EP2532877A1 - Fuel injection valve for combustion engines - Google Patents

Fuel injection valve for combustion engines Download PDF

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Publication number
EP2532877A1
EP2532877A1 EP20120169087 EP12169087A EP2532877A1 EP 2532877 A1 EP2532877 A1 EP 2532877A1 EP 20120169087 EP20120169087 EP 20120169087 EP 12169087 A EP12169087 A EP 12169087A EP 2532877 A1 EP2532877 A1 EP 2532877A1
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EP
European Patent Office
Prior art keywords
fuel injection
clamping nut
injection valve
holding body
valve 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.)
Granted
Application number
EP20120169087
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German (de)
French (fr)
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EP2532877B1 (en
Inventor
Dietmar Uhlmann
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2532877A1 publication Critical patent/EP2532877A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/803—Fuel injection apparatus manufacture, repair or assembly using clamp elements and fastening means; e.g. bolts or screws
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8076—Fuel injection apparatus manufacture, repair or assembly involving threaded members

Definitions

  • the invention relates to a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • Such a fuel injection valve is out of DE 10 2008 001 330 A1 the applicant known. It essentially comprises, on the side facing the combustion chamber of the internal combustion engine, a nozzle body accommodated in a housing, in which a nozzle needle is moved up and down.
  • the nozzle needle is at least indirectly axially braced together with the nozzle body by means of a clamping nut against a holding body arranged in the housing.
  • the clamping nut has an internal thread as part of a threaded connection, which cooperates with a corresponding external thread on the holding body and in particular also forms a seal of the housing arranged in the region of the nozzle body fuel, which is meant when operating fuel injection valve under relatively high pressure, here a pressure of more than 1500bar, stands.
  • the present invention seeks to further develop a fuel injection valve for internal combustion engines according to the preamble of claim 1 such that the threaded connection, which connects the clamping nut with the holding body and a seal of the housing after forms on the outside, so educate, that it is particularly dense, especially at relatively high fuel pressures.
  • the invention is based on the idea of designing the threaded connection in such a way that at least two toothing regions with different thread dimensions are present which follow one another axially in the longitudinal direction of the housing. This makes it possible to optimize the respective toothed areas with regard to their specific properties or tasks. In particular, this makes it possible, for example, optimally form a first toothed area with respect to its tightness, while a second toothed area is optimized with respect to the relatively simple mounting of the clamping nut.
  • a thread-free intermediate section is formed between the two toothed regions.
  • This unthreaded intermediate section makes it possible, in particular, to manufacture the two toothing regions on the clamping nut or on the holding body in a relatively simple manner.
  • the axial length of the unthreaded intermediate region corresponds to the axial length of a first toothed region on the clamping nut, which is arranged on the side of the clamping nut facing the holding body.
  • the second toothed region on the side of the clamping nut facing the nozzle body have the smaller thread diameter and a double number of teeth than the first toothed region.
  • the wall thickness of the clamping nut in the second toothed region is greater than in the first toothed region. Due to the increased wall thickness of the clamping nut, the occurring compressive stresses can be absorbed particularly well, or a widening of the clamping nut due to the hydraulic pressure compared to the prior art is reduced, which increases the tightness of the second toothed region.
  • Fig. 1 is a section of a fuel injection valve 100 according to the invention shown, as it is used for injecting fuel in a combustion chamber of an internal combustion engine, not shown, in particular a self-igniting internal combustion engine.
  • the fuel injection valve 100 is part of a so-called common-rail injection system, in which each cylinder of the internal combustion engine, a separate, supplied by a common rail with fuel fuel injection valve 100 is assigned.
  • the injection pressure of the fuel injection valve 100 is preferably more than 1500 bar.
  • the fuel injection valve 100 has a housing 10, which is shown only in regions, in which, inter alia, an injection valve member (not shown), in particular in the form of a nozzle needle, is arranged to be movable up and down.
  • a nozzle body 11 is arranged, which simultaneously forms the combustion chamber of the internal combustion engine facing the end of the fuel injection valve 100.
  • the nozzle body 11 has a step 12 on its outer periphery.
  • a throttle plate 13 is arranged, as well as on the nozzle body 11 side facing the throttle plate 13, a valve plate 14.
  • a holding body 15 of the housing 10 against which the nozzle body eleventh , the throttle plate 13 and the valve plate 14 are axially braced.
  • the axial clamping of the addressed components of the fuel injection valve 100 by means of a clamping nut 18, which has at its end facing the nozzle body 11 at its inner wall a diameter stage 19 which rests flush against the step 12 of the nozzle body 11.
  • the Fig. 1 is formed between the holding body 15 and the clamping nut 18, a threaded connection 20.
  • the threaded connection 20 has a first toothed region 21 on the side facing away from the nozzle body 11 and a second toothed region 22 on the side facing the nozzle body 11.
  • a first toothed region 21 on the side facing away from the nozzle body 11
  • a second toothed region 22 on the side facing the nozzle body 11.
  • the intermediate region 23 is formed in the region of the holding body 15 as a cylindrical portion 17 with a continuous same outer diameter.
  • two sections 24, 25 are formed, each of which is cylindrical, the section 24 facing the first gear section 21 having a larger inner diameter than that of the second gear section 22 facing portion 25.
  • the two portions 24, 25 in about the same length, z. B. each about 2mm, formed.
  • the second toothed region 22 is located near the lower end face 26 of the holding body 15 in the region of the holding body 15 on the side facing the valve plate 14.
  • FIG. 2 to 4 different phases of the assembly process of the clamping nut 18 are shown on the holding body 15.
  • the state is shown in which the first toothed region 21 of the clamping nut 18 is located in the region of the second toothed region 22 of the holding body 15.
  • a gap 27 is formed between the teeth of the second toothed region 22 of the holding body 15.
  • the state is shown in which the first toothed region 21 of the clamping nut 18 in the region of the first toothed region 21 of the holding body 15 arrived. It is essential that at the beginning of the engagement of the thread of the first toothed portion 21 of the clamping nut 18 in the first gear portion of the holding body 15, the output of the winding of the first toothed portion 21 of the clamping nut 18 is still in abutting contact with the second toothed portion 22 of the holding body 15. As a result, the first toothed region 21 of the clamping nut 18 is always in engagement with one of the two toothed regions 21, 22 of the holding body 15, so that slippage or falling through of the clamping nut 18 during assembly on the holding body 15 is avoided.

