EP2715103B1 - 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
EP2715103B1
EP2715103B1 EP12723468.0A EP12723468A EP2715103B1 EP 2715103 B1 EP2715103 B1 EP 2715103B1 EP 12723468 A EP12723468 A EP 12723468A EP 2715103 B1 EP2715103 B1 EP 2715103B1
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EP
European Patent Office
Prior art keywords
nozzle
nozzle needle
throttle bore
throttle
needle
Prior art date
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Application number
EP12723468.0A
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German (de)
French (fr)
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EP2715103A1 (en
Inventor
Andreas Koeninger
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2715103A1 publication Critical patent/EP2715103A1/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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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
    • F02M61/20—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 nozzle assembly for a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine having the features of the preamble of claim 1. Furthermore, the invention relates to a fuel injector with such a nozzle assembly.
  • a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine with eienr generic nozzle assembly comprises an axially adjustable injection valve member having a combustion chamber near portion which projects into a nozzle chamber, can flow into the fuel through a closing throttle.
  • the nozzle assembly further comprises a spring-loaded in the axial direction sleeve or disc, which is penetrated by the injection valve element and at least one throttle opening forming the closing throttle.
  • a fuel injector which has a longitudinally movable nozzle needle, which is surrounded by a throttle bore body.
  • the throttle body is located on the nozzle needle and is acted upon by a closing spring.
  • the proposed nozzle assembly comprises a nozzle needle which is guided in a high-pressure bore of a nozzle body for releasing and closing at least one injection opening via at least one guide portion and at least indirectly acted upon by the spring force of a closing spring, and a spring-loaded in the axial direction throttle bore body.
  • the throttle bore body bears against the nozzle needle and is acted upon in the axial direction by the spring force of the closing spring.
  • the throttle body is thus biased axially corresponding to the nozzle needle in the closing direction, so that it requires only a closing spring for biasing the nozzle needle and throttle body.
  • the spring force of the closing spring is transmitted via the throttle bore body to the nozzle needle.
  • the closing spring is preferably received in a first pressure chamber, which is in communication with a high pressure source.
  • the throttle bore body separates the first pressure chamber from a second pressure chamber, which communicates with the at least one injection port. Both pressure chambers are in turn connected via at least one throttle bore in the throttle bore body.
  • the at least one throttle bore has the effect that in the first pressure chamber, a hydraulic pressure p 1 and in the second pressure chamber, a hydraulic pressure p 2 act, where p 1 > p 2 .
  • the hydraulic pressure p 1 thus causes an additional hydraulic closing force, which supports the function of the closing spring.
  • the section of the nozzle needle passing through the throttle body has an outer diameter D 3 which is smaller than the outer diameter D 2 of the nozzle needle.
  • the ratio of the outer diameter D 3 ⁇ D 2 ensures a hydraulic effective area ratio A 1 > A 2 and thus an additional acting in the axial direction hydraulic force.
  • the nozzle needle passes through the throttle bore body, the nozzle needle can be connected directly or indirectly via a plunger body with an actuator for actuating the nozzle needle.
  • the actuator may have an actuator ram, which is supported directly or indirectly on the nozzle needle.
  • the throttle bore body is formed like a piston and has an outer diameter D 1 , which is greater than the outer diameter D 2 of the nozzle needle in the contact region with the throttle bore body. Due to the larger outer diameter are preferably formed on both end faces of the piston-like throttle bore body, which limit the two pressure chambers, hydraulic active surfaces A 1 and A 2 , on the size ratio of an effective axial force can be effected, which additionally acts on the throttle bore body including the nozzle needle. The ratio is preferably chosen such that the hydraulic effective area A 1 delimiting the first pressure chamber is greater than the hydraulic effective area A 2 delimiting the second pressure chamber.
  • the throttle bore body further has at least one throttle bore, which is preferably designed as an axial bore.
  • An axial bore has the advantage over other throttle designs, such as inclined bores, that it has a lower temperature sensitivity.
  • the formation of at least one throttle bore as an axial bore is possible because the outer diameter D 1 of the piston-like throttle body is greater than the outer diameter D 2 of the nozzle needle.
  • the throttle bore body cooperate to guide the nozzle needle with a guide portion of the nozzle body.
  • a first guide portion which is preferably formed as a stepped bore in the nozzle body high pressure bore and cooperates with a portion of the nozzle needle having an enlarged diameter
  • the throttle bore body can cooperate with an axially spaced from the first guide portion formed second guide portion.
  • the leadership of the nozzle needle can be optimized so that the axial distance between the two guide sections is selected as large as possible.
  • the throttle bore body is located not only on the nozzle needle, but is integrally connected to the nozzle needle.
  • the connection can be made for example by means of laser welding.
  • a non-positive or positive connection can be provided. Due to the integral connection of the throttle bore body with the nozzle needle, the assembly of the nozzle assembly can be simplified because fewer components are to be inserted into the nozzle body.
  • the centering of the nozzle needle is preferably carried out via the guide sections.
  • the portion of the nozzle needle passing through the throttle body is a plunger body integrally connected to the nozzle needle.
  • the connection can be made for example by means of laser welding. Alternatively or additionally, a non-positive and / or positive connection can be selected.
  • plunger body may be the Aktorst Congressel or operatively connected to the Aktorst Schemeel further plunger body. Since usually the outer diameter of the Aktorstsammlungels is smaller than the outer diameter D 2 of the nozzle needle is selected to effect a gain of the actuator force, it is further ensured that the hydraulic effective area ratio at the throttle body A 1 is greater than A 2 .
  • actuator plunger and nozzle needle are usually designed as two components, which must be assembled consuming during assembly. Due to the proposed one-piece design, therefore, the assembly can be simplified.
  • the portion of the nozzle needle passing through the throttle bore body or the plunger body integrally connected to the nozzle needle is mounted radially floating in the throttle bore body.
  • the radially floating bearing bending loads on the nozzle needle or the plunger body can be prevented, which can be initiated for example due to lack of coaxiality of the components during assembly of the nozzle assembly in the nozzle needle or the plunger body.
  • the radially floating mounting can take place, for example, by providing an annular gap between the throttle bore body and the throttle bore body penetrating portion of the nozzle needle or the plunger body.
  • the annular gap has a maximum outer diameter which is smaller than the outer diameter D 2 of the nozzle needle. The annular gap is thus covered by an end face or a radially extending shoulder of the nozzle needle.
  • the section of the nozzle needle or the tappet body passing through the throttle body is centered via an intermediate disk axially attached to the nozzle body.
  • the washer has an annular centering portion received in the nozzle body to facilitate assembly of the nozzle assembly.
