EP2387661B1 - Fuel injector for internal combustion engines - Google Patents

Fuel injector for internal combustion engines Download PDF

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Publication number
EP2387661B1
EP2387661B1 EP09753107A EP09753107A EP2387661B1 EP 2387661 B1 EP2387661 B1 EP 2387661B1 EP 09753107 A EP09753107 A EP 09753107A EP 09753107 A EP09753107 A EP 09753107A EP 2387661 B1 EP2387661 B1 EP 2387661B1
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EP
European Patent Office
Prior art keywords
nozzle needle
annular
fuel injector
pressure chamber
injector according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP09753107A
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German (de)
French (fr)
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EP2387661A1 (en
Inventor
Wilhelm Christ
Thilo Kreher
Gerhard Suenderhauf
Andreas Koeninger
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP2387661A1 publication Critical patent/EP2387661A1/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
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/022—Mechanically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • 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
    • F02M61/161—Means for adjusting injection-valve lift
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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 fuel injector for internal combustion engines with the features of the preamble of claim 1.
  • Such a fuel injector is out DE 10 2006 036 447 A1 known.
  • This fuel injector has a so-called leak-free nozzle needle, which is surrounded over the entire length of an annular pressure chamber in which the system pressure of the Commen-Rails is applied.
  • the pressure chamber is divided into two partial pressure chambers with a nozzle needle seat remote storage pressure chamber and a nozzle needle near the nozzle needle pressure chamber, the nozzle needle remote storage pressure chamber forms the larger volume. Between both pressure chambers there is a hydraulic connection. Due to the fact that all pressure surfaces of the nozzle needle are exposed to the system pressure, no pressure stage is present, which ensures a fast closing of the nozzle needle.
  • it is provided to connect the storage pressure chamber and the nozzle needle pressure chamber via a hydraulic closing throttle, so that when the nozzle needle is open there is a pressure difference between the two pressure chambers, which ensures a fast closing of the nozzle needle.
  • a hydraulic throttle element is also in the document DE10149961 A to see at the nozzle needle.
  • Object of the present invention is to carry out a hydraulic throttle element between the accumulator pressure chamber and the nozzle needle pressure chamber, which places lower demands on the manufacturing tolerances.
  • the object of the invention is achieved with the characterizing measures of claim 1.
  • a hydraulic throttling to form a closing force acting on the nozzle needle, which has a lower sensitivity in terms of the gap width of the gap throttle in the overall effect.
  • This makes it possible to dimension the gap width at the individual annular gap throttle elements larger, whereby the demands on the manufacturing accuracy can be reduced.
  • the sensitivity to entrained particles in the fuel is reduced.
  • FIG. 1 shows a fuel injector with a housing 10, which is composed for example of an injector body 11 and a nozzle body 12.
  • a nozzle needle 15 is longitudinally displaceably arranged in a pressure chamber 16, which is driven for example by an electromagnetic control valve 30.
  • injection nozzles 13 are provided, is injected via the fuel into the combustion chamber of an internal combustion engine.
  • the nozzle needle 15 has a nozzle needle seat near portion 17 and a nozzle needle seat remote piston portion 18, wherein the piston portion 18 is guided hydraulically tight in a guide bore 19 of a valve member 20.
  • a control chamber 21 is formed, to which the piston portion 18 of the nozzle needle 15 is exposed to a pressure surface.
  • the nozzle needle 15 has a sealing surface which presses against a formed on the nozzle body 12 nozzle needle seat 14.
  • a closing spring 29 acting on the nozzle needle 15 ensures that the nozzle needle 15 remains in the nozzle needle seat 14 when the engine is switched off.
  • a guide bore 22 is formed, in which the nozzle needle 15 is guided with a guide portion 23 in addition to the guide bore 19 in the valve piece 20 nozzle needle seat close.
  • the guide portion 23 is provided with flats 24 which form a substantially unthrottled hydraulic connection between the adjacent pressure chambers.
  • the nozzle needle 15 in the region of the nozzle needle seat near portion 17 has a smaller diameter, so that between the nozzle body 12 and Nozzle needle seat near section 17 forms an annular space, which is referred to as nozzle needle pressure chamber 25.
  • the nozzle needle 15 is also surrounded by an annular space which has a larger volume than the nozzle needle pressure chamber 25 and which is referred to as storage pressure chamber 26.
  • Nozzle needle pressure chamber 25 and accumulator pressure chamber 26 together form the pressure chamber 16.
