EP2362074B1 - Device for variable valve timing on a combustion engine - Google Patents

Device for variable valve timing on a combustion engine Download PDF

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Publication number
EP2362074B1
EP2362074B1 EP11151488A EP11151488A EP2362074B1 EP 2362074 B1 EP2362074 B1 EP 2362074B1 EP 11151488 A EP11151488 A EP 11151488A EP 11151488 A EP11151488 A EP 11151488A EP 2362074 B1 EP2362074 B1 EP 2362074B1
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EP
European Patent Office
Prior art keywords
pressure
drive element
drive
combustion engine
depression
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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EP11151488A
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German (de)
French (fr)
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EP2362074A1 (en
Inventor
Jürgen Weber
Stefan Schelter
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of EP2362074A1 publication Critical patent/EP2362074A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2303/00—Manufacturing of components used in valve arrangements

Definitions

  • the invention relates to a device for variably setting the timing of gas exchange valves of an internal combustion engine with a drive element which can be brought into drive connection with a crankshaft of the internal combustion engine, an output element which is arranged in drive connection with a camshaft of the internal combustion engine and pivotally mounted to the drive element, and at least one side cover, which is arranged on an axial side surface of the output element or the drive element and rotatably connected to the drive element or the driven element and having a disk-shaped portion, wherein within the device at least one pressure chamber is provided and wherein by pressure medium supply to or pressure fluid discharge of the Pressure chamber a phase angle between the drive element and the output element is variably adjustable.
  • devices for variable adjustment of the timing of gas exchange valves are used to adjust the phase relation between a crankshaft and a camshaft in a defined angular range, between a maximum early and a maximum late position variable.
  • the device is integrated in a drive train via which torque is transmitted from the crankshaft to the camshaft.
  • This drive train can be realized for example as a belt, chain or gear drive.
  • the device is non-rotatably connected to a camshaft and, for example, have one or more pressure chambers, by means of which the phase relation between the crankshaft and the camshaft can be selectively changed by pressure medium.
  • Such a device is for example from the DE 10 2004 026 865 A1 known.
  • the device has a drive element, an output element and two side covers, wherein the drive element is in driving connection with a crankshaft and the output element is non-rotatably attached to a camshaft.
  • the output element is arranged in a defined angular interval pivotally to the drive element.
  • the drive element, the output element and the side cover define a plurality of pressure chambers, which are divided by wings in opposing pressure chambers.
  • the pressure chambers form a hydraulic actuator, by means of which the phase angle between the driven element and the drive element can be variably adjusted.
  • the side covers are arranged on the axial side surfaces of the output element and the drive element and rotatably connected by screws with the drive element.
  • the device has a locking mechanism comprising a gate and a spring-loaded locking element.
  • the scenery is realized by means of a machining post-processing step in the form of a groove on a side surface of the solidly formed side cover.
  • the locking element is disposed axially displaceable within a receptacle which is formed within the driven element. Stand the backdrop and the locking element in the axial direction opposite, so the locking element can engage in the gate and mechanically couple the output member with the drive element.
  • To release the locking of the backdrop pressure medium is supplied, which pushes back the locking element into the receptacle.
  • One of the side covers is also solid in this embodiment, wherein a central circular area of the side cover is formed thick-walled, as its radial appearance. In the thick-walled area, radial grooves are introduced by means of machining post-processing steps, which communicate on the one hand with a pressure medium line and on the other hand with a group of pressure chambers.
  • the present invention has for its object to provide a reliable and inexpensive device.
  • the disc-shaped portion on the drive element facing away from the side surface has at least one bulge, which limits a recess on the driven element side facing the disc-shaped portion, wherein the recess of the shape of the bulge is adjusted and the pressure fluid guide within the Device serves.
  • the device has a drive element and an output element, wherein the drive element is driven by a crankshaft of the internal combustion engine and the output element drives a camshaft of the internal combustion engine.
  • the drive element can be in drive connection with the crankshaft, for example, by means of a traction mechanism or gear drive.
  • the output member may be rotatably connected to the camshaft, for example.
  • a hydraulic actuator with at least one pressure chamber is provided, by means of which the driven element can be pivoted in a defined angular range relative to the drive element. Consequently a phase relation between the output element and the drive element is variably adjustable.
  • a side cover is provided which is rotatably connected to one of these components.
  • the side cover on a disc-shaped portion optionally with a central opening, which seals, for example, the pressure chambers in the axial direction.
  • the side cover at the disc-shaped portion one or more protrusions are provided on the side facing away from the driven element side surface.
  • Each of the bulges defines on the side facing the driven element side of the disc-shaped portion a recess which is thus adapted to the shape of the bulge.
  • the depression serves to guide the pressure medium within the device.
  • the depression communicates with the pressure chamber.
  • at least one pressure medium line is provided, by means of the pressure medium to the device feedable or can be discharged from this, wherein the recess communicates with the pressure medium line.
  • the depression (s) may serve to supply pressure to or discharge fluid from the pressure chamber (s).
  • the radial bores in the driven element which serve to supply pressure medium to the pressure chambers and are to be produced by means of elaborate, machining post-processing steps, omitted.
  • the depressions may be formed on one of the side covers or on both side covers of the device. In the latter case, the costly drilling accounts completely, in the first case, only half of the holes are necessary.
  • the recess at least partially forms a link into which a locking element, which is received in a receptacle of the drive element or of the driven element, can engage, wherein the link communicates with a pressure medium line or a pressure chamber.
  • the recesses forming the depression increase the surface of the side cover and, on the other hand, generate air turbulence in the region of the side cover during operation of the internal combustion engine.
  • the cooling of the side cover improves, whereby its thermal load decreases.
  • the bulges cause an increase in the rigidity of the side cover, so that its deformation decreases during operation of the internal combustion engine and thus the leakage sinking in and out of the device.
  • the side cover can be made thin-walled and therefore weight-optimized with the same rigidity.
  • the disc-shaped portion is formed as a sheet metal part and the bulge and the recess by means of a chipless forming process, for example, a deep-drawing process is prepared.
  • a chipless forming process for example, a deep-drawing process is prepared.
  • it may be provided to produce the disk-shaped section by means of a metal or plastic injection molding method, a sintering method, by means of casting, forging or stamped packetizing.
  • the bulge-well pairs can be formed cost-neutral during the manufacture of the disc-shaped portion.
  • FIG. 1 schematically an internal combustion engine 1 is sketched, wherein a seated on a crankshaft 2 piston 3 is indicated in a cylinder 4.
  • the crankshaft 2 is in the illustrated embodiment via a respective traction drive 5 with an intake camshaft 6 and exhaust camshaft 7 in combination, wherein a first and a second device 11 for the variable adjustment of the timing of gas exchange valves 9, 10 for a relative rotation between the crankshaft 2 and the Camshafts 6, 7 can provide.
  • Cams 8 of the camshafts 6, 7 actuate one or more intake gas exchange valves 9 or one or more exhaust gas exchange valves 10.
  • FIGS. 2 and 3 show a device 11 according to the invention in the longitudinal or cross section.
  • the device 11 has a drive element 13, an output element 14 and two side covers 15, 16, which are arranged on axial side surfaces of the drive member 13 and secured by screws 12 thereto.
  • the output element 14 is designed in the form of an impeller and has a substantially cylindrically designed hub member 17, extending from the outer cylindrical surface area wings 18 in the radial direction outwards. Starting from an outer peripheral wall 19 of the drive element 13, projections 20 extend radially inwards.
  • the drive element 13 is mounted by means of radially inner circumferential walls of the projections 20 relative to the output element 14 rotatably mounted on this.
  • the drive element 13 is provided with a belt pulley 21, via which torque can be transmitted from the crankshaft 2 to the drive element 13 by means of a belt drive (not shown).
  • the output member 14 is rotatably connected by means of a central screw 22 with the camshaft 6, 7.
  • pressure chambers 23 are formed between each two circumferentially adjacent projections.
  • Each of the pressure spaces 23 is circumferentially bounded by adjacent projections 20, axially of the side covers 15, 16, radially inwardly of the hub member 17, and radially outward of the peripheral wall 19.
  • In each of the pressure chambers 23 protrudes a wing 18, wherein the wings 18 bear against both the side covers 15, 16, and on the peripheral wall 19.
  • Each wing 18 thus divides the respective pressure chamber 23 into two counteracting pressure chambers 24, 25th
  • the output element 14 is arranged rotatably in a defined Winkelbreich to the drive element 13. The angular range is limited in a direction of rotation of the output element 14 in that each of the vanes 18 abuts an early stop 26.
  • the angular range in the other direction of rotation is limited by the fact that each of the wings 18 comes to rest on a late stop 27.
  • pressurizing a group of pressure chambers 24, 25 and pressure relief of the other group the phase position of the drive element 13 to the output element 14 (and thus the phase angle of the camshaft 6, 7 to the crankshaft 2) can be varied.
  • pressurizing both groups of pressure chambers 24, 25, the phase position can be kept constant.
  • the camshaft 6, 7 has a central pressure medium line 28 and a plurality of axially parallel pressure medium lines 29, which extend in the axial direction.
  • the pressure medium lines 28, 29 communicate via annular grooves 30a, b, which are formed on an outer circumferential surface of the camshaft 6, 7, with a control valve, not shown.
  • the axially parallel pressure medium lines 29 communicate via radial bores 39 with a first group of pressure chambers 24.
  • the central pressure medium line 28 extends through the central screw 22 to the side of the output element 14 facing away from the camshaft 6, 7 and opens into a closed space 31, which is sealed by a plug 32.
  • the FIGS. 4 and 5 show a voltage applied to the drive member 13 side surface and a back of the first side cover 15.
  • the first side cover 15 has a disc-shaped portion 33 with a central opening 34 and consists of a steel sheet.
  • a plurality of recesses 35a-c are formed on the side surface facing away from the output element 14 ( FIG. 5 ).
  • a first protrusion 35a extends annularly around the central opening 34.
  • five second protrusions 35b are provided which are rib-shaped and extend radially outward from the first protrusion 35a.
  • a third bulge 35c adjoins the first bulge 35a in the area of one of the second bulges 35b and covers a portion of the disc-shaped section 33 between two of the second bulges 35b.
  • the bulges 35a-c By the bulges 35a-c, the surface of the first side cover 15 is increased, so that the cooling of the device 11 is improved.
  • the bulges 35a-c generate air turbulences in the region of the first side cover 15, thereby further improving its cooling. Overall, this leads to a lower thermal load on the first side cover 15 and to a more effective cooling of the pressure medium present in the device 11, usually engine oil of the internal combustion engine 1.
  • the protrusions 35a-c increase the rigidity of the first side cover 15, whereby the leakage decreases or the first side cover 15 can be made thinner walled.
  • corresponding recesses 36a-c are formed on the side surface of the disk-shaped section 33 facing the output element 14 (FIG. FIG. 4 ).
  • the first recess 36a is formed in the form of an annular channel and communicates with the central pressure medium line 28 via the space 31.
  • the second recesses 36b are in the form of radially extending grooves which open into the first recess 36a and are connected to a second group of Pressure chambers 25 communicate.
  • the pressure medium supply to or the pressure medium discharge from the second pressure chambers 25 thus takes place via the first and second recesses 36 a, b, which are formed on the disk-shaped portion 33 of the first side cover 15.
  • the otherwise usual radial bores within the output element 14, which must be introduced by means of machining Nachbearbeitungs Kunststoffe in a blank, can be omitted, whereby its manufacturing cost is significantly reduced.
  • the device 11 further comprises a locking mechanism, by means of which a releasable mechanical connection between the driven element 14 and the drive element 13 can be produced.
  • the driven element 14 has a receptacle 37, in which an axially displaceable locking element 38 is accommodated.
  • the locking element 38 is acted upon by means of a compression spring with a force in the direction of the disk-shaped portion 33.
  • the third recess 36 c is made with excess to the locking element 38 and receives a stop element 40.
  • the stop element 38 and the third recess 36c delimit a slide into which the locking element 38 can engage when it faces the slide in the axial direction.
  • the stop element 40 has two grooves 41, 42 on a side surface facing the first side cover 15.
  • the first groove 41 connects the first recess 36a with the second recess 36b, which adjoins the stop element 40, so that the pressure medium supply of this second recess 36b and thus of the corresponding pressure chamber 25 via the first groove.
  • the second groove 42 connects the first groove 41 with the third recess 36c and thus provides the pressure medium supply of the gate, for releasing the mechanical connection between the output element 13 and the drive element 14, safe.
  • the grooves 41, 42 may alternatively or additionally be formed in the third recess 36c in the region of the stop element 40.
  • the bulges 35a-c and the corresponding recesses 36a-c can be produced cost-neutral.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Description

