EP2108081B1 - Fixing element for an expansion sleeve - Google Patents

Fixing element for an expansion sleeve Download PDF

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Publication number
EP2108081B1
EP2108081B1 EP07847920A EP07847920A EP2108081B1 EP 2108081 B1 EP2108081 B1 EP 2108081B1 EP 07847920 A EP07847920 A EP 07847920A EP 07847920 A EP07847920 A EP 07847920A EP 2108081 B1 EP2108081 B1 EP 2108081B1
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EP
European Patent Office
Prior art keywords
fuel injector
expansion sleeve
injector according
lateral surface
cylinder head
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.)
Not-in-force
Application number
EP07847920A
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German (de)
French (fr)
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EP2108081A1 (en
Inventor
Juergen Hanneke
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP2108081A1 publication Critical patent/EP2108081A1/en
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Publication of EP2108081B1 publication Critical patent/EP2108081B1/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
    • F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors
    • 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
    • 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
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00

Definitions

  • Out DE 196 50 865 A1 is a solenoid valve for controlling the fuel pressure in a control chamber of an injection valve, known as a common rail high-pressure accumulator injection system. About the prevailing in the control chamber fuel pressure under the influence of a stroke movement of a valve piston is controlled with an injection port of the injection valve is opened or closed.
  • the solenoid valve comprises an electromagnet, a movable armature and a valve member moved in the direction of flow with the armature and acted upon by a valve closing spring, which cooperates with the valve seat of the solenoid valve and thus controls the fuel drain from the control chamber.
  • fuel injectors are fastened to the cylinder head, for example by means of a clamping claw or the like, depending on the configuration of the cylinder head of the engine manufacturer.
  • a fastening device for fastening a fuel injection valve in a cylinder head is known, wherein the fastening device is in the form of a hold-down sleeve.
  • the injector body of the fuel injector with a hydraulic line for acting on a hydraulic fluid, a pressure piston and an expansion bushing. If the pressure piston is screwed into the injector body, the hydraulic fluid stored in the conduit system for the tension medium is released displaced the tension line system. As a result of the displaced fluid, the expansion bushing, which has at least one pocket-shaped, thin-walled, formed area, is deformed and the thin-walled design of the hydraulic fluid makes it possible to elastically deform the wall of the expansion bushing. At the expansion sleeve two pocket-shaped thin-walled areas are preferably formed, which are seen in the axial direction of the expansion sleeve, arranged one above the other.
  • the two pocket-shaped areas ensure that the injector body of the fuel injector centered evenly to the center of its receiving bore in the cylinder head area. If the pressure on the expansion region, ie the thin-walled region of the expansion bush further increased by further screwing the pressure piston in the injector body, results in a radial strain of the expansion sleeve in the bore of the cylinder head, since the outer sides of the expansion sleeve to the inner walls of the receiving bore of the cylinder apply relevant fuel injector in the cylinder head of the internal combustion engine. This radial tension can be increased to such an extent by further displacement of hydraulic fluid from the tension line system formed in the injector body that the axial force, which results from the combustion pressure and acts on the fuel injector, can easily be sustained.
  • a release of the inventively proposed compound of the fuel injector is achieved in that the pressure piston which acts on the tension line system for the hydraulic medium in the injector body of the fuel injector is unscrewed from the injector body and thereby a pressure relief of the tension line system in which the hydraulic fluid is stored, takes place. If the formation of two pocket-shaped, thin-walled regions on the expansion bushing is not possible, for example due to lack of space, then the radial prestressing force can be made by forming a radial prestressing region by utilizing a second guidance of the fuel injector in the region of the nozzle tightening nut.
  • FIG. 1 The representation according to FIG. 1 the inventively proposed fuel injector, embedded in a receiving bore on the cylinder head of an internal combustion engine, can be seen.
  • FIG. 1 shows a cylinder head 10 shown cut, in which a receiving bore 12 extends.
  • the receiving bore 12 has a bore inner wall 14 and a first bore portion 16 and a second bore portion 18.
  • the first bore portion 16 is formed in a larger compared to the second bore portion 18 diameter in the material of the cylinder head 10 above a combustion chamber of the internal combustion engine.
  • the fuel injector 20 includes a holding body 22; the axis of the fuel injector 20 is designated by reference numeral 24.
  • the fuel injector 20 includes a nozzle retaining nut 26, whose lateral surface is designated by reference numeral 28.
  • a Dehnbuchse 30 in the untensioned state 64 On the lateral surface 28 of the holding body 22 of the fuel injector 20 is shown in the illustration FIG. 1 a Dehnbuchse 30 in the untensioned state 64.
  • the expansion sleeve 30 is preferably stoffschtüssig connected to the on the lateral surface 28 of the holding body 22 of the fuel injector 22 at a first joint 32 and at a second joint 34.
  • first joint 32 and the second joint 34 By forming the first joint 32 and the second joint 34 as cohesive joints, a pressure-tight attachment of the bushing 30 is achieved on the lateral surface 28 of the holding body 22.
  • a tensioning line 50 extends in the holding body 22 of the fuel injector 20, a tensioning line 50 extends.
  • the tension line 50 comprises a blind hole 58 and a parallel to the axis 24 of the fuel injector 20 extending channel 60, which opens at an orifice point 62 in the lateral surface 28 of the holding body 22.
  • the tensioning line 50 which comprises at least the above-listed components, is filled with a hydraulic fluid.
  • the tensioning line 50 opens on the one hand at the mouth 62 of the lateral surface 28 of the holding body 22 of the fuel injector 20;
  • the tensioning line 50 as shown in FIG FIG. 1 a pressure piston 48 designed, for example, as a grub screw or the like.
  • the pressure piston 48 may be accommodated, for example, in the form of the grub screw mentioned in the blind hole 58 of the tensioning line 50.
  • the pressure piston 48 comprises a sealing element 56, by means of which the escape of hydraulic fluid from the tensioning line 50 to the environment is prevented.
  • the pressure piston 48 is in an indicated by reference numeral 72 unscrewed position 72 that is, the end face of the pressure piston 48 is located in the lateral surface of the holding body 22 of the fuel injector 20th
  • the two pocket-shaped recesses 40 and 42 as shown in FIG FIG. 1 lie, seen in the axial direction, parallel to the axis 24 of the holding body 22nd
  • expansion sleeve 30 has an inner side 38 which is located at a small distance from the lateral surface 28 of the holding body 22 and an overflow of the hydraulic fluid, for example, from the designated by reference numeral 42 second pocket-shaped recess via an annular gap between the Inside 38 and the lateral surface 28 in the first pocket-shaped recess 40 allowed. This ensures that when the hydraulic fluid exits at the outlet point 62, the entire inner side 38 of the expansion bushing 30 fastened to the lateral surface 28 is acted upon by hydraulic fluid.
  • the fuel injector 20 has a guide surface 68 underneath the holding body 22 on the nozzle clamping nut 26.
  • the guide surface 68 serves to guide or center the fuel injector 20 within the receiving bore 12 when this is made shorter for space and installation reasons and the expansion sleeve 30 within the first bore portion 16 only one of the pocket-shaped recesses 40 or 42 has.
  • the solution proposed by the invention following by pressurizing the expansion sleeve 30 with a pocket-shaped recess 40 or 42, a fixing and centering of the fuel injector 20 can be achieved in the receiving bore 12, because by the guide surface 68 on the circumference of the nozzle lock nut 26th whose centering is ensured in the receiving bore 12.
  • the pressure piston 48 is shown in the screwed into the blind hole 58 state 70.
  • the pressure piston 48 is screwed by the stroke in the blind hole 58. Due to this fact, the stored in the tensioning line 50 hydraulic fluid is displaced from the blind hole 48 via the channel 60 and exits at the mouth point 62 on the lateral surface 28 of the holding body 22 within the expansion sleeve 30.
  • a second clamping force 46 acts in the region of the first pocket-shaped recess 40 of the expansion sleeve 30 by the deformation in the radial direction outwardly a first clamping force F 1 and by the deformation of the wall of the expansion sleeve 30 in the second pocket-shaped recess 42, a second clamping force 46 (F 2nd ).
  • the clamping forces 44 and 46 (F 1 , F 2 ) acting in the radial direction produce a holding force acting in the axial direction with which the fuel injector 20 with its holding body 22 is fixed in the receiving bore 12 of the cylinder head 10.
  • an axial holding force can be generated, which counteracts the pressure force acting in the combustion chamber of the internal combustion engine and exceeds them so far that the fuel injector 22 reliably and sealed by the fixed to the lateral surface 28 of the holding body 22 expansion sleeve 30 remains fixed in the receiving bore 12 of the cylinder head 10.
  • the in the region of the first pocket-shaped recess 40, acting in the radial direction clamping force 44 (F 1 ) also acts as a seal, so that the expansion sleeve 30 in addition to the bias of the fuel injector 20 in the receiving bore 12 also assumes a sealing, so that additional sealing elements omitted can.
  • a pocket-shaped recess 40 or 42 may be provided.
  • the generation of a clamping force F 1 or F 2 is sufficient to fix the holding body 22 of the fuel injector 22 in the receiving bore 12, when the fuel injector 20 with its formed on the nozzle retaining nut 26 guide surface 68 in the second bore portion 18 of the receiving bore 12 in Cylinder head 10 remains guided.
  • the expansion sleeve 30 can be clamped in the radial direction within the receiving bore 12.
  • This radial tension according to the clamping forces 44 and 46 can be increased by the hydraulic fluid so that it can easily resist the axial force resulting from the combustion pressure.
  • Loosening of the connection can be achieved by moving the pressure piston 48 out of the blind bore 58 of the tensioning line 50 and with an associated pressure relief of the expansion bush 30. If the conditions in the region of the receiving bore 12 do not permit a second embodiment of two pocket-shaped recesses 40, 42, the fuel injector 20 can be guided and centered by means of the guide surface 68 formed on the nozzle clamping nut 26.