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  • Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The valve (100) has a nozzle body (11) indirectly axially braced in a housing (10) against a support body (15) by a clamping nut (18). A threaded connection (20) is formed between the support body and the clamping nut in a region axially spaced to the nozzle body. The threaded connection comprises toothed regions (21, 22) with different screw thread dimensions, which are axially arranged one behind the other along longitudinal direction of the housing. A screw thread-free intermediate region (23) is formed between the toothed regions.

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Kraftstoffeinspritzventil für Brennkraftmaschinen nach dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injection valve for internal combustion engines according to the preamble of claim 1.

Ein derartiges Kraftstoffeinspritzventil ist aus der DE 10 2008 001 330 A1 der Anmelderin bekannt. Es umfasst im Wesentlichen auf der dem Brennraum der Brennkraftmaschine zugewandten Seite einen in einem Gehäuse aufgenommenen Düsenkörper, in dem eine Düsennadel auf- und abbeweglich geführt ist. Die Düsennadel ist zusammen mit dem Düsenkörper mittels einer Spannmutter gegen einen im Gehäuse angeordneten Haltekörper zumindest mittelbar axial verspannt. Die Spannmutter weist ein Innengewinde als Teil einer Gewindeverbindung auf, das mit einem entsprechenden Außengewinde an dem Haltekörper zusammenwirkt und insbesondere auch eine Abdichtung des Gehäuses für im Bereich des Düsenkörpers angeordneten Kraftstoff ausbildet, der beim Betrieb Kraftstoffeinspritzventils unter relativ hohem Druck, gemeint ist hier ein Druck von mehr als 1500bar, steht.Such a fuel injection valve is out of DE 10 2008 001 330 A1 the applicant known. It essentially comprises, on the side facing the combustion chamber of the internal combustion engine, a nozzle body accommodated in a housing, in which a nozzle needle is moved up and down. The nozzle needle is at least indirectly axially braced together with the nozzle body by means of a clamping nut against a holding body arranged in the housing. The clamping nut has an internal thread as part of a threaded connection, which cooperates with a corresponding external thread on the holding body and in particular also forms a seal of the housing arranged in the region of the nozzle body fuel, which is meant when operating fuel injection valve under relatively high pressure, here a pressure of more than 1500bar, stands.

Der Trend in der Kraftstoffeinspritztechnik geht zu immer höheren Kraftstoffeinspritzdrücken zur Erzielung besserer Wirkungsgrade bzw. eines geringeren Verbrauchs. Dadurch sind auch die Anforderungen an die Dichtigkeit des Gehäuses, im vorliegenden Fall insbesondere im Bereich der Gewindeverbindung, immer höher.The trend in fuel injection technology is towards ever higher fuel injection pressures to achieve better efficiencies or lower consumption. As a result, the requirements for the tightness of the housing, in the present case in particular in the field of threaded connection, always higher.

Offenbarung der ErfindungDisclosure of the invention

Ausgehend von dem dargestellten Stand der Technik liegt der Erfindung die Aufgabe zugrunde, ein Kraftstoffeinspritzventil für Brennkraftmaschinen nach dem Oberbegriff des Anspruchs 1 derart weiterzubilden, dass dessen Gewindeverbindung, die die Spannmutter mit dem Haltekörper verbindet und eine Abdichtung des Gehäuses nach außen hin ausbildet, derart weiterzubilden, dass diese besonders dicht ist, insbesondere bei relativ hohen Kraftstoffdrücken.Based on the illustrated prior art, the present invention seeks to further develop a fuel injection valve for internal combustion engines according to the preamble of claim 1 such that the threaded connection, which connects the clamping nut with the holding body and a seal of the housing after forms on the outside, so educate, that it is particularly dense, especially at relatively high fuel pressures.