Gebiet der ErfindungField of the invention

Die Erfindung betrifft eine Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine mit einem Antriebselement, das in Antriebsverbindung mit einer Kurbelwelle der Brennkraftmaschine bringbar ist, einem Abtriebselement, das in Antriebsverbindung mit einer Nockenwelle der Brennkraftmaschine bringbar und schwenkbar zu dem Antriebselement angeordnet ist, und mindestens einem Seitendeckel, der an einer axialen Seitenfläche des Abtriebselements oder des Antriebselements angeordnet und drehfest mit dem Antriebselement oder dem Abtriebselement verbunden ist und einen scheibenförmigen Abschnitt aufweist, wobei innerhalb der Vorrichtung zumindest ein Druckraum vorgesehen ist und wobei durch Druckmittelzufuhr zu bzw. Druckmittelabfuhr von dem Druckraum eine Phasenlage zwischen dem Antriebselement und dem Abtriebselement variabel einstellbar ist.The invention relates to a device for variably setting the timing of gas exchange valves of an internal combustion engine with a drive element which can be brought into drive connection with a crankshaft of the internal combustion engine, an output element which is arranged in drive connection with a camshaft of the internal combustion engine and pivotally mounted to the drive element, and at least one side cover, which is arranged on an axial side surface of the output element or the drive element and rotatably connected to the drive element or the driven element and having a disk-shaped portion, wherein within the device at least one pressure chamber is provided and wherein by pressure medium supply to or pressure fluid discharge of the Pressure chamber a phase angle between the drive element and the output element is variably adjustable.