  • the storage pressure chamber 26 performs a high-pressure supply line 27, which connects the storage pressure chamber 26 with the designed as a common rail high-pressure accumulator 28.
  • the system pressure of the common rail 28 is present in the accumulator pressure chamber 26.
  • From the storage pressure chamber 26 performs an inlet bore 32 with an inlet throttle into the control chamber 21.
  • From the control chamber 21 performs a drain hole 33 with an outlet throttle in a valve chamber 34.
  • the valve chamber 34 is connected via a valve seat 35 with a low-pressure chamber 36 connected to a low-pressure return line 39 is connected.
  • a valve sleeve 38 of a magnet armature 51 of the control valve 30 acts.
  • the control valve 30 is actuated, whereby the armature 51 lifts the valve sleeve 38 from the valve seat 35, so that the valve chamber 34 is hydraulically connected to the low-pressure chamber 36.
  • the control chamber 21 is depressurized and the force acting on the nozzle needle 15 in the nozzle needle pressure chamber 25 opening force exceeds the voltage applied in the control chamber 21 closing force.
  • the solenoid of the control valve 30 is deactivated, the hydraulic connection between the low-pressure chamber 36 and the valve chamber 34 is closed again by closing the valve seat 35 and the control chamber 21 is filled via the inlet bore 23.
  • the pressure in the control chamber 21 increases and the nozzle needle 15 is again placed in the nozzle needle seat 14.
  • a hydraulic throttle element 40 is arranged between the storage pressure chamber 26 and the nozzle needle pressure chamber 25, a hydraulic throttle element 40 is arranged.
  • the hydraulic throttle element 40 is at least two in the flow direction of the fuel in series lying gap throttle elements 41.1 to 41.n formed.
  • the hydraulic throttle element 40 In the embodiment in FIG. 1 and 2 form two gap throttles 41.1 and 41.2, the hydraulic throttle element 40.
  • the two gap throttling elements 41.1, 41.2 are formed on the nozzle needle seat near portion 17 of the nozzle needle 15 each as an annular collar 44.
  • Each annular collar 44 has a narrow cylindrical peripheral surface 45 and a first annular surface 46 and a second annular surface 47.
  • the annular surfaces 46, 47 may be designed to be flat or inclined.
  • a circumferential annular gap s is formed between the peripheral surfaces 45 of each annular collar 40 and an inner wall 49 of the nozzle body 12.
  • a circumferential annular gap s is formed between the peripheral surfaces 45 of each annular collar 40 and an inner wall 49 of the nozzle body 12.
  • Fig. 2 is the annular gap s in the two gap throttle elements 41.1 and 41.2 the same size. But it is also possible to place the gap throttling elements 41.1, 41.2 on the nozzle needle 15 so that the annular gap s between the peripheral surfaces 45 and an inner wall on the injector body 11 is formed.
  • annular gap throttling elements 41.1 to 41.4 which - as in the embodiment in Fig. 2 - Are each formed by a collar 44.
  • the annular collars 44 form with their respective peripheral surfaces 45 to the inner wall 49 of the nozzle body 12, the annular gap s, which is dimensioned substantially equal for all gap throttle element 41.1 to 41.4.
  • the annular gap s between the peripheral surfaces 45 and an inner wall on the injector 11 may be formed.
  • Fig. 4 are also four annular gap throttles 41.1 to 41.4 formed on the nozzle needle 15, in which the annular collars 44 have a decreasing in the flow direction of the fuel diameter d2.1 to d2.4.
  • the nozzle body 12 is designed in this embodiment with a corresponding to the different diameters d2.1 to d2.4 the various annular collars 44 corresponding stepped inner wall 50, so that between the stepped inner wall 50 and the respective peripheral surfaces 45 of the annular collars 44 each have an annular gap s1 to s4 forms, wherein the annular gaps s1 to s4 are dimensioned substantially equal.
  • the annular gap throttling elements 41.1 to 41.4 form a cascade-shaped fuel Step maze off.
  • the step-shaped inner wall 50 can also be formed on the injector body 11.
  • FIG. 5 and 6 is a nozzle body side section of a fuel injector according to further embodiments, in which the nozzle needle 15 has a shorter longitudinal extent than in the embodiment according to Fig. 1 and the control chamber 21 is delimited by a piston chamber portion 18 longitudinally displaceable control chamber sleeve 51.
  • the control chamber sleeve 51 is pressed by means of a compression spring 52 against an end face of a further Injektor stressesteils 53, which is formed for example by a throttle plate with not shown, leading into the control chamber 21 inlet and outlet throttles.
  • the nozzle needle guide 23 is formed in the vicinity of the nozzle needle seat 14.
  • the annular gap throttling elements 41.1 to 41.n are - as in the embodiment in FIG Fig. 1 - In the flow direction of the fuel upstream of the nozzle needle guide 23 is arranged.
  • Fig. 6 is next to the nozzle needle seat near nozzle needle guide 23 a spaced therefrom further nozzle needle guide 55 is provided with further flats 56, which also form a substantially unthrottled hydraulic connection.
  • the annular gap throttles 41.1 to 41.n are in this embodiment between the two nozzle needle guides 23 and 55th