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

Abstract

The invention relates to a fuel injector which has a retaining body and an injection nozzle nut. An expansion sleeve, which can be supplied with hydraulic fluid, is provided around the periphery of the fuel injector, in particular around the periphery of the retaining body. The expansion sleeve includes at least one pocket-type recess, which can be supplied with hydraulic fluid.

Description

Stand der TechnikState of the art

Aus DE 196 50 865 A1 ist ein Magnetventil zur Steuerung des Kraftstoffdruckes in einem Steuerraum eines Einspritzventils, etwa eine Common-Rail-Hochdruckspeichereinspritzsystems bekannt. Über den im Steuerraum herrschenden Kraftstoffdruckes unter dessen Beeinflussung wird eine Hubbewegung eines Ventilkolbens gesteuert, mit dem eine Einspritzöffnung des Einspritzventiles geöffnet oder geschlossen wird. Das Magnetventil umfasst einen Elektromagneten, einen beweglichen Anker und ein mit dem Anker bewegtes und von einer Ventilschließfeder in Fließrichtung beaufschlagtes Ventilglied, dass mit dem Ventilsitz des Magnetventiles zusammenwirkt und so den Kraftstoffabfluss aus dem Steuerraum steuert.Out DE 196 50 865 A1 is a solenoid valve for controlling the fuel pressure in a control chamber of an injection valve, known as a common rail high-pressure accumulator injection system. About the prevailing in the control chamber fuel pressure under the influence of a stroke movement of a valve piston is controlled with an injection port of the injection valve is opened or closed. The solenoid valve comprises an electromagnet, a movable armature and a valve member moved in the direction of flow with the armature and acted upon by a valve closing spring, which cooperates with the valve seat of the solenoid valve and thus controls the fuel drain from the control chamber.