Hintergrund der ErfindungBackground of the invention

In modernen Brennkraftmaschinen werden Vorrichtungen zur variablen Einstellung der Steuerzeiten von Gaswechselventilen eingesetzt, um die Phasenrelation zwischen einer Kurbelwelle und einer Nockenwelle in einem definierten Winkelbereich, zwischen einer maximalen Früh- und einer maximalen Spätposition, variabel einstellen zu können. Die Vorrichtung ist in einen Antriebsstrang integriert, über welchen Drehmoment von der Kurbelwelle auf die Nockenwelle übertragen wird. Dieser Antriebsstrang kann beispielsweise als Riemen-, Ketten- oder Zahnradtrieb realisiert sein. Darüber hinaus ist die Vorrichtung drehfest mit einer Nockenwelle verbunden und kann beispielsweise eine oder mehrere Druckkammern aufweisen, mittels derer die Phasenrelation zwischen der Kurbelwelle und der Nockenwelle durch Druckmittelbeaufschlagung gezielt verändert werden kann.In modern internal combustion engines devices for variable adjustment of the timing of gas exchange valves are used to adjust the phase relation between a crankshaft and a camshaft in a defined angular range, between a maximum early and a maximum late position variable. The device is integrated in a drive train via which torque is transmitted from the crankshaft to the camshaft. This drive train can be realized for example as a belt, chain or gear drive. In addition, the device is non-rotatably connected to a camshaft and, for example, have one or more pressure chambers, by means of which the phase relation between the crankshaft and the camshaft can be selectively changed by pressure medium.

Eine derartige Vorrichtung ist beispielsweise aus der DE 10 2004 026 865 A1 bekannt. Die Vorrichtung weist ein Antriebselement, ein Abtriebselement und zwei Seitendeckel auf, wobei das Antriebselement in Antriebsverbindung mit einer Kurbelwelle steht und das Abtriebselement drehfest an einer Nockenwelle befestigt ist. Das Abtriebselement ist in einem definierten Winkelintervall schwenkbar zu dem Antriebselement angeordnet. Das Antriebselement, das Abtriebselement und die Seitendeckel begrenzen mehrere Druckräume, die von Flügeln in gegeneinander wirkende Druckkammern geteilt werden. Die Druckkammern bilden einen hydraulischen Stellantrieb aus, mittels dem die Phasenlage zwischen dem Abtriebselement und dem Antriebselement variabel eingestellt werden kann. Die Seitendeckel sind an den axialen Seitenflächen des Abtriebselements und des Antriebselements angeordnet und mittels Schrauben drehfest mit dem Antriebselement verbunden. Zur Druckmittelversorgung der Druckkammern sind Bohrungen in das Abtriebselement eingebracht, die ausgehend von einer zentralen Öffnung des Abtriebselements in radialer Richtung verlaufen und in die Druckkammern münden. Die Vorrichtung weist einen Verriegelungsmechanismus auf, der eine Kulisse und ein federbeaufschlagtes Verriegelungselement umfasst. Die Kulisse ist mittels eines spanenden Nachbearbeitungsschritts in Form einer Nut an einer Seitenfläche des massiv ausgebildeten Seitendeckels realisiert. Das Verriegelungselement ist innerhalb einer Aufnahme, die innerhalb des Abtriebselements ausgebildet ist, axial verschiebbar angeordnet. Stehen sich die Kulisse und das Verriegelungselement in axialer Richtung gegenüber, so kann das Verriegelungselement in die Kulisse eingreifen und das Abtriebselement mechanisch mit dem Antriebselement koppeln. Zum Lösen der Verriegelung wird der Kulisse Druckmittel zugeführt, das das Verriegelungselement in die Aufnahme zurückdrängt.Such a device is for example from the DE 10 2004 026 865 A1 known. The device has a drive element, an output element and two side covers, wherein the drive element is in driving connection with a crankshaft and the output element is non-rotatably attached to a camshaft. The output element is arranged in a defined angular interval pivotally to the drive element. The drive element, the output element and the side cover define a plurality of pressure chambers, which are divided by wings in opposing pressure chambers. The pressure chambers form a hydraulic actuator, by means of which the phase angle between the driven element and the drive element can be variably adjusted. The side covers are arranged on the axial side surfaces of the output element and the drive element and rotatably connected by screws with the drive element. To supply pressure to the pressure chambers bores are introduced into the driven element, which extend starting from a central opening of the driven element in the radial direction and open into the pressure chambers. The device has a locking mechanism comprising a gate and a spring-loaded locking element. The scenery is realized by means of a machining post-processing step in the form of a groove on a side surface of the solidly formed side cover. The locking element is disposed axially displaceable within a receptacle which is formed within the driven element. Stand the backdrop and the locking element in the axial direction opposite, so the locking element can engage in the gate and mechanically couple the output member with the drive element. To release the locking of the backdrop pressure medium is supplied, which pushes back the locking element into the receptacle.

Aus der DE 100 38 607 A1 ist eine weitere Vorrichtung bekannt, die im Wesentlichen der der DE 10 2004 026 865 A1 entspricht. Einer der Seitendeckel ist in dieser Ausführungsform ebenfalls massiv ausgebildet, wobei ein zentraler kreisrunder Bereich des Seitendeckels dickwandiger ausgebildet ist, als dessen radiales Äußeres. In dem dickwandigen Bereich sind mittels spanender Nachbearbeitungsschritte radiale Nuten eingebracht, die einerseits mit einer Druckmittelleitung und andererseits mit einer Gruppe von Druckkammern kommunizieren.From the DE 100 38 607 A1 Another device is known, which is essentially that of DE 10 2004 026 865 A1 equivalent. One of the side covers is also solid in this embodiment, wherein a central circular area of the side cover is formed thick-walled, as its radial appearance. In the thick-walled area, radial grooves are introduced by means of machining post-processing steps, which communicate on the one hand with a pressure medium line and on the other hand with a group of pressure chambers.

Aufgabe der ErfindungObject of the invention

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, eine zuverlässige und kostengünstige Vorrichtung vorzuschlagen.The present invention has for its object to provide a reliable and inexpensive device.

