EP2582962B1 - Damping element for an arrangement of a cylinder head of an internal combustion engine and an injection valve - Google Patents

Damping element for an arrangement of a cylinder head of an internal combustion engine and an injection valve Download PDF

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Publication number
EP2582962B1
EP2582962B1 EP11725067.0A EP11725067A EP2582962B1 EP 2582962 B1 EP2582962 B1 EP 2582962B1 EP 11725067 A EP11725067 A EP 11725067A EP 2582962 B1 EP2582962 B1 EP 2582962B1
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EP
European Patent Office
Prior art keywords
damping element
injection valve
cylinder head
longitudinal axis
internal combustion
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
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EP11725067.0A
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German (de)
French (fr)
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EP2582962A1 (en
Inventor
Jens Fath
Joachim Wagner
Rainer Weber
Marco Haller
Robert Kuchler
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Continental Automotive GmbH
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Continental Automotive GmbH
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Publication of EP2582962A1 publication Critical patent/EP2582962A1/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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/09—Fuel-injection apparatus having means for reducing noise
    • 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
    • F02M2200/85—Mounting of fuel injection apparatus
    • F02M2200/858—Mounting of fuel injection apparatus sealing arrangements between injector and engine

Definitions

  • the invention relates to a damping element and an arrangement comprising a cylinder head of an internal combustion engine and an injection valve with a damping element ( FR-A-2862717 ).
  • injection valves For injecting fuel into combustion chambers of an internal combustion engine injection valves are used.
  • the fuel is injected in the case of a gasoline engine under a pressure of up to 200 bar, in the case of a diesel engine under a very high pressure of up to 2000 bar in the combustion chambers.
  • the injection valves for internal combustion engines used for this purpose place high demands on the accuracy of the parameters determining the injection of the fuel into the combustion chambers of the internal combustion engine. This is particularly important as more and more stringent legislation on the permissible pollutant emissions of internal combustion engines located in motor vehicles is enacted. These make it necessary to carry out various measures by which the pollutant emissions are reduced.
  • the injectors are exposed to high mechanical loads. In particular, shaking of the injection valves in the cylinder heads of the internal combustion engine may occur.
  • the object of the invention is to provide an arrangement of a cylinder head of an internal combustion engine and an injection valve, by the operation of the internal combustion engine is made possible with low pollutant emissions and a simple structure of the arrangement of the cylinder head of an internal combustion engine and the injection valve.
  • the invention is characterized by a damping element which is designed for damping an oscillation transmitted between an injection valve with a central longitudinal axis and a cylinder head of an internal combustion engine.
  • the damping element has an annular disk-shaped base body.
  • the damping element has at least two first contact sections fixedly coupled to the base body and projecting beyond the base body in the first axial direction, in a second contact section projecting beyond the base body in a second axial direction opposite the first axial direction.
  • a first contact portion has a radial distance from the longitudinal axis that is unequal to a radial distance of the second contact portion from the longitudinal axis.
  • the radial distance of the second contact portion from the longitudinal axis has a value that is between the values of the radial distances of the first contact portions from the longitudinal axis. This has the advantage that in addition to the damping behavior and a very good sealing behavior of the damping element can be achieved.
  • axial direction and “longitudinal axis” here preferably relate to the central longitudinal axis of the injection valve.
  • the damping element (44) according to the invention is preferably used in an arrangement with a cylinder head of an internal combustion engine, which has a recess and a step formed in the recess, an injection valve with a central longitudinal axis, which is at least partially disposed in the recess, and damping element.
  • the damping element is preferably arranged in the recess axially between the injection valve and the step.
  • the damping element is designed in particular for damping a vibration transmitted between the injection valve and the cylinder head in the direction of the longitudinal axis.
  • damping elements have the advantage that a transformation of an axial movement of the injection valve into an internal movement of the damping element is possible, which is transmitted only to a small extent or not at all to the cylinder head. Due to its design, the damping element can thus advantageously effect a deflection of the power flow. Thus, a low noise level of the internal combustion engine can be achieved.
  • Another advantageous effect of the damping element is a change in the vibration system, which consists inter alia of the cylinder head and the injection valve. This allows a frequency shift to a frequency range acceptable for humans. Furthermore, the vibrations generated by the injection valve in this frequency range can be superimposed by the noise generated by the combustion and the aggregates.
  • At least one of the contact portions is at least partially annularly formed around the central longitudinal axis.