Je nach Einbaufall werden Kraftstoffinjektoren zum Beispiel mittels einer Spannpratze oder dergleichen abhängig von der Konfiguration des Zylinderkopfes des Motorenherstellers, am Zylinderkopf befestigt. Aus WO 02/066827 ist eine Befestigungsvorrichtung zur Befestigung eines Kraftstoffeinspritzventils in einem Zylinderkopf bekannt, wobei die Befestigungsvorrichtung in Form einer Niederhaltehülse ausgeprägt ist.Depending on the installation case, fuel injectors are fastened to the cylinder head, for example by means of a clamping claw or the like, depending on the configuration of the cylinder head of the engine manufacturer. Out WO 02/066827 a fastening device for fastening a fuel injection valve in a cylinder head is known, wherein the fastening device is in the form of a hold-down sleeve.

Bisher eingesetzten Pratzenlösungen, mit denen Kraftstoffinjektoren im Zylinderkopfbereich für Verbrennungskraftmaschinen befestigt werden, führen toleranzbedingt zur Einleitung von Querkräfte und damit zu einer Verkippung des Kraftstoffinjektors in seiner Aufnahmebohrung. Dies wiederum führt zu funktionellen Nachteilen, die sich in der Verbrennung des Kraftstoffes sowie in einem erhöhten Verschleiß mechanischer Komponenten im Injektor selbst widerspiegeln.Previously used Pratzenlösungen with which fuel injectors are mounted in the cylinder head area for internal combustion engines, tolerances caused by the introduction of shear forces and thus to a tilt of the fuel injector in its receiving bore. This in turn leads to functional disadvantages, which are reflected in the combustion of the fuel and in an increased wear of mechanical components in the injector itself.

Offenbarung der ErfindungDisclosure of the invention

Erfindungsgemäß wird vorgeschlagen, den Injektorkörper des Kraftstoffinjektors mit einer hydraulischen Leitung zur Beaufschlagung mit einem Hydraulikfluid, einem Druckkolben sowie einer Dehnbuchse zu versehen. Wird der Druckkolben in den Injektorkörper eingeschraubt, wird das im Leitungssystem für das Spannmedium bevorratete Hydraulikfluid aus dem Spannleitungssystem verdrängt. Durch das verdrängte Fluid wird die Dehnbuchse, die zumindest einen taschenförmigen dünnwandigen ausgebildeten Bereich aufweist, verformt und durch deren dünnwandige Auslegung dem Hydraulikfluid die Möglichkeit gegeben, die Wand der Dehnbuchse elastisch zu verformen. An der Dehnbuchse werden bevorzugt zwei taschenförmig ausgebildete dünnwandige Bereiche ausgebildet, die in axialer Richtung der Dehnbuchse gesehen, übereinander liegend angeordnet sind. Die beiden taschenförmigen Bereiche sorgen dafür, dass sich der Injektorkörper des Kraftstoffinjektors gleichmäßig zur Mitte seiner Aufnahmebohrung im Zylinderkopfbereich zentriert. Wird der Druck auf den Ausdehnungsbereich, d.h. den dünnwandig ausgebildeten Bereich der Dehnbuchse durch weiteres Einschrauben des Druckkolbens in den Injektorkörper weiter erhöht, ergibt sich eine radiale Verspannung der Dehnbuchse in der Bohrung des Zylinderkopfes, da sich die Außenseiten der Dehnbuchse an die Innenwände der Aufnahmebohrung des betreffenden Kraftstoffinjektors im Zylinderkopf der Verbrennungskraftmaschine anlegen. Diese radiale Verspannung kann durch weiteres Verdrängen von Hydraulikfluid aus dem im Injektorkörper ausgebildeten Spannleitungssystem soweit erhöht werden, dass ohne weiteres die Axialkraft, die aus dem Verbrennungsdruck resultiert und auf den Kraftstoffinjektor wirkt, ausgehalten werden kann.According to the invention, it is proposed to provide the injector body of the fuel injector with a hydraulic line for acting on a hydraulic fluid, a pressure piston and an expansion bushing. If the pressure piston is screwed into the injector body, the hydraulic fluid stored in the conduit system for the tension medium is released displaced the tension line system. As a result of the displaced fluid, the expansion bushing, which has at least one pocket-shaped, thin-walled, formed area, is deformed and the thin-walled design of the hydraulic fluid makes it possible to elastically deform the wall of the expansion bushing. At the expansion sleeve two pocket-shaped thin-walled areas are preferably formed, which are seen in the axial direction of the expansion sleeve, arranged one above the other. The two pocket-shaped areas ensure that the injector body of the fuel injector centered evenly to the center of its receiving bore in the cylinder head area. If the pressure on the expansion region, ie the thin-walled region of the expansion bush further increased by further screwing the pressure piston in the injector body, results in a radial strain of the expansion sleeve in the bore of the cylinder head, since the outer sides of the expansion sleeve to the inner walls of the receiving bore of the cylinder apply relevant fuel injector in the cylinder head of the internal combustion engine. This radial tension can be increased to such an extent by further displacement of hydraulic fluid from the tension line system formed in the injector body that the axial force, which results from the combustion pressure and acts on the fuel injector, can easily be sustained.