Zusammenfassung der ErfindungSummary of the invention

Die Aufgabe wird erfindungsgemäß dadurch gelöst, dass der scheibenförmige Abschnitt an der dem Antriebselement abgewandten Seitenfläche zumindest eine Ausbuchtung aufweist, die eine Vertiefung an der dem Abtriebselement zugewandten Seite des scheibenförmigen Abschnitts begrenzt, wobei die Vertiefung der Form der Ausbuchtung angepasst ist und zur Druckmittelführung innerhalb der Vorrichtung dient.The object is achieved in that the disc-shaped portion on the drive element facing away from the side surface has at least one bulge, which limits a recess on the driven element side facing the disc-shaped portion, wherein the recess of the shape of the bulge is adjusted and the pressure fluid guide within the Device serves.

Die Vorrichtung weist ein Antriebselement und ein Abtriebselement auf, wobei das Antriebselement von einer Kurbelwelle der Brennkraftmaschine angetrieben wird und das Abtriebselement eine Nockenwelle der Brennkraftmaschine antreibt. Das Antriebselement kann beispielsweise mittels eines Zugmittel- oder Zahnradtriebs in Antriebsverbindung mit der Kurbelwelle stehen. Das Abtriebselement kann beispielsweise drehfest mit der Nockenwelle verbunden sein. Des Weiteren ist ein hydraulischer Stellantrieb mit zumindest einem Druckraum vorgesehen, mittels dem das Abtriebselement in einem defmierten Winkelbereich relativ zu dem Antriebselement verschwenkt werden kann. Somit ist eine Phasenrelation zwischen dem Abtriebselement und dem Antriebselement variabel einstellbar. An einer axialen Seitenfläche des Antriebselements oder des Abtriebselements ist ein Seitendeckel vorgesehen der drehfest mit einem dieser Bauteile verbunden ist. Dabei weist der Seitendeckel einen scheibenförmigen Abschnitt, gegebenenfalls mit einer zentralen Öffnung, auf, der beispielsweise die Druckräume in axialer Richtung abdichtet. An dem scheibenförmigen Abschnitt sind auf der dem Abtriebselement abgewandten Seitenfläche eine oder mehrere Ausbuchtungen vorgesehen. Jede der Ausbuchtungen begrenzt auf der dem Abtriebselement zugewandten Seite des scheibenförmigen Abschnitts eine Vertiefung, die somit der Form der Ausbuchtung angepasst ist. Die Vertiefung dient zur Druckmittelführung innerhalb der Vorrichtung.The device has a drive element and an output element, wherein the drive element is driven by a crankshaft of the internal combustion engine and the output element drives a camshaft of the internal combustion engine. The drive element can be in drive connection with the crankshaft, for example, by means of a traction mechanism or gear drive. The output member may be rotatably connected to the camshaft, for example. Furthermore, a hydraulic actuator with at least one pressure chamber is provided, by means of which the driven element can be pivoted in a defined angular range relative to the drive element. Consequently a phase relation between the output element and the drive element is variably adjustable. On an axial side surface of the drive element or the output element, a side cover is provided which is rotatably connected to one of these components. In this case, the side cover on a disc-shaped portion, optionally with a central opening, which seals, for example, the pressure chambers in the axial direction. At the disc-shaped portion one or more protrusions are provided on the side facing away from the driven element side surface. Each of the bulges defines on the side facing the driven element side of the disc-shaped portion a recess which is thus adapted to the shape of the bulge. The depression serves to guide the pressure medium within the device.

Beispielsweise kann vorgesehen sein, dass die Vertiefung mit dem Druckraum kommuniziert. Zusätzlich oder alternativ kann vorgesehen sein, dass zumindest eine Druckmittelleitung vorgesehen ist, mittels der Druckmittel zu der Vorrichtung zuleitbar oder von dieser abführbar ist, wobei die Vertiefung mit der Druckmittelleitung kommuniziert. Somit können die Vertiefung/en zur Druckmittelzufuhr zu bzw. Druckmittelabfuhr von dem oder den Druckräumen dienen. Somit können die radialen Bohrungen in dem Abtriebselement, die zur Druckmittelversorgung der Druckräume dienen und mittels aufwändigen, spanenden Nachbearbeitungsschritten herzustellen sind, entfallen. Die Vertiefungen können an einem der Seitendeckel oder an beiden Seitendeckeln der Vorrichtung ausgebildet sein. In letzterem Fall entfallen die kostenintensiven Bohrungen komplett, im ersten Fall sind nur die Hälfte der Bohrungen notwendig.For example, it can be provided that the depression communicates with the pressure chamber. Additionally or alternatively, it may be provided that at least one pressure medium line is provided, by means of the pressure medium to the device feedable or can be discharged from this, wherein the recess communicates with the pressure medium line. Thus, the depression (s) may serve to supply pressure to or discharge fluid from the pressure chamber (s). Thus, the radial bores in the driven element, which serve to supply pressure medium to the pressure chambers and are to be produced by means of elaborate, machining post-processing steps, omitted. The depressions may be formed on one of the side covers or on both side covers of the device. In the latter case, the costly drilling accounts completely, in the first case, only half of the holes are necessary.

In einer Weiterbildung der Erfindung wird vorgeschlagen, dass die Vertiefung eine Kulisse zumindest teilweise ausbildet, in die ein Verriegelungselement, das in einer Aufnahme des Antriebselements oder des Abtriebselements aufgenommen ist, eingreifen kann, wobei die Kulisse mit einer Druckmittelleitung oder einem Druckraum kommuniziert. Somit entfällt der kostenintensive, spanende Verfahrensschritt zur Ausbildung der Kulisse.In a further development of the invention, it is proposed that the recess at least partially forms a link into which a locking element, which is received in a receptacle of the drive element or of the driven element, can engage, wherein the link communicates with a pressure medium line or a pressure chamber. Thus eliminates the costly, cutting process step to form the backdrop.

Die die Vertiefung ausbildenden Ausbuchtungen vergrößern zum Einen die Oberfläche des Seitendeckels und erzeugen zum Anderen während des Betriebs der Brennkraftmaschine Luftverwirbelungen im Bereich des Seitendeckels. Somit verbessert sich die Kühlung des Seitendeckels, wodurch dessen thermische Belastung sinkt. Des Weiteren bewirken die Ausbuchtungen eine Steigerung der Steifigkeit des Seitendeckels, so dass dessen Verformung während des Betriebs der Brennkraftmaschine sinkt und somit die Leckage innerhalb und aus der Vorrichtung heraus sinkt. Alternativ kann der Seitendeckel dünnwandiger und damit gewichtsoptimiert bei gleicher Steifigkeit ausgebildet werden.On the one hand, the recesses forming the depression increase the surface of the side cover and, on the other hand, generate air turbulence in the region of the side cover during operation of the internal combustion engine. Thus, the cooling of the side cover improves, whereby its thermal load decreases. Furthermore, the bulges cause an increase in the rigidity of the side cover, so that its deformation decreases during operation of the internal combustion engine and thus the leakage sinking in and out of the device. Alternatively, the side cover can be made thin-walled and therefore weight-optimized with the same rigidity.

