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EP1828594B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP1828594B1
EP1828594B1 EP05807953.4A EP05807953A EP1828594B1 EP 1828594 B1 EP1828594 B1 EP 1828594B1 EP 05807953 A EP05807953 A EP 05807953A EP 1828594 B1 EP1828594 B1 EP 1828594B1
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EP
European Patent Office
Prior art keywords
fuel injection
injection valve
cylinder head
receiving bore
shoulder surface
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.)
Ceased
Application number
EP05807953.4A
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German (de)
French (fr)
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EP1828594A1 (en
Inventor
Martin Scheffel
Christina Gerescher
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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 EP1828594A1 publication Critical patent/EP1828594A1/en
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Publication of EP1828594B1 publication Critical patent/EP1828594B1/en
Ceased legal-status Critical Current
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/14Arrangements of injectors with respect to engines; Mounting of injectors

Definitions

  • the invention relates to a fuel injection valve with a bearing surface on a shoulder surface in a receiving bore in the cylinder head according to the preamble of claim 1.
  • a compensation element for supporting a fuel injection valve in a cylinder head which is annular and is arranged between a valve housing of the fuel injection valve and a wall of a receiving bore of the cylinder head.
  • the compensation element has at least two legs, which are supported on the fuel injection valve and the cylinder head.
  • the disadvantage here is that an additional part must be installed in the final assembly of the fuel injection valve in the cylinder head.
  • High axial forces, which act on the built-in fuel injection valve and thus on the compensation element, can cause a bead, characterized in that the compensation element is impressed into the wall of the receiving bore in the cylinder head.
  • Such an impression of the compensation element complicates the Tolerance compensation when a new fuel injector is loaded into the receiving bore of the cylinder head, since a shoulder of a valve housing can tilt in the bead.
  • a disadvantage of the above document is in particular that no compact design results because an additional part that may obstruct the functionality of tolerance compensation, is installed and caused by the installation also additional costs.
  • a fuel injector for direct fuel injection into a combustion chamber in which a seal seals the gap between the fuel injection valve and the cylinder head.
  • a non-stick coating is applied in the annular gap between the nozzle body of the fuel injection valve and the wall of the cylinder head, which, depending on whether it has a solid, viscous or liquid consistency, fills the entire gap and ensures that no fuel can penetrate and burn there or incineration of the fuel fuel does not cause the combustion of parts of the fuel injection valve and the wall of the cylinder head with each other by charring a solid connection, which makes the expansion of the fuel injection valve difficult.
  • the fuel injection valve has a conically shaped transition between the valve housing and the nozzle body. So that the receiving bore in the cylinder head can accommodate the valve housing, this is also formed conical.
  • a disadvantage of the above document is that manufacturing tolerances in the valve body and the Receiving bore in previously known downstream shoulder surfaces can cause the fuel injection valve can be aligned only by applying a high force, which causes beads can arise in the downstream shoulder surface, which cause that by replacing the old fuel injection valve, the new no longer align.
  • An advantage of the invention is that the bearing surface between a downstream shoulder surface of a valve housing and a shoulder surface of a receiving bore of a cylinder head is designed so that an exchanged fuel injection valve whose valve housing has a downstream shoulder surface, which also to the geometry of the shoulder surface of the receiving bore in the cylinder head positively abuts, without problems in the receiving bore in the cylinder head can be used.
  • a pivoting of the newly inserted fuel injection valve in the receiving bore of the cylinder head for tolerance compensation is possible without the newly inserted fuel injection valve on the shoulder surface of the receiving bore in the cylinder head by tilting a bead leaves.
  • Another advantage is that the number of required between fuel injector and Räilasse sealing points on the inlet side reduced to a sealing point.
  • Fig. 1 shows a schematic and simplified view of a fuel injection system 1, which comprises a fuel injection valve 2, which is introduced into a receiving bore 3 of a cylinder head 4 of an internal combustion engine.
  • the fuel injection valve 2 is designed in the form of a direct-injection fuel injection valve 2, which can serve for the direct injection of fuel into a combustion chamber of the mixture-compressing, spark-ignition internal combustion engine (not shown).