Ein Lösen der erfindungsgemäß vorgeschlagenen Verbindung des Kraftstoffinjektors wird dadurch erreicht, dass der Druckkolben, der das Spannleitungssystem für das Hydraulikmedium im Injektorkörper des Kraftstoffinjektors beaufschlagt, wieder aus dem Injektorkörper herausgeschraubt wird und dadurch eine Druckentlastung des Spannleitungssystems, in dem das Hydraulikfluid bevorratet wird, erfolgt. Ist die Ausbildung von zwei taschenförmigen, dünnwandig ausgebildeten Bereichen an der Dehnbuchse nicht möglich, z.B. aus Platzgründen, so kann die radiale Vorspannkraft unter Ausbildung eines radialen Vorspannbereiches unter Ausnutzung einer zweiten Führung des Kraftstoffinjektors im Bereich der Düsenspannmutter vorgenommen werden. Durch den anliegenden Druck, den die Dehnbuchse auf die Innenmantelfläche der Zylinderkopfbohrung ausübt, entfallen sonst übliche Dichtelemente am Injektorkörper oder in der Zylinderkopfabdeckung. Der erfmdungsgemäß vorgeschlagenen Lösung folgend, werden keine zusätzlichen Bauteile wie Pratzen oder Flansche mit den dazugehörenden Befestigungsschrauben benötigt. Der Abstand zwischen den einzelnen Zylindern der Verbrennungskraftmaschine lässt sich auf ein Minimum reduzieren. Der Bauaum kann für andere Bauteile wie zum Beispiel Nocken der Nockenwelle, Ventile der Ventilfedern oder zur Implementierung eines hydraulischen Ventilspielausgleichs sowie anderer technischer Feinheiten, die an Verbrennungskraftmaschinen eingesetzt werden, ausgenutzt werden.A release of the inventively proposed compound of the fuel injector is achieved in that the pressure piston which acts on the tension line system for the hydraulic medium in the injector body of the fuel injector is unscrewed from the injector body and thereby a pressure relief of the tension line system in which the hydraulic fluid is stored, takes place. If the formation of two pocket-shaped, thin-walled regions on the expansion bushing is not possible, for example due to lack of space, then the radial prestressing force can be made by forming a radial prestressing region by utilizing a second guidance of the fuel injector in the region of the nozzle tightening nut. Due to the applied pressure exerted by the expansion sleeve on the inner circumferential surface of the cylinder head bore, otherwise omitted conventional sealing elements on the injector body or in the cylinder head cover. Following the solution proposed according to the invention, no additional components such as claws or flanges are required with the associated mounting screws. The distance between the individual cylinders of the internal combustion engine can be reduced to a minimum. The construction space can be exploited for other components such as camshaft lobes, valves of the valve springs or for implementing a hydraulic lash adjuster and other technical refinements that are used on internal combustion engines.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Anhand der Zeichnung wird die Erfindung nachstehend eingehender beschrieben.With reference to the drawing, the invention will be described below in more detail.

Es zeigt:

Figur 1
einen Schnitt durch den erfindungsgemäß vorgeschlagenen Kraftstoffinjektor mit Dehnbuchs im ungespannten Zustand
Figur 2
den Kraftstoffinjektor mit am Injektorkörper aufgenommener Dehnbuchse im gespannten Zustand.
It shows:
FIG. 1
a section through the inventively proposed fuel injector with Dehnbuchs in the untensioned state
FIG. 2
the fuel injector with recorded on the injector expansion sleeve in the tensioned state.

Ausführungsformenembodiments

Der Darstellung gemäß Figur 1 ist der erfindungsgemäß vorgeschlagene Kraftstoffinjektor, in eine Aufnahmebohrung am Zylinderkopf einer Verbrennungskraftmaschine eingelassen, zu entnehmen.The representation according to FIG. 1 the inventively proposed fuel injector, embedded in a receiving bore on the cylinder head of an internal combustion engine, can be seen.

Figur 1 zeigt einen geschnitten dargestellten Zylinderkopf 10, in dem eine Aufnahmebohrung 12 verläuft. Die Aufnahmebohrung 12 weist eine Bohrungsinnenwand 14 auf und einen ersten Bohrungsabschnitt 16 sowie einen zweiten Bohrungsabschnitt 18. Der erste Bohrungsabschnitt 16 ist in einem im Vergleich zum zweiten Bohrungsabschnitt 18 vergrößertem Durchmesser im Material des Zylinderkopfes 10 oberhalb eines Brennraums der Verbrennungskraftmaschine ausgebildet. FIG. 1 shows a cylinder head 10 shown cut, in which a receiving bore 12 extends. The receiving bore 12 has a bore inner wall 14 and a first bore portion 16 and a second bore portion 18. The first bore portion 16 is formed in a larger compared to the second bore portion 18 diameter in the material of the cylinder head 10 above a combustion chamber of the internal combustion engine.

In der Aufnahmebohrung 12 ist ein Kraftstoffinjektor 10 eingelassen. Der Kraftstoffinjektor 20 umfasst einen Haltekörper 22; die Achse des Kraftstoffinjektors 20 ist durch Bezugszeichen 24 bezeichnet. Neben dem Haltekörper 22 umfasst der Kraftstoffinjektor 20 eine Düsenspannmutter 26, deren Mantelfläche mit Bezugszeichen 28 bezeichnet ist.In the receiving bore 12, a fuel injector 10 is embedded. The fuel injector 20 includes a holding body 22; the axis of the fuel injector 20 is designated by reference numeral 24. In addition to the holding body 22, the fuel injector 20 includes a nozzle retaining nut 26, whose lateral surface is designated by reference numeral 28.