In einer Konkretisierung der Erfindung wird vorgeschlagen, dass der scheibenförmige Abschnitt als Blechteil ausgebildet ist und die Ausbuchtung und die Vertiefung mittels eines spanlosen Umformverfahrens, beispielsweise eines Tiefziehverfahrens, hergestellt ist. Alternativ kann vorgesehen sein den scheibenförmigen Abschnitt mittels eines Metall- oder Kunststoffspritzgussverfahrens, eines Sinterverfahrens, mittels Gießen, Schmieden oder Stanzpaketieren herzustellen. Somit können die Ausbuchtungs-Vertiefungspaare kostenneutral während der Herstellung des scheibenförmigen Abschnitts ausgeformt werden.In a concretization of the invention it is proposed that the disc-shaped portion is formed as a sheet metal part and the bulge and the recess by means of a chipless forming process, for example, a deep-drawing process is prepared. Alternatively, it may be provided to produce the disk-shaped section by means of a metal or plastic injection molding method, a sintering method, by means of casting, forging or stamped packetizing. Thus, the bulge-well pairs can be formed cost-neutral during the manufacture of the disc-shaped portion.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Weitere Merkmale der Erfindung ergeben sich aus der nachfolgenden Beschreibung und aus den Zeichnungen in denen ein Ausführungsbeispiel der Erfindung vereinfacht dargestellt ist. Es zeigen:

  • Figur 1 nur sehr schematisch eine Brennkraftmaschine,
  • Figur 2 einen Längsschnitt durch eine erfindungsgemäßen Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine,
  • Figur 3 einen Querschnitt durch die erfindungsgemäße Vorrichtung entlang der Linie III-III in Figur 2,
  • Figur 4 einen Draufsicht auf eine an dem Antriebselement anliegende Seitenfläche des Seitendeckels,
  • Figur 5 eine perspektivische Darstellung der Außenseite des Seitendeckels aus Figur 4.
Further features of the invention will become apparent from the following description and from the drawings in which an embodiment of the invention is shown in simplified form. Show it:
  • FIG. 1 only very schematically an internal combustion engine,
  • FIG. 2 a longitudinal section through a device according to the invention for the variable adjustment of the timing of gas exchange valves of an internal combustion engine,
  • FIG. 3 a cross section through the device according to the invention along the line III-III in FIG. 2 .
  • FIG. 4 a plan view of a voltage applied to the drive element side surface of the side cover,
  • FIG. 5 a perspective view of the outside of the side cover FIG. 4 ,

Ausführliche Beschreibung der ZeichnungenDetailed description of the drawings

In Figur 1 ist schematisch eine Brennkraftmaschine 1 skizziert, wobei ein auf einer Kurbelwelle 2 sitzender Kolben 3 in einem Zylinder 4 angedeutet ist. Die Kurbelwelle 2 steht in der dargestellten Ausführungsform über je einen Zugmitteltrieb 5 mit einer Einlassnockenwelle 6 bzw. Auslassnockenwelle 7 in Verbindung, wobei eine erste und eine zweite Vorrichtung 11 zur variablen Einstellung der Steuerzeiten von Gaswechselventilen 9, 10 für eine Relativdrehung zwischen Kurbelwelle 2 und den Nockenwellen 6, 7 sorgen können. Nocken 8 der Nockenwellen 6, 7 betätigen ein oder mehrere Einlassgaswechselventile 9 bzw. ein oder mehrere Auslassgaswechselventile 10.In FIG. 1 schematically an internal combustion engine 1 is sketched, wherein a seated on a crankshaft 2 piston 3 is indicated in a cylinder 4. The crankshaft 2 is in the illustrated embodiment via a respective traction drive 5 with an intake camshaft 6 and exhaust camshaft 7 in combination, wherein a first and a second device 11 for the variable adjustment of the timing of gas exchange valves 9, 10 for a relative rotation between the crankshaft 2 and the Camshafts 6, 7 can provide. Cams 8 of the camshafts 6, 7 actuate one or more intake gas exchange valves 9 or one or more exhaust gas exchange valves 10.

Die Figuren 2 und 3 zeigen eine erfindungsgemäße Vorrichtung 11 im Längs- bzw. Querschnitt. Die Vorrichtung 11 weist ein Antriebselement 13, ein Abtriebselement 14 und zwei Seitendeckel 15, 16 auf, die an axialen Seitenflächen des Antriebselements 13 angeordnet und mittels Schrauben 12 an diesem befestigt sind. Das Abtriebselement 14 ist in Form eines Flügelrades ausgeführt und weist ein im Wesentlichen zylindrisch ausgeführtes Nabenelement 17 auf, von dessen äußerer zylindrischer Mantelfläche sich Flügel 18 in radialer Richtung nach außen erstrecken.
Ausgehend von einer äußeren Umfangswand 19 des Antriebselements 13 erstrecken sich Vorsprünge 20 radial nach innen. Das Antriebselement 13 ist mittels radial innen liegender Umfangswände der Vorsprünge 20 relativ zu dem Abtriebselement 14 drehbar auf diesem gelagert.The FIGS. 2 and 3 show a device 11 according to the invention in the longitudinal or cross section. The device 11 has a drive element 13, an output element 14 and two side covers 15, 16, which are arranged on axial side surfaces of the drive member 13 and secured by screws 12 thereto. The output element 14 is designed in the form of an impeller and has a substantially cylindrically designed hub member 17, extending from the outer cylindrical surface area wings 18 in the radial direction outwards.
Starting from an outer peripheral wall 19 of the drive element 13, projections 20 extend radially inwards. The drive element 13 is mounted by means of radially inner circumferential walls of the projections 20 relative to the output element 14 rotatably mounted on this.

Das Antriebselement 13 ist mit einem Riemenrad 21 versehen, über das mittels eines nicht dargestellten Riementriebs Drehmoment von der Kurbelwelle 2 auf das Antriebselement 13 übertragen werden kann. Das Abtriebselement 14 ist mittels einer Zentralschraube 22 drehfest mit der Nockenwelle 6, 7 verbunden.The drive element 13 is provided with a belt pulley 21, via which torque can be transmitted from the crankshaft 2 to the drive element 13 by means of a belt drive (not shown). The output member 14 is rotatably connected by means of a central screw 22 with the camshaft 6, 7.

