens 9 in den sacklochartigen Endabschnitt 5 der Hochdruckbohrung 4, ein Anschlagen des Zapfens 9 am Düsenkörper 1 zu verhindern, weist die dargestellte Düsenbaugruppe einen ventilsitznahen Führungsbereich 10 stromaufwärts der Ventilsitzes 7 auf. Der Führungsbereich 10 wird durch mehrere, sich axial erstreckende Führungsrippen 12 des Düsenkörpers 1 ausgebildet, die mit einem zylinderförmigen Schaftabschnitt der Düsennadel 2 spaltbildend zusammenwirken. Die Führungsrippen 12 ragen hierzu von einer zylinderförmigen Wandungsfläche des Düsenkörpers 1 zur radialen Begrenzung der Hochdruckbohrung 4 in die Hochdruckbohrung 4 hinein. Vorliegend sind vier Führungsrippen 12 in einem Winkelabstand von jeweils 90° vorgesehen, wobei zwischen den Führungsrippen 12 sich axial erstreckende Strömungskanäle ausgebildet werden, welche die Zuströmung von Kraftstoff zu den Einspritzöffnungen 3 sicherstellen. Der Führungsbereich 10 stellt eine permanente Führung der Düsennadel 2 in der Hochdruckbohrung 4 unabhängig vom Hub der Düsennadel 2 sicher. Dadurch ist gewährleistet, dass die Düsennadel 2 keine radiale Auslenkung erfährt, welche zum Anschlagen des Zapfens 9 am Düsenkörper 1 führen könnte. Um zu verhindern, dass der Radialspalt 11 stromabwärts des Ventilsitzes 7 - zumindest zeitweise - ebenfalls eine Führungsfunktion übernimmt, ist der Radialspalt 11 größer als das radiale Führungsspiel des ventilsitznahen Führungsbereichs 10 gewählt.In order to prevent striking of the pin 9 on the nozzle body 1 when closing the nozzle needle 2, ie the complete re-immersion of the pin 9 in the blind hole-like end portion 5 of the high-pressure bore 4, the nozzle assembly shown has a valve seat near guide portion 10 upstream of the valve seat 7. The guide region 10 is formed by a plurality of axially extending guide ribs 12 of the nozzle body 1, which cooperate with a cylindrical shaft portion of the nozzle needle 2 forming a gap. For this purpose, the guide ribs 12 protrude from a cylindrical wall surface of the nozzle body 1 to the radial boundary of the high-pressure bore 4 into the high-pressure bore 4. In the present case four guide ribs 12 are provided at an angular distance of 90 °, wherein between the guide ribs 12 axially extending flow channels are formed, which ensure the inflow of fuel to the injection openings 3. The guide region 10 ensures a permanent guidance of the nozzle needle 2 in the high-pressure bore 4 independently of the stroke of the nozzle needle 2. This ensures that the nozzle needle 2 undergoes no radial deflection, which could lead to the striking of the pin 9 on the nozzle body 1. To prevent the radial gap 11 downstream of the valve seat 7 - at least temporarily - also assumes a leadership function, is the Radial gap 11 greater than the radial guide clearance of the valve seat near the guide region 10 is selected.

Ein weiterer Vorteil der permanenten Führung der Düsennadel 2 über den ventilsitznahen Führungsbereich 10 ist darin zu sehen, dass ein mit einer Desachsierung der Düsennadel 2 einhergehendes asymmetrisches Spritzbild verhindert wird. Dies wirkt sich bei Einsatz der Düsenbaugruppe in einem Kraftstoffinjektor zur Einspritzung von Kraftstoff in den Brennraum einer Brennkraftmaschine günstig auf die Schadstoffemissionen aus. Das heißt, dass die Schadstoffemissionen verringert werden.Another advantage of the permanent guidance of the nozzle needle 2 via the valve seat near guide region 10 is the fact that an asymmetric spray pattern associated with a desalination of the nozzle needle 2 is prevented. This has a favorable effect on the pollutant emissions when using the nozzle assembly in a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine. This means that pollutant emissions are reduced.

Die Erfindung ist nicht auf die dargestellte bevorzugte Ausführungsform beschränkt. Abwandlungen sind möglich, die insbesondere die Anzahl, die Anordnung und konkrete Ausgestaltung der Führungsrippen 12 zur Ausbildung des Führungsbereichs 10 betreffen. Beispielsweise können die Führungsrippen 12 auch an der Düsennadel 2 ausgebildet sein. Ferner ist die Anzahl, die Anordnung und die konkrete Ausgestaltung der vorzugsweise mehreren Einspritzöffnungen 3 frei wählbar.The invention is not limited to the illustrated preferred embodiment. Modifications are possible, which relate in particular to the number, arrangement and specific design of the guide ribs 12 for forming the guide region 10. For example, the guide ribs 12 may also be formed on the nozzle needle 2. Furthermore, the number, the arrangement and the specific configuration of preferably a plurality of injection openings 3 are freely selectable.