  • FIG. 1 3 is a schematic view of an internal combustion engine 10 with an intake manifold 12, an engine block 14, a cylinder head 16, and an exhaust tract 18.
  • the intake manifold 12 is toward a cylinder Z via an intake passage guided into a combustion chamber 20 of the engine block 14.
  • the engine block 14 further comprises a crankshaft 22, which is coupled via a connecting rod 24 with a piston 26 of the cylinder Z.
  • further cylinders are preferably provided.
  • FIG. 2 shows an arrangement of the cylinder head 16 and an injection valve 30.
  • the cylinder head 16 has a recess 28. In the recess 28, a step 29 of the cylinder head 16 is formed. In the recess 28, a portion of the injection valve 30 is arranged.
  • the injection valve 30 has an injector body 32.
  • the injector body 32 is formed in several pieces in the embodiment shown here.
  • the injector body 32 can also be made in one piece.
  • the injector body 32 has a central longitudinal axis L and a recess 34.
  • a nozzle needle 36 is arranged, which may be made in one or more parts.
  • the injector body 32 comprises a high-pressure line 38, via which the injection valve 30 is connected to a high-pressure circuit (not shown) of a fluid.
  • a high-pressure circuit (not shown) of a fluid.
  • one or more injection openings 40 are or are arranged in the injector body 32. In a closed position of the nozzle needle 36, a fluid flow through the at least one injection opening 40 is prevented and otherwise a fluid flow through the at least one injection opening 40 is released.
  • the injection valve 30 has a clamping element 42 which is arranged in the recess 28 of the cylinder head 16.
  • the clamping element 42 is preferably designed as a nozzle retaining nut and serves to fix the injection valve 30 relative to the cylinder head 16.
  • a damping element 44 is arranged in the recess 28 of the cylinder head 16.
  • the damping element 44 is arranged axially between the injection valve 30 and the step 28 formed in the recess 29 of the cylinder head 16.
  • the damping element 44 is arranged axially between the injector body 32 and the step 29 of the cylinder head 16.
  • damping element 44 By the damping element 44, a change of the vibration system, which consists of the cylinder head 16, the injection valve 30 and fasteners 60, carried out to a frequency shift in a well-tolerated human frequency range. Furthermore, either an increase of the surface pressure or a reduction of the biasing force of the injection valve 30 can be achieved. By a corresponding design of the damping element 44, a compensation of the different coefficients of expansion of the cylinder head 16 with the fastening elements 60 and the injection valve 30 is additionally achieved. This can lead to a constant over the entire temperature range biasing force.
  • the damping element 44 is designed in particular as a one-piece ring.
  • the damping element consists at least partially of a material with high vibration damping capacity (internal damping) in the desired frequency and temperature range.
  • internal damping internal damping
  • the material used is also preferably resistant to fuels and their combustion products.
  • the damping element 44 is in particular wholly or partly made of a metal alloy, with which a good resistance of the damping element 44 can be achieved even at temperatures of up to 250 ° C and pressures of up to 250 bar. Furthermore, such alloys can be particularly resistant to fuels and their combustion products.
  • the damping element 44 has a base body 46.
  • the base body 46 is formed as an annular disc.
  • the damping element 44 has a first contact section 48a fixedly coupled to the main body 46, which extends in a first axial direction R_1 beyond the main body 46 to the injection valve 30.
  • the first contact portion 48a has a radial distance A_11 from the longitudinal axis L.
  • the damping member 44 has a second fixedly coupled to the base 46 contact portion 50 which extends in a second axial direction R_2 on the base body 46 to the step 29.
  • the second contact portion 50 has a radial distance A_2 from the longitudinal axis L.
  • the radial distance A_11 of the first contact portion 48a is not equal to the radial distance A_2 of the second contact portion 50 (FIG. FIGS. 3A and 3B ).
  • a transmission of an axial movement of the injection valve 30 into a vibration movement of the damping element 44 and thus a dissipation of energy in the damping element 44 can take place, so that kinetic energy only slightly or not at all is transferred to the cylinder head, including in particular the small contact surface between the damping element 44 and the stage 29 can contribute.
  • a good vibration damping by the damping element 44 can be achieved.
  • the damping element 44 has a further first contact section 48b fixedly coupled to the main body 46, which extends in the first axial direction R_1 beyond the main body 46 to the injection valve 30 and has a radial distance A_12 from the longitudinal axis L.
  • the radial distance A_2 of the second contact portion 50 is smaller than the radial distance A_11 of the first contact portion 48a and greater than the radial distance A_12 of the further first contact portion 48b.
  • the contact portions 48a, 48b, 50 are preferably arranged annularly around the central longitudinal axis L (see in particular FIGS. 3A, 4A ). Such annular contact portions 48a, 50 allow both a good vibration damping over the circumference of the damping element 44 and a good seal by the damping element 44th

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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

Die Erfindung betrifft ein Dämpfungselement und eine Anordnung aus einem Zylinderkopf einer Brennkraftmaschine und einem Einspritzventil mit einem Dämpfungselement ( FR-A-2862717 ).The invention relates to a damping element and an arrangement comprising a cylinder head of an internal combustion engine and an injection valve with a damping element ( FR-A-2862717 ).