  • a holding body is preferably attached axially and clamped axially with the nozzle body via a nozzle retaining nut.
  • the holding body may also be provided with an annular centering section, so that the assembly of nozzle assembly and holding body is simplified when the intermediate disk is omitted.
  • the further proposed for solving the input task asked fuel injector for injecting fuel into the combustion chamber of an internal combustion engine comprises a nozzle assembly according to the invention and an actuator assembly for actuating the nozzle needle.
  • the nozzle needle via the Aktorbaueria is directly operable.
  • Direct actuation of the nozzle needle is understood here to mean an actuation in which the actuator force, for example via a hydraulic coupler, is possibly amplified.
  • the proposed nozzle assembly allows a fuel injector which is particularly compact in the axial direction and is also easy to assemble.
  • the functions guide / centering of the nozzle needle, closing throttle, sealing of the pressure chambers before / after the closing throttle and / or support of the spring force can be realized by a simple and therefore cost-effective component.
  • the component may have a throttle stepping for different application areas and be maintained according to the principle of a modular system.
  • the nozzle needle is connected to the plunger body and the closing spring and the throttle bore body are pushed onto the plunger body. Thereafter, the plunger body is inserted into the washer or a holding body. Finally, the nozzle body is connected to the intermediate disc and / or the holding body via a nozzle retaining nut.
  • the in the FIG. 1 illustrated nozzle assembly comprises a nozzle needle 1, which is guided in a high-pressure bore 2 of a nozzle body 3 in a liftable manner.
  • a nozzle needle 1 is guided in a high-pressure bore 2 of a nozzle body 3 in a liftable manner.
  • at least one injection port 4 can be opened and closed, via which high-pressure fuel in the combustion chamber of an internal combustion engine (not shown) can be injected.
  • the nozzle needle 1 is actuated via an actuator assembly, not shown.
  • the actuation of the nozzle needle 1 is carried out directly, possibly with the interposition of a hydraulic coupler.
  • the actuator assembly may include, for example, a magnetic actuator or a piezoelectric actuator.
  • two guide sections 5, 6 are formed in the nozzle body 3, which cooperate leading with corresponding portions of the nozzle needle 1.
  • the nozzle needle 1 In the region of the guide section 5, which is formed in the vicinity of a nozzle seat 13, the nozzle needle 1 has a section with an enlarged diameter, via which the nozzle needle 1 is guided in the guide section 5.
  • the enlarged diameter portion of the nozzle needle 1 has outer peripheral side polished portions to form flow passages for the fuel.
  • the polished sections are uniformly distributed over the circumference of the nozzle needle 1.
  • Another guide section 6 is arranged at an axial distance from the guide section 5.
  • the guide section 6 cooperates with a throttle bore body 7, which is supported on a radially extending shoulder of the nozzle needle 1.
  • the throttle bore body 7 has an outer diameter D 1 , which is greater than the outer diameter D 2 of the nozzle needle 1 in the contact area with the throttle body 7 is.
  • the throttle bore body 7 may also be formed integrally with the nozzle needle 1.
  • the throttle body 7 is then formed by an enlarged diameter portion of the nozzle needle 1 or a throttle body 7 integrally connected to the nozzle needle 1.
  • the compound can be chosen such that a force, shape and / or material bond is effected.
  • At least one throttle bore 9 designed as an axial bore is formed.
  • a first, in connection with an inlet bore 16 standing pressure chamber and a second, in connection with the at least one injection port 4 stationary pressure chamber are hydraulically connected in such a way that the hydraulic pressure p 1 in the first pressure chamber greater than that hydraulic pressure p 2 in the second pressure chamber is.
  • the hydraulic pressure p 1 in the first pressure chamber consequently causes a force acting in the closing direction of the nozzle needle 1 on the throttle bore body 7, which acts to assist the needle closure.
  • the effect can be further enhanced by the hydraulic active surfaces formed on the throttle body 7.
  • the active hydraulic surfaces are designed in such a way that the hydraulic effective area A 1 delimiting the first pressure chamber is greater than the hydraulic effective area A 2 delimiting the second pressure chamber.
  • the closing direction of the throttle bore body 7 is further acted upon by the spring force of a closing spring 8, on the one hand on the throttle body 7 on the other hand to a holding body 15 and a support body 15 and the nozzle body 3 arranged intermediate disc 11 is supported.
  • the intermediate disc 11 or in the holding body 15 and the inlet bore 16 is formed, which connects the first pressure chamber with a high-pressure source.
  • the intermediate plate 11 and the holding body 15 is axially attached to the nozzle body 3 and axially clamped with this via a nozzle lock nut (not shown).
  • the second guide portion 6 extends substantially to the sealing surfaces 14 in order to ensure the greatest possible axial distance between the two guide sections 5, 6, whereby the guide of the nozzle needle. 1 is optimized.
  • the guide portion 6 is limited only by the fact that the recorded in the first pressure chamber closing spring 8 limits the stroke of the throttle body 7.
  • the throttle body 7 is penetrated by a plunger body 10 which is integrally connected to the nozzle needle 1.
  • the connection 18 may in turn be a positive, positive and / or cohesive connection 18.
  • the plunger body 10 has an outer diameter D 3 , which is smaller than the outer diameter D 2 of the nozzle needle 1 is selected. This ensures a hydraulic effective area ratio A 1 > A 2 .
  • the plunger body 10 serves for the operative connection of the nozzle needle 1 with the actuator assembly, not shown, wherein the active compound can also be produced via a coupler body and / or a coupler volume.
  • This component is also easy and inexpensive to produce.
  • the assembly of the nozzle assembly is simplified. Over the two axially spaced guide portions 5, 6 an optimal guidance of the nozzle needle 1 in the nozzle body 3 is ensured.
  • the hydraulic active surfaces A 1 and A 2 formed on the throttle body 7 cause, due to their size ratio, an additional hydraulic force acting in the axial direction.
  • FIG. 2 shows a modification of the embodiment of the FIG. 1 ,
  • the nozzle needle 1 and the throttle bore body 7 are designed as separate components. This allows a radially floating mounting of the nozzle needle 1 in the region of the guide section 6. By the radially floating mounting of the nozzle needle 1, a bending stress of the nozzle needle 1 is avoided in the absence of coaxiality of the components to each other.
  • the nozzle needle 1 is integrally connected to a plunger body 10, wherein the plunger body 10 further is received in the washer 11 and the holding body 15.
  • the nozzle needle 1 thus experiences on the integrally connected plunger body 10, a further guide or centering, which can lead to a bending stress of the nozzle needle 1 in the absence of coaxiality of the components plunger body 10, nozzle needle 1 and throttle bore body 7. This can be counteracted by the nozzle needle 1 or the plunger body 10 integrally connected to the nozzle needle 1 being mounted radially floating in the throttle bore body 7.
  • an annular gap 17 is formed in the throttle body 7 in the present case.
  • the annular gap 17 is covered to the side of the second pressure chamber out by an annular end face of the nozzle needle 1, so that no additional flow channel is provided, via which fuel from the first
  • Pressure chamber can flow into the second pressure chamber.
  • annular centering portion 12 is formed on the washer 11 and on the holding body 15, with which the washer 11 and the holding body 15 can be inserted into the high-pressure bore 2 of the nozzle body 3 , In this respect, a guide or centering of the nozzle needle 1 in an area remote from the seat is still ensured via the intermediate disk 11 or the holding body 15.