  • the fuel injection valve 2 has at a feed side end 5 a plug connection to a fuel distributor line 6, which is sealed by a seal 7 between the fuel distributor line 6 and a feed pipe 8 of the fuel injection valve 2.
  • the fuel injection valve 2 has an electrical connection 9 for the electrical contacting for actuating the fuel injection valve 2.
  • the fuel injection valve 2 is at least in its part projecting over the cylinder head 4 with a Plastic injection 10 provided, which also surrounds the electrical connection 9.
  • the fuel injection valve 2 is not shown by measures such. B. a clamping claw, fixed in the cylinder head 4 and secured against rotation.
  • an annular compensating element 11 is provided for centering and mounting of the fuel injection valve 2.
  • the annular compensation element 11 may also be a support plate installed as an attachment.
  • the compensation element 11 in this case has an approximately V-shaped cross-section and ensures a reliable tolerance compensation of the fuel injection valve 2 in all degrees of freedom.
  • a seal 13 for. B. Teflon® provided which seals the fuel injection valve 2 against the cylinder head 4 of the engine.
  • Fuel injection valves 2 are usually rigidly installed in the cylinder head 4 of internal combustion engines and both fixed and guided by an intermediate sleeve, which connects the fuel injection valve 2 to the fuel rail 6. Lateral offsets of the fuel injection valve 2 can be compensated. If the fuel injection valve 2, however, be installed without intermediate sleeve, the tolerances must be compensated otherwise. In addition, it is not sufficient to compensate only lateral offsets or tilting. Also, thermal changes during operation of the internal combustion engine must be considered. Furthermore, it is desirable that a replaced and newly inserted into the receiving bore 3 of the cylinder head 4 fuel injection valve 2 no beads 31 (FIG. Fig. 4 ) in the Support surface 24, ie in the shoulder surface 18 of the receiving bore 3 in the cylinder head 4 leaves.
  • Fig. 2 shows a fuel injection valve 2 incorporated in a receiving bore 3 of a cylinder head 4 as a first embodiment of the present invention with a shoulder surface 18 of the receiving bore 3 and with a downstream shoulder surface 16 of the valve housing 14. Both surfaces are second-order hypersurfaces in three-dimensional space and deviate from a planar shape from, wherein the downstream side shoulder surface 16 of the valve housing 14 is constructed so that it forms the concave or the convex counterpart to the adjacent shoulder surface 18 of the receiving bore 3 in the cylinder head 4.
  • the valve housing 14 can be pivoted with respect to the longitudinal axis 26, whereby a tolerance compensation takes place 32 and unnecessary loads are reduced by lateral forces in the material.
  • Fig. 3 shows the definition of an inclination angle ⁇ of the downstream shoulder surface 16 of the valve housing 14 with respect to the longitudinal axis 26 of the fuel injection valve 2, wherein in this second embodiment, the support surface 24, the downstream shoulder surface 16 of the valve housing 14 and the shoulder surface 18 of the receiving bore 3 of the cylinder head 4 are flat surfaces and a normal vector 27 of the support surface 24 is not oriented parallel to the longitudinal axis 26 of the fuel injection valve 2, wherein also the inclination angle ⁇ of the outboard shoulder surface 16 coincident bearing surface 24 with respect to the longitudinal axis 26 of the fuel injection valve 2 results. Further, there is an inclination angle ⁇ between the normal vector 27 and the longitudinal axis 26 of the fuel injection valve 2, which is smaller than 45 °.
  • Fig. 4 shows a bead 31 in the shoulder surface 18 of the receiving bore 3 in the cylinder head 4, which can then come about when the inclination angle ⁇ of the downstream shoulder surface 16 of the valve housing 14 with respect to a longitudinal axis 26 of the fuel injector 2 due to tolerances in the production is slightly larger than At a pronounced bead 31 in the shoulder surface 18 of the receiving bore 3 in the cylinder head 4, it may happen that a replaced fuel injector 2 is fixed therein and thus is no longer pivotable.
  • Fig. 5 shows that a normal vector 28 of the downstream shoulder surface 16 of the valve housing 14 and a normal vector 29 of the shoulder surface 18 of the receiving bore 3 of the cylinder head 4 are not oriented parallel to each other.
  • Fig. 6 shows that the support surface 24 is a partial surface 30 of the shoulder surface 18 of the receiving bore 3 in the cylinder head 4, wherein the partial surface 30 is inclined relative to the shoulder surface 18 of the receiving bore 3 by a third inclination angle ⁇ .
  • the invention is not limited to the illustrated embodiments.
  • the invention for any construction of fuel injection valves 2, for example, for fuel injection valves 2 for injection into the combustion chamber of a self-igniting internal combustion engine, applicable. All features are arbitrarily combinable.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Brennstoffeinspritzventil mit einer Auflagefläche auf einer Schulterfläche in einer Aufnahmebohrung im Zylinderkopf nach der Gattung des Anspruchs 1.The invention relates to a fuel injection valve with a bearing surface on a shoulder surface in a receiving bore in the cylinder head according to the preamble of claim 1.