Zum Einspritzen von Kraftstoff in Brennräume einer Brennkraftmaschine kommen Einspritzventile zum Einsatz. Der Kraftstoff wird im Fall einer Benzinbrennkraftmaschine unter einem Druck von bis zu 200 bar, im Fall einer Dieselbrennkraftmaschine unter einem sehr hohen Druck von bis über 2000 bar in die Brennräume eingespritzt. Die dabei zum Einsatz kommenden Einspritzventile für Brennkraftmaschinen stellen hohe Anforderungen an die Genauigkeit der die Einspritzung des Kraftstoffs in die Brennräume der Brennkraftmaschine bestimmenden Parameter. Dies ist besonders wichtig, da immer strengere Gesetzesvorschriften bezüglich der zulässigen Schadstoffemission von Brennkraftmaschinen, die in Kraftfahrzeugen angeordnet sind, erlassen werden. Diese machen es erforderlich, diverse Maßnahmen vorzunehmen, durch welche die Schadstoffemissionen gesenkt werden.For injecting fuel into combustion chambers of an internal combustion engine injection valves are used. The fuel is injected in the case of a gasoline engine under a pressure of up to 200 bar, in the case of a diesel engine under a very high pressure of up to 2000 bar in the combustion chambers. The injection valves for internal combustion engines used for this purpose place high demands on the accuracy of the parameters determining the injection of the fuel into the combustion chambers of the internal combustion engine. This is particularly important as more and more stringent legislation on the permissible pollutant emissions of internal combustion engines located in motor vehicles is enacted. These make it necessary to carry out various measures by which the pollutant emissions are reduced.

Während des Betriebs der Brennkraftmaschine werden die Einspritzventile hohen mechanischen Belastungen ausgesetzt. So kann es insbesondere zu Erschütterungen der Einspritzventile in den Zylinderköpfen der Brennkraftmaschine kommen.During operation of the internal combustion engine, the injectors are exposed to high mechanical loads. In particular, shaking of the injection valves in the cylinder heads of the internal combustion engine may occur.

Die Aufgabe der Erfindung ist es, eine Anordnung aus einem Zylinderkopf einer Brennkraftmaschine und einem Einspritzventil zu schaffen, durch die ein Betrieb der Brennkraftmaschine mit geringen Schadstoffemissionen und ein einfacher Aufbau der Anordnung aus dem Zylinderkopf einer Brennkraftmaschine und dem Einspritzventil ermöglicht wird.The object of the invention is to provide an arrangement of a cylinder head of an internal combustion engine and an injection valve, by the operation of the internal combustion engine is made possible with low pollutant emissions and a simple structure of the arrangement of the cylinder head of an internal combustion engine and the injection valve.

Die Aufgabe wird gelöst durch die Merkmale der unabhängigen Ansprüche. Vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen gekennzeichnet.The object is solved by the features of the independent claims. Advantageous embodiments of the invention are characterized in the subclaims.

Die Erfindung zeichnet sich aus durch ein Dämpfungselement, welches ausgebildet ist zum Dämpfen einer zwischen einem Einspritzventil mit einer zentralen Längsachse und einem Zylinderkopf einer Brennkraftmaschine übertragenen Schwingung. Das Dämpfungselement weist einen ringscheibenförmigen Grundkörper auf. Das Dämpfungselement weist mindestens zwei fest mit dem Grundkörper gekoppelte, in der ersten axialen Richtung über den Grundkörper hinaus vorspringende erste Kontaktabschnitte auf, in einer der ersten axialen Richtung entgegengesetzten zweiten axialen Richtung über den Grundkörper hinaus vorspringenden zweiten Kontaktabschnitt. Ein erster Kontaktabschnitt hat einen radialen Abstand von der Längsachse, der ungleich einem radialen Abstand des zweiten Kontaktabschnitts von der Längsachse ist.The invention is characterized by a damping element which is designed for damping an oscillation transmitted between an injection valve with a central longitudinal axis and a cylinder head of an internal combustion engine. The damping element has an annular disk-shaped base body. The damping element has at least two first contact sections fixedly coupled to the base body and projecting beyond the base body in the first axial direction, in a second contact section projecting beyond the base body in a second axial direction opposite the first axial direction. A first contact portion has a radial distance from the longitudinal axis that is unequal to a radial distance of the second contact portion from the longitudinal axis.