An der Mantelfläche 28 des Haltekörpers 22 des Kraftstoffinjektors 20 befindet sich in der Darstellung gemäß Figur 1 eine Dehnbuchse 30 im ungespannten Zustand 64. Die Dehnbuchse 30 ist an einer ersten Fügestelle 32 und an einer zweiten Fügestelle 34 bevorzugt stoffschtüssig mit dem an der Mantelfläche 28 des Haltekörpers 22 des Kraftstoffinjektors 22 verbunden. Durch die Ausbildung der ersten Fügestelle 32 sowie der zweiten Fügestelle 34 als stoffschlüssige Verbindungsstellen wird eine druckdichte Befestigung der Buchse 30 an der Mantelfläche 28 des Haltekörpers 22 erreicht.On the lateral surface 28 of the holding body 22 of the fuel injector 20 is shown in the illustration FIG. 1 a Dehnbuchse 30 in the untensioned state 64. The expansion sleeve 30 is preferably stoffschtüssig connected to the on the lateral surface 28 of the holding body 22 of the fuel injector 22 at a first joint 32 and at a second joint 34. By forming the first joint 32 and the second joint 34 as cohesive joints, a pressure-tight attachment of the bushing 30 is achieved on the lateral surface 28 of the holding body 22.

Der Darstellung gemäß Figur 1 ist des Weiteren zu entnehmen, dass im Haltekörper 22 des Kraftstoffinjektors 20 eine Spannleitung 50 verläuft. Die Spannleitung 50 umfasst eine Sacklochbohrung 58 sowie einen sich parallel zur Achse 24 des Kraftstoffinjektors 20 erstreckenden Kanal 60, der an eine Mündungsstelle 62 in der Mantelfläche 28 des Haltekörpers 22 mündet. Die Spannleitung 50, welche zumindest die obenstehend aufgezählte Komponenten umfasst, ist mit einem Hydraulikfluid befüllt. Die Spannleitung 50 mündet einerseits an der Mündungsstelle 62 der Mantelfläche 28 des Haltekörpers 22 des Kraftstoffmjektors 20; andererseits umfasst die Spannleitung 50 gemäß der Darstellung in Figur 1 einen z.B. als Madenschraube oder dergleichen ausgebildeten Druckkolben 48. Der Druckkolben 48 kann z.B. in Gestalt der erwähnten Madenschraube in der Sacklochbohrung 58 der Spannleitung 50 aufgenommen sein. Der Druckkolben 48 umfasst ein Dichtelement 56, durch welches der Austritt von Hydraulikfluid aus der Spannleitung 50 an die Umgebung verhindert wird. In der Darstellung gemäß Figur 1 befindet sich der Druckkolben 48 in einer durch Bezugszeichen 72 angedeuteten herausgeschraubten Position 72 d.h. die Stirnfläche des Druckkolbens 48 liegt in der Mantelfläche des Haltekörpers 22 des Kraftstoffinjektors 20.The representation according to FIG. 1 It can also be seen that in the holding body 22 of the fuel injector 20, a tensioning line 50 extends. The tension line 50 comprises a blind hole 58 and a parallel to the axis 24 of the fuel injector 20 extending channel 60, which opens at an orifice point 62 in the lateral surface 28 of the holding body 22. The tensioning line 50, which comprises at least the above-listed components, is filled with a hydraulic fluid. The tensioning line 50 opens on the one hand at the mouth 62 of the lateral surface 28 of the holding body 22 of the fuel injector 20; On the other hand, the tensioning line 50 as shown in FIG FIG. 1 a pressure piston 48 designed, for example, as a grub screw or the like. The pressure piston 48 may be accommodated, for example, in the form of the grub screw mentioned in the blind hole 58 of the tensioning line 50. The pressure piston 48 comprises a sealing element 56, by means of which the escape of hydraulic fluid from the tensioning line 50 to the environment is prevented. In the illustration according to FIG. 1 the pressure piston 48 is in an indicated by reference numeral 72 unscrewed position 72 that is, the end face of the pressure piston 48 is located in the lateral surface of the holding body 22 of the fuel injector 20th

Der Darstellung gemäß Figur 1 ist des weiteren entnehmbar, dass die Dehnbuchse 30, an der ersten Fügestelle 32 und an der zweiten Fügestelle 34 mit der Mantelfläche 28 des Haltekörpers 22 verbunden, zumindest eine taschenförmige Ausnehmung 40, bevorzugt eine erste taschenförmige Ausnehmung 40 sowie eine zweite taschenförmige Ausnehmung 42 aufweist. Die beiden taschenförmigen Ausnehmungen 40 bzw. 42 gemäß der Darstellung in Figur 1 liegen, in axialer Richtung gesehen, parallel zur Achse 24 des Haltekörpers 22.The representation according to FIG. 1 Furthermore, it can be seen that the expansion bushing 30, connected to the lateral surface 28 of the holding body 22 at the first joint 32 and at the second joint 34, has at least one pocket-shaped recess 40, preferably a first pocket-shaped recess 40 and a second pocket-shaped recess 42. The two pocket-shaped recesses 40 and 42 as shown in FIG FIG. 1 lie, seen in the axial direction, parallel to the axis 24 of the holding body 22nd

Die an der Mantelfläche 28 des Haltekörpers 22 aufgenommene Dehnbuchse 30 weist eine Innenseite 38 auf, welche in einem geringen Abstand zur Mantelfläche 28 des Haltekörpers 22 liegt und ein Überströmen des Hydraulikfluides zum Beispiel von der mit Bezugszeichen 42 bezeichneten zweiten taschenförmigen Ausnehmung über einen Ringspalt zwischen der Innenseite 38 und der Mantelfläche 28 in die erste taschenförmige Ausnehmung 40 erlaubt. Somit ist sichergestellt, dass bei Austritt des Hydraulikfluides an der Mündungsstelle 62 die gesamte Innenseite 38 der an der Mantelfläche 28 befestigten Dehnbuchse 30 mit Hydraulikfluid beaufschlagt ist.The accommodated on the lateral surface 28 of the holding body 22 expansion sleeve 30 has an inner side 38 which is located at a small distance from the lateral surface 28 of the holding body 22 and an overflow of the hydraulic fluid, for example, from the designated by reference numeral 42 second pocket-shaped recess via an annular gap between the Inside 38 and the lateral surface 28 in the first pocket-shaped recess 40 allowed. This ensures that when the hydraulic fluid exits at the outlet point 62, the entire inner side 38 of the expansion bushing 30 fastened to the lateral surface 28 is acted upon by hydraulic fluid.