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

Description

Die Erfindung betrifft einen Kraftstoffinjektor für Brennkraftmaschinen mit den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to a fuel injector for internal combustion engines with the features of the preamble of claim 1.

Stand der TechnikState of the art

Ein derartiger Kraftstoffinjektor ist aus DE 10 2006 036 447 A1 bekannt. Dieser Kraftstoffinjektor weist eine sogenannte leckagefreie Düsennadel auf, die über die gesamte Länge von einem ringförmigen Druckraum umgeben ist, in dem der Systemdruck des Commen-Rails anliegt. Der Druckraum ist dabei in zwei Teildruckräume mit einem düsennadelsitzfernen Speicherdruckraum und einem düsennadelsitznahen Düsennadeldruckraum aufgeteilt, wobei der düsennadelsitzferne Speicherdruckraum das größere Volumen bildet. Zwischen beiden Druckräumen ist eine hydraulische Verbindung vorhanden. Dadurch, dass alle Druckflächen der Düsennadel dem Systemdruck ausgesetzt sind, ist auch keine Druckstufe vorhanden, die für ein schnelles Schließen der Düsennadel sorgt. Dazu ist vorgesehen, den Speicherdruckraum und den Düsennadeldruckraum über eine hydraulische Schließdrossel zu verbinden, so dass bei geöffneter Düsennadel zwischen beiden Druckräumen eine Druckdifferenz vorliegt, die für ein schnelles Schließen der Düsennadel sorgt.Such a fuel injector is out DE 10 2006 036 447 A1 known. This fuel injector has a so-called leak-free nozzle needle, which is surrounded over the entire length of an annular pressure chamber in which the system pressure of the Commen-Rails is applied. The pressure chamber is divided into two partial pressure chambers with a nozzle needle seat remote storage pressure chamber and a nozzle needle near the nozzle needle pressure chamber, the nozzle needle remote storage pressure chamber forms the larger volume. Between both pressure chambers there is a hydraulic connection. Due to the fact that all pressure surfaces of the nozzle needle are exposed to the system pressure, no pressure stage is present, which ensures a fast closing of the nozzle needle. For this purpose, it is provided to connect the storage pressure chamber and the nozzle needle pressure chamber via a hydraulic closing throttle, so that when the nozzle needle is open there is a pressure difference between the two pressure chambers, which ensures a fast closing of the nozzle needle.

Zur hydraulischen Drosselung der hydraulischen Verbindung zwischen dem Speicherdruckraum und dem Düsennadeldruckraum wurde in der DE-Patentanmeldung 10 2007 032 741.4 bereits vorgeschlagen, an der Düsennadel zwischen den beiden Druckräumen einen umlaufenden Ringbund auszuführen, der einen Ringspalt um die Düsennadel bildet, der als sogenannte Ringspaltdrossel wirkt. Damit die Drosselwirkung die erforderliche Schließkraft bewirkt, ist eine sehr kleine Spaltweite der Ringspaltdrossel notwendig. Um die Spaltweite geometrisch zu definieren, sind übliche Anforderungen hinsichtlich der Toleranz an Düsenkörper und Düsennadel notwendig.For hydraulic throttling of the hydraulic connection between the accumulator pressure chamber and the nozzle needle pressure chamber was in the DE patent application 10 2007 032 741.4 already proposed to perform on the nozzle needle between the two pressure chambers a circumferential annular collar which forms an annular gap around the nozzle needle, which acts as a so-called annular gap throttle. So that the throttling effect causes the required closing force, a very small gap width of the annular gap throttle is necessary. To the To define gap width geometrically, usual requirements with regard to the tolerance to the nozzle body and nozzle needle are necessary.

Ein hydraulisches Drosselelement ist auch beim Dokument DE10149961 A an der Düsennadel zu sehen.A hydraulic throttle element is also in the document DE10149961 A to see at the nozzle needle.

Aufgabe der vorliegenden Erfindung ist es, ein hydraulisches Drosselelement zwischen dem Speicherdruckraum und dem Düsennadeldruckraum auszuführen, das geringere Anforderungen an die Fertigungstoleranzen stellt.Object of the present invention is to carry out a hydraulic throttle element between the accumulator pressure chamber and the nozzle needle pressure chamber, which places lower demands on the manufacturing tolerances.

Offenbarung der ErfindungDisclosure of the invention

Die Aufgabe der Erfindung wird mit den kennzeichnenden Maßnahmen des Anspruchs 1 gelöst. Durch die Ausbildung von mindestens zwei in Strömungsrichtung des zugeführten Kraftstoffs hintereinander liegenden Ringspaltdrosselelementen ist es möglich, ein hydraulische Drosselung zur Ausbildung einer auf die Düsennadel wirkenden Schließkraft zu realisieren, die in der Gesamtwirkung eine geringere Sensitivität hinsichtlich der Spaltweite der Spaltdrossel aufweist. Dadurch ist es möglich, die Spaltweite an den einzelnen Ringspaltdrosselelementen größer zu dimensionieren, wodurch die Anforderungen an die Fertigungsgenauigkeit reduziert werden kann. Zusätzlich wird wegen der größeren Spaltweiten an den einzelnen Ringspaltdrosselelementen die Empfindlichkeit gegenüber im Kraftstoff mitgeführten Partikeln reduziert.The object of the invention is achieved with the characterizing measures of claim 1. By forming at least two annular gap throttling elements arranged one behind the other in the flow direction of the supplied fuel, it is possible to realize a hydraulic throttling to form a closing force acting on the nozzle needle, which has a lower sensitivity in terms of the gap width of the gap throttle in the overall effect. This makes it possible to dimension the gap width at the individual annular gap throttle elements larger, whereby the demands on the manufacturing accuracy can be reduced. In addition, due to the larger gap widths at the individual annular gap throttle elements, the sensitivity to entrained particles in the fuel is reduced.