Der radiale Abstand des zweiten Kontaktabschnitts von der Längsachse hat einen Wert, der zwischen den Werten der radialen Abstände der ersten Kontaktabschnitte von der Längsachse ist. Dies hat den Vorteil, dass neben dem Dämpfungsverhalten auch ein sehr gutes Dichtungsverhalten des Dämpfungselements erreicht werden kann.The radial distance of the second contact portion from the longitudinal axis has a value that is between the values of the radial distances of the first contact portions from the longitudinal axis. This has the advantage that in addition to the damping behavior and a very good sealing behavior of the damping element can be achieved.

Die Begriffe "axiale Richtung" und "Längsachse" beziehen sich hierbei vorzugsweise auf die zentrale Längsachse des Einspritzventils.The terms "axial direction" and "longitudinal axis" here preferably relate to the central longitudinal axis of the injection valve.

Das erfindungsgemäße Dämpfungselement (44) kommt vorzugsweise zum Einsatz in einer Anordnung, mit einem Zylinderkopf einer Brennkraftmaschine, der aufweist eine Ausnehmung und eine in der Ausnehmung ausgebildete Stufe, einem Einspritzventil mit einer zentralen Längsachse, das mindestens teilweise in der Ausnehmung angeordnet ist, und dem Dämpfungselement. Das Dämpfungselement ist dabei vorzugsweise in der Ausnehmung axial zwischen dem Einspritzventil und der Stufe angeordnet.The damping element (44) according to the invention is preferably used in an arrangement with a cylinder head of an internal combustion engine, which has a recess and a step formed in the recess, an injection valve with a central longitudinal axis, which is at least partially disposed in the recess, and damping element. The damping element is preferably arranged in the recess axially between the injection valve and the step.

Das Dämpfungselement ist insbesondere zum Dämpfen einer zwischen dem Einspritzventil und dem Zylinderkopf in Richtung der Längsachse übertragenen Schwingung ausgebildet.The damping element is designed in particular for damping a vibration transmitted between the injection valve and the cylinder head in the direction of the longitudinal axis.

Derartige Dämpfungselemente haben den Vorteil, dass eine Transformation einer axialen Bewegung des Einspritzventils in eine innere Bewegung des Dämpfungselements möglich ist, die nur in geringem Maße oder gar nicht auf den Zylinderkopf übertragen wird. Durch seine Bauform kann das Dämpfungselement somit vorteilhaft eine Umlenkung des Kraftflusses bewirken. Damit kann eine geringe Geräuschentwicklung der Brennkraftmaschine erreicht werden. Ein weiterer vorteilhafter Effekt des Dämpfungselements liegt in einer Änderung des Schwingungssystems, das unter anderem aus dem Zylinderkopf und dem Einspritzventil besteht. Damit ist eine Frequenzverschiebung in einen für den Menschen verträglichen Frequenzbereich möglich. Des Weiteren können die von dem Einspritzventil erzeugten Erschütterungen in diesem Frequenzbereich von dem durch die Verbrennung und die Aggregate erzeugten Geräusche überlagert werden. Des Weiteren kann entweder eine Erhöhung der Flächenpressung oder eine Reduzierung der Vorspannkraft des Einspritzventils erzielt werden. Durch eine entsprechende Auslegung des Dämpfungselements wird zusätzlich eine Kompensierung der unterschiedlichen Ausdehnungskoeffizienten des Zylinderkopfs und des Einspritzventils erreicht. Dies kann zu einer über den gesamten Temperaturbereich konstanten Vorspannkraft führen.Such damping elements have the advantage that a transformation of an axial movement of the injection valve into an internal movement of the damping element is possible, which is transmitted only to a small extent or not at all to the cylinder head. Due to its design, the damping element can thus advantageously effect a deflection of the power flow. Thus, a low noise level of the internal combustion engine can be achieved. Another advantageous effect of the damping element is a change in the vibration system, which consists inter alia of the cylinder head and the injection valve. This allows a frequency shift to a frequency range acceptable for humans. Furthermore, the vibrations generated by the injection valve in this frequency range can be superimposed by the noise generated by the combustion and the aggregates. Furthermore, either an increase of the surface pressure or a reduction of the biasing force of the injection valve can be achieved. By an appropriate design of the damping element is in addition achieved a compensation of the different expansion coefficients of the cylinder head and the injection valve. This can lead to a constant over the entire temperature range biasing force.

In einer vorteilhaften Ausführungsform ist mindestens eine der Kontaktabschnitte wenigstens abschnittsweise kreisringförmig um die zentrale Längsachse ausgebildet. Dies hat den Vorteil, dass eine gute Dämpfung der Schwingungen über den gesamten Umfang des Dämpfungselements sowie ein gutes Dichtungsverhalten des Dämpfungselements erreichbar ist.In an advantageous embodiment, at least one of the contact portions is at least partially annularly formed around the central longitudinal axis. This has the advantage that a good damping of the vibrations over the entire circumference of the damping element and a good sealing behavior of the damping element can be achieved.