Der Darstellung gemäß Figur 1 ist weiterhin zu entnehmen, dass der Kraftstoffinjektor 20 unterhalb des Haltekörpers 22 an der Düsenspannmutter 26 eine Führungsfläche 68 aufwist. Die Führungsfläche 68 dient dem Führen bzw. dem Zentrieren des Kraftstoffinjektors 20 innerhalb der Aufnahmebohrung 12, wenn diese aus Platz und Einbaugründen verkürzt ausgebildet wird und die Dehnbuchse 30 innerhalb des ersten Bohrungsabschnittes 16 lediglich eine der taschenförmigen Ausnehmungen 40 oder 42 aufweist. In diesem Falle kann, der erfindungsgemäß vorgeschlagenen Lösung folgend, durch eine Druckbeaufschlagung der Dehnbuchse 30 auch nur mit einer taschenförmigen Ausnehmung 40 oder 42 ein Fixieren und Zentrieren des Kraftstoffinjektors 20 in der Aufnahmebohrung 12 erreicht werden, weil durch die Führungsfläche 68 am Umfang der Düsenspannmutter 26 dessen Zentrierung in der Aufnahmebohrung 12 gewährleistet ist.The representation according to FIG. 1 It can also be seen that the fuel injector 20 has a guide surface 68 underneath the holding body 22 on the nozzle clamping nut 26. The guide surface 68 serves to guide or center the fuel injector 20 within the receiving bore 12 when this is made shorter for space and installation reasons and the expansion sleeve 30 within the first bore portion 16 only one of the pocket-shaped recesses 40 or 42 has. In this case, the solution proposed by the invention following, by pressurizing the expansion sleeve 30 with a pocket-shaped recess 40 or 42, a fixing and centering of the fuel injector 20 can be achieved in the receiving bore 12, because by the guide surface 68 on the circumference of the nozzle lock nut 26th whose centering is ensured in the receiving bore 12.

In der Darstellung gemäß Figur 2 ist der erfindungsgemäß vorgeschlagene Kraftstoffinjektor in einem im Zylinderkopf eingespannten Zustand gezeigt.In the illustration according to FIG. 2 the inventively proposed fuel injector is shown in a clamped state in the cylinder head.

In der Darstellung gemäß Figur 2 ist der Druckkolben 48 im in die Sacklochbohrung 58 hineingeschraubten Zustand 70 gezeigt. Im Vergleich zur Position des Druckkolbens 48 in Figur 1, welche den ungespannten Zustand 64 darstellt, ist der Druckkolben 48 um den Hubweg in die Sacklochbohrung 58 eingeschraubt. Aufgrund dieses Umstandes wird das in der Spannleitung 50 bevorratete Hydraulikfluid von der Sacklochbohrung 48 über den Kanal 60 verdrängt und tritt an der Mündungsstelle 62 an der Mantelfläche 28 des Haltekörpers 22 innerhalb der Dehnbuchse 30 aus. Je nach Hubweg um den der Druckkolben 48 in die Sacklochbohrung 48 hineinbewegt wird, tritt mehr oder weniger Hydraulikfluid an der Mündungsstelle 62 aus und beaufschlagt die Innenseite 38 der Dehnbuchse 30. Aufgrund der Ausbildung der ersten Fügestelle 32 bzw. der zweiten Fügestelle 34 als stoffschlüssige Verbindungsstellen, tritt das Hydraulikfluid nicht in die Aufnahmebohrung 12 ein, sondern bewirkt eine Verformung der Dehnbuchse 30. Diese wird zum Beispiel wie in Figur 2, welche den gespannten Zustand 66 repräsentiert, verformt. Aufgrund der Verformung der ersten taschenförmigen Ausnehmung 40 und der zweiten taschenförmigen Ausnehmung 42 der Dehnbuchse 30, legt sich deren Außenseite 36 an die Bohrungswand 14 der Aufnahmebohrung 12.In the illustration according to FIG. 2 the pressure piston 48 is shown in the screwed into the blind hole 58 state 70. In comparison to the position of the pressure piston 48 in FIG FIG. 1 , which represents the untensioned state 64, the pressure piston 48 is screwed by the stroke in the blind hole 58. Due to this fact, the stored in the tensioning line 50 hydraulic fluid is displaced from the blind hole 48 via the channel 60 and exits at the mouth point 62 on the lateral surface 28 of the holding body 22 within the expansion sleeve 30. Depending on the stroke by which the pressure piston 48 is moved into the blind hole 48, more or less hydraulic fluid exits at the outlet 62 and acts on the inner side 38 of the expansion sleeve 30 , The hydraulic fluid does not enter the receiving bore 12, but causes a deformation of the expansion sleeve 30. This is, for example, as in FIG. 2 , which represents the tensioned state 66, deformed. Due to the deformation of the first pocket-shaped recess 40 and the second pocket-shaped recess 42 of the expansion sleeve 30, the outer side 36 lays against the bore wall 14 of the receiving bore 12th