Vorteilhafte Weiterbildungen der Erfindung sind durch die Maßnahmen der Unteransprüche möglich.Advantageous developments of the invention are possible by the measures of the subclaims.

Ausführungsbeispieleembodiments

Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert.Embodiments of the invention are illustrated in the drawings and explained in more detail in the following description.

Es zeigen:

Fig. 1
eine Schnittdarstellung durch einen Kraftstoffinjektor gemäß einem ersten Ausführungsbeispiel,
Fig. 2
einen vergrößerten Ausschnitt X von Figur 1 gemäß einer ersten Ausführungsform eines hydraulischen Drosselelements ,
Fig. 3
eine zweite Ausführungsform eines hydraulischen Drosselelements im Teilschnitt,
Fig. 4
eine dritte Ausführungsform eines hydraulischen Drosselelements im Teilschnitt,
Fig. 5
eine Schnittdarstellung durch einen düsennadelseitigen Abschnitt eines Kraftstoffinjektkors gemäß einem zweiten Ausführungsbeispiel und
Fig. 6
eine Schnittdarstellung durch einen düsennadelseitigen Abschnitt eines Kraftstoffinjektors gemäß einem dritten Ausführungsbeispiel.
Show it:
Fig. 1
a sectional view through a fuel injector according to a first embodiment,
Fig. 2
an enlarged section X of FIG. 1 according to a first embodiment of a hydraulic throttle element,
Fig. 3
a second embodiment of a hydraulic throttle element in partial section,
Fig. 4
a third embodiment of a hydraulic throttle element in partial section,
Fig. 5
a sectional view through a nozzle needle side portion of a Kraftstoffinjektkors according to a second embodiment and
Fig. 6
a sectional view through a nozzle needle side portion of a fuel injector according to a third embodiment.

Figur 1 zeigt einen Kraftstoffinjektor mit einem Gehäuse 10, das beispielsweise aus einem Injektorkörper 11 und einem Düsenkörper 12 zusammengesetzt ist. Im Gehäuse 10 ist in einem Druckraum 16 eine Düsennadel 15 längsverschiebbar angeordnet, die beispielsweise von einem elektromagnetischen Steuerventil 30 angesteuert wird. Im Düsenkörper 12 sind Einspritzdüsen 13 vorhanden, über die Kraftstoff in den Brennraum einer Brennkraftmaschine eingespritzt wird. FIG. 1 shows a fuel injector with a housing 10, which is composed for example of an injector body 11 and a nozzle body 12. In the housing 10, a nozzle needle 15 is longitudinally displaceably arranged in a pressure chamber 16, which is driven for example by an electromagnetic control valve 30. In the nozzle body 12 injection nozzles 13 are provided, is injected via the fuel into the combustion chamber of an internal combustion engine.

Die Düsennadel 15 weist einen düsennadelsitznahen Abschnitt 17 und einen düsennadelsitzfernen Kolbenabschnitt 18 auf, wobei der Kolbenabschnitt 18 in einer Führungsbohrung 19 eines Ventilstücks 20 hydraulisch dicht geführt ist. Im Ventilstück 20 ist ein Steuerraum 21 ausgebildet, dem der Kolbenabschnitt 18 der Düsennadel 15 mit einer Druckfläche ausgesetzt ist. Am düsennadelsitznahen Abschnitt 17 weist die Düsennadel 15 eine Dichtfläche auf, die gegen eine am Düsenkörper 12 ausgebildeten Düsennadelsitz 14 drückt. Eine auf die Düsennadel 15 wirkende Schließfeder 29 sorgt dafür, dass die Düsennadel 15 bei abgestellten Motor im Düsennadelsitz 14 bleibt.The nozzle needle 15 has a nozzle needle seat near portion 17 and a nozzle needle seat remote piston portion 18, wherein the piston portion 18 is guided hydraulically tight in a guide bore 19 of a valve member 20. In the valve piece 20, a control chamber 21 is formed, to which the piston portion 18 of the nozzle needle 15 is exposed to a pressure surface. At the nozzle needle seat near section 17, the nozzle needle 15 has a sealing surface which presses against a formed on the nozzle body 12 nozzle needle seat 14. A closing spring 29 acting on the nozzle needle 15 ensures that the nozzle needle 15 remains in the nozzle needle seat 14 when the engine is switched off.