Aus der nicht vorveröffentlichten Druckschrift DE 103 38 715 A1 ist ein Ausgleichselement zur Lagerung eines Brennstoffeinspritzventils in einem Zylinderkopf bekannt, das ringförmig ausgebildet ist und zwischen einem Ventilgehäuse des Brennstoffeinspritzventils und einer Wandung einer Aufnahmebohrung des Zylinderkopfes angeordnet ist. Das Ausgleichselement weist zumindest zwei Schenkel auf, welche sich an dem Brennstoffeinspritzventil und dem Zylinderkopf abstützen.From the not previously published document DE 103 38 715 A1 a compensation element for supporting a fuel injection valve in a cylinder head is known, which is annular and is arranged between a valve housing of the fuel injection valve and a wall of a receiving bore of the cylinder head. The compensation element has at least two legs, which are supported on the fuel injection valve and the cylinder head.

Nachteilig dabei ist, daß ein zusätzliches Teil bei der Endmontage des Brennstoffeinspritzventils in den Zylinderkopf verbaut werden muß. Hohe axiale Kräfte, die auf das eingebaute Brennstoffeinspritzventil und somit auf das Ausgleichselement wirken, können eine Sicke dadurch verursachen, daß das Ausgleichselement sich in die Wandung der Aufnahmebohrung im Zylinderkopf eingeprägt. Eine solche Einprägung des Ausgleichselementes erschwert den Toleranzausgleich, wenn ein neues Brennstoffeinspritzventil in die Aufnahmebohrung des Zylinderkopfes eingewechselt wird, da sich eine Schulter eines Ventilgehäuses in der Sicke verkanten kann.The disadvantage here is that an additional part must be installed in the final assembly of the fuel injection valve in the cylinder head. High axial forces, which act on the built-in fuel injection valve and thus on the compensation element, can cause a bead, characterized in that the compensation element is impressed into the wall of the receiving bore in the cylinder head. Such an impression of the compensation element complicates the Tolerance compensation when a new fuel injector is loaded into the receiving bore of the cylinder head, since a shoulder of a valve housing can tilt in the bead.

Nachteilig bei der oben genannten Druckschrift ist insbesondere, daß sich keine kompakte Bauform ergibt, da ein zusätzliches Teil, das die Funktionalität des Toleranzausgleichs eventuell behindert, eingebaut wird und durch den Einbau auch zusätzliche Kosten verursacht.A disadvantage of the above document is in particular that no compact design results because an additional part that may obstruct the functionality of tolerance compensation, is installed and caused by the installation also additional costs.

Weiterhin ist aus der Druckschrift US 2004/0124276 A1 ein Brennstoffeinspritzventil für die Brennstoffdirekteinspritzung in eine Verbrennungskammer bekannt, in der eine Dichtung den Spalt zwischen dem Brennstoffeinspritzventil und dem Zylinderkopf abdichtet. Außerdem ist eine Antihaftbeschichtung in dem ringförmigen Spalt zwischen dem Düsenkörper des Brennstoffeinspritzventils und der Wand des Zylinderkopfs aufgetragen, die je nachdem ob sie eine feste, zähflüssige oder flüssige Konsistenz hat, den ganzen Spalt ausfüllt und dafür sorgt, dass kein Brennkraftstoff eindringen und dort verbrennen kann, oder ein Eindringen und Verbrennen des Brennkraftstoffs nicht dazu führt, dass durch die Verbrennung Teile des Brennstoffeinspritzventils und der Wand des Zylinderkopfes miteinander durch Verkohlung eine feste Verbindung eingehen, die den Ausbau des Brennstoffeinspritzventils erschwert. Vorteilhafterweise müssen beim Ausbau des Brennstoffeinspritzventils keine derart hohen Kräfte aufgebracht werden, als dass sich Sicken an den abströmseitigen Schulterflächen bilden würden. Weiterhin weist das Brennstoffeinspritzventil einen konisch ausgeformten Übergang zwischen Ventilgehäuse und Düsenkörper auf. Damit die Aufnahmebohrung im Zylinderkopf das Ventilgehäuse aufnehmen kann, ist diese ebenfalls konisch ausgeformt.Furthermore, from the document US 2004/0124276 A1 a fuel injector for direct fuel injection into a combustion chamber is known, in which a seal seals the gap between the fuel injection valve and the cylinder head. In addition, a non-stick coating is applied in the annular gap between the nozzle body of the fuel injection valve and the wall of the cylinder head, which, depending on whether it has a solid, viscous or liquid consistency, fills the entire gap and ensures that no fuel can penetrate and burn there or incineration of the fuel fuel does not cause the combustion of parts of the fuel injection valve and the wall of the cylinder head with each other by charring a solid connection, which makes the expansion of the fuel injection valve difficult. Advantageously, no such high forces must be applied when removing the fuel injection valve, that would form beads on the downstream shoulder surfaces. Furthermore, the fuel injection valve has a conically shaped transition between the valve housing and the nozzle body. So that the receiving bore in the cylinder head can accommodate the valve housing, this is also formed conical.

Nachteilig an der oben genannten Druckschrift ist, dass Fertigungstoleranzen im Ventilkörper und der Aufnahmebohrung in bisher bekannten abströmseitigen Schulterflächen dazu führen können, dass das Brennstoffeinspritzventil nur unter Aufbringung einer hohen Kraft ausgerichtet werden kann, die dazu führt, dass Sicken in der abströmseitigen Schulterfläche entstehen können, die dazu führen, dass durch einen Tausch des alten Brennstoffeinspritzventils sich das Neue nichtmehr ausrichten lässt.A disadvantage of the above document is that manufacturing tolerances in the valve body and the Receiving bore in previously known downstream shoulder surfaces can cause the fuel injection valve can be aligned only by applying a high force, which causes beads can arise in the downstream shoulder surface, which cause that by replacing the old fuel injection valve, the new no longer align.