Innerhalb der Vorrichtung 11 sind zwischen jeweils zwei in Umfangsrichtung benachbarten Vorsprüngen 20 Druckräume 23 ausgebildet. Jeder der Druckräume 23 wird in Umfangsrichtung von benachbarten Vorsprünge 20, in axialer Richtung von den Seitendeckeln 15, 16, radial nach innen von dem Nabenelement 17 und radial nach außen von der Umfangswand 19 begrenzt. In jeden der Druckräume 23 ragt ein Flügel 18, wobei die Flügel 18 sowohl an den Seitendeckeln 15, 16, als auch an der Umfangswand 19 anliegen. Jeder Flügel 18 teilt somit den jeweiligen Druckraum 23 in zwei gegeneinander wirkende Druckkammern 24, 25.
Das Abtriebselement 14 ist in einem definierten Winkelbreich drehbar zu dem Antriebselement 13 angeordnet. Der Winkelbereich wird in einer Drehrichtung des Abtriebselements 14 dadurch begrenzt, dass jeder der Flügel 18 an einem Frühanschlag 26 zum Anliegen kommt. Analog wird der Winkelbereich in der anderen Drehrichtung dadurch begrenzt, dass jeder der Flügel 18 an einem Spätanschlag 27 zum Anliegen kommt. Durch Druckbeaufschlagung einer Gruppe von Druckkammern 24, 25 und Druckentlastung der anderen Gruppe kann die Phasenlage des Antriebselements 13 zum Abtriebselement 14 (und damit die Phasenlage der Nockenwelle 6, 7 zur Kurbelwelle 2) variiert werden. Durch Druckbeaufschlagung beider Gruppen von Druckkammern 24, 25 kann die Phasenlage konstant gehalten werden.Within the device 11 20 pressure chambers 23 are formed between each two circumferentially adjacent projections. Each of the pressure spaces 23 is circumferentially bounded by adjacent projections 20, axially of the side covers 15, 16, radially inwardly of the hub member 17, and radially outward of the peripheral wall 19. In each of the pressure chambers 23 protrudes a wing 18, wherein the wings 18 bear against both the side covers 15, 16, and on the peripheral wall 19. Each wing 18 thus divides the respective pressure chamber 23 into two counteracting pressure chambers 24, 25th
The output element 14 is arranged rotatably in a defined Winkelbreich to the drive element 13. The angular range is limited in a direction of rotation of the output element 14 in that each of the vanes 18 abuts an early stop 26. Similarly, the angular range in the other direction of rotation is limited by the fact that each of the wings 18 comes to rest on a late stop 27. By pressurizing a group of pressure chambers 24, 25 and pressure relief of the other group, the phase position of the drive element 13 to the output element 14 (and thus the phase angle of the camshaft 6, 7 to the crankshaft 2) can be varied. By pressurizing both groups of pressure chambers 24, 25, the phase position can be kept constant.

Die Nockenwelle 6, 7 weist eine zentrale Druckmittelleitung 28 und mehrere achsparallele Druckmittelleitungen 29 auf, die sich in axialer Richtung erstrecken. Die Druckmittelleitungen 28, 29 kommunizieren über Ringnuten 30a, b, die an einer Außenmantelfläche der Nockenwelle 6, 7 ausgebildet sind, mit einem nicht dargestellten Steuerventil. Die achsparallelen Druckmittelleitungen 29 kommunizieren über radiale Bohrungen 39 mit einer ersten Gruppe von Druckkammern 24.
Die zentrale Druckmittelleitung 28 erstreckt sich durch die Zentralschraube 22 hindurch zu der der Nockenwelle 6, 7 abgewandten Seite des Abtriebselements 14 und mündet in einen abgeschlossenen Raum 31, der von einem Verschlußstopfen 32 abgedichtet wird. Die Figuren 4 und 5 zeigen eine an dem Antriebselement 13 anliegende Seitenfläche bzw. eine Rückseite des ersten Seitendeckels 15. Der erste Seitendeckel 15 weist einen scheibenförmigen Abschnitt 33 mit einer zentralen Öffnung 34 auf und besteht aus einem Stahlblech. An dem scheibenförmigen Abschnitt 33 sind auf der dem Abtriebselement 14 abgewandten Seitenfläche mehrere Ausbuchtungen 35a-c ausgebildet (Figur 5). Eine erste Ausbuchtung 35a erstreckt sich ringförmig um die zentrale Öffnung 34. Darüber hinaus sind fünf zweite Ausbuchtungen 35b vorgesehen, die rippenförmig ausgebildet sind und sich ausgehend von der ersten Ausbuchtung 35a radial nach außen erstrecken. Eine dritte Ausbuchtung 35c schließt sich im Bereich einer der zweiten Ausbuchtungen 35b an die erste Ausbuchtung 35a an und überdeckt einen Teilbereich des scheibenförmigen Abschnitts 33 zwischen zwei der zweiten Ausbuchtungen 35b. Durch die Ausbuchtungen 35a-c wird die Oberfläche des ersten Seitendeckels 15 vergrößert, so dass die Kühlung der Vorrichtung 11 verbessert wird. Darüber hinaus erzeugen die Ausbuchtungen 35a-c während des Betriebs der Brennkraftmaschine 1 Luftverwirbelungen im Bereich des ersten Seitendeckels 15, wodurch dessen Kühlung weiter verbessert wird. Insgesamt führt dies zu einer geringeren thermischen Belastung des ersten Seitendeckels 15 und zu einer effektiveren Kühlung des in der Vorrichtung 11 vorhandenen Druckmittels, in der Regel Motoröl der Brennkraftmaschine 1.
Gleichzeitig erhöhen die Ausbuchtungen 35a-c die Steifigkeit des ersten Seitendeckels 15, wodurch die Leckage sinkt oder der erste Seitendeckel 15 dünnwandiger ausgebildet werden kann.The camshaft 6, 7 has a central pressure medium line 28 and a plurality of axially parallel pressure medium lines 29, which extend in the axial direction. The pressure medium lines 28, 29 communicate via annular grooves 30a, b, which are formed on an outer circumferential surface of the camshaft 6, 7, with a control valve, not shown. The axially parallel pressure medium lines 29 communicate via radial bores 39 with a first group of pressure chambers 24.
The central pressure medium line 28 extends through the central screw 22 to the side of the output element 14 facing away from the camshaft 6, 7 and opens into a closed space 31, which is sealed by a plug 32. The FIGS. 4 and 5 show a voltage applied to the drive member 13 side surface and a back of the first side cover 15. The first side cover 15 has a disc-shaped portion 33 with a central opening 34 and consists of a steel sheet. On the disc-shaped section 33, a plurality of recesses 35a-c are formed on the side surface facing away from the output element 14 ( FIG. 5 ). A first protrusion 35a extends annularly around the central opening 34. In addition, five second protrusions 35b are provided which are rib-shaped and extend radially outward from the first protrusion 35a. A third bulge 35c adjoins the first bulge 35a in the area of one of the second bulges 35b and covers a portion of the disc-shaped section 33 between two of the second bulges 35b. By the bulges 35a-c, the surface of the first side cover 15 is increased, so that the cooling of the device 11 is improved. In addition, during operation of the internal combustion engine 1, the bulges 35a-c generate air turbulences in the region of the first side cover 15, thereby further improving its cooling. Overall, this leads to a lower thermal load on the first side cover 15 and to a more effective cooling of the pressure medium present in the device 11, usually engine oil of the internal combustion engine 1.
At the same time, the protrusions 35a-c increase the rigidity of the first side cover 15, whereby the leakage decreases or the first side cover 15 can be made thinner walled.