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 having 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 2009 001 704 A1 ist ein Kraftstoff-Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine mit eienr gattungsgemäßen Düsenbaugruppe bekannt. Die Düsenbaugruppe umfasst ein axial verstellbares Einspritzventilelement mit einem brennraumnahen Abschnitt, welcher in einen Düsenraum ragt, in den Kraftstoff durch eine Schließdrossel strömen kann. Um eine einfache, toleranz- und temperaturunempfindliche Schließdrosselausbildung und -anordnung anzugeben, umfasst die Düsenbaugruppe ferner eine in axialer Richtung federkraftbeaufschlagte Hülse oder Scheibe, welche von dem Einspritzventilelement durchsetzt ist und mindestens eine die Schließdrossel bildende Drosselbohrung aufweist.From the publication DE 10 2009 001 704 A1 a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine with eienr generic nozzle assembly is known. The nozzle assembly comprises an axially adjustable injection valve member having a combustion chamber near portion which projects into a nozzle chamber, can flow into the fuel through a closing throttle. In order to provide a simple, tolerance and temperature-insensitive closing throttle formation and arrangement, the nozzle assembly further comprises a spring-loaded in the axial direction sleeve or disc, which is penetrated by the injection valve element and at least one throttle opening forming the closing throttle.

Aus der EP 1 990 532 A1 ist darüber hinaus ein Kraftstoffinjektor bekannt, der eine längsbewegliche Düsennadel aufweist, die von einem Drosselbohrungskörper umgeben ist. Der Drosselbohrungskörper liegt an der Düsennadel an und wird von einer Schließfeder beaufschlagt.From the EP 1 990 532 A1 In addition, a fuel injector is known, which has a longitudinally movable nozzle needle, which is surrounded by a throttle bore body. The throttle body is located on the nozzle needle and is acted upon by a closing spring.

Ausgehend von dem vorstehend genannten Stand der Technik ist es Aufgabe der vorliegenden Erfindung, eine funktions- und fertigungsoptimierte Düsenbaugruppe, insbesondere für direktgeschaltete Dieseleinspritzinjektoren, anzugeben.Based on the above-mentioned prior art, it is an object of the present invention to provide a functional and production-optimized nozzle assembly, in particular for directly switched Dieseleinspritzinjektoren.

Die Aufgabe wird gelöst durch eine Düsenbaugruppe mit den Merkmalen des Anspruchs 1. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen angegeben. Zur Lösung der Aufgabe wird ferner ein Kraftstoffinjektor mit den Merkmalen des Anspruchs 10 vorgeschlagen.The object is achieved by a nozzle assembly having the features of claim 1. Advantageous developments of the invention are specified in the subclaims. To solve the problem, a fuel injector with the features of claim 10 is also proposed.

Offenbarung der ErfindungDisclosure of the invention

Die vorgeschlagene Düsenbaugruppe umfasst eine Düsennadel, die in einer Hochdruckbohrung eines Düsenkörpers zum Freigeben und Verschließen wenigstens einer Einspritzöffnung über wenigstens einen Führungsabschnitt hubbeweglich geführt und zumindest mittelbar von der Federkraft einer Schließfeder beaufschlagt ist, sowie einen in axialer Richtung federkraftbeaufschlagten Drosselbohrungskörper. Erfindungsgemäß liegt der Drosselbohrungskörper an der Düsennadel an und ist in axialer Richtung von der Federkraft der Schließfeder beaufschlagt. Der Drosselbohrungskörper ist somit entsprechend der Düsennadel in Schließrichtung axial vorgespannt, so dass es zur Vorspannung von Düsennadel und Drosselbohrungskörper lediglich einer Schließfeder bedarf. Die Federkraft der Schließfeder wird über den Drosselbohrungskörper auf die Düsennadel übertragen. Die Schließfeder ist dabei bevorzugt in einem ersten Druckraum aufgenommen, welcher in Verbindung mit einer Hochdruckquelle steht. Der Drosselbohrungskörper trennt den ersten Druckraum von einem zweiten Druckraum, welcher in Verbindung mit der wenigstens einen Einspritzöffnung steht. Beide Druckräume sind wiederum über wenigstens eine Drosselbohrung im Drosselbohrungskörper verbunden. Die wenigstens eine Drosselbohrung hat den Effekt, dass im ersten Druckraum ein hydraulischer Druck p1 und im zweiten Druckraum ein hydraulischer Druck p2 wirken, wobei p1 > p2 ist. Der hydraulische Druck p1 bewirkt demnach eine zusätzliche hydraulische Schließkraft, welche die Funktion der Schließfeder unterstützt.The proposed nozzle assembly comprises a nozzle needle which is guided in a high-pressure bore of a nozzle body for releasing and closing at least one injection opening via at least one guide portion and at least indirectly acted upon by the spring force of a closing spring, and a spring-loaded in the axial direction throttle bore body. According to the invention, the throttle bore body bears against the nozzle needle and is acted upon in the axial direction by the spring force of the closing spring. The throttle body is thus biased axially corresponding to the nozzle needle in the closing direction, so that it requires only a closing spring for biasing the nozzle needle and throttle body. The spring force of the closing spring is transmitted via the throttle bore body to the nozzle needle. The closing spring is preferably received in a first pressure chamber, which is in communication with a high pressure source. The throttle bore body separates the first pressure chamber from a second pressure chamber, which communicates with the at least one injection port. Both pressure chambers are in turn connected via at least one throttle bore in the throttle bore body. The at least one throttle bore has the effect that in the first pressure chamber, a hydraulic pressure p 1 and in the second pressure chamber, a hydraulic pressure p 2 act, where p 1 > p 2 . The hydraulic pressure p 1 thus causes an additional hydraulic closing force, which supports the function of the closing spring.

Erfindungsgemäß besitzt der den Drosselbohrungskörper durchsetzende Abschnitt der Düsennadel einen Außendurchmesser D3, der kleiner als der Außendurchmesser D2 der Düsennadel ist. Das Verhältnis der Außendurchmesser D3 < D2 gewährleistet ein hydraulisches Wirkflächenverhältnis A1 >A2 und damit eine zusätzliche in axialer Richtung wirkende hydraulische Kraft. Indem die Düsennadel den Drosselbohrungskörper durchsetzt, kann die Düsennadel direkt oder indirekt über einen Stößelkörper mit einem Aktor zur Betätigung der Düsennadel verbunden werden. Beispielsweise kann der Aktor einen Aktorstößel aufweisen, der unmittelbar oder mittelbar an der Düsennadel abgestützt ist.According to the invention, the section of the nozzle needle passing through the throttle body has an outer diameter D 3 which is smaller than the outer diameter D 2 of the nozzle needle. The ratio of the outer diameter D 3 <D 2 ensures a hydraulic effective area ratio A 1 > A 2 and thus an additional acting in the axial direction hydraulic force. By the nozzle needle passes through the throttle bore body, the nozzle needle can be connected directly or indirectly via a plunger body with an actuator for actuating the nozzle needle. For example, the actuator may have an actuator ram, which is supported directly or indirectly on the nozzle needle.