Aus der Druckschrift US2002/148446 A ist ein Brennstoffeinspritzventil mit einem Ventilgehäuse, wobei das Ventilgehäuse zumindest eine abströmseitige erste Schulterfläche aufweist, die auf einer zweiten Schulterfläche einer Aufnahmenbohrung in einem Zylinderkopf anliegt, wobei durch die Schulterflächen eine Auflagefläche definiert ist.From the publication US2002 / 148446 A is a fuel injector with a valve housing, wherein the valve housing has at least one downstream first shoulder surface, which rests on a second shoulder surface of a receiving bore in a cylinder head, wherein a bearing surface is defined by the shoulder surfaces.

Vorteile der ErfindungAdvantages of the invention

Ein Vorteil der Erfindung besteht darin, daß die Auflagefläche zwischen einer abströmseitigen Schulterfläche eines Ventilgehäuses und einer Schulterfläche einer Aufnahmebohrung eines Zylinderkopfes so gestaltet ist, daß ein ausgetauschtes Brennstoffeinspritzventil, dessen Ventilgehäuse eine abströmseitige Schulterfläche aufweist, die ebenfalls an die Geometrie der Schulterfläche der Aufnahmebohrung im Zylinderkopf formschlüssig anliegt, ohne Probleme in die Aufnahmebohrung im Zylinderkopf einsetzbar ist. Ein Schwenken des neu eingesetzten Brennstoffeinspritzventils in der Aufnahmebohrung des Zylinderkopfs zum Toleranzausgleich ist dabei möglich, ohne daß das neu eingesetzte Brennstoffeinspritzventil auf der Schulterfläche der Aufnahmebohrung im Zylinderkopf durch Verkanten eine Sicke hinterläßt.An advantage of the invention is that the bearing surface between a downstream shoulder surface of a valve housing and a shoulder surface of a receiving bore of a cylinder head is designed so that an exchanged fuel injection valve whose valve housing has a downstream shoulder surface, which also to the geometry of the shoulder surface of the receiving bore in the cylinder head positively abuts, without problems in the receiving bore in the cylinder head can be used. A pivoting of the newly inserted fuel injection valve in the receiving bore of the cylinder head for tolerance compensation is possible without the newly inserted fuel injection valve on the shoulder surface of the receiving bore in the cylinder head by tilting a bead leaves.

Des weiteren ist es von Vorteil, daß auf die Anbauteile Stützring und Stützblech verzichtet werden kann, wenn die Schulterfläche der Aufnahmebohrung des Zylinderkopfes im Bereich der Auflagefläche und die abströmseitige Schulterfläche des Ventilgehäuses gemäß Anspruch 1 gestaltet ist. Dabei ist die konkave bzw. die konvexe Gegenfläche zu der Schulterfläche der Aufnahmebohrung des Zylinderkopfes im Ventilgehäuse nachzubilden. Dies hat den Vorteil, daß das Brennstoffeinspritzventil zum Toleranzausgleich geschwenkt werden kann, ohne daß ein Verkanten des Ventilgehäuses an der Schulterfläche der Aufnahmebohrung auftritt.Furthermore, it is advantageous that can be dispensed with the attachments support ring and support plate when the shoulder surface of the receiving bore of the cylinder head in the region of the support surface and the downstream side shoulder surface of the valve housing is designed according to claim 1. In this case, the concave or the convex counter surface to the shoulder surface of the receiving bore of the cylinder head in To simulate valve housing. This has the advantage that the fuel injection valve can be pivoted to compensate for tolerances without a tilting of the valve housing on the shoulder surface of the receiving bore occurs.

Ein weiterer Vorteil besteht darin, daß sich die Anzahl der zwischen Brennstoffeinspritzventil und Räiltasse erforderlichen Dichtstellen zulaufseitig auf eine Dichtstelle reduziert.Another advantage is that the number of required between fuel injector and Räilasse sealing points on the inlet side reduced to a sealing point.

Zeichnungdrawing

Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
eine schematische Gesamtansicht eines Brennstoffeinspritzventils, das mit einem bekannten Ausgleichselement in einen Zylinderkopf einer Brennkraftmaschine eingebaut ist;
Fig. 2
einen schematischen Teilschnitt eines ersten Ausführungsbeispiels eines erfindungsgemäßen Brennstoffeinspritzventils, das in einen Zylinderkopf eingebaut ist;
Fig. 3
einen schematischen Teilschnitt eines zweiten Ausführungsbeispiels eines erfindungsgemäßen Brennstoffeinspritzventils, das in einen Zylinderkopf eingebaut ist;
Fig. 4
eine beispielhafte Darstellung der durch Auflagekräfte verursachten Verformung der abstützenden Schulterfläche in einer Aufnahmebohrung eines Zylinderkopfes;
Fig. 5
einen schematischen Teilschnitt eines dritten Ausführungsbeispiels eines erfindungsgemäßen Brennstoffeinspritzventils, das in einen Zylinderkopf eingebaut ist und
Fig. 6
eine beispielhafte Darstellung der durch Auflagekräfte eines erfindungsgemäßen Brennstoffeinspritzventils gemäß des dritten Ausführungsbeispiels verursachten Verformung der abstützenden Schulterfläche in einer Aufnahmebohrung des Zylinderkopfes.
Embodiments of the invention are shown in simplified form in the drawing and explained in more detail in the following description. Show it:
Fig. 1
a schematic overall view of a fuel injection valve, which is installed with a known compensation element in a cylinder head of an internal combustion engine;
Fig. 2
a schematic partial section of a first embodiment of a fuel injection valve according to the invention, which is installed in a cylinder head;
Fig. 3
a schematic partial section of a second embodiment of a fuel injection valve according to the invention, which is installed in a cylinder head;
Fig. 4
an exemplary representation of the bearing forces caused by deformation of the supporting shoulder surface in a receiving bore of a cylinder head;
Fig. 5
a schematic partial section of a third embodiment of a fuel injection valve according to the invention, which is installed in a cylinder head and
Fig. 6
an exemplary representation of the bearing forces of a fuel injection valve according to the invention according to the third embodiment caused deformation of the supporting shoulder surface in a receiving bore of the cylinder head.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Fig. 1 zeigt eine schematisierte und vereinfachte Ansicht eines Brennstoffeinspritzsystems 1, welches ein Brennstoffeinspritzventil 2 umfaßt, das in eine Aufnahmebohrung 3 eines Zylinderkopfes 4 einer Brennkraftmaschine eingebracht ist. Fig. 1 shows a schematic and simplified view of a fuel injection system 1, which comprises a fuel injection valve 2, which is introduced into a receiving bore 3 of a cylinder head 4 of an internal combustion engine.