Diese Aufgabe wird bei einem Kraftstoffeinspritzventil für Brennkraftmaschinen mit den Merkmalen des Anspruchs 1 gelöst. Der Erfindung liegt dabei die Idee zugrunde, die Gewindeverbindung derart auszubilden, dass wenigstens zwei Verzahnungsbereiche mit unterschiedlichen Gewindeabmessungen vorhanden sind, die sich in Längsrichtung des Gehäuses axial hintereinander anschließen. Dadurch wird es ermöglicht, die jeweiligen Verzahnungsbereiche hinsichtlich ihrer spezifischen Eigenschaften bzw. Aufgaben zu optimieren. Insbesondere wird es dadurch ermöglicht, beispielsweise einen ersten Verzahnungsbereich hinsichtlich seiner Dichtigkeit optimal auszubilden, während ein zweiter Verzahnungsbereich hinsichtlich der relativ einfachen Montage der Spannmutter optimiert wird.This object is achieved in a fuel injection valve for internal combustion engines with the features of claim 1. The invention is based on the idea of designing the threaded connection in such a way that at least two toothing regions with different thread dimensions are present which follow one another axially in the longitudinal direction of the housing. This makes it possible to optimize the respective toothed areas with regard to their specific properties or tasks. In particular, this makes it possible, for example, optimally form a first toothed area with respect to its tightness, while a second toothed area is optimized with respect to the relatively simple mounting of the clamping nut.

Vorteilhafte Weiterbildungen des erfindungsgemäßen Kraftstoffeinspritzventils sind in den Unteransprüchen angegeben. In den Rahmen der Erfindung fallen sämtliche Kombinationen aus zumindest zwei von in den Ansprüchen, der Beschreibung und/oder den Figuren offenbarten Merkmalen.Advantageous developments of the fuel injection valve according to the invention are specified in the subclaims. All combinations of at least two of the features disclosed in the claims, the description and / or the figures fall within the scope of the invention.

In konstruktiv bevorzugter Ausgestaltung wird vorgeschlagen, dass zwischen den beiden Verzahnungsbereichen ein gewindefreier Zwischenabschnitt ausgebildet ist. Dieser gewindefreie Zwischenabschnitt ermöglicht insbesondere eine fertigungstechnisch relativ einfache Ausbildung der beiden Verzahnungsbereiche an der Spannmutter bzw. an dem Haltekörper.In a structurally preferred embodiment, it is proposed that a thread-free intermediate section is formed between the two toothed regions. This unthreaded intermediate section makes it possible, in particular, to manufacture the two toothing regions on the clamping nut or on the holding body in a relatively simple manner.

Besonders bevorzugt ist eine Ausgestaltung, bei der sich die Gewindeabmessungen der beiden Verzahnungsbereiche in den Gewindedurchmessern und der Zähneanzahl unterscheiden, und dass die Steigung der Verzahnungsbereiche gleich groß ist. Mittels einer derartigen unterschiedlichen Ausbildung der Gewindeabmessungen wird zum einen die gewünschte Dichtigkeit erzielt, währen zum anderen eine problemlose Montage der Spannmutter an dem Haltekörper ermöglicht wird.Particularly preferred is an embodiment in which the thread dimensions of the two toothed areas in the thread diameters and the number of teeth differ, and that the pitch of the toothed portions is equal. By means of such a different design of the thread dimensions, on the one hand, the desired tightness is achieved while, on the other hand, a trouble-free assembly of the clamping nut on the holding body is made possible.

In besonders bevorzugter konstruktiver Ausgestaltung wird vorgeschlagen, dass die axiale Länge des gewindefreien Zwischenbereichs der axialen Länge eines ersten Verzahnungsbereichs an der Spannmutter entspricht, der auf der dem Haltekörper zugewandten Seite der Spannmutter angeordnet ist. Durch eine derartige Ausbildung wird beim Verschrauben der Spannmutter auf den Haltekörper stets eine Führung bzw. ein Eingriff der Spannmutter an dem Haltekörper in axialer Richtung ermöglicht.In a particularly preferred structural embodiment, it is proposed that the axial length of the unthreaded intermediate region corresponds to the axial length of a first toothed region on the clamping nut, which is arranged on the side of the clamping nut facing the holding body. By such a training is when screwing the clamping nut on the holder body always allows a guide or engagement of the clamping nut on the holding body in the axial direction.