Vorzugsweise ist der Drosselbohrungskörper kolbenartig ausgebildet und besitzt einen Außendurchmesser D1, der größer als der Außendurchmesser D2 der Düsennadel im Kontaktbereich mit dem Drosselbohrungskörper ist. Aufgrund des größeren Außendurchmessers werden vorzugsweise an beiden Stirnflächen des kolbenartig ausgebildeten Drosselbohrungskörpers, welche die beiden Druckräume begrenzen, hydraulische Wirkflächen A1 und A2 ausgebildet, über deren Größenverhältnis eine in axialer Richtung wirksame hydraulische Kraft bewirkbar ist, welche den Drosselbohrungskörper einschließlich der Düsennadel zusätzlich beaufschlagt. Das Verhältnis ist vorzugsweise derart gewählt, dass die den ersten Druckraum begrenzende hydraulische Wirkfläche A1 größer als die den zweiten Druckraum begrenzende hydraulische Wirkfläche A2 ist.Preferably, the throttle bore body is formed like a piston and has an outer diameter D 1 , which is greater than the outer diameter D 2 of the nozzle needle in the contact region with the throttle bore body. Due to the larger outer diameter are preferably formed on both end faces of the piston-like throttle bore body, which limit the two pressure chambers, hydraulic active surfaces A 1 and A 2 , on the size ratio of an effective axial force can be effected, which additionally acts on the throttle bore body including the nozzle needle. The ratio is preferably chosen such that the hydraulic effective area A 1 delimiting the first pressure chamber is greater than the hydraulic effective area A 2 delimiting the second pressure chamber.

Der Drosselbohrungskörper besitzt ferner wenigstens eine Drosselbohrung, die vorzugsweise als Axialbohrung ausgeführt ist. Eine Axialbohrung weist gegenüber anderen Drosselausführungen, wie beispielsweise Schrägbohrungen, den Vorteil auf, dass sie eine geringere Temperatursensitivität besitzt. Die Ausbildung der wenigstens einen Drosselbohrung als Axialbohrung ist möglich, da der Außendurchmesser D1 des kolbenartig ausgeführten Drosselbohrungskörpers größer als der Außendurchmesser D2 der Düsennadel ist.The throttle bore body further has at least one throttle bore, which is preferably designed as an axial bore. An axial bore has the advantage over other throttle designs, such as inclined bores, that it has a lower temperature sensitivity. The formation of at least one throttle bore as an axial bore is possible because the outer diameter D 1 of the piston-like throttle body is greater than the outer diameter D 2 of the nozzle needle.

Des Weiteren wird vorgeschlagen, dass der Drosselbohrungskörper zur Führung der Düsennadel mit einem Führungsabschnitt des Düsenkörpers zusammenwirkt. Neben einem ersten Führungsabschnitt, der vorzugsweise über eine als Stufenbohrung im Düsenkörper ausgeführte Hochdruckbohrung ausgebildet wird und mit einem Abschnitt der Düsennadel zusammenwirkt, welcher einen vergrößerten Durchmesser besitzt, kann der Drosselbohrungskörper mit einem axial beabstandet zum ersten Führungsabschnitt ausgebildeten zweiten Führungsabschnitt zusammenwirken. Die Führung der Düsennadel kann dadurch optimiert werden, dass der axiale Abstand der beiden Führungsabschnitte möglichst groß gewählt wird.Furthermore, it is proposed that the throttle bore body cooperate to guide the nozzle needle with a guide portion of the nozzle body. In addition to a first guide portion, which is preferably formed as a stepped bore in the nozzle body high pressure bore and cooperates with a portion of the nozzle needle having an enlarged diameter, the throttle bore body can cooperate with an axially spaced from the first guide portion formed second guide portion. The leadership of the nozzle needle can be optimized so that the axial distance between the two guide sections is selected as large as possible.

Gemäß einer Weiterbildung der Erfindung, liegt der Drosselbohrungskörper nicht nur an der Düsennadel an, sondern ist mit der Düsennadel einstückig verbunden. Die Verbindung kann beispielsweise mittels Laserschweißens erfolgen. Darüber hinaus kann alternativ oder ergänzend auch eine kraft- oder formschlüssige Verbindung vorgesehen sein. Durch die einstückige Verbindung des Drosselbohrungskörpers mit der Düsennadel kann die Montage der Düsenbaugruppe vereinfacht werden, da weniger Bauteile in den Düsenkörper einzusetzen sind. Die Zentrierung der Düsennadel erfolgt dabei bevorzugt über die Führungsabschnitte.According to one embodiment of the invention, the throttle bore body is located not only on the nozzle needle, but is integrally connected to the nozzle needle. The connection can be made for example by means of laser welding. In addition, alternatively or additionally, a non-positive or positive connection can be provided. Due to the integral connection of the throttle bore body with the nozzle needle, the assembly of the nozzle assembly can be simplified because fewer components are to be inserted into the nozzle body. The centering of the nozzle needle is preferably carried out via the guide sections.

Vorteilhafterweise ist der den Drosselbohrungskörper durchsetzende Abschnitt der Düsennadel ein Stößelkörper, der einstückig mit der Düsennadel verbunden ist. Die Verbindung kann beispielsweise mittels Laserschweißens erfolgen. Alternativ oder ergänzend kann auch eine kraft- und/oder formschlüssige Verbindung gewählt werden. Bei dem einstückig mit der Düsennadel verbundenen Stößelkörper kann es sich um den Aktorstößel handeln oder einen mit dem Aktorstößel wirkverbundenen weiteren Stößelkörper. Da in der Regel der Außendurchmesser des Aktorstößels kleiner als der Außendurchmesser D2 der Düsennadel gewählt ist, um eine Verstärkung der Aktorkraft zu bewirken, ist weiterhin gewährleistet, dass das hydraulische Wirkflächenverhältnis am Drosselbohrungskörper A1 größer A2 ist. Bei herkömmlichen, insbesondere direkt geschalteten Injektoren, sind Aktorstößel und Düsennadel in der Regel als zwei Bauteile ausgeführt, welche bei der Montage aufwändig zusammengefügt werden müssen. Durch die vorgeschlagene einstückige Ausbildung kann demnach die Montage vereinfacht werden.Advantageously, the portion of the nozzle needle passing through the throttle body is a plunger body integrally connected to the nozzle needle. The connection can be made for example by means of laser welding. Alternatively or additionally, a non-positive and / or positive connection can be selected. In the integrally connected to the nozzle needle plunger body may be the Aktorstößel or operatively connected to the Aktorstößel further plunger body. Since usually the outer diameter of the Aktorstößels is smaller than the outer diameter D 2 of the nozzle needle is selected to effect a gain of the actuator force, it is further ensured that the hydraulic effective area ratio at the throttle body A 1 is greater than A 2 . In conventional, especially directly connected injectors, actuator plunger and nozzle needle are usually designed as two components, which must be assembled consuming during assembly. Due to the proposed one-piece design, therefore, the assembly can be simplified.