Ausführungsbeispiele der Erfindung sind im Folgenden in den Figuren 1, 2, 4A und 4B anhand von schematischen Zeichnungen näher erläutert. Es zeigen:

Figur 1
eine schematische Ansicht einer Brennkraftmaschine,
Figur 2
einen Teil eines Einspritzventils und eines Zylinderkopfs der Brennkraftmaschine,
Figuren 4A und 4B
ein Dämpfungselement in einer Aufsicht und in einem Längsschnitt,
Die Figuren 3A und 3B
zeigen auch ein Dämpfungselement in einer Aufsicht und in einem Längsschnitt.
Embodiments of the invention are hereinafter in the FIGS. 1, 2 . 4A and 4B explained in more detail with reference to schematic drawings. Show it:
FIG. 1
a schematic view of an internal combustion engine,
FIG. 2
a part of an injection valve and a cylinder head of the internal combustion engine,
FIGS. 4A and 4B
a damping element in a plan view and in a longitudinal section,
Figures 3A and 3B
also show a damping element in a plan view and in a longitudinal section.

In Figur 1 ist eine schematische Ansicht einer Brennkraftmaschine 10 gezeigt, mit einem Ansaugtrakt 12, einem Motorblock 14, einem Zylinderkopf 16 und einem Abgastrakt 18. Der Ansaugtrakt 12 ist hin zu einem Zylinder Z über einen Einlasskanal in einen Brennraum 20 des Motorblocks 14 geführt. Der Motorblock 14 umfasst ferner eine Kurbelwelle 22, welche über eine Pleuelstange 24 mit einem Kolben 26 des Zylinders Z gekoppelt ist. Neben dem Zylinder Z sind bevorzugt noch weitere Zylinder vorgesehen.In FIG. 1 3 is a schematic view of an internal combustion engine 10 with an intake manifold 12, an engine block 14, a cylinder head 16, and an exhaust tract 18. The intake manifold 12 is toward a cylinder Z via an intake passage guided into a combustion chamber 20 of the engine block 14. The engine block 14 further comprises a crankshaft 22, which is coupled via a connecting rod 24 with a piston 26 of the cylinder Z. In addition to the cylinder Z, further cylinders are preferably provided.

Figur 2 zeigt eine Anordnung aus dem Zylinderkopf 16 und einem Einspritzventil 30. Der Zylinderkopf 16 hat eine Ausnehmung 28. In der Ausnehmung 28 ist eine Stufe 29 des Zylinderkopfs 16 ausgebildet. In der Ausnehmung 28 ist ein Abschnitt des Einspritzventils 30 angeordnet. Das Einspritzventil 30 weist einen Injektorkörper 32 auf. Der Injektorkörper 32 ist in der hier gezeigten Ausführungsform mehrstückig ausgebildet. Der Injektorkörper 32 kann auch einstückig ausgeführt sein. Der Injektorkörper 32 hat eine zentrale Längsachse L und eine Ausnehmung 34. In der Ausnehmung 34 des Injektorkörpers 32 ist eine Düsennadel 36 angeordnet, die einteilig oder mehrteilig ausgeführt sein kann. Der Injektorkörper 32 umfasst eine Hochdruckleitung 38, über die das Einspritzventil 30 mit einem nicht dargestellten Hochdruckkreis eines Fluids verbunden ist. An einem axialen Ende ist oder sind in dem Injektorkörper 32 eine oder mehrere Einspritzöffnungen 40 angeordnet. In einer Schließposition der Düsennadel 36 ist ein Fluidfluss durch die mindestens eine Einspritzöffnung 40 verhindert und ansonsten ein Fluidfluss durch die mindestens eine Einspritzöffnung 40 freigegeben. FIG. 2 shows an arrangement of the cylinder head 16 and an injection valve 30. The cylinder head 16 has a recess 28. In the recess 28, a step 29 of the cylinder head 16 is formed. In the recess 28, a portion of the injection valve 30 is arranged. The injection valve 30 has an injector body 32. The injector body 32 is formed in several pieces in the embodiment shown here. The injector body 32 can also be made in one piece. The injector body 32 has a central longitudinal axis L and a recess 34. In the recess 34 of the injector body 32, a nozzle needle 36 is arranged, which may be made in one or more parts. The injector body 32 comprises a high-pressure line 38, via which the injection valve 30 is connected to a high-pressure circuit (not shown) of a fluid. At one axial end, one or more injection openings 40 are or are arranged in the injector body 32. In a closed position of the nozzle needle 36, a fluid flow through the at least one injection opening 40 is prevented and otherwise a fluid flow through the at least one injection opening 40 is released.