Zur Erzielung der gewünschten erhöhten Dichtigkeit der Gewindeverbindung wird vorgeschlagen, dass der zweite Verzahnungsbereich auf der dem Düsenkörper zugewandten Seite der Spannmutter den kleineren Gewindedurchmesser und eine doppelte Zähnezahl aufweist wie der erste Verzahnungsbereich. Dadurch wird es auf besonders einfache Art und Weise gemäß einer weiteren Ausgestaltung der Erfindung ermöglicht, dass die Wanddicke der Spannmutter im zweiten Verzahnungsbereich größer ist als im ersten Verzahnungsbereich. Durch die erhöhte Wanddicke der Spannmutter können dabei besonders gut die auftretenden Druckspannungen aufgenommen werden bzw. es wird ein Aufweiten der Spannmutter infolge des hydraulischen Drucks gegenüber dem Stand der Technik reduziert, was die Dichtigkeit des zweiten Verzahnungsbereichs erhöht.In order to achieve the desired increased tightness of the threaded connection, it is proposed that the second toothed region on the side of the clamping nut facing the nozzle body have the smaller thread diameter and a double number of teeth than the first toothed region. This makes it possible in a particularly simple manner according to a further embodiment of the invention that the wall thickness of the clamping nut in the second toothed region is greater than in the first toothed region. Due to the increased wall thickness of the clamping nut, the occurring compressive stresses can be absorbed particularly well, or a widening of the clamping nut due to the hydraulic pressure compared to the prior art is reduced, which increases the tightness of the second toothed region.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnung.Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawing.

Diese zeigt in:

Fig. 1
einen Teilausschnitt eines erfindungsgemäßen Kraftstoffeinspritzventils für Brennkraftmaschinen in einem Teillängsschnitt und
Fig. 2 bis 4
das Detail X gemäß der Fig. 1 im Verschraubungsbereich einer Spannmutter mit einem Haltekörper während verschiedener Phasen der Verschraubung der Spannmutter mit dem Haltekörper, in jeweils vergrößerter Ansicht.
This shows in:
Fig. 1
a partial section of a fuel injection valve according to the invention for internal combustion engines in a partial longitudinal section and
Fig. 2 to 4
the detail X according to the Fig. 1 in the screwing of a clamping nut with a holding body during different phases of screwing the clamping nut with the holding body, in each enlarged view.

In der Fig. 1 ist ein Ausschnitt aus einem erfindungsgemäßen Kraftstoffeinspritzventil 100 dargestellt, wie es zum Einspritzen von Kraftstoff in einem Brennraum einer nicht dargestellten Brennkraftmaschine, insbesondere einer selbstzündenden Brennkraftmaschine, dient. Insbesondere ist das Kraftstoffeinspritzventil 100 Bestandteil eines sogenannten Common-Rail-Einspritzsystems, bei dem jedem Zylinder der Brennkraftmaschine ein separates, durch ein gemeinsames Rail mit Kraftstoff versorgtes Kraftstoffeinspritzventil 100 zugeordnet ist. Hierbei beträgt der Einspritzdruck des Kraftstoffeinspritzventils 100 vorzugsweise mehr als 1500bar.In the Fig. 1 is a section of a fuel injection valve 100 according to the invention shown, as it is used for injecting fuel in a combustion chamber of an internal combustion engine, not shown, in particular a self-igniting internal combustion engine. In particular, the fuel injection valve 100 is part of a so-called common-rail injection system, in which each cylinder of the internal combustion engine, a separate, supplied by a common rail with fuel fuel injection valve 100 is assigned. Here, the injection pressure of the fuel injection valve 100 is preferably more than 1500 bar.

Das Kraftstoffeinspritzventil 100 weist ein lediglich bereichsweise dargestelltes Gehäuse 10 auf, in dem unter anderem ein nicht dargestelltes Einspritzventilglied, insbesondere in Form einer Düsennadel, auf- und abbeweglich angeordnet ist. Innerhalb des Gehäuses 10 ist ein Düsenkörper 11 angeordnet, der gleichzeitig das dem Brennraum der Brennkraftmaschine zugewandte Ende des Kraftstoffeinspritzventils 100 ausbildet. Der Düsenkörper 11 weist an seinem Außenumfang eine Stufe 12 auf. In der Darstellung der Fig. 1 oberhalb des Düsenkörpers 11 ist eine Drosselplatte 13 angeordnet, sowie auf der dem Düsenkörper 11 abgewandten Seite der Drosselplatte 13 eine Ventilplatte 14. Auf der der Drosselplatte 13 gegenüberliegenden Seite der Ventilplatte 14 schließt sich ein Haltekörper 15 des Gehäuses 10 an, gegen den der Düsenkörper 11, die Drosselplatte 13 und die Ventilplatte 14 axial verspannt sind. Das axiale Verspannen der angesprochenen Bauteile des Kraftstoffeinspritzventils 100 erfolgt mittels einer Spannmutter 18, die an ihrem dem Düsenkörper 11 zugewandten Ende an ihrer Innenwandung eine Durchmesserstufe 19 aufweist, die an der Stufe 12 des Düsenkörpers 11 bündig anliegt.The fuel injection valve 100 has a housing 10, which is shown only in regions, in which, inter alia, an injection valve member (not shown), in particular in the form of a nozzle needle, is arranged to be movable up and down. Within the housing 10, a nozzle body 11 is arranged, which simultaneously forms the combustion chamber of the internal combustion engine facing the end of the fuel injection valve 100. The nozzle body 11 has a step 12 on its outer periphery. In the presentation of the Fig. 1 above the nozzle body 11, a throttle plate 13 is arranged, as well as on the nozzle body 11 side facing the throttle plate 13, a valve plate 14. On the throttle plate 13 opposite side of the valve plate 14 is followed by a holding body 15 of the housing 10, against which the nozzle body eleventh , the throttle plate 13 and the valve plate 14 are axially braced. The axial clamping of the addressed components of the fuel injection valve 100 by means of a clamping nut 18, which has at its end facing the nozzle body 11 at its inner wall a diameter stage 19 which rests flush against the step 12 of the nozzle body 11.