Gemäß einer alternativen Ausführungsform der Erfindung ist vorgesehen, dass der den Drosselbohrungskörper durchsetzende Abschnitt der Düsennadel bzw. der einstückig mit der Düsennadel verbundenen Stößelkörper radial schwimmend im Drosselbohrungskörper gelagert ist. Durch die radial schwimmende Lagerung können Biegebelastungen auf die Düsennadel bzw. den Stößelkörper verhindert werden, die beispielsweise aufgrund fehlender Koaxialität der Bauteile bei der Montage der Düsenbaugruppe in die Düsennadel bzw. den Stößelkörper eingeleitet werden können. Die radial schwimmende Lagerung kann beispielsweise dadurch erfolgen, dass ein Ringspalt zwischen Drosselbohrungskörper und den Drosselbohrungskörper durchsetzenden Abschnitt der Düsennadel bzw. dem Stößelkörper vorgesehen ist. Vorzugsweise weist der Ringspalt einen maximalen Außendurchmesser auf, der kleiner als der Außendurchmesser D2 der Düsennadel ist. Der Ringspalt wird somit von einer Stirnfläche bzw. einem radial verlaufenden Absatz der Düsennadel überdeckt.According to an alternative embodiment of the invention, it is provided that the portion of the nozzle needle passing through the throttle bore body or the plunger body integrally connected to the nozzle needle is mounted radially floating in the throttle bore body. By the radially floating bearing bending loads on the nozzle needle or the plunger body can be prevented, which can be initiated for example due to lack of coaxiality of the components during assembly of the nozzle assembly in the nozzle needle or the plunger body. The radially floating mounting can take place, for example, by providing an annular gap between the throttle bore body and the throttle bore body penetrating portion of the nozzle needle or the plunger body. Preferably, the annular gap has a maximum outer diameter which is smaller than the outer diameter D 2 of the nozzle needle. The annular gap is thus covered by an end face or a radially extending shoulder of the nozzle needle.

Bei radial schwimmender Lagerung der Düsennadel im Drosselbohrungskörper ist ggf. keine ausreichende Führung der Düsennadel mehr gewährleistet. Um eine weitere Führung bzw. Zentrierung der Düsennadel sicherzustellen, wird gemäß einer Weiterbildung vorgeschlagen, dass der den Drosselbohrungskörper durchsetzende Abschnitt der Düsennadel bzw. der Stößelkörper über eine axial an den Düsenkörper angesetzte Zwischenscheibe zentriert ist. Vorzugsweise besitzt die Zwischenscheibe einen im Düsenkörper aufgenommenen ringförmigen Zentrierabschnitt, um die Montage der Düsenbaugruppe zu erleichtern. An die Zwischenscheibe ist vorzugsweise ein Haltekörper axial angesetzt und mit dem Düsenkörper über eine Düsenspannmutter axial verspannt. Alternativ kann anstelle der Zwischenscheibe auch der Haltekörper mit einem ringförmigen Zentrierabschnitt versehen sein, so dass bei Wegfall der Zwischenscheibe die Montage von Düsenbaugruppe und Haltekörper vereinfacht wird.In the case of radially floating mounting of the nozzle needle in the throttle body, adequate guidance of the nozzle needle may no longer be ensured. In order to ensure a further guidance or centering of the nozzle needle, it is proposed according to a development that the section of the nozzle needle or the tappet body passing through the throttle body is centered via an intermediate disk axially attached to the nozzle body. Preferably, the washer has an annular centering portion received in the nozzle body to facilitate assembly of the nozzle assembly. To the intermediate disc, a holding body is preferably attached axially and clamped axially with the nozzle body via a nozzle retaining nut. Alternatively, instead of the intermediate disk, the holding body may also be provided with an annular centering section, so that the assembly of nozzle assembly and holding body is simplified when the intermediate disk is omitted.

Der Ferner zur Lösung der Eingangs gestellten Aufgabe vorgeschlagene Kraftstoffinjektor zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine umfasst eine erfindungsgemäße Düsenbaugruppe sowie eine Aktorbaugruppe zur Betätigung der Düsennadel. Vorzugsweise ist die Düsennadel über die Aktorbaugruppe direkt betätigbar. Unter direkter Betätigung der Düsennadel wird vorliegend eine Betätigung verstanden, bei welcher die Aktorkraft, beispielsweise über einen hydraulischen Koppler, ggf. verstärkt wird. Die vorgeschlagene Düsenbaugruppe ermöglicht einen insbesondere in axialer Richtung kompaktbauenden Kraftstoffinjektor, der zudem einfach zu montieren ist. Ferner können die Funktionen Führung/Zentrierung der Düsennadel, Schließdrossel, Abdichtung der Druckräume vor/nach der Schließdrossel und/oder Abstützung der Federkraft durch ein einfaches und damit kostengünstiges Bauteil realisiert werden. Das Bauteil kann eine Drosselabstufung für verschiedene Applikationsbereiche aufweisen und nach dem Prinzip eines Baukastens vorgehalten werden. Zur Montage des Bauteils wird die Düsennadel mit dem Stößelkörper verbunden und die Schließfeder und der Drosselbohrungskörper auf den Stößelkörper aufgeschoben. Danach wird der Stößelkörper in die Zwischenscheibe oder einen Haltekörper eingesteckt. Abschließend wird der Düsenkörper mit der Zwischenscheibe und/oder dem Haltekörper über eine Düsenspannmutter verbunden.The further proposed for solving the input task asked fuel injector for injecting fuel into the combustion chamber of an internal combustion engine comprises a nozzle assembly according to the invention and an actuator assembly for actuating the nozzle needle. Preferably, the nozzle needle via the Aktorbaugruppe is directly operable. Direct actuation of the nozzle needle is understood here to mean an actuation in which the actuator force, for example via a hydraulic coupler, is possibly amplified. The proposed nozzle assembly allows a fuel injector which is particularly compact in the axial direction and is also easy to assemble. Furthermore, the functions guide / centering of the nozzle needle, closing throttle, sealing of the pressure chambers before / after the closing throttle and / or support of the spring force can be realized by a simple and therefore cost-effective component. The component may have a throttle stepping for different application areas and be maintained according to the principle of a modular system. To assemble the component, the nozzle needle is connected to the plunger body and the closing spring and the throttle bore body are pushed onto the plunger body. Thereafter, the plunger body is inserted into the washer or a holding body. Finally, the nozzle body is connected to the intermediate disc and / or the holding body via a nozzle retaining nut.

Bevorzugte Ausführungsformen der Erfindung werden nachfolgend anhand der beigefügten Zeichnungen näher erläutert. Diese zeigen:

Figur 1
einen Längsschnitt durch eine erste erfindungsgemäße Düsenbaugruppe und
Figur 2
einen ausschnittsweisen Längsschnitt durch eine zweite erfindungsgemäße Düsenbaugruppe.
Preferred embodiments of the invention are explained below with reference to the accompanying drawings. These show:
FIG. 1
a longitudinal section through a first nozzle assembly according to the invention and
FIG. 2
a partial longitudinal section through a second nozzle assembly according to the invention.

Ausführliche Beschreibung der ZeichnungenDetailed description of the drawings

Die in der Figur 1 dargestellte Düsenbaugruppe umfasst eine Düsennadel 1, welche in einer Hochdruckbohrung 2 eines Düsenkörpers 3 hubbeweglich geführt ist. Über die Hubbewegung der Düsennadel 1 ist wenigstens eine Einspritzöffnung 4 freigebbar und verschließbar, über welche unter hohem Druck stehender Kraftstoff in den Brennraum einer Brennkraftmaschine (nicht dargestellt) einspritzbar ist. Die Düsennadel 1 wird über eine nicht dargestellte Aktorbaugruppe betätigt. Vorzugsweise erfolgt die Betätigung der Düsennadel 1 direkt, ggf. unter Zwischenschaltung eines hydraulischen Kopplers. Die Aktorbaugruppe kann beispielsweise einen Magnetaktor oder einen Piezoaktor umfassen.The in the FIG. 1 illustrated nozzle assembly comprises a nozzle needle 1, which is guided in a high-pressure bore 2 of a nozzle body 3 in a liftable manner. About the lifting movement of the nozzle needle 1 is at least one injection port 4 can be opened and closed, via which high-pressure fuel in the combustion chamber of an internal combustion engine (not shown) can be injected. The nozzle needle 1 is actuated via an actuator assembly, not shown. Preferably, the actuation of the nozzle needle 1 is carried out directly, possibly with the interposition of a hydraulic coupler. The actuator assembly may include, for example, a magnetic actuator or a piezoelectric actuator.