Das Einspritzventil 30 hat ein Spannelement 42, das in der Ausnehmung 28 des Zylinderkopfs 16 angeordnet ist. Das Spannelement 42 ist vorzugsweise als Düsenspannmutter ausgebildet und dient der Festlegung des Einspritzventils 30 gegenüber dem Zylinderkopf 16.The injection valve 30 has a clamping element 42 which is arranged in the recess 28 of the cylinder head 16. The clamping element 42 is preferably designed as a nozzle retaining nut and serves to fix the injection valve 30 relative to the cylinder head 16.

In der Ausnehmung 28 des Zylinderkopfs 16 ist ein Dämpfungselement 44 angeordnet. Das Dämpfungselement 44 ist axial zwischen dem Einspritzventil 30 und der in der Ausnehmung 28 ausgebildeten Stufe 29 des Zylinderkopfs 16 angeordnet. Vorzugsweise ist das Dämpfungselement 44 axial zwischen dem Injektorkörper 32 und der Stufe 29 des Zylinderkopfs 16 angeordnet. Mittels des Dämpfungselements 44 können zwischen dem Einspritzventil 30 und dem Zylinderkopf 16 übertragenene Schwingungen, wie sie während des Betriebs der Brennkraftmaschine aufgrund der auftretenden Erschütterungen entstehen können, gedämpft werden. Insbesondere kann eine zwischen dem Einspritzventil 30 und dem Zylinderkopf 16 in Richtung der Längsachse L des Einspritzventils 30 übertragene Schwingung gedämpft werden. Durch das Dämpfungselement 44 kann eine Änderung des Schwingungssystems, das aus dem Zylinderkopf 16, dem Einspritzventil 30 und Befestigungselementen 60 besteht, zu einer Frequenzverschiebung in einen für den Menschen gut verträglichen Frequenzbereich erfolgen. Des Weiteren kann entweder eine Erhöhung der Flächenpressung oder eine Reduzierung der Vorspannkraft des Einspritzventils 30 erzielt werden. Durch eine entsprechende Auslegung des Dämpfungselements 44 wird zusätzlich eine Kompensierung der unterschiedlichen Ausdehnungskoeffizienten des Zylinderkopfs 16 mit den Befestigungselementen 60 und des Einspritzventils 30 erreicht. Dies kann zu einer über den gesamten Temperaturbereich konstanten Vorspannkraft führen. Das Dämpfungselement 44 ist insbesondere als einstückiger Ring ausgebildet.In the recess 28 of the cylinder head 16, a damping element 44 is arranged. The damping element 44 is arranged axially between the injection valve 30 and the step 28 formed in the recess 29 of the cylinder head 16. Preferably, the damping element 44 is arranged axially between the injector body 32 and the step 29 of the cylinder head 16. By means of the damping element 44 can be damped between the injection valve 30 and the cylinder head 16 transmitted vibrations, such as may occur during operation of the internal combustion engine due to the vibrations occurring. In particular, a vibration transmitted between the injection valve 30 and the cylinder head 16 in the direction of the longitudinal axis L of the injection valve 30 can be damped. By the damping element 44, a change of the vibration system, which consists of the cylinder head 16, the injection valve 30 and fasteners 60, carried out to a frequency shift in a well-tolerated human frequency range. Furthermore, either an increase of the surface pressure or a reduction of the biasing force of the injection valve 30 can be achieved. By a corresponding design of the damping element 44, a compensation of the different coefficients of expansion of the cylinder head 16 with the fastening elements 60 and the injection valve 30 is additionally achieved. This can lead to a constant over the entire temperature range biasing force. The damping element 44 is designed in particular as a one-piece ring.

Vorzugsweise besteht das Dämpfungselement zumindest teilweise aus einem Material mit hohem Schwingungsdäpfungsvermögen (Eigendämpfung) im gewünschten Frequenz- und Temperaturbereich. Insbesondere werden vorzugsweise in einem Temperaturbereich von über -40°C und von unter 250°C sowie bis zu einem Druck von bis zu 250 bar eine hohe axiale Steifigkeit und Positionierung der Düsenspitze erreicht. Das verwendete Material ist darüber hinaus vorzugsweise resistent gegenüber Kraftstoffen und deren Verbrennungsprodukten.Preferably, the damping element consists at least partially of a material with high vibration damping capacity (internal damping) in the desired frequency and temperature range. In particular, preferably in a temperature range of above -40 ° C and below 250 ° C and up to a pressure of up to 250 bar achieved a high axial stiffness and positioning of the nozzle tip. The material used is also preferably resistant to fuels and their combustion products.