Hinsichtlich des weiteren Aufbaus eines Kraftstoffeinspritzventils 100 sowie dessen Funktionsweise wird auf die DE 10 2008 001 330 A1 der Anmelderin verwiesen, die insofern Bestandteil dieser Anmeldung sein soll.With regard to the further construction of a fuel injection valve 100 and its operation is on the DE 10 2008 001 330 A1 referred to the applicant, which should be part of this application.

Im Bereich des Details X der Fig. 1 ist zwischen dem Haltekörper 15 und der Spannmutter 18 eine Gewindeverbindung 20 ausgebildet. Die Gewindeverbindung 20 weist auf der dem Düsenkörper 11 abgewandten Seite einen ersten Verzahnungsbereich 21 und auf der dem Düsenkörper 11 zugewandten Seite einen zweiten Verzahnungsbereich 22 auf. Wie insbesondere anhand der Fig. 3 erkennbar ist, ist zwischen dem ersten Verzahnungsbereich 21 und dem zweiten Verzahnungsbereich 22 sowohl an dem Düsenkörper 11, als auch an dem Haltekörper 15 jeweils ein verzahnungsfreier Zwischenbereich 23 vorgesehen. Der Zwischenbereich 23 ist im Bereich des Haltekörpers 15 als zylindrischer Abschnitt 17 mit durchgehend gleichem Außendurchmesser ausgebildet. Demgegenüber sind im Bereich der Spannmutter 18 im Bereich des Zwischenbereichs 23 zwei Abschnitte 24, 25 ausgebildet, die jeweils zylindrisch ausgebildet sind, wobei der dem ersten Verzahnungsbereich 21 zugewandte Abschnitt 24 einen größeren Innendurchmesser aufweist als der dem zweiten Verzahnungsbereich 22 zugewandte Abschnitt 25. Bevorzugt sind die beiden Abschnitte 24, 25 in etwa gleich lang, z. B. jeweils etwa 2mm, ausgebildet.In the area of the detail X the Fig. 1 is formed between the holding body 15 and the clamping nut 18, a threaded connection 20. The threaded connection 20 has a first toothed region 21 on the side facing away from the nozzle body 11 and a second toothed region 22 on the side facing the nozzle body 11. As in particular on the basis of Fig. 3 can be seen, is provided between the first gear portion 21 and the second gear portion 22 both on the nozzle body 11, and on the holding body 15 each have a tooth-free intermediate region 23. The intermediate region 23 is formed in the region of the holding body 15 as a cylindrical portion 17 with a continuous same outer diameter. In contrast, in the region of the clamping nut 18 in the region of the intermediate region 23, two sections 24, 25 are formed, each of which is cylindrical, the section 24 facing the first gear section 21 having a larger inner diameter than that of the second gear section 22 facing portion 25. Preferably, the two portions 24, 25 in about the same length, z. B. each about 2mm, formed.

Während der erste Verzahnungsbereich 21 im Bereich der Spannmutter 18 an dem dem Düsenkörper 11 abgewandten Ende der Spannmutter 18 angeordnet ist, befindet sich der zweite Verzahnungsbereich 22 im Bereich des Haltekörpers 15 auf der der Ventilplatte 14 zugewandten Seite nahe der unteren Stirnfläche 26 des Haltekörpers 15.While the first toothed region 21 in the region of the clamping nut 18 is arranged at the end of the clamping nut 18 facing away from the nozzle body 11, the second toothed region 22 is located near the lower end face 26 of the holding body 15 in the region of the holding body 15 on the side facing the valve plate 14.

Der erste Verzahnungsbereich 21, der am Haltekörper 15 als Außengewinde ausgebildet ist, weist ein Gewinde mit der Dimensionierung M17 x 0,75mm auf, während der zweite Verzahnungsbereich 22 am Haltekörper 15 als Außengewinde mit einer Dimensionierung von M16 x 0,75mm ausgebildet ist. Weiterhin weist der als Innengewinde ausgebildete erste Verzahnungsbereich 21 an der Spannmutter 18 die halbe Zähnezahl des zweiten Verzahungsbereichs 22 an der Spannmutter 18 auf.The first toothed area 21, which is formed on the holding body 15 as an external thread, has a thread with the dimensioning M17 x 0.75 mm, while the second toothed area 22 is formed on the holding body 15 as an external thread with a dimensioning of M16 x 0.75 mm. Furthermore, the first toothing region 21 formed as an internal thread on the clamping nut 18 has half the number of teeth of the second toothing region 22 on the clamping nut 18.