Das Brennstoffeinspritzventil 2 ist dabei in Form eines direkt einspritzenden Brennstoffeinspritzventils 2 ausgeführt, das zum direkten Einspritzen von Brennstoff in einen Brennraum der nicht weiter dargestellten gemischverdichtenden, fremdgezündeten Brennkraftmaschine dienen kann. Das Brennstoffeinspritzventil 2 weist an einem zulaufseitigen Ende 5 eine Steckverbindung zu einer Brennstoffverteilerleitung 6 auf, die durch eine Dichtung 7 zwischen der Brennstoffverteilerleitung 6 und einem Zuleitungsstutzen 8 des Brennstoffeinspritzventils 2 abgedichtet ist. Das Brennstoffeinspritzventil 2 verfügt über einen elektrischen Anschluß 9 für die elektrische Kontaktierung zur Betätigung des Brennstoffeinspritzventils 2. Das Brennstoffeinspritzventil 2 ist zumindest in seinem den Zylinderkopf 4 überragenden Teil mit einer Kunststoffumspritzung 10 versehen, welche auch den elektrischen Anschluß 9 umgibt.The fuel injection valve 2 is designed in the form of a direct-injection fuel injection valve 2, which can serve for the direct injection of fuel into a combustion chamber of the mixture-compressing, spark-ignition internal combustion engine (not shown). The fuel injection valve 2 has at a feed side end 5 a plug connection to a fuel distributor line 6, which is sealed by a seal 7 between the fuel distributor line 6 and a feed pipe 8 of the fuel injection valve 2. The fuel injection valve 2 has an electrical connection 9 for the electrical contacting for actuating the fuel injection valve 2. The fuel injection valve 2 is at least in its part projecting over the cylinder head 4 with a Plastic injection 10 provided, which also surrounds the electrical connection 9.

Das Brennstoffeinspritzventil 2 ist durch nicht weiter dargestellte Maßnahmen, wie z. B. eine Spannpratze, im Zylinderkopf 4 fixiert und gegen Verdrehen gesichert. In der Aufnahmebohrung 3 ist ein ringförmiges Ausgleichselement 11 zur Zentrierung und Lagerung des Brennstoffeinspritzventils 2 vorgesehen. Statt des ringförmigen Ausgleichselement 11 kann auch ein Stützblech als Anbauteil verbaut sein. Das Ausgleichselement 11 weist dabei einen ungefähr V-förmigen Querschnitt auf und sorgt für einen zuverlässigen Toleranzausgleich des Brennstoffeinspritzventils 2 in allen Freiheitsgraden.The fuel injection valve 2 is not shown by measures such. B. a clamping claw, fixed in the cylinder head 4 and secured against rotation. In the receiving bore 3, an annular compensating element 11 is provided for centering and mounting of the fuel injection valve 2. Instead of the annular compensation element 11 may also be a support plate installed as an attachment. The compensation element 11 in this case has an approximately V-shaped cross-section and ensures a reliable tolerance compensation of the fuel injection valve 2 in all degrees of freedom.

An einem Düsenkörper 12 des Brennstoffeinspritzventils 2 ist eine Dichtung 13, z. B. aus Teflon®, vorgesehen, die das Brennstoffeinspritzventil 2 gegen den Zylinderkopf 4 der Brennkraftmaschine abdichtet.On a nozzle body 12 of the fuel injection valve 2, a seal 13, for. B. Teflon®, provided which seals the fuel injection valve 2 against the cylinder head 4 of the engine.