Das Dämpfungselement 44 besteht insbesondere ganz oder teilweise aus einer Metalllegierung, mit der eine gute Beständigkeit des Dämpfungselements 44 auch bei Temperaturen von bis zu 250°C und Drücken von bis zu 250 bar erreicht werden kann. Des Weiteren können derartige Legierungen besonders resistent gegenüber Kraftstoffen und deren Verbrennungsprodukten sein.The damping element 44 is in particular wholly or partly made of a metal alloy, with which a good resistance of the damping element 44 can be achieved even at temperatures of up to 250 ° C and pressures of up to 250 bar. Furthermore, such alloys can be particularly resistant to fuels and their combustion products.

Das Dämpfungselement 44 hat einen Grundkörper 46. Der Grundkörper 46 ist als Ringscheibe ausgebildet. Das Dämpfungselement 44 hat einen fest mit dem Grundkörper 46 gekoppelten ersten Kontaktabschnitt 48a, der sich in einer ersten axialen Richtung R_1 über den Grundkörper 46 hinaus zu dem Einspritzventil 30 erstreckt. Der erste Kontaktabschnitt 48a hat einen radialen Abstand A_11 von der Längsachse L. Das Dämpfungselement 44 hat einen zweiten fest mit dem Grundkörper 46 gekoppelten Kontaktabschnitt 50, der sich in einer zweiten axialen Richtung R_2 über den Grundkörper 46 hinaus zu der Stufe 29 erstreckt. Der zweite Kontaktabschnitt 50 hat einen radialen Abstand A_2 von der Längsachse L. Der radiale Abstand A_11 des ersten Kontaktabschnitts 48a ist ungleich dem radialen Abstand A_2 des zweiten Kontaktabschnitts 50 (Figuren 3A und 3B). Mittels der unterschiedlichen radialen Abstände A_11, A_2 der Kontaktabschnitte 48a, 50 kann eine Übertragung einer axialen Bewegung des Einspritzventils 30 in eine Schwingungsbewegung des Dämpfungselements 44 und damit eine Dissipation von Energie in dem Dämpfungselement 44 erfolgen, so dass Bewegungsenergie nur in geringem Maße oder gar nicht auf den Zylinderkopf übertragen wird, wozu insbesondere auch die kleine Kontaktfläche zwischen dem Dämpfungselement 44 und der Stufe 29 beitragen kann. Damit kann eine gute Schwingungsdämpfung durch das Dämpfungselement 44 erreicht werden.The damping element 44 has a base body 46. The base body 46 is formed as an annular disc. The damping element 44 has a first contact section 48a fixedly coupled to the main body 46, which extends in a first axial direction R_1 beyond the main body 46 to the injection valve 30. The first contact portion 48a has a radial distance A_11 from the longitudinal axis L. The damping member 44 has a second fixedly coupled to the base 46 contact portion 50 which extends in a second axial direction R_2 on the base body 46 to the step 29. The second contact portion 50 has a radial distance A_2 from the longitudinal axis L. The radial distance A_11 of the first contact portion 48a is not equal to the radial distance A_2 of the second contact portion 50 (FIG. FIGS. 3A and 3B ). By means of the different radial distances A_11, A_2 of the contact portions 48a, 50, a transmission of an axial movement of the injection valve 30 into a vibration movement of the damping element 44 and thus a dissipation of energy in the damping element 44 can take place, so that kinetic energy only slightly or not at all is transferred to the cylinder head, including in particular the small contact surface between the damping element 44 and the stage 29 can contribute. Thus, a good vibration damping by the damping element 44 can be achieved.

In der Ausführungsform der Figuren 4A und 4B hat das Dämpfungselement 44 einen fest mit dem Grundkörper 46 gekoppelten weiteren ersten Kontaktabschnitt 48b, der sich in der ersten axialen Richtung R_1 über den Grundkörper 46 hinaus zu dem Einspritzventil 30 erstreckt und einen radialen Abstand A_12 von der Längsachse L hat. Der radiale Abstand A_2 des zweiten Kontaktabschnitts 50 ist kleiner als der radiale Abstand A_11 des ersten Kontaktabschnitte 48a und größer als der radiale Abstand A_12 des Weiteren ersten Kontaktabschnitts 48b. Durch die Ausbildung der beiden ersten Kontaktabschnitte 48a, 48b ist ein gutes Dichtungsverhalten des Dämpfungselements 44 erreichbar.In the embodiment of the FIGS. 4A and 4B the damping element 44 has a further first contact section 48b fixedly coupled to the main body 46, which extends in the first axial direction R_1 beyond the main body 46 to the injection valve 30 and has a radial distance A_12 from the longitudinal axis L. The radial distance A_2 of the second contact portion 50 is smaller than the radial distance A_11 of the first contact portion 48a and greater than the radial distance A_12 of the further first contact portion 48b. By forming the two first contact portions 48a, 48b, a good sealing behavior of the damping element 44 can be achieved.