Wie man insbesondere anhand der Fig. 3 erkennt, wird durch die unterschiedliche Dimensionierung der Gewinde der beiden Gewindeabschnitte 21, 22 bei durchgehend zylindrischer Außenkontur der Spannmutter 18 im Bereich der Gewindeverbindung 20 im Bereich des zweiten Verzahnungsbereichs 22 der Spannmutter 18 vom Zahngrund der Verzahnung eine Wanddicke A der Spannmutter 18 ausgebildet, die größer ist als die Wanddicke a der Spannmutter 18 im Bereich des ersten Verzahnungsbereichs 21. Wie man ferner anhand der Fig. 1 erkennt, ist die Länge L1 des ersten Verzahnungsbereichs 21 an der Spannmutter 18 vorzugsweise gleich lang ausgebildet wie die Länge LZB des gewindefreien Zwischenbereichs 23.How to particular on the basis of Fig. 3 detects, is formed by the different sizing of the threads of the two threaded portions 21, 22 with continuous cylindrical outer contour of the clamping nut 18 in the region of the threaded connection 20 in the region of the second toothed region 22 of the clamping nut 18 from the tooth base of the toothing a wall thickness A of the clamping nut 18, the larger is as the wall thickness a of the clamping nut 18 in the region of the first toothed region 21. As can also be seen from the Fig. 1 recognizes the length L 1 of the first toothed portion 21 is formed on the clamping nut 18 is preferably the same length as the length L ZB of the unthreaded intermediate portion 23rd

In den Fig. 2 bis 4 sind unterschiedliche Phasen des Montagevorganges der Spannmutter 18 an dem Haltekörper 15 dargestellt. Bei der Fig. 2 ist der Zustand dargestellt, bei dem der erste Verzahnungsbereich 21 der Spannmutter 18 sich im Bereich des zweiten Verzahnungsbereichs 22 des Haltekörpers 15 befindet. Hierbei erkennt man insbesondere, dass aufgrund der halben Zähneanzahl des ersten Verzahnungsbereichs 21 an der Spannmutter 18 sich zwischen den Zähnen des zweiten Verzahnungsbereichs 22 des Haltekörpers 15 jeweils eine Lücke 27 ausbildet.In the Fig. 2 to 4 different phases of the assembly process of the clamping nut 18 are shown on the holding body 15. In the Fig. 2 the state is shown in which the first toothed region 21 of the clamping nut 18 is located in the region of the second toothed region 22 of the holding body 15. In this case, it can be seen in particular that due to half the number of teeth of the first toothed region 21 on the clamping nut 18, a gap 27 is formed between the teeth of the second toothed region 22 of the holding body 15.

In der Fig. 3 ist der Zustand dargestellt, bei dem der erste Verzahnungsbereich 21 der Spannmutter 18 in dem Bereich des ersten Verzahnungsbereichs 21 des Haltekörpers 15 gelangt. Wesentlich dabei ist, dass zu Beginn des Eingriffs der Gewindewindung des ersten Verzahnungsbereichs 21 der Spannmutter 18 in den ersten Verzahnungsbereich des Haltekörpers 15 der Ausgang der Windung des ersten Verzahnungsbereichs 21 der Spannmutter 18 sich noch in Anlagekontakt mit dem zweiten Verzahnungsbereich 22 des Haltekörpers 15 befindet. Dadurch befindet sich der erste Verzahnungsbereich 21 der Spannmutter 18 stets in Eingriff mit einem der beiden Verzahnungsbereiche 21, 22 des Haltekörpers 15, so dass ein Durchrutschen bzw. Durchfallen der Spannmutter 18 bei der Montage an dem Haltekörper 15 vermieden wird.In the Fig. 3 the state is shown in which the first toothed region 21 of the clamping nut 18 in the region of the first toothed region 21 of the holding body 15 arrived. It is essential that at the beginning of the engagement of the thread of the first toothed portion 21 of the clamping nut 18 in the first gear portion of the holding body 15, the output of the winding of the first toothed portion 21 of the clamping nut 18 is still in abutting contact with the second toothed portion 22 of the holding body 15. As a result, the first toothed region 21 of the clamping nut 18 is always in engagement with one of the two toothed regions 21, 22 of the holding body 15, so that slippage or falling through of the clamping nut 18 during assembly on the holding body 15 is avoided.

Aus einer Zusammenschau der Fig. 1 und 4 ist der Endzustand der Montage der Spannmutter 18 an dem Haltekörper 15 dargestellt, bei der die Durchmesserstufe 19 der Spannmutter 18 sich in Anlagekontakt mit der Stufe 12 des Düsenkörpers 11 befindet und somit dem Düsenkörper 11 über die Ventilplatte 14 und den Haltekörper 15 gegen den Haltekörper 15 axial verspannt.From a synopsis of Fig. 1 and 4 the final state of assembly of the clamping nut 18 is shown on the holding body 15, in which the diameter stage 19 of the clamping nut 18 is in abutting contact with the step 12 of the nozzle body 11 and thus the nozzle body 11 via the valve plate 14 and the holding body 15 against the holding body 15th axially braced.