Brennstoffeinspritzventile 2 werden gewöhnlich starr in den Zylinderkopf 4 von Brennkraftmaschinen eingebaut und durch eine Zwischenhülse, welche das Brennstoffeinspritzventil 2 mit der Brennstoffverteilerleitung 6 verbindet, sowohl fixiert als auch geführt. Laterale Versätze des Brennstoffeinspritzventils 2 können dadurch ausgeglichen werden. Soll das Brennstoffeinspritzventil 2 dagegen ohne Zwischenhülse eingebaut werden, müssen die Toleranzen anders ausgeglichen werden. Zudem reicht es nicht aus, nur seitliche Versätze oder Verkippungen auszugleichen. Auch thermische Veränderungen während des Betriebs der Brennkraftmaschine müssen berücksichtigt werden. Weiterhin ist es wünschenswert, daß ein ausgewechseltes und neu in die Aufnahmebohrung 3 des Zylinderkopfes 4 eingesetztes Brennstoffeinspritzventil 2 keine Sicken 31 (Fig. 4) in der Auflagefläche 24, d.h. in der Schulterfläche 18 der Aufnahmebohrung 3 im Zylinderkopf 4 hinterläßt.Fuel injection valves 2 are usually rigidly installed in the cylinder head 4 of internal combustion engines and both fixed and guided by an intermediate sleeve, which connects the fuel injection valve 2 to the fuel rail 6. Lateral offsets of the fuel injection valve 2 can be compensated. If the fuel injection valve 2, however, be installed without intermediate sleeve, the tolerances must be compensated otherwise. In addition, it is not sufficient to compensate only lateral offsets or tilting. Also, thermal changes during operation of the internal combustion engine must be considered. Furthermore, it is desirable that a replaced and newly inserted into the receiving bore 3 of the cylinder head 4 fuel injection valve 2 no beads 31 (FIG. Fig. 4 ) in the Support surface 24, ie in the shoulder surface 18 of the receiving bore 3 in the cylinder head 4 leaves.

Die oben genannten Anforderungen werden durch die erfindungsgemäß ausgestalteten Schulterflächen 18, 16 der Aufnahmebohrung 3 im Zylinderkopf 4 bzw. der erfindungsgemäßen Ausgestaltung der abströmseitigen Schulterfläche 16 eines Ventilgehäuses 14 gelöst.The above-mentioned requirements are achieved by the inventively designed shoulder surfaces 18, 16 of the receiving bore 3 in the cylinder head 4 and the inventive design of the downstream shoulder surface 16 of a valve housing 14.

Fig. 2 zeigt ein in eine Aufnahmebohrung 3 eines Zylinderkopfes 4 eingebautes Brennstoffeinspritzventil 2 als erstes Ausführungsbeispiel der vorliegenden Erfindung mit einer Schulterfläche 18 der Aufnahmebohrung 3 und mit einer abströmseitigen Schulterfläche 16 des Ventilgehäuses 14. Beide Flächen sind Hyperflächen zweiter Ordnung im dreidimensionalen Raum und weichen von einer ebenen Form ab, wobei die abströmseitige Schulterfläche 16 des Ventilgehäuses 14 so konstruiert ist, daß sie das konkave oder das konvexe Gegenstück zur anliegenden Schulterfläche 18 der Aufnahmebohrung 3 im Zylinderkopf 4 bildet. Das Ventilgehäuse 14 kann bezüglich der Längsachse 26 geschwenkt werden, wodurch ein Toleranzausgleich 32 stattfindet und unnötige Belastungen durch Querkräfte im Material reduziert werden. Fig. 2 shows a fuel injection valve 2 incorporated in a receiving bore 3 of a cylinder head 4 as a first embodiment of the present invention with a shoulder surface 18 of the receiving bore 3 and with a downstream shoulder surface 16 of the valve housing 14. Both surfaces are second-order hypersurfaces in three-dimensional space and deviate from a planar shape from, wherein the downstream side shoulder surface 16 of the valve housing 14 is constructed so that it forms the concave or the convex counterpart to the adjacent shoulder surface 18 of the receiving bore 3 in the cylinder head 4. The valve housing 14 can be pivoted with respect to the longitudinal axis 26, whereby a tolerance compensation takes place 32 and unnecessary loads are reduced by lateral forces in the material.

Fig. 3 zeigt die Definition eines Neigungswinkels α der abströmseitigen Schulterfläche 16 des Ventilgehäuses 14 bezüglich der Längsachse 26 des Brennstoffeinspritzventils 2, wobei in diesem zweiten Ausführungsbeispiel die Auflagefläche 24, die abströmseitige Schulterfläche 16 des Ventilgehäuses 14 und die Schulterfläche 18 der Aufnahmebohrung 3 des Zylinderkopfes 4 ebene Flächen sind und ein Normalenvektor 27 der Auflagefläche 24 nicht parallel zu der Längsachse 26 des Brennstoffeinspritzventils 2 orientiert ist, wobei sich ebenfalls der Neigungswinkel α der mit der abströmseitigen Schulterfläche 16 zusammenfallenden Auflagefläche 24 bezüglich der Längsachse 26 des Brennstoffeinspritzventils 2 ergibt. Ferner ergibt sich ein Neigungswinkel γ zwischen dem Normalenvektor 27 und der Längsachse 26 des Brennstoffeinspritzventils 2, der kleiner als 45° ist. Fig. 3 shows the definition of an inclination angle α of the downstream shoulder surface 16 of the valve housing 14 with respect to the longitudinal axis 26 of the fuel injection valve 2, wherein in this second embodiment, the support surface 24, the downstream shoulder surface 16 of the valve housing 14 and the shoulder surface 18 of the receiving bore 3 of the cylinder head 4 are flat surfaces and a normal vector 27 of the support surface 24 is not oriented parallel to the longitudinal axis 26 of the fuel injection valve 2, wherein also the inclination angle α of the outboard shoulder surface 16 coincident bearing surface 24 with respect to the longitudinal axis 26 of the fuel injection valve 2 results. Further, there is an inclination angle γ between the normal vector 27 and the longitudinal axis 26 of the fuel injection valve 2, which is smaller than 45 °.