Claims (6)

  1. Nozzle assembly for a fuel injector, comprising a nozzle body (1) and a nozzle needle (2) which, for the purposes of opening up and closing at least one injection opening (3), is received, such that it can perform stroke movements, in a high-pressure bore (4) of the nozzle body (1), wherein a conical section (6), which transitions into a blind-hole-like end section (5), of the high-pressure bore (4) interacts sealingly, in order to form a valve seat (7), with a conical sealing surface (8) of the nozzle needle (2), which conical sealing surface is adjoined by a peg (9) which can protrude into the blind-hole-like end section (5), wherein, for the permanent guidance of the nozzle needle (2) in the high-pressure bore (4), a guide region (10) close to the valve seat is formed, upstream of the valve seat (7), between the nozzle needle (2) and the nozzle body (1), the radial guide clearance of which guide region is smaller than a radial gap (11) between a cylindrical part of the blind-hole-like end section (5) of the high-pressure bore (4) and a cylindrical part of the peg (9) of the nozzle needle (2), wherein the peg (9) of the nozzle needle (2) interacts, so as to form a throttle, with the cylindrical part of the blind-hole-like end section (5), and here, the formation of a throttle is dependent on the stroke of the nozzle needle (2), characterized in that the radial gap (11) is smaller than 20 µm, preferably smaller than 10 µm, and in that at least two injection openings (3) are provided which are arranged with an axial spacing to one another, wherein at least one injection opening (3) opens into the high-pressure bore (4) in the region of the blind-hole-like end section (5) and at least one further injection opening (3) opens into the high-pressure bore (4) in the region of the conical section (6) downstream of the valve seat (7).
  2. Nozzle assembly according to Claim 1, characterized in that, for the purposes of forming the guide region (10) close to the valve seat, the nozzle body (1) or the nozzle needle (2) has, upstream of the valve seat (7), at least two axially extending guide ribs (12) between which flow ducts are formed.
  3. Nozzle assembly according to Claim 2, characterized in that the axially extending guide ribs (12) for the purposes of forming the guide region (10) close to the valve seat are arranged at uniform angular intervals with respect to one another upstream of the valve seat (7).
  4. Nozzle assembly according to one of the preceding claims, characterized in that multiple injection openings (3) are provided for forming at least one spray hole row, wherein the multiple injection openings (3) of a spray hole row are preferably arranged at uniform angular intervals with respect to one another.
  5. Nozzle assembly according to one of the preceding claims, characterized in that at least two injection openings (3) are provided, the longitudinal axes of which are inclined differently relative to a longitudinal axis (A) of the high-pressure bore (4).
  6. Fuel injector having a nozzle assembly according to one of the preceding claims.
EP14720622.1A 2013-06-25 2014-04-30 Nozzle assembly for a fuel injector, and fuel injector Active EP3014104B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013212142.3A DE102013212142A1 (en) 2013-06-25 2013-06-25 Nozzle assembly for a fuel injector and fuel injector
PCT/EP2014/058928 WO2014206610A1 (en) 2013-06-25 2014-04-30 Nozzle assembly for a fuel injector, and fuel injector

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EP3014104A1 EP3014104A1 (en) 2016-05-04
EP3014104B1 true EP3014104B1 (en) 2017-06-14

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DE (1) DE102013212142A1 (en)
WO (1) WO2014206610A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018206101A1 (en) * 2018-04-20 2019-10-24 Robert Bosch Gmbh Nozzle assembly for a fuel injector, fuel injector
DE102019210631A1 (en) * 2019-07-18 2021-01-21 Robert Bosch Gmbh Fuel injector for internal combustion engines

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2050592A5 (en) * 1969-06-18 1971-04-02 Ffsa
IT1167325B (en) * 1983-04-11 1987-05-13 Roberto Bosio PULVERIZER FOR DIESEL ENGINE FUEL INJECTORS
EP0283154A1 (en) * 1987-03-14 1988-09-21 LUCAS INDUSTRIES public limited company Fuel injection nozzle
DE19642513A1 (en) * 1996-10-15 1998-04-16 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE10207189A1 (en) * 2001-03-03 2002-09-12 Fev Motorentech Gmbh Switchable injection device for injecting different fuel quantities, has nozzle holes in only a first plane or in two planes exposed to fuel depending on the valve needle's stroke
DE10348928A1 (en) * 2003-10-18 2005-05-12 Bosch Gmbh Robert Fuel injection device for automobile internal combustion engine has throttle in path of fuel to injection opening for reducing force acting on jet needle in opening direction
DE202006007883U1 (en) * 2006-05-17 2006-10-19 Robert Bosch Gmbh Fuel injector for internal combustion engine, has two guides arranged at two sides that are turned towards and away of injection opening, respectively, where ratio of length in relation to diameter of each guide lies in specific range
DE102008039920A1 (en) 2008-08-27 2010-03-04 Continental Automotive Gmbh Nozzle body, nozzle assembly and fuel injector, and method of making a nozzle body
DE102011076665A1 (en) * 2011-05-30 2012-12-06 Robert Bosch Gmbh Nozzle assembly for a fuel injector and fuel injector

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DE102013212142A1 (en) 2015-01-08
EP3014104A1 (en) 2016-05-04

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