Im Düsenkörper 12 ist eine Führungsbohrung 22 ausgebildet, in der die Düsennadel 15 mit einem Führungsabschnitt 23 zusätzlich zur Führungsbohrung 19 im Ventilstück 20 düsennadelsitznah geführt ist. Der Führungsabschnitt 23 ist mit Abflachungen 24 versehen, die eine im Wesentlichen ungedrosselte hydraulische Verbindung zwischen den benachbarten Druckräumen ausbilden. Zwischen Düsennadelbohrung 22 und Düsennadelsitz 14 weist die Düsennadel 15 im Bereich des düsennadelsitznahen Abschnitts 17 einen geringeren Durchmesser auf, so dass sich zwischen Düsenkörper 12 und düsennadelsitznahen Abschnitt 17 ein Ringraum ausbildet, der als Düsennadeldruckraum 25 bezeichnet wird.In the nozzle body 12, a guide bore 22 is formed, in which the nozzle needle 15 is guided with a guide portion 23 in addition to the guide bore 19 in the valve piece 20 nozzle needle seat close. The guide portion 23 is provided with flats 24 which form a substantially unthrottled hydraulic connection between the adjacent pressure chambers. Between the nozzle needle bore 22 and nozzle needle seat 14, the nozzle needle 15 in the region of the nozzle needle seat near portion 17 has a smaller diameter, so that between the nozzle body 12 and Nozzle needle seat near section 17 forms an annular space, which is referred to as nozzle needle pressure chamber 25.

Am düsennadelsitzfernen Kolbenabschnitt 18 ist die Düsennadel 15 ebenfalls von einem Ringraum umgeben, welcher ein größeres Volumen als der Düsennadeldruckraum 25 besitzt und welcher als Speicherdruckraum 26 bezeichnet wird. Düsennadeldruckraum 25 und Speicherdruckraum 26 bilden zusammen den Druckraum 16.At nozzle needle remote piston portion 18, the nozzle needle 15 is also surrounded by an annular space which has a larger volume than the nozzle needle pressure chamber 25 and which is referred to as storage pressure chamber 26. Nozzle needle pressure chamber 25 and accumulator pressure chamber 26 together form the pressure chamber 16.

In den Speicherdruckraum 26 führt eine Hochdruckzuleitung 27, die den Speicherdruckraum 26 mit dem als Common-Rail ausgeführten Hochdruckspeicher 28 verbindet. Dadurch liegt im Speicherdruckraum 26 der Systemdruck des Common-Rails 28 an. Vom Speicherdruckraum 26 führt eine Zulaufbohrung 32 mit einer Zulaufdrossel in den Steuerraum 21. Vom Steuerraum 21 führt eine Ablaufbohrung 33 mit einer Ablaufdrossel in eine Ventilkammer 34. Die Ventilkammer 34 ist über einen Ventilsitz 35 mit einem Niederdruckraum 36 verbindbar, der an eine Niederdruck-Rücklaufleitung 39 angeschlossen ist. Auf den Ventilsitz 36 wirkt eine Ventilhülse 38 eines Magnetankers 51 des Steuerventils 30.In the storage pressure chamber 26 performs a high-pressure supply line 27, which connects the storage pressure chamber 26 with the designed as a common rail high-pressure accumulator 28. As a result, the system pressure of the common rail 28 is present in the accumulator pressure chamber 26. From the storage pressure chamber 26 performs an inlet bore 32 with an inlet throttle into the control chamber 21. From the control chamber 21 performs a drain hole 33 with an outlet throttle in a valve chamber 34. The valve chamber 34 is connected via a valve seat 35 with a low-pressure chamber 36 connected to a low-pressure return line 39 is connected. On the valve seat 36, a valve sleeve 38 of a magnet armature 51 of the control valve 30 acts.

Zum Öffnen der Düsennadel 15 wird das Steuerventil 30 angesteuert, wodurch der Magnetanker 51 die Ventilhülse 38 vom Ventilsitz 35 abhebt, so dass die Ventilkammer 34 mit dem Niederdruckraum 36 hydraulisch verbunden wird. Dadurch wird der Steuerraum 21 druckentlastet und die auf die Düsennadel 15 im Düsennadeldruckraum 25 wirkende Öffnungskraft übersteigt die im Steuerraum 21 anliegende Schließkraft. Wird der Elektromagnet des Steuerventils 30 deaktiviert, wird die hydraulische Verbindung zwischen Niederdruckraum 36 und Ventilkammer 34 durch Schließen des Ventilsitzes 35 wieder geschlossen und der Steuerraum 21 wird über die Zulaufbohrung 23 befüllt. Dadurch steigt der Druck im Steuerraum 21 an und die Düsennadel 15 wird wieder in den Düsenadelsitz 14 gestellt.To open the nozzle needle 15, the control valve 30 is actuated, whereby the armature 51 lifts the valve sleeve 38 from the valve seat 35, so that the valve chamber 34 is hydraulically connected to the low-pressure chamber 36. As a result, the control chamber 21 is depressurized and the force acting on the nozzle needle 15 in the nozzle needle pressure chamber 25 opening force exceeds the voltage applied in the control chamber 21 closing force. If the solenoid of the control valve 30 is deactivated, the hydraulic connection between the low-pressure chamber 36 and the valve chamber 34 is closed again by closing the valve seat 35 and the control chamber 21 is filled via the inlet bore 23. As a result, the pressure in the control chamber 21 increases and the nozzle needle 15 is again placed in the nozzle needle seat 14.