Fig. 4 zeigt eine Sicke 31 in der Schulterfläche 18 der Aufnahmebohrung 3 im Zylinderkopf 4, die dann zustande kommen kann, wenn der Neigungswinkel α der abströmseitigen Schulterfläche 16 des Ventilgehäuses 14 bezüglich einer Längsachse 26 des Brennstoffeinspritzventils 2 aufgrund von Toleranzen in der Fertigung etwas größer ist, als ein Neigungswinkel β der Schulterfläche 18 der Aufnahmebohrung 3 im Zylinderkopf 4. Bei einer ausgeprägten Sicke 31 in der Schulterfläche 18 der Aufnahmebohrung 3 im Zylinderkopf 4 kann es dazu kommen, daß ein ausgewechseltes Brennstoffeinspritzventil 2 sich darin festsetzt und somit nicht mehr schwenkbar ist. Dem kann dadurch entgegengewirkt werden, daß der Neigungswinkel α der abströmseitigen Schulterfläche 18 des Ventilgehäuses 14 bezüglich der Längsachse 26 des Brennstoffeinspritzventils 2 kleiner ausgelegt wird als der Neigungswinkel β der Schulterfläche 18 der Aufnahmebohrung 3 bezüglich der Längsachse 26 des Brennstoffeinspritzventils 2. Dies ist in Fig. 5 gezeigt. Fig. 4 shows a bead 31 in the shoulder surface 18 of the receiving bore 3 in the cylinder head 4, which can then come about when the inclination angle α of the downstream shoulder surface 16 of the valve housing 14 with respect to a longitudinal axis 26 of the fuel injector 2 due to tolerances in the production is slightly larger than At a pronounced bead 31 in the shoulder surface 18 of the receiving bore 3 in the cylinder head 4, it may happen that a replaced fuel injector 2 is fixed therein and thus is no longer pivotable. This can be counteracted that the inclination angle α of the downstream shoulder surface 18 of the valve housing 14 with respect to the longitudinal axis 26 of the fuel injection valve 2 is designed to be smaller than the inclination angle β of the shoulder surface 18 of the receiving bore 3 with respect to the longitudinal axis 26 of the fuel injection valve 2. This is in Fig. 5 shown.

Fig. 5 zeigt, daß ein Normalenvektor 28 der abströmseitigen Schulterfläche 16 des Ventilgehäuses 14 und ein Normalenvektor 29 der Schulterfläche 18 der Aufnahmebohrung 3 des Zylinderkopfes 4 nicht parallel zu einander orientiert sind. Fig. 5 shows that a normal vector 28 of the downstream shoulder surface 16 of the valve housing 14 and a normal vector 29 of the shoulder surface 18 of the receiving bore 3 of the cylinder head 4 are not oriented parallel to each other.

Fig. 6 zeigt, daß die Auflagefläche 24 eine Teilfläche 30 der Schulterfläche 18 der Aufnahmebohrung 3 im Zylinderkopf 4 ist, wobei die Teilfläche 30 gegenüber der Schulterfläche 18 der Aufnahmebohrung 3 um einen dritten Neigungswinkel δ geneigt ist. Fig. 6 shows that the support surface 24 is a partial surface 30 of the shoulder surface 18 of the receiving bore 3 in the cylinder head 4, wherein the partial surface 30 is inclined relative to the shoulder surface 18 of the receiving bore 3 by a third inclination angle δ.

Kommt es aufgrund der hohen, von oben durch den Druck in der Brennstoffverteilerleitung auf das Brennstoffeinspritzventil 2 einwirkenden Axialkräfte zu einer plastischen Verformung am Zylinderkopf 4, so führt dies nicht zu einer Sicke 31 in der Schulterfläche 18 der Aufnahmebohrung 3, in die sich ein Brennstoffeinspritzventil 2 mit unterschiedlicher Toleranzlage festsetzen kann, da sich auf der Schulterfläche 18 der Aufnahmebohrung 3 im Zylinderkopf 4 durch das Einwirken einer Niederhaltekraft von oben und durch das Einwirken einer Abstützkraft von unten eine Auflagefläche 24 ausbildet, die den Neigungswinkel δ aufweist, der kleiner ist als der Neigungswinkel β der Schulterfläche 18 der Aufnahmebohrung 3 im Zylinderkopf 4.If, owing to the high axial forces exerted on the fuel injection valve 2 by the pressure in the fuel distributor line, plastic deformation on the cylinder head 4 occurs, this does not lead to a bead 31 in the shoulder surface 18 of the receiving bore 3, into which a fuel injection valve 2 can set with different tolerance position, as formed on the shoulder surface 18 of the receiving bore 3 in the cylinder head 4 by the action of a hold-down force from above and by the action of a support force from below a support surface 24 having the inclination angle δ, which is smaller than the inclination angle β of the shoulder surface 18 of the receiving bore 3 in the cylinder head 4.