Wie aus der Darstellung gemäß Figur 2 weiter hervorgeht, wirkt im Bereich der ersten taschenförmigen Ausnehmung 40 der Dehnbuchse 30 durch deren Verformung in radialer Richtung nach Außen eine erste Spannkraft F1 und durch die Verformung der Wand der Dehnbuchse 30 im Bereich der zweiten taschenförmigen Ausnehmung 42 eine zweite Spannkraft 46 (F2). Die in radialer Richtung wirkenden Spannkräfte 44 bzw. 46 (F1, F2) erzeugen eine in axiale Richtung wirkende Haltekraft, mit welcher der Kraftstoffinjektor 20 mit seinem Haltekörper 22 in der Aufnahmebohrung 12 des Zylinderkopfes 10 fixiert wird. Je nach Druckbeaufschlagung der Innenseite 38 der Dehnbuchse 30 kann eine axiale Haltekraft erzeugt werden, die der im Brennraum der Verbrennungskraftmaschine wirkenden Druckkraft entgegenwirkt und diese soweit übersteigt, dass der Kraftstoffinjektor 22 durch die an der Mantelfläche 28 des Haltekörpers 22 fixierte Dehnbuchse 30 zuverlässig und abgedichtet in der Aufnahmebohrung 12 des Zylinderkopfes 10 fixiert bleibt. Die im Bereich der ersten taschenförmigen Ausnehmung 40, wirkende in radialer Richtung verlaufende Spannkraft 44 (F1) wirkt zudem als Abdichtung, so dass die Dehnbuchse 30 neben der Vorspannung des Kraftstoffinjektors 20 in der Aufnahmebohrung 12 auch eine Abdichtwirkung übernimmt, so dass zusätzliche Dichtungselemente entfallen können.As shown in the illustration FIG. 2 Further, acts in the region of the first pocket-shaped recess 40 of the expansion sleeve 30 by the deformation in the radial direction outwardly a first clamping force F 1 and by the deformation of the wall of the expansion sleeve 30 in the second pocket-shaped recess 42, a second clamping force 46 (F 2nd ). The clamping forces 44 and 46 (F 1 , F 2 ) acting in the radial direction produce a holding force acting in the axial direction with which the fuel injector 20 with its holding body 22 is fixed in the receiving bore 12 of the cylinder head 10. Depending on the pressurization of the inner side 38 of the expansion sleeve 30, an axial holding force can be generated, which counteracts the pressure force acting in the combustion chamber of the internal combustion engine and exceeds them so far that the fuel injector 22 reliably and sealed by the fixed to the lateral surface 28 of the holding body 22 expansion sleeve 30 remains fixed in the receiving bore 12 of the cylinder head 10. The in the region of the first pocket-shaped recess 40, acting in the radial direction clamping force 44 (F 1 ) also acts as a seal, so that the expansion sleeve 30 in addition to the bias of the fuel injector 20 in the receiving bore 12 also assumes a sealing, so that additional sealing elements omitted can.

Wie bereits im Zusammenhang mit Figur 1 erwähnt, kann aus Bauraumgründen an der Dehnbuchse 30 auch lediglich eine taschenförmige Ausnehmung 40 oder 42 vorgesehen sein. In diesem Falle reicht die Erzeugung einer Spannkraft F1 oder F2 aus, um den Haltekörper 22 des Kraftstoffinjektor 22 in der Aufnahmebohrung 12 zu fixieren, wenn der Kraftstoffinjektor 20 mit seiner an der Düsenspannmutter 26 ausgebildeten Führungsfläche 68 im zweiten Bohrungsabschnitt 18 der Aufnahmebohrung 12 im Zylinderkopf 10 geführt bleibt.As already related to FIG. 1 mentioned, for reasons of space on the expansion sleeve 30, only a pocket-shaped recess 40 or 42 may be provided. In this case, the generation of a clamping force F 1 or F 2 is sufficient to fix the holding body 22 of the fuel injector 22 in the receiving bore 12, when the fuel injector 20 with its formed on the nozzle retaining nut 26 guide surface 68 in the second bore portion 18 of the receiving bore 12 in Cylinder head 10 remains guided.

Über die in der Ausführungsform gemäß den Figuren 1 und 2 dargestellten beiden taschenförmigen Ausnehmungen 40 bzw. 42 kann die Dehnbuchse 30 in radialer Richtung innerhalb der Aufnahmebohrung 12 verspannt werden. Diese radiale Verspannung gemäß der Spannkräfte 44 bzw. 46 kann durch das Hydraulikfluid so weit erhöht werden, dass diese ohne weiteres die Axialkraft, die aus dem Verbrennungsdruck resultiert, widerstehen kann. Ein Lösen der Verbindung kann durch ein Herausbewegen des Druckkolbens 48 aus der Sacklochbohrung 58 der Spannleitung 50 und mit einer damit einhergehenden Druckentlastung der Dehnbuchse 30 erreicht werden. Lassen die Verhältnisse im Bereich der Aufnahmebohrung 12 eine zweite Ausbildung zweier taschenförmiger Ausnehmungen 40, 42 nicht zu, kann der Kraftstoffinjektor 20 mittels der an der Düsenspannmutter 26 ausgebildeten Führungsfläche 68 geführt und zentriert werden.About in the embodiment according to the Figures 1 and 2 shown two pocket-shaped recesses 40 and 42, the expansion sleeve 30 can be clamped in the radial direction within the receiving bore 12. This radial tension according to the clamping forces 44 and 46 can be increased by the hydraulic fluid so that it can easily resist the axial force resulting from the combustion pressure. Loosening of the connection can be achieved by moving the pressure piston 48 out of the blind bore 58 of the tensioning line 50 and with an associated pressure relief of the expansion bush 30. If the conditions in the region of the receiving bore 12 do not permit a second embodiment of two pocket-shaped recesses 40, 42, the fuel injector 20 can be guided and centered by means of the guide surface 68 formed on the nozzle clamping nut 26.