Im Bereich der Ausbuchtungen 35a-c sind an der dem Abtriebselement 14 zugewandten Seitenfläche des scheibenförmigen Abschnitts 33 korrespondierende Vertiefungen 36a-c ausgebildet (Figur 4). Die erste Vertiefung 36a ist in Form eines Ringkanals ausgebildet, und kommuniziert über den Raum 31 mit der zentralen Druckmittelleitung 28. Die zweiten Vertiefungen 36b sind in Form von sich radial erstreckenden Nuten ausgebildet, die in die erste Vertiefung 36a münden und mit einer zweiten Gruppe von Druckkammern 25 kommunizieren.
Während des Betriebs der Brennkraftmaschine 1 wird über eine nicht dargestellte Druckmittelpumpe Druckmittel zu dem nicht dargestellten Steuerventil gefördert. Wird von der Motorsteuerung eine Phasenverstellung in Richtung früher Steuerzeiten angefordert, so gelangt Druckmittel von dem nicht dargestellten Steuerventil über die Ringnut 30a, die achsparallelen Druckmittelleitungen 29 und die radialen Bohrungen 39 zu den ersten Druckkammern 24. Gleichzeitig wird Druckmittel aus den zweiten Druckkammern 25 über die zweiten Vertiefungen 36b, die erste Vertiefung 36a, den Raum 31, die zentrale Druckmittelleitung 28 und die Ringnut 30b zu dem Steuerventil abgeführt und von dort in einen Tank der Brennkraftmaschine 1 ausgestoßen. Somit werden die Flügel 18 in Richtung der Frühanschläge 26 gedrängt und die Steuerzeiten in Richtung früh verstellt. Wird von der Motorsteuerung eine Phasenverstellung in Richtung später Steuerzeiten angefordert, so gelangt Druckmittel von dem nicht dargestellten Steuerventil über die Ringnut 30b, die zentrale Druckmittelleitung 28, den Raum 31, die erste Vertiefung 36a und die zweiten Vertiefungen 36b in die zweiten Druckkammern 25. Gleichzeitig wird Druckmittel aus den ersten Druckkammern 24 über die radialen Bohrungen 39, die achsparallelen Druckmittelleitungen 29 und die Ringnut 30a zu dem Steuerventil abgeführt und von dort in einen Tank der Brennkraftmaschine 1 ausgestoßen. Somit werden die Flügel 18 in Richtung der Spätanschläge 27 gedrängt und die Steuerzeiten in Richtung spät verstellt.
Die Druckmittelzufuhr zu bzw. die Druckmittelabfuhr von den zweiten Druckkammern 25 erfolgt somit über die ersten und zweiten Vertiefungen 36a, b, die an dem scheibenförmigen Abschnitt 33 des ersten Seitendeckels 15 ausgebildet sind. Die sonst üblichen radialen Bohrungen innerhalb des Abtriebselements 14, die mittels spanender Nachbearbeitungsschritte in einen Rohling eingebracht werden müssen, können entfallen, wodurch dessen Herstellungsaufwand signifikant verringert wird.In the area of the bulges 35a-c, corresponding recesses 36a-c are formed on the side surface of the disk-shaped section 33 facing the output element 14 (FIG. FIG. 4 ). The first recess 36a is formed in the form of an annular channel and communicates with the central pressure medium line 28 via the space 31. The second recesses 36b are in the form of radially extending grooves which open into the first recess 36a and are connected to a second group of Pressure chambers 25 communicate.
During operation of the internal combustion engine 1 pressure medium is conveyed to the control valve, not shown, via a pressure medium pump, not shown. If a phase adjustment in the direction of early control times requested by the engine control, then pressure medium from the control valve, not shown via the annular groove 30a, the paraxial pressure medium lines 29 and the radial bores 39 to the first pressure chambers 24. At the same pressure medium from the second pressure chambers 25 via the second recesses 36 b, the first recess 36 a, the space 31, the central pressure medium line 28 and the annular groove 30 b discharged to the control valve and discharged from there into a tank of the internal combustion engine 1. Thus, the wings 18 are urged in the direction of the early stops 26 and adjusted the timing in the direction early. If a phase adjustment in the direction of later control times requested by the engine control, pressure medium from the control valve, not shown via the annular groove 30b, the central pressure medium line 28, the space 31, the first recess 36a and the second recesses 36b in the second pressure chambers 25th Simultaneously Pressure medium is discharged from the first pressure chambers 24 via the radial bores 39, the axis-parallel pressure medium lines 29 and the annular groove 30a to the control valve and ejected from there into a tank of the internal combustion engine 1. Thus, the wings 18 are urged in the direction of the late stops 27 and adjusted the timing in the late direction.
The pressure medium supply to or the pressure medium discharge from the second pressure chambers 25 thus takes place via the first and second recesses 36 a, b, which are formed on the disk-shaped portion 33 of the first side cover 15. The otherwise usual radial bores within the output element 14, which must be introduced by means of machining Nachbearbeitungsschritte in a blank, can be omitted, whereby its manufacturing cost is significantly reduced.

Die Vorrichtung 11 weist des Weiteren einen Verrieglungsmechanismus auf, mittels dem eine lösbare mechanische Verbindung zwischen dem Abtriebselement 14 und dem Antriebselement 13 hergestellt werden kann. Zu diesem Zweck weist das Abtriebselement 14 eine Aufnahme 37 auf, in der ein axial verschiebbares Verriegelungselement 38 aufgenommen ist. Das Verriegelungselement 38 wird mittels einer Druckfeder mit einer Kraft in Richtung des scheibenförmigen Abschnitts 33 beaufschlagt. Die dritte Vertiefung 36c ist mit Übermaß zu dem Verriegelungselement 38 gefertigt und nimmt ein Anschlagelement 40 auf. Das Anschlagelement 38 und die dritte Vertiefung 36c begrenzen eine Kulisse, in die das Verriegelungselement 38 eingreifen kann, wenn dieses der Kulisse in axialer Richtung gegenübersteht. Somit wird die mechanische Kopplung zwischen dem Abtriebselement 14 und dem Antriebselement 13 hergestellt. Soll die Kopplung gelöst werden, wird der Kulisse über die erste Vertiefung 36a Druckmittel zugeführt, das das Verriegelungselement 38 in die Aufnahme 37 zurückdrängt.
Das Anschlagelement 40 weist auf einer dem ersten Seitendeckel 15 zugewandten Seitenfläche zwei Nuten 41, 42 auf. Die erste Nut 41 verbindet die erste Vertiefung 36a mit der zweiten Vertiefung 36b, die sich an das Anschlagselement 40 anschließt, so dass die Druckmittelversorgung dieser zweiten Vertiefung 36b und damit der korrespondierenden Druckkammer 25 über die erste Nut erfolgt. Die zweite Nut 42 verbindet die erste Nut 41 mit der dritten Vertiefung 36c und stellt somit die Druckmittelversorgung der Kulisse, zum Lösen der mechanischen Verbindung zwischen dem Abtriebselement 13 und dem Antriebselement 14, sicher. Die Nuten 41, 42 können alternativ oder zusätzlich in der dritten Vertiefung 36c im Bereich des Anschlagselements 40 ausgebildet sein.The device 11 further comprises a locking mechanism, by means of which a releasable mechanical connection between the driven element 14 and the drive element 13 can be produced. For this purpose, the driven element 14 has a receptacle 37, in which an axially displaceable locking element 38 is accommodated. The locking element 38 is acted upon by means of a compression spring with a force in the direction of the disk-shaped portion 33. The third recess 36 c is made with excess to the locking element 38 and receives a stop element 40. The stop element 38 and the third recess 36c delimit a slide into which the locking element 38 can engage when it faces the slide in the axial direction. Thus, the mechanical coupling between the output member 14 and the drive member 13 is produced. If the coupling is to be released, the backdrop is fed via the first recess 36a pressure medium, which pushes the locking member 38 into the receptacle 37.
The stop element 40 has two grooves 41, 42 on a side surface facing the first side cover 15. The first groove 41 connects the first recess 36a with the second recess 36b, which adjoins the stop element 40, so that the pressure medium supply of this second recess 36b and thus of the corresponding pressure chamber 25 via the first groove. The second groove 42 connects the first groove 41 with the third recess 36c and thus provides the pressure medium supply of the gate, for releasing the mechanical connection between the output element 13 and the drive element 14, safe. The grooves 41, 42 may alternatively or additionally be formed in the third recess 36c in the region of the stop element 40.