Die soweit beschriebene Gewindeverbindung 20 an dem Kraftstoffeinspritzventil 100 kann in vielfältiger Art und Weise abgewandelt bzw. modifiziert werden, ohne vom Erfindungsgedanken abzuweichen.The threaded connection 20 described so far on the fuel injection valve 100 can be modified or modified in many ways, without departing from the spirit of the invention.

Claims (10)

Kraftstoffeinspritzventil (100) für Brennkraftmaschinen, mit einem Gehäuse (10), in dem ein Düsenkörper (11) mittels einer Spannmutter (18) gegen einen Haltekörper (15) zumindest mittelbar axial verspannt ist, wobei die Spannmutter (18) den Düsenkörper (11) radial umfasst, und wobei zwischen der Spannmutter (18) und dem Haltekörper (15) in einem zum Düsenkörper (11) axial beabstandeten Bereich eine Gewindeverbindung (20) zwischen dem Haltekörper (15) und der Spannmutter (18) ausgebildet ist,
dadurch gekennzeichnet,
dass die Gewindeverbindung (20) wenigstens zwei Verzahnungsbereiche (21, 22) mit unterschiedlichen Gewindeabmessungen umfasst, die in Längsrichtung des Gehäuses (10) axial hintereinander angeordnet sind.Fuel injection valve (100) for internal combustion engines, comprising a housing (10) in which a nozzle body (11) is clamped axially at least indirectly against a holding body (15) by means of a clamping nut (18), wherein the clamping nut (18) clamps the nozzle body (11). radially formed, and wherein between the clamping nut (18) and the holding body (15) in a nozzle body (11) axially spaced area a threaded connection (20) between the holding body (15) and the clamping nut (18) is formed
characterized,
in that the threaded connection (20) comprises at least two toothed regions (21, 22) with different thread dimensions, which are arranged axially one behind the other in the longitudinal direction of the housing (10). Kraftstoffeinspritzventil nach Anspruch 1,
dadurch gekennzeichnet,
dass zwischen den beiden Verzahnungsbereichen (21, 22) ein gewindefreier Zwischenbereich (23) ausgebildet ist.Fuel injection valve according to claim 1,
characterized,
in that a thread-free intermediate region (23) is formed between the two toothed regions (21, 22). Kraftstoffeinspritzventil nach Anspruch 1 oder 2,
dadurch gekennzeichnet,
dass sich die Gewindeabmessungen in den Gewindedurchmessern und der Zähneanzahl unterscheiden, und dass die Steigungen der Verzahnungsbereiche (21, 22) gleich groß sind.Fuel injection valve according to Claim 1 or 2,
characterized,
that the thread dimensions differ in the thread diameters and the number of teeth, and that the pitches of the toothed portions (21, 22) are the same size. Kraftstoffeinspritzventil nach Anspruch 2 oder 3,
dadurch gekennzeichnet,
dass die axiale Länge (LZB) des gewindefreien Zwischenbereichs (23) an dem Haltekörper (15) der axialen Länge (L1) eines ersten Verzahnungsbereichs (21) an der Spannmutter (18) entspricht, der auf der dem Haltekörper (15) zugewandten Seite der Spannmutter (18) angeordnet ist.Fuel injection valve according to claim 2 or 3,
characterized,
in that the axial length (L ZB ) of the unthreaded intermediate region (23) on the holding body (15) corresponds to the axial length (L 1 ) of a first toothed region (21) corresponds to the clamping nut (18) which is arranged on the holding body (15) facing side of the clamping nut (18). Kraftstoffeinspritzventil nach Anspruch 4,
dadurch gekennzeichnet,
dass ein zweiter Verzahnungsbereich (22) auf der dem Düsenkörper (11) zugewandten Seite an dem Haltekörper (15) und an der Spannmutter (18) den kleineren Gewindedurchmesser und eine doppelte Zähnezahl aufweist wie der erste Verzahnungsbereich (21).Fuel injection valve according to claim 4,
characterized,
that a second toothed portion (22) on the nozzle body (11) side facing to the holding body (15) and on the clamping nut (18), the smaller thread diameter and a double number of teeth as that of said first toothed portion (21). Kraftstoffeinspritzventil nach Anspruch 5,
dadurch gekennzeichnet,
dass die Wanddicke (A) der Spannmutter (18) im zweiten Verzahnungsbereich (22) größer ist als die Wanddicke (a) im ersten Verzahnungsbereich (21).Fuel injection valve according to claim 5,
characterized,
that the wall thickness (A) of the clamping nut (18) in the second gear portion (22) is greater than the wall thickness (a) in the first gear portion (21). Kraftstoffeinspritzventil nach einem der Ansprüche 3 bis 6,
dadurch gekennzeichnet,
dass der erste Verzahnungsbereich (21) an dem Haltekörper (15) als Au-βengewinde mit der Dimensionierung M17x0,75mm und der zweite Verzahnungsbereich (22) an dem Haltekörper (15) als Außengewinde mit der Dimensionierung M16x0,75mm ausgebildet ist.Fuel injection valve according to one of claims 3 to 6,
characterized,
that the first gear portion (21) on the retaining body (15) Au βengewinde with the dimensioning M17x0,75mm and the second gear portion (22) at the holding body (15) is designed as an external thread with the dimensioning M16x0,75mm. Kraftstoffeinspritzventil nach einem der Ansprüche 4 bis 7,
dadurch gekennzeichnet,
dass in der verschraubten Endstellung der Spannmutter (18) der zweite Verzahnungsbereich (22) am Haltekörper (15) zumindest nahezu vollständig von dem zweiten Verzahnungsbereich (22) der Spannmutter (18) überdeckt ist.Fuel injection valve according to one of claims 4 to 7,
characterized,
that in the screwed end position of the tensioning nut (18) of the second gear portion (22) is covered on the holding body (15) at least almost completely from the second gear portion (22) of the clamping nut (18). Kraftstoffeinspritzventil nach einem der Ansprüche 1 bis 8,
dadurch gekennzeichnet,
dass zwischen dem Haltekörper (15) und dem Düsenkörper (11) im Gehäuse (10) weitere Bauteile, insbesondere eine Drosselplatte (13) und eine Ventilplatte (14) angeordnet sind.Fuel injection valve according to one of claims 1 to 8,
characterized,
that between the holding body (15) and the nozzle body (11) in the housing (10) further components, in particular a throttle plate (13) and a valve plate (14) are arranged. Kraftstoffeinspritzventil nach einem der Ansprüche 1 bis 9,
dadurch gekennzeichnet,
dass im Bereich des Düsenkörpers (11) befindlicher Kraftstoff einen Druck von mehr als 1500bar aufweist.Fuel injection valve according to one of claims 1 to 9,
characterized,
that in the region of the nozzle body (11) located fuel has a pressure of more than 1500 bar.
EP12169087.9A 2011-06-06 2012-05-23 Fuel injection valve for combustion engines Active EP2532877B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201110076957 DE102011076957A1 (en) 2011-06-06 2011-06-06 Fuel injection valve for internal combustion engines