Die Kontaktabschnitte 48a, 48b, 50 sind vorzugsweise kreisringförmig um die zentrale Längsachse L angeordnet (siehe insbesondere Figuren 3A, 4A). Derartige kreisringförmige Kontaktabschnitte 48a, 50 ermöglichen sowohl eine gute Schwingungsdämpfung über den Umfang des Dämpfungselements 44 als auch eine gute Abdichtung durch das Dämpfungselement 44.The contact portions 48a, 48b, 50 are preferably arranged annularly around the central longitudinal axis L (see in particular FIGS. 3A, 4A ). Such annular contact portions 48a, 50 allow both a good vibration damping over the circumference of the damping element 44 and a good seal by the damping element 44th

Claims (3)

  1. Damping element (44) which is designed to damp a vibration transmitted between an injection valve (30) with a central longitudinal axis (L) and a cylinder head (16) of an internal combustion engine (10),
    wherein the damping element (44) has
    - a ring-washer-shaped base body (46),
    - two first contact sections (48a, 48b) which are fixedly coupled to the base body (46) and protrude beyond the base body (46) in the first axial direction (R_1), and a second contact section (50) which is fixedly coupled to the base body (46) and protrudes beyond the base body (46) in a second axial direction (R_2) opposed to the first axial direction (R_1), wherein one of the first contact section is (48a, 48b) has a radial distance (A_11, A_12) from the longitudinal axis (L) which is unequal to a radial distance (A_2) of the second contact section (50) from the longitudinal axis (L), and
    - wherein the radial distance (A_2) of the second contact section (50) from the longitudinal axis (L) has a value which is between the values of the radial distances (A_11, A_12) of the first contact sections (48a, 48b) from the longitudinal axis (L).
  2. Damping element (44) according to Claim 1, wherein at least one of the contact sections (48a, 48b, 50) is embodied at least partially in a ring shape around the central longitudinal axis (L).
  3. Arrangement having
    - a cylinder head (16) of an internal combustion engine (10), which cylinder head (16) has a recess (28) and a step (29) which is formed in the recess (28),
    - an injection valve (30) which has a central longitudinal axis (L) and is at least partially arranged in the recess (28), and
    - a damping element (44) according to either one of Claims 1 and 2, which is arranged axially in the recess (28) between the injection valve (30) and the step (29).
EP11725067.0A 2010-06-17 2011-06-09 Damping element for an arrangement of a cylinder head of an internal combustion engine and an injection valve Not-in-force EP2582962B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010024140A DE102010024140A1 (en) 2010-06-17 2010-06-17 Damping element for an arrangement of a cylinder head of an internal combustion engine and an injection valve
PCT/EP2011/059574 WO2011157619A1 (en) 2010-06-17 2011-06-09 Damping element for an arrangement of a cylinder head of an internal combustion engine and an injection valve

Publications (2)

Publication Number Publication Date
EP2582962A1 EP2582962A1 (en) 2013-04-24
EP2582962B1 true EP2582962B1 (en) 2015-08-26

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Application Number Title Priority Date Filing Date
EP11725067.0A Not-in-force EP2582962B1 (en) 2010-06-17 2011-06-09 Damping element for an arrangement of a cylinder head of an internal combustion engine and an injection valve

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US (1) US9347412B2 (en)
EP (1) EP2582962B1 (en)
CN (1) CN103221679B (en)
DE (1) DE102010024140A1 (en)
WO (1) WO2011157619A1 (en)

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DE102010024140A1 (en) 2010-06-17 2011-12-22 Continental Automotive Gmbh Damping element for an arrangement of a cylinder head of an internal combustion engine and an injection valve
EP2857671A1 (en) * 2013-10-04 2015-04-08 Continental Automotive GmbH Fluid injector
DE102016211689A1 (en) * 2016-06-29 2018-01-04 Robert Bosch Gmbh Injector with damping element
DE102017218008A1 (en) * 2017-10-10 2019-04-11 Robert Bosch Gmbh Decoupling element for a fuel injection device

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Also Published As

Publication number Publication date
EP2582962A1 (en) 2013-04-24
WO2011157619A1 (en) 2011-12-22
CN103221679A (en) 2013-07-24
DE102010024140A1 (en) 2011-12-22
CN103221679B (en) 2017-04-05
US9347412B2 (en) 2016-05-24
US20130146026A1 (en) 2013-06-13

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