Zwischen dem Speicherdruckraum 26 und dem Düsennadeldruckraum 25 ist ein hydraulisches Drosselelement 40 angeordnet. Das hydraulische Drosselelement 40 wird von mindesten zwei in Strömungsrichtung des Kraftstoffs hintereinander liegenden Spaltdrosselelementen 41.1 bis 41.n gebildet. Beim Ausführungsbeispiel in Figur 1 und 2 bilden zwei Spaltdrosselelemente 41.1 und 41.2 das hydraulische Drosselelement 40. Die beiden Spaltdrosselelemente 41.1, 41.2 sind an dem düsennadelsitznahen Abschnitt 17 der Düsennadel 15 jeweils als ein Ringbund 44 ausgebildet. Jeder Ringbund 44 weist eine schmale zylindrische Umfangsfläche 45 sowie eine erste Ringfläche 46 und eine zweite Ringfläche 47 auf. Die Ringflächen 46, 47 können plan oder schräg verlaufend ausgeführt sein. Zwischen den Umfangsflächen 45 jedes Ringbundes 40 und einer Innenwandung 49 des Düsenkörpers 12 ist ein umlaufender Ringspalt s ausgebildet. Beim Ausführungsbeispiel gemäß Fig. 2 ist der Ringspalt s bei den beiden Spaltdrosselelementen 41.1 und 41.2 gleich dimensioniert. Es ist aber auch möglich, die Spaltdrosselelemente 41.1, 41.2 an der Düsennadel 15 so zu platzieren, dass sich der Ringspalt s zwischen den Umfangsflächen 45 und einer Innenwandung am Injektorkörper 11 ausbildet.Between the storage pressure chamber 26 and the nozzle needle pressure chamber 25, a hydraulic throttle element 40 is arranged. The hydraulic throttle element 40 is at least two in the flow direction of the fuel in series lying gap throttle elements 41.1 to 41.n formed. In the embodiment in FIG. 1 and 2 form two gap throttles 41.1 and 41.2, the hydraulic throttle element 40. The two gap throttling elements 41.1, 41.2 are formed on the nozzle needle seat near portion 17 of the nozzle needle 15 each as an annular collar 44. Each annular collar 44 has a narrow cylindrical peripheral surface 45 and a first annular surface 46 and a second annular surface 47. The annular surfaces 46, 47 may be designed to be flat or inclined. Between the peripheral surfaces 45 of each annular collar 40 and an inner wall 49 of the nozzle body 12, a circumferential annular gap s is formed. According to the embodiment Fig. 2 is the annular gap s in the two gap throttle elements 41.1 and 41.2 the same size. But it is also possible to place the gap throttling elements 41.1, 41.2 on the nozzle needle 15 so that the annular gap s between the peripheral surfaces 45 and an inner wall on the injector body 11 is formed.

Beim Ausführungsbeispiel in Fig. 3 sind an der Düsennadel 15 vier Ringspaltdrosselelemente 41.1 bis 41.4 ausgebildet, die - wie beim Ausführungsbeispiel in Fig. 2 - jeweils von einem Ringbund 44 ausgebildet sind. Die Ringbunde 44 bilden mit ihrer jeweiligen Umfangsflächen 45 zur Innenwandung 49 des Düsenkörpers 12 den Ringspalt s, der für alle Spaltdrosselelement 41.1 bis 41.4 im Wesentlichen gleich bemessen ist. Auch hier kann der Ringspalt s zwischen den Umfangsflächen 45 und einer Innenwandung am Injektorkörper 11 ausbildet sein.In the embodiment in Fig. 3 are formed on the nozzle needle 15 four annular gap throttling elements 41.1 to 41.4, which - as in the embodiment in Fig. 2 - Are each formed by a collar 44. The annular collars 44 form with their respective peripheral surfaces 45 to the inner wall 49 of the nozzle body 12, the annular gap s, which is dimensioned substantially equal for all gap throttle element 41.1 to 41.4. Again, the annular gap s between the peripheral surfaces 45 and an inner wall on the injector 11 may be formed.

Beim Ausführungsbeispiel gemäß Fig. 4 sind ebenfalls vier Ringspaltdrosselelemente 41.1 bis 41.4 an der Düsennadel 15 ausgebildet, bei denen die Ringbunde 44 einen in Strömungsrichtung des Kraftstoffs abnehmende Durchmesser d2.1 bis d2.4 aufweisen. Der Düsenkörper 12 ist bei diesem Ausführungsbeispiel mit einer an die unterschiedlichen Durchmesser d2.1 bis d2.4 der verschiedenen Ringbunde 44 entsprechend angepassten stufenförmigen Innenwandung 50 ausgeführt, so dass sich zwischen der gestuften Innenwandung 50 und den jeweiligen Umfangsflächen 45 der Ringbunde 44 jeweils ein Ringspalt s1 bis s4 ausbildet, wobei die Ringspalte s1 bis s4 im Wesentlichen gleich dimensioniert sind. Dadurch bilden die Ringspaltdrosselelemente 41.1 bis 41.4 für den Kraftstoff ein kaskadenförmiges Stufenlabyrinth aus. Die stufenförmige Innenwandung 50 kann dabei auch am Injektorkörper 11 ausgebildet sein.According to the embodiment Fig. 4 are also four annular gap throttles 41.1 to 41.4 formed on the nozzle needle 15, in which the annular collars 44 have a decreasing in the flow direction of the fuel diameter d2.1 to d2.4. The nozzle body 12 is designed in this embodiment with a corresponding to the different diameters d2.1 to d2.4 the various annular collars 44 corresponding stepped inner wall 50, so that between the stepped inner wall 50 and the respective peripheral surfaces 45 of the annular collars 44 each have an annular gap s1 to s4 forms, wherein the annular gaps s1 to s4 are dimensioned substantially equal. As a result, the annular gap throttling elements 41.1 to 41.4 form a cascade-shaped fuel Step maze off. The step-shaped inner wall 50 can also be formed on the injector body 11.