Publications (2)

Publication Number Publication Date
EP2532877A1 true EP2532877A1 (en) 2012-12-12
EP2532877B1 EP2532877B1 (en) 2015-07-29

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US (1) US8833735B2 (en)
EP (1) EP2532877B1 (en)
DE (1) DE102011076957A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012208075A1 (en) * 2012-05-15 2013-11-21 Man Diesel & Turbo Se Injector for a fuel supply system of an internal combustion engine and fuel supply system
JP6406118B2 (en) * 2015-05-07 2018-10-17 株式会社デンソー Fuel injection device

Citations (5)

* Cited by examiner, † Cited by third party
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WO2003004866A1 (en) * 2001-07-07 2003-01-16 Robert Bosch Gmbh High-pressure fuel device
WO2003042531A1 (en) * 2001-11-10 2003-05-22 Robert Bosch Gmbh Valve for the control of fluids
DE102005020833A1 (en) * 2005-05-04 2006-11-09 Robert Bosch Gmbh Modular jet for automotive fuel injection system has modular components held in line by threaded nuts
EP1775460A1 (en) * 2005-10-17 2007-04-18 Robert Bosch Gmbh Fuel injection valve with an indication as a positioning aid
DE102008001330A1 (en) 2008-04-23 2009-10-29 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10044933A1 (en) * 2000-09-12 2002-03-21 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
JP3928362B2 (en) * 2001-02-14 2007-06-13 株式会社デンソー Structure to improve seal surface pressure of fluid transfer device
DE10121531A1 (en) * 2001-05-03 2002-11-14 Siemens Ag fuel injector
DE10250720A1 (en) * 2002-10-31 2004-05-13 Robert Bosch Gmbh Injector

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003004866A1 (en) * 2001-07-07 2003-01-16 Robert Bosch Gmbh High-pressure fuel device
WO2003042531A1 (en) * 2001-11-10 2003-05-22 Robert Bosch Gmbh Valve for the control of fluids
DE102005020833A1 (en) * 2005-05-04 2006-11-09 Robert Bosch Gmbh Modular jet for automotive fuel injection system has modular components held in line by threaded nuts
EP1775460A1 (en) * 2005-10-17 2007-04-18 Robert Bosch Gmbh Fuel injection valve with an indication as a positioning aid
DE102008001330A1 (en) 2008-04-23 2009-10-29 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

Also Published As

Publication number Publication date
US20120305823A1 (en) 2012-12-06
EP2532877B1 (en) 2015-07-29
DE102011076957A1 (en) 2012-12-06
US8833735B2 (en) 2014-09-16

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