Zur Führung der Düsennadel 1 sind im Düsenkörper 3 zwei Führungsabschnitte 5, 6 ausgebildet, welche mit entsprechenden Abschnitten an der Düsennadel 1 führend zusammenwirken. Im Bereich des Führungsabschnitts 5, welcher in der Nähe eines Düsensitzes 13 ausgebildet ist, weist die Düsennadel 1 einen Abschnitt mit vergrößertem Durchmesser auf, über welchen die Düsennadel 1 im Führungsabschnitt 5 geführt ist. Der Abschnitt mit vergrößertem Durchmesser der Düsennadel 1 weist außenumfangsseitig Anschliffe auf, um Durchströmkanäle für den Kraftstoff auszubilden. Vorzugsweise sind die Anschliffe über den Umfang der Düsennadel 1 gleichmäßig verteilt ausgebildet. Ein weiterer Führungsabschnitt 6 ist in axialem Abstand zum Führungsabschnitt 5 angeordnet. Hier wirkt der Führungsabschnitt 6 mit einem Drosselbohrungskörper 7 zusammen, welcher an einem radial verlaufenden Absatz der Düsennadel 1 abgestützt ist. Der Drosselbohrungskörper 7 weist einen Außendurchmesser D1 auf, welcher größer als der Außendurchmesser D2 der Düsennadel 1 im Kontaktbereich mit dem Drosselbohrungskörper 7 ist. Dadurch ist die Führungsfunktion des Drosselbohrungskörpers 7 gewährleistet.To guide the nozzle needle 1, two guide sections 5, 6 are formed in the nozzle body 3, which cooperate leading with corresponding portions of the nozzle needle 1. In the region of the guide section 5, which is formed in the vicinity of a nozzle seat 13, the nozzle needle 1 has a section with an enlarged diameter, via which the nozzle needle 1 is guided in the guide section 5. The enlarged diameter portion of the nozzle needle 1 has outer peripheral side polished portions to form flow passages for the fuel. Preferably, the polished sections are uniformly distributed over the circumference of the nozzle needle 1. Another guide section 6 is arranged at an axial distance from the guide section 5. Here, the guide section 6 cooperates with a throttle bore body 7, which is supported on a radially extending shoulder of the nozzle needle 1. The throttle bore body 7 has an outer diameter D 1 , which is greater than the outer diameter D 2 of the nozzle needle 1 in the contact area with the throttle body 7 is. As a result, the guiding function of the throttle body 7 is ensured.

Gemäß einer alternativen Ausführungsform der Erfindung kann der Drosselbohrungskörper 7 auch einstückig mit der Düsennadel 1 ausgebildet sein. Der Drosselbohrungskörper 7 wird dann durch einen Abschnitt mit vergrößertem Durchmesser der Düsennadel 1 oder einem mit der Düsennadel 1 einstückig verbundenen Drosselbohrungskörper 7 gebildet. Die Verbindung kann derart gewählt sein, dass ein Kraft-, Form- und/oder Stoffschluss bewirkt wird.According to an alternative embodiment of the invention, the throttle bore body 7 may also be formed integrally with the nozzle needle 1. The throttle body 7 is then formed by an enlarged diameter portion of the nozzle needle 1 or a throttle body 7 integrally connected to the nozzle needle 1. The compound can be chosen such that a force, shape and / or material bond is effected.

Im Drosselbohrungskörper 7 ist wenigstens eine als Axialbohrung ausgeführte Drosselbohrung 9 ausgebildet. Über die wenigstens eine Drosselbohrung 9 werden ein erster, in Verbindung mit einer Zulaufbohrung 16 stehender Druckraum und ein zweiter, in Verbindung mit der wenigstens einen Einspritzöffnung 4 stehender Druckraum in der Weise hydraulisch verbunden, dass der hydraulische Druck p1 im ersten Druckraum größer als der hydraulische Druck p2 im zweiten Druckraum ist. Der hydraulische Druck p1 im ersten Druckraum bewirkt demzufolge eine in Schließrichtung der Düsennadel 1 auf den Drosselbohrungskörper 7 wirkende Kraft, welche beim Nadelschließen unterstützend wirkt. Der Effekt kann durch die am Drosselbohrungskörper 7 ausgebildeten hydraulischen Wirkflächen noch verstärkt werden. Vorliegend sind die hydraulischen Wirkflächen derart gestaltet, dass die den ersten Druckraum begrenzende hydraulische Wirkfläche A1 größer als die den zweiten Druckraum begrenzende hydraulische Wirkfläche A2 ist. In Schließrichtung wird der Drosselbohrungskörper 7 ferner von der Federkraft einer Schließfeder 8 beaufschlagt, die einerseits am Drosselbohrungskörper 7 andererseits an einem Haltekörper 15 bzw. einer zwischen Haltekörper 15 und dem Düsenkörper 3 angeordneten Zwischenscheibe 11 abgestützt ist. In der Zwischenscheibe 11 bzw. im Haltekörper 15 ist auch die Zulaufbohrung 16 ausgebildet, welche den ersten Druckraum mit einer Hochdruckquelle verbindet. Die Zwischenscheibe 11 bzw. der Haltekörper 15 ist axial an den Düsenkörper 3 angesetzt und mit diesem über eine Düsenspannmutter (nicht dargestellt) axial verspannt. Die aneinander liegenden Stirnflächen bilden Dichtflächen 14 aus, über welche der erste Druckraum gegenüber der Umgebung hochdruckfest abgedichtet ist. Der zweite Führungsabschnitt 6 erstreckt sich im Wesentlichen bis an die Dichtflächen 14, um einen möglichst großen axialen Abstand der beiden Führungsabschnitte 5, 6 zu gewährleisten, wodurch die Führung der Düsennadel 1 optimiert wird. Der Führungsabschnitt 6 wird lediglich dadurch begrenzt, dass die im ersten Druckraum aufgenommene Schließfeder 8 den Hub des Drosselbohrungskörpers 7 beschränkt.In the throttle bore body 7, at least one throttle bore 9 designed as an axial bore is formed. About the at least one throttle bore 9, a first, in connection with an inlet bore 16 standing pressure chamber and a second, in connection with the at least one injection port 4 stationary pressure chamber are hydraulically connected in such a way that the hydraulic pressure p 1 in the first pressure chamber greater than that hydraulic pressure p 2 in the second pressure chamber is. The hydraulic pressure p 1 in the first pressure chamber consequently causes a force acting in the closing direction of the nozzle needle 1 on the throttle bore body 7, which acts to assist the needle closure. The effect can be further enhanced by the hydraulic active surfaces formed on the throttle body 7. In the present case, the active hydraulic surfaces are designed in such a way that the hydraulic effective area A 1 delimiting the first pressure chamber is greater than the hydraulic effective area A 2 delimiting the second pressure chamber. In the closing direction of the throttle bore body 7 is further acted upon by the spring force of a closing spring 8, on the one hand on the throttle body 7 on the other hand to a holding body 15 and a support body 15 and the nozzle body 3 arranged intermediate disc 11 is supported. In the intermediate disc 11 or in the holding body 15 and the inlet bore 16 is formed, which connects the first pressure chamber with a high-pressure source. The intermediate plate 11 and the holding body 15 is axially attached to the nozzle body 3 and axially clamped with this via a nozzle lock nut (not shown). The abutting end faces form sealing surfaces 14, via which the first pressure chamber is sealed against high pressure in relation to the environment. The second guide portion 6 extends substantially to the sealing surfaces 14 in order to ensure the greatest possible axial distance between the two guide sections 5, 6, whereby the guide of the nozzle needle. 1 is optimized. The guide portion 6 is limited only by the fact that the recorded in the first pressure chamber closing spring 8 limits the stroke of the throttle body 7.