Die Erfindung ist nicht auf die dargestellten Ausführungsbeispiele beschränkt. Insbesondere ist die Erfindung für beliebige Bauweisen von Brennstoffeinspritzventilen 2, beispielsweise für Brennstoffeinspritzventile 2 zur Einspritzung in den Brennraum einer selbstzündenden Brennkraftmaschine, anwendbar. Alle Merkmale sind dabei beliebig miteinander kombinierbar.The invention is not limited to the illustrated embodiments. In particular, the invention for any construction of fuel injection valves 2, for example, for fuel injection valves 2 for injection into the combustion chamber of a self-igniting internal combustion engine, applicable. All features are arbitrarily combinable.

Claims (6)

  1. Fuel injection valve (2) having a valve housing (14), wherein the valve housing (14) has at least one outflow-side first shoulder surface (16) which bears against a second shoulder surface (18) of a receiving bore (3) in a cylinder head (4), wherein a support surface (24) is defined by the shoulder surfaces (16, 18),
    characterized
    in that the support surface (24) is a second-order hypersurface in three-dimensional space,
    in that a first angle of inclination (α) of the outflow-side first shoulder surface (16) of the valve housing (14) is smaller than a second angle of inclination (β) of the second shoulder surface (18) of the receiving bore (3) in the cylinder head (4), and
    in that the support surface (24) is a surface part (30) of the second shoulder surface (18) of the receiving bore (3) in the cylinder head (4), wherein the surface part (30) is inclined by an angle of inclination (δ) with respect to the second shoulder surface (18) of the receiving bore (3) in the cylinder head (4).
  2. Fuel injection valve (2) according to Claim 1, characterized
    in that a first normal vector (27) of the support surface (24) is oriented non-parallel with respect to a longitudinal axis (26) of the fuel injection valve (2).
  3. Fuel injection valve (2) according to Claim 2, characterized
    in that a second normal vector (28) of the outflow-side first shoulder surface (16) of the valve housing (14) and a third normal vector (29) of the second shoulder surface (18) of the receiving bore (3) are oriented non-parallel with respect to one another.
  4. Fuel injection valve (2) according to Claim 2 or 3,
    characterized
    in that the normal vector (27) of the support surface (24) encloses an acute angle (γ) of less than 45° with the longitudinal axis (26) of the fuel injection valve (2).
  5. Fuel injection valve (2) according to one of Claims 1 to 4,
    characterized
    in that the support surface (24) is spherical and/or substantially conical.
  6. Fuel injection valve (2) according to Claim 1 or 5,
    characterized
    in that the shoulder surface (16) of the valve housing (14) is concavely domed, and the shoulder surface (18) of the receiving bore (3) in the cylinder head (4) is convexly domed.
EP05807953.4A 2004-12-17 2005-10-07 Fuel injection valve Ceased EP1828594B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004060983.7A DE102004060983B4 (en) 2004-12-17 2004-12-17 Fuel injector
PCT/EP2005/055094 WO2006063880A1 (en) 2004-12-17 2005-10-07 Fuel injection valve

Publications (2)

Publication Number Publication Date
EP1828594A1 EP1828594A1 (en) 2007-09-05
EP1828594B1 true EP1828594B1 (en) 2015-10-07

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Application Number Title Priority Date Filing Date
EP05807953.4A Ceased EP1828594B1 (en) 2004-12-17 2005-10-07 Fuel injection valve

Country Status (6)

Country Link
US (1) US20110094478A1 (en)
EP (1) EP1828594B1 (en)
JP (1) JP2008523316A (en)
CN (1) CN101124399B (en)
DE (1) DE102004060983B4 (en)
WO (1) WO2006063880A1 (en)

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JP5309063B2 (en) * 2010-03-23 2013-10-09 日立オートモティブシステムズ株式会社 Fuel injection valve
US8516996B2 (en) * 2010-12-01 2013-08-27 Ford Global Technologies Direct fuel injection system for internal combustion engine with conical ring injector isolator
KR101776335B1 (en) * 2011-12-09 2017-09-08 현대자동차주식회사 Independent fuel injecting system of Compressed Natural Gas engine
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Also Published As

Publication number Publication date
CN101124399A (en) 2008-02-13
JP2008523316A (en) 2008-07-03
EP1828594A1 (en) 2007-09-05
CN101124399B (en) 2010-05-26
WO2006063880A1 (en) 2006-06-22
DE102004060983A1 (en) 2006-06-22
US20110094478A1 (en) 2011-04-28
DE102004060983B4 (en) 2017-02-02

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