Durch die radiale Verspannung und die damit einhergehende Verformung der Wand der Dehnbuchse 30 gegen die Bohrungswand 14 der Aufnahmebohrung 12 können sonst üblicherweise eingesetzte Dichtelemente zur Abdichtung der Haltekörper 22 in der Zylinderkopfabdeckung des Zylinderkopfes 10 entfallen. Da keine zusätzlichen Bauteile wie z.B. Spannpratzen oder Flansche oder dergleichen mit den dazugehörigen Befestigungsschrauben erforderlich sind, lässt sich der Abstand zwischen einzelnen Zylindern einer Verbrennungskraftmaschine auf ein Minimum reduzieren oder alternativ der Bauraum für andere Bauteile vie z.B. Nocken der Nockenwelle, Ventile, Ventilfedern für die hydraulischen Ventile und dergleichen nutzen.Due to the radial tension and the concomitant deformation of the wall of the expansion sleeve 30 against the bore wall 14 of the receiving bore 12 otherwise commonly used sealing elements for sealing the holding body 22 omitted in the cylinder head cover of the cylinder head 10. Since no additional components such as Spannspatzen or flanges or the like are required with the associated mounting screws, the distance between individual cylinders of an internal combustion engine can be reduced to a minimum or alternatively the space for other components vie example. Use cam lobes, valves, valve springs for the hydraulic valves and the like.

Claims (10)

  1. Fuel injector (20) having a retaining body (22) and having a nozzle clamping nut (26), characterized in that the fuel injector (20) has an expansion sleeve (30) which can be acted on with a hydraulic fluid and by means of which the fuel injector (20) is fixed, fastened and centred in a receiving bore (12) of a cylinder head (10), the expansion sleeve (30) being arranged in a receiving bore (12) of the cylinder head (10).
  2. Fuel injector according to Claim 1, characterized in that the expansion sleeve (30) is fastened to a lateral surface (28) of a retaining body (22) of the fuel injector (20).
  3. Fuel injector according to Claim 2, characterized in that the expansion sleeve is cohesively fastened to the lateral surface (28) of the retaining body (22) at a first joining point (32) and at a further joining point (34).
  4. Fuel injector according to Claim 1, characterized in that at least one pocket-like recess (40, 42) is formed on an inner side (38) of the expansion sleeve (30).
  5. Fuel injector according to Claim 4, characterized in that, in the material of the expansion sleeve (30), the wall thickness of the expansion sleeve (30) is reduced in the region of the at least one pocket-like recess (40, 42).
  6. Fuel injector according to Claim 1, characterized in that a clamping line (50) for a hydraulic medium is formed in the retaining body (22) of the fuel injector (20) .
  7. Fuel injector according to one or more of the preceding claims, characterized in that the clamping line (50) has a blind bore and has a duct (60) which opens out at an opening point (62) of the lateral surface (28) within that region of the lateral surface (28) which is enclosed by the expansion sleeve (30).
  8. Fuel injector according to Claim 1, characterized in that a pressure piston (48) which pressurizes the hydraulic fluid or relieves the hydraulic fluid of pressure is held in the clamping line (50).
  9. Fuel injector according to Claim 8, characterized in that the pressure piston (48) is formed in the manner of a grub screw and has at least one sealing element (56).
  10. Fuel injector according to Claim 1, characterized in that the nozzle clamping nut (26) of the fuel injector (20) serves, in the case of a receiving bore of shortened axial length in the cylinder head (10), as a guide surface (68) for the centring and guidance of the fuel injector (20) .
EP07847920A 2007-01-10 2007-12-06 Fixing element for an expansion sleeve Not-in-force EP2108081B1 (en)

Applications Claiming Priority (2)

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DE102007001549A DE102007001549A1 (en) 2007-01-10 2007-01-10 Dehnhülsenbefestigung
PCT/EP2007/063447 WO2008083883A1 (en) 2007-01-10 2007-12-06 Fixing element for an expansion sleeve

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EP2108081A1 EP2108081A1 (en) 2009-10-14
EP2108081B1 true EP2108081B1 (en) 2011-09-14

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EP (1) EP2108081B1 (en)
JP (1) JP2010515854A (en)
AT (1) ATE524652T1 (en)
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US9976527B1 (en) * 2017-01-13 2018-05-22 Caterpillar Inc. Fuel injector assembly having sleeve for directing fuel flow
US11200670B2 (en) * 2020-05-05 2021-12-14 International Business Machines Corporation Real-time detection and correction of shadowing in hyperspectral retinal images

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JP3058339B2 (en) * 1990-07-23 2000-07-04 株式会社東芝 Dynamic semiconductor memory device
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DE19962968A1 (en) * 1999-12-24 2001-06-28 Bosch Gmbh Robert Compensating element for a fuel injection valve of an internal combustion engine comprises a compensating sleeve which is provided with a flexible section between its connector and support sections
JP2001329931A (en) * 2000-05-23 2001-11-30 Nissan Motor Co Ltd Injector supporting structure for internal combustion engine
DE10055641A1 (en) * 2000-11-10 2002-06-13 Siemens Ag Sealing element for arrangement between an injector and a cylinder head and injector and cylinder head with such a sealing element
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DE10145988A1 (en) * 2001-09-18 2003-05-08 Siemens Ag Fastening arrangement for fastening injectors to a cylinder head
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WO2008083883A1 (en) 2008-07-17
US7992544B2 (en) 2011-08-09
DE102007001549A1 (en) 2008-07-17
ATE524652T1 (en) 2011-09-15
US20100043756A1 (en) 2010-02-25
EP2108081A1 (en) 2009-10-14
JP2010515854A (en) 2010-05-13

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