Der Drosselbohrungskörper 7 wird von einem Stößelkörper 10 durchsetzt, welcher mit der Düsennadel 1 einstückig verbunden ist. Die Verbindung 18 kann wiederum eine kraft-, form- und/oder stoffschlüssige Verbindung 18 sein. Der Stößelkörper 10 weist einen Außendurchmesser D3 auf, welcher kleiner als der Außendurchmesser D2 der Düsennadel 1 gewählt ist. Dadurch ist ein hydraulisches Wirkflächenverhältnis A1 > A2 sichergestellt. Der Stößelkörper 10 dient der Wirkverbindung der Düsennadel 1 mit der nicht dargestellten Aktorbaugruppe, wobei die Wirkverbindung auch über einen Kopplerkörper und/oder ein Kopplervolumen herstellbar ist.The throttle body 7 is penetrated by a plunger body 10 which is integrally connected to the nozzle needle 1. The connection 18 may in turn be a positive, positive and / or cohesive connection 18. The plunger body 10 has an outer diameter D 3 , which is smaller than the outer diameter D 2 of the nozzle needle 1 is selected. This ensures a hydraulic effective area ratio A 1 > A 2 . The plunger body 10 serves for the operative connection of the nozzle needle 1 with the actuator assembly, not shown, wherein the active compound can also be produced via a coupler body and / or a coupler volume.

Bei dem in der Figur 1 dargestellten Ausführungsbeispiel einer erfindungsgemäßen Düsenbaugruppe werden die Funktionen Führung/Zentrierung, Schließdrossel, Abdichtung der Druckräume vor/nach der Schließdrossel und Abstützung der Federkraft in einem einzigen Bauteil realisiert. Dieses Bauteil ist zudem einfach und kostengünstig herstellbar. Ferner wird die Montage der Düsenbaugruppe vereinfacht. Über die beiden axial beabstandeten Führungsabschnitte 5, 6 ist eine optimale Führung der Düsennadel 1 im Düsenkörper 3 gewährleistet. Ferner bewirken die am Drosselbohrungskörper 7 ausgebildeten hydraulischen Wirkflächen A1 und A2 aufgrund ihres Größenverhältnisses eine zusätzliche in axialer Richtung wirkende hydraulische Kraft. Gleiches gilt in Bezug auf die wenigstens eine im Drosselbohrungskörper 7 ausgebildete Drosselbohrung 9, welche vorzugsweise als Axialbohrung ausgeführt ist. Auf diese Weise wird eine funktionsund fertigungsoptimierte Düsenbaugruppe geschaffen.In the in the FIG. 1 illustrated embodiment of a nozzle assembly according to the invention, the functions guide / centering, closing throttle, sealing the pressure chambers before / after the closing throttle and support the spring force realized in a single component. This component is also easy and inexpensive to produce. Furthermore, the assembly of the nozzle assembly is simplified. Over the two axially spaced guide portions 5, 6 an optimal guidance of the nozzle needle 1 in the nozzle body 3 is ensured. Furthermore, the hydraulic active surfaces A 1 and A 2 formed on the throttle body 7 cause, due to their size ratio, an additional hydraulic force acting in the axial direction. The same applies with respect to the at least one throttle bore formed in the throttle body 7 7, which is preferably designed as an axial bore. In this way, a function and production optimized nozzle assembly is created.

Figur 2 zeigt eine Abwandlung der Ausführungsform der Figur 1. Im Unterschied zur Ausführungsform der Figur 1 sind vorliegend die Düsennadel 1 und der Drosselbohrungskörper 7 als separate Bauteile ausgeführt. Dies ermöglicht eine radial schwimmende Lagerung der Düsennadel 1 im Bereich des Führungsabschnitts 6. Durch die radial schwimmende Lagerung der Düsennadel 1 wird eine Biegebeanspruchung der Düsennadel 1 bei fehlender Koaxialität der Bauteile zueinander vermieden. Auch im Ausführungsbeispiel der Figur 2 ist die Düsennadel 1 mit einem Stößelkörper 10 einstückig verbunden, wobei der Stößelkörper 10 ferner in der Zwischenscheibe 11 bzw. dem Haltekörper 15 aufgenommen ist. Die Düsennadel 1 erfährt somit über den einstückig verbundenen Stößelkörper 10 eine weitere Führung bzw. Zentrierung, welche bei fehlender Koaxialität der Bauteile Stößelkörper 10, Düsennadel 1 und Drosselbohrungskörper 7 zu einer Biegebeanspruchung der Düsennadel 1 führen kann. Dem kann dadurch entgegengewirkt werden, dass die Düsennadel 1 bzw. der einstückig mit der Düsennadel 1 verbundene Stößelkörper 10 radial schwimmend im Drosselbohrungskörper 7 gelagert ist. Zur radial schwimmenden Lagerung der Düsennadel 1 bzw. des Stößelkörpers 10 ist im Drosselbohrungskörper 7 vorliegend ein Ringspalt 17 ausgebildet. Der Ringspalt 17 wird zur Seite des zweiten Druckraumes hin von einer ringförmigen Stirnfläche der Düsennadel 1 überdeckt, so dass kein zusätzlicher Strömungskanal geschaffen wird, über welchen Kraftstoff aus dem ersten FIG. 2 shows a modification of the embodiment of the FIG. 1 , In contrast to the embodiment of FIG. 1 In the present case, the nozzle needle 1 and the throttle bore body 7 are designed as separate components. This allows a radially floating mounting of the nozzle needle 1 in the region of the guide section 6. By the radially floating mounting of the nozzle needle 1, a bending stress of the nozzle needle 1 is avoided in the absence of coaxiality of the components to each other. Also in the embodiment of FIG. 2 the nozzle needle 1 is integrally connected to a plunger body 10, wherein the plunger body 10 further is received in the washer 11 and the holding body 15. The nozzle needle 1 thus experiences on the integrally connected plunger body 10, a further guide or centering, which can lead to a bending stress of the nozzle needle 1 in the absence of coaxiality of the components plunger body 10, nozzle needle 1 and throttle bore body 7. This can be counteracted by the nozzle needle 1 or the plunger body 10 integrally connected to the nozzle needle 1 being mounted radially floating in the throttle bore body 7. For radially floating mounting of the nozzle needle 1 and the plunger body 10, an annular gap 17 is formed in the throttle body 7 in the present case. The annular gap 17 is covered to the side of the second pressure chamber out by an annular end face of the nozzle needle 1, so that no additional flow channel is provided, via which fuel from the first