Aus den Figuren 5 und 6 geht ein düsenkörperseitiger Ausschnitt eines Kraftstoffinjektors gemäß weiteren Ausführungsbeispielen hervor, bei denen die Düsennadel 15 eine kürzere Längserstreckung als beim Ausführungsbeispiel gemäß Fig. 1 aufweist und der Steuerraum 21 von einer am Kolbenabschnitt 18 längs verschiebbaren Steuerraumhülse 51 begrenzt wird. Die Steuerraumhülse 51 wird mittels einer Druckfeder 52 gegen eine Stirnfläche eines weiteren Injektorkörperteils 53 gedrückt, das beispielsweise von einer Drosselplatte mit nicht dargestellten, in den Steuerraum 21 führenden Zu- und Ablaufdrosseln ausgebildet ist.From the Figures 5 and 6 is a nozzle body side section of a fuel injector according to further embodiments, in which the nozzle needle 15 has a shorter longitudinal extent than in the embodiment according to Fig. 1 and the control chamber 21 is delimited by a piston chamber portion 18 longitudinally displaceable control chamber sleeve 51. The control chamber sleeve 51 is pressed by means of a compression spring 52 against an end face of a further Injektorkörperteils 53, which is formed for example by a throttle plate with not shown, leading into the control chamber 21 inlet and outlet throttles.

Beim Ausführungsbeispiel gemäß Fig. 5 ist die Düsennadelführung 23 in der Nähe des Düsennadelsitzes 14 ausgebildet. Die Ringspaltdrosselelemente 41.1 bis 41.n sind - wie bei der Ausführungsform in Fig. 1 - in Strömungsrichtung des Kraftstoffs stromauf von der Düsennadelführung 23 angeordnet.According to the embodiment Fig. 5 the nozzle needle guide 23 is formed in the vicinity of the nozzle needle seat 14. The annular gap throttling elements 41.1 to 41.n are - as in the embodiment in FIG Fig. 1 - In the flow direction of the fuel upstream of the nozzle needle guide 23 is arranged.

Beim Ausführungsbeispiel gemäß Fig. 6 ist neben der düsennadelsitznahen Düsennadelführung 23 eine davon beabstandete weitere Düsennadelführung 55 mit weiteren Abflachungen 56 vorgesehen, die ebenfalls eine in Wesentlichen ungedrosselte hydraulische Verbindung ausbilden. Die Ringspaltdrosselelemente 41.1 bis 41.n befinden sich bei diesem Ausführungsbeispiel zwischen den beiden Düsennadelführungen 23 und 55.According to the embodiment Fig. 6 is next to the nozzle needle seat near nozzle needle guide 23 a spaced therefrom further nozzle needle guide 55 is provided with further flats 56, which also form a substantially unthrottled hydraulic connection. The annular gap throttles 41.1 to 41.n are in this embodiment between the two nozzle needle guides 23 and 55th

Claims (11)