Druckraum in den zweiten Druckraum strömen kann. Um die Zentrierung der Düsennadel 1 bzw. des Stößelkörpers 10 zu erleichtern, ist an der Zwischenscheibe 11 bzw. am Haltekörper 15 ein ringförmiger Zentrierabschnitt 12 ausgebildet, mit welchem die Zwischenscheibe 11 bzw. der Haltekörper 15 in die Hochdruckbohrung 2 des Düsenkörpers 3 eingesetzt werden kann. Insofern ist über die Zwischenscheibe 11 bzw. den Haltekörper 15 weiterhin eine Führung bzw. Zentrierung der Düsennadel 1 in einem sitzfernen Bereich gewährleistet.Pressure chamber can flow into the second pressure chamber. To facilitate the centering of the nozzle needle 1 and the plunger body 10, an annular centering portion 12 is formed on the washer 11 and on the holding body 15, with which the washer 11 and the holding body 15 can be inserted into the high-pressure bore 2 of the nozzle body 3 , In this respect, a guide or centering of the nozzle needle 1 in an area remote from the seat is still ensured via the intermediate disk 11 or the holding body 15.

Claims (9)

  1. Nozzle assembly for a fuel injector, having a nozzle needle (1) which is guided in a highpressure bore (2) of a nozzle body (3), for the purposes of opening up and closing off at least one injection opening (4), by way of at least one guide section (5, 6) and which is acted on at least indirectly by the spring force of a closing spring (8), and having a throttle bore body (7) which is spring-loaded in an axial direction, wherein the throttle bore body (7) bears against the nozzle needle (1) and is acted on in an axial direction by the spring force of the closing spring (8), characterized in that the throttle bore body (7) is extended through by the nozzle needle (1), wherein that section of the nozzle needle (1) which extends through the throttle bore body (7) has an outer diameter D3 which is smaller than the outer diameter D2 of the nozzle needle (1).
  2. Nozzle assembly according to Claim 1,
    characterized in that the throttle bore body (7) is of piston-like form and has an outer diameter D1 which is greater than the outer diameter D2 of the nozzle needle (1) in the contact region with the throttle bore body (7).
  3. Nozzle assembly according to Claim 1 or 2,
    characterized in that the throttle bore body (7) has at least one throttle bore which is formed as an axial bore.
  4. Nozzle assembly according to one of the preceding claims,
    characterized in that the throttle bore body (7) interacts, for the purposes of guiding the nozzle needle (1), with a guide section (6) of the nozzle body (3).
  5. Nozzle assembly according to one of the preceding claims,
    characterized in that the throttle bore body (7) is connected integrally to the nozzle needle (1).
  6. Nozzle assembly according to one of the preceding claims, characterized in that that section of the nozzle needle (1) which extends through the throttle bore body (7) is a plunger body (10) which is connected integrally to the nozzle needle (1).
  7. Nozzle assembly according to Claim 1 or 6,
    characterized in that that section of the nozzle needle (1) which extends through the nozzle bore body (7), or the plunger body (10), is mounted in radially floating fashion in the throttle bore body (7).
  8. Nozzle assembly according to Claim 1, 6 or 7,
    characterized in that that section of the nozzle needle (1) which extends through the throttle bore body (7), or the plunger body (10), is centred by way of an intermediate disk (11) which is mounted axially on the nozzle body (3), which intermediate disk preferably has a ring-shaped centring section (12) which is received in the nozzle body (3).
  9. Fuel injector for injecting fuel into the combustion chamber of an internal combustion engine, having a nozzle assembly according to one of the preceding claims and having an actuator assembly for the actuation of the nozzle needle (1), wherein the nozzle needle (1) can be actuated preferably directly by way of the actuator assembly.
EP12723468.0A 2011-05-30 2012-05-23 Nozzle assembly for a fuel injector, and fuel injector Active EP2715103B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110076665 DE102011076665A1 (en) 2011-05-30 2011-05-30 Nozzle assembly for a fuel injector and fuel injector
PCT/EP2012/059601 WO2012163759A1 (en) 2011-05-30 2012-05-23 Nozzle assembly for a fuel injector, and fuel injector

Publications (2)

Publication Number Publication Date
EP2715103A1 EP2715103A1 (en) 2014-04-09
EP2715103B1 true EP2715103B1 (en) 2016-08-10

Family

ID=46149458

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12723468.0A Active EP2715103B1 (en) 2011-05-30 2012-05-23 Nozzle assembly for a fuel injector, and fuel injector

Country Status (4)

Country Link
EP (1) EP2715103B1 (en)
CN (1) CN103582751A (en)
DE (1) DE102011076665A1 (en)
WO (1) WO2012163759A1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013212142A1 (en) * 2013-06-25 2015-01-08 Robert Bosch Gmbh Nozzle assembly for a fuel injector and fuel injector
DE102014209961A1 (en) * 2014-05-26 2015-11-26 Robert Bosch Gmbh Nozzle assembly for a fuel injector and fuel injector
GB201421885D0 (en) * 2014-12-09 2015-01-21 Delphi International Operations Luxembourg S.�.R.L. Fuel injector
DE102015219646A1 (en) * 2015-10-09 2017-04-13 Continental Automotive Gmbh Fluid injection device for internal combustion engines
CN105673280B (en) * 2016-03-15 2018-07-03 任一虎 A kind of fuel nozzle
GB2585064B (en) * 2019-06-27 2021-11-10 Delphi Tech Ip Ltd Fuel injector with closed loop detection
CN112065627A (en) * 2020-09-04 2020-12-11 温州弘腾科技有限公司 Area compensation manufacturing method of pressure balance oil nozzle and pressure balance oil injection manufactured by method

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3796986B2 (en) * 1998-11-24 2006-07-12 いすゞ自動車株式会社 Method and apparatus for measuring fuel injection nozzle characteristics
DE10213441A1 (en) * 2002-03-26 2003-10-23 Hatz Motoren Fuel injector with hydraulic nozzle needle control
DE102007021330A1 (en) * 2007-05-07 2008-11-13 Robert Bosch Gmbh Fuel injector for an internal combustion engine with common rail injection system
DE102009001704B4 (en) 2009-03-20 2018-06-28 Robert Bosch Gmbh Fuel injector
DE102010008467A1 (en) * 2010-02-18 2011-08-18 Continental Automotive GmbH, 30165 High pressure fuel injector for an internal combustion engine

Also Published As

Publication number Publication date
EP2715103A1 (en) 2014-04-09
DE102011076665A1 (en) 2012-12-06
CN103582751A (en) 2014-02-12
WO2012163759A1 (en) 2012-12-06

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