  1. Fuel injector for internal combustion engines, having a pressure chamber (16) which is formed in a housing (10) and in which a nozzle needle (15) is arranged such that it can perform a stroke movement, said nozzle needle interacting, by means of a sealing surface, with a nozzle needle seat (14), wherein a flow of fuel through at least one injection opening (13) is permitted or blocked by an interaction of the nozzle needle (15) with the nozzle needle seat (14), wherein the pressure chamber (16) is divided into an accumulator pressure chamber (26) remote from the nozzle needle seat and a nozzle needle pressure chamber (25) close to the nozzle needle seat, and wherein a hydraulic throttle element (40) in the form of an annular gap throttle is arranged between the accumulator pressure chamber (26) and the nozzle needle pressure chamber (25), characterized in that the nozzle needle (15) has arranged on it at least two annular gap throttle elements (41.1 to 41.n) which are situated in series in the flow direction of the fuel.
  2. Fuel injector according to Claim 1, characterized in that the at least two annular gap throttle elements (41.1 to 41.n) are formed in each case by an annular collar (44) which is arranged on the nozzle needle (15) and which has a narrow-walled circumferential surface (45).
  3. Fuel injector according to Claim 2, characterized in that an annular gap (s) is formed between the circumferential surface (45) of each annular collar (44) and a wall (49, 50) of the pressure chamber (16).
  4. Fuel injector according to Claim 3, characterized in that the circumferential surfaces (45) of each annular collar (44) have a substantially equal diameter (d1), and in that the respective annular gaps (s) between the circumferential surface (45) of each annular collar (44) and the wall (49) of the pressure chamber (16) are substantially equal.
  5. Fuel injector according to Claim 3, characterized in that the circumferential surfaces (45) of the annular collars (44) of the at least two annular gap throttle elements (41.1 to 41.n) have diameters (d2.1 to d2.n) which decrease in the flow direction of the fuel.
  6. Fuel injector according to Claim 5, characterized in that the pressure chamber (16) has a stepped wall (50) which is adapted to the diameters (d2.1 to d2.n) of the circumferential surfaces (45) of the annular collars (44), so as to yield a cascade-like flow of the fuel.
  7. Fuel injector according to Claim 6, characterized in that the annular gaps (s1 to sn) formed between the circumferential surfaces (45) of each annular collar (44) with the respective diameters (d2.1 to d2.n) and the respectively stepped wall (50) are substantially equal.
  8. Fuel injector according to one of the preceding claims, characterized in that the wall (49, 50) for forming the annular gaps (s, s1 to sn) is formed on a nozzle body (12) in which the nozzle needle (15) is guided in a nozzle needle guide (23) close to the nozzle needle seat.
  9. Fuel injector according to Claim 8, characterized in that the at least two annular gap throttle elements (41.1 to 41.n) are arranged upstream of the nozzle needle guide (23) in the flow direction of the fuel.
  10. Fuel injector according to Claim 1, characterized in that a control chamber sleeve (51) is guided on the nozzle needle (15), which control chamber sleeve hydraulically delimits a control chamber (21), and in that the at least two annular gap throttle elements (41.1 to 41.n) are arranged between the control chamber sleeve (51) and a nozzle needle guide (23) close to the nozzle needle seat.
  11. Fuel injector according to Claim 10, characterized in that the nozzle needle (15) is guided, at a distance from the nozzle needle guide (23) close to the nozzle needle seat, in a further nozzle needle guide (56), and in that the at least two annular gap throttle elements (41.1 to 41.n) are arranged between the two nozzle needle guides (23, 56).
EP09753107A 2009-01-14 2009-11-17 Fuel injector for internal combustion engines Active EP2387661B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910000206 DE102009000206A1 (en) 2009-01-14 2009-01-14 Fuel injector for internal combustion engines
PCT/EP2009/065278 WO2010081574A1 (en) 2009-01-14 2009-11-17 Fuel injector for internal combustion engines

Publications (2)

Publication Number Publication Date
EP2387661A1 EP2387661A1 (en) 2011-11-23
EP2387661B1 true EP2387661B1 (en) 2012-10-03

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EP (1) EP2387661B1 (en)
CN (1) CN102282354A (en)
DE (1) DE102009000206A1 (en)
WO (1) WO2010081574A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009029562A1 (en) * 2009-07-30 2011-02-03 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
DE102010043363A1 (en) 2010-11-04 2012-05-10 Robert Bosch Gmbh Magnet armature assembly of fuel injector for injecting fuel into combustion chamber of combustion engine, has compression springs that are arranged radially at equal angular distances from one another along longitudinal axis
DE102011077464A1 (en) 2011-06-14 2012-12-20 Robert Bosch Gmbh Fuel injector for an internal combustion engine
EP2568157A1 (en) * 2011-09-08 2013-03-13 Delphi Technologies Holding S.à.r.l. Injection Nozzle
EP2818687A1 (en) * 2013-06-27 2014-12-31 Delphi International Operations Luxembourg S.à r.l. Fuel injector
CN104847556A (en) * 2015-05-19 2015-08-19 中国重汽集团重庆燃油喷射***有限公司 Non-static leakage oil sprayer
CN109681360A (en) * 2019-02-28 2019-04-26 一汽解放汽车有限公司 A kind of long needle-valve for fuel injection valve
CN110529317A (en) * 2019-08-23 2019-12-03 一汽解放汽车有限公司 A kind of fuel injection valve valve pocket assembly

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Publication number Priority date Publication date Assignee Title
DE10019153A1 (en) * 2000-04-18 2001-10-25 Bosch Gmbh Robert Fuel injection valve for IC engines has valve bore with valve member and valve piston loaded by hydraulic closing force to engage on valve member
DE10149961A1 (en) * 2001-10-10 2003-04-30 Bosch Gmbh Robert Fuel injection device for internal combustion engine, especially common rail injector, has flow path control sections interacting to give defined flow characteristic against time
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
JP4608555B2 (en) * 2005-02-22 2011-01-12 シーメンス ヴィディーオー オートモーティヴ コーポレイション Fuel injection assembly
DE102006036447A1 (en) 2006-08-04 2008-02-07 Robert Bosch Gmbh Injector for a fuel injection system
DE102007032741A1 (en) 2007-07-13 2009-01-15 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
US7690588B2 (en) * 2007-07-31 2010-04-06 Caterpillar Inc. Fuel injector nozzle with flow restricting device

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CN102282354A (en) 2011-12-14
DE102009000206A1 (en) 2010-07-15
EP2387661A1 (en) 2011-11-23
WO2010081574A1 (en) 2010-07-22

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