Wird der erste Seitendeckel 15 mittels eines spanlosen Umformverfahrens oder eines Metall- oder Kunststoffspritzgussverfahrens hergestellt, so können die Ausbuchtungen 35a-c und die korrespondierenden Vertiefungen 36a-c kostenneutral gefertigt werden.If the first side cover 15 is produced by means of a non-cutting shaping method or a metal or plastic injection molding method, the bulges 35a-c and the corresponding recesses 36a-c can be produced cost-neutral.

Bezugszeichenreference numeral

11
BrennkraftmaschineInternal combustion engine
22
Kurbelwellecrankshaft
33
Kolbenpiston
44
Zylindercylinder
55
Zugmitteltriebtraction drive
66
Einlassnockenwelleintake camshaft
77
Auslassnockenwelleexhaust
88th
Nockencam
99
EinlassgaswechselventilInlet gas exchange valve
1010
AuslassgaswechselventilAuslassgaswechselventil
1111
Vorrichtungcontraption
1212
Schraubescrew
1313
Antriebselementdriving element
1414
Abtriebselementoutput element
1515
Seitendeckelside cover
1616
Seitendeckelside cover
1717
Nabenelementhub element
1818
Flügelwing
1919
Umfangswandperipheral wall
2020
Vorsprunghead Start
2121
Riemenradpulley
2222
Zentralschraubecentral screw
2323
Druckraumpressure chamber
2424
erste Druckkammerfirst pressure chamber
2525
zweite Druckkammersecond pressure chamber
2626
Frühanschlagearly stop
2727
Spätanschlaglate stop
2828
zentrale Druckmittelleitungcentral pressure medium line
2929
achsparallele Druckmittelleitungaxis-parallel pressure medium line
30ab30 ab
Ringnuteannular groove
3131
Raumroom
3232
Verschlußstopfenplugs
3333
scheibenförmiger Abschnittdisc-shaped section
3434
Öffnungopening
35abc35 abc
Ausbuchtungenbulges
36abc36abc
Vertiefungdeepening
3737
Aufnahmeadmission
3838
Verriegelungselementlocking element
3939
radiale Bohrungradial bore
4040
Anschlagelementstop element
4141
erste Nutfirst groove
4242
zweite Nutsecond groove

Claims (5)

  1. Apparatus (11) for variably setting the control times of gas exchange valves (9, 10) of an internal combustion engine (1) having
    - a drive element (13) which can be brought into a drive connection with a crankshaft (2) of the internal combustion engine (1),
    - an output element (14) which can be brought into a drive connection with a camshaft (6, 7) of the internal combustion engine (1) and is arranged pivotably with respect to the drive element (13),
    - and at least one side cover (15) which is arranged on an axial side face of the output element (14) or of the drive element (13) and is connected fixedly to the drive element (13) or the output element (14) so as to rotate with it and has a disc-shaped section (33),
    - at least one pressure space (23) being provided within the apparatus (11), and it being possible for a phase position between the drive element (13) and the output element (14) to be set variably by feeding in pressure medium or discharging pressure medium, characterized in that
    - the disc-shaped section (33) has at least one bulge (35a-c) on the side face which faces away from the drive element (13), which bulge (35a-c) delimits a depression (36a-c) on that side of the disc-shaped section (33) which faces the output element (13), the depression (36a-c) being adapted to the shape of the bulge (35a-c) and serving to guide pressure medium within the apparatus (11).
  2. Apparatus (11) according to Claim 1, characterized in that the depression (36a-c) communicates with the pressure space (23).
  3. Apparatus (11) according to Claim 1, characterized in that at least one pressure-medium line (28) is provided, by means of which pressure medium can be fed to the apparatus (11) or can be discharged from the latter, the depression (36a-c) communicating with the pressure-medium line (28).
  4. Apparatus (11) according to Claim 1, characterized in that the depression (36c) at least partially forms a slotted guide, into which a locking element (38) can engage which is received in a receptacle (37) of the drive element (13) or of the output element (14), the slotted guide communicating with a pressure-medium line (28) or a pressure space (23).
  5. Apparatus (11) according to Claim 1, characterized in that the disc-shaped section (33) is configured as a sheet-metal part, and the bulge (35a-c) and the depression (36a-c) are produced by means of a chipless forming process.
EP11151488A 2010-02-26 2011-01-20 Device for variable valve timing on a combustion engine Not-in-force EP2362074B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010009392A DE102010009392A1 (en) 2010-02-26 2010-02-26 Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine

Publications (2)

Publication Number Publication Date
EP2362074A1 EP2362074A1 (en) 2011-08-31
EP2362074B1 true EP2362074B1 (en) 2013-03-20

Family

ID=43982170

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11151488A Not-in-force EP2362074B1 (en) 2010-02-26 2011-01-20 Device for variable valve timing on a combustion engine

Country Status (2)

Country Link
EP (1) EP2362074B1 (en)
DE (1) DE102010009392A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013210495B4 (en) * 2013-06-06 2020-06-18 Schaeffler Technologies AG & Co. KG Camshaft adjuster
CN107208505B (en) * 2015-02-20 2019-11-12 舍弗勒技术股份两合公司 Camshaft phase modifier
DE102016217968A1 (en) 2016-09-20 2018-03-22 Schaeffler Technologies AG & Co. KG Centering connection of a trigger wheel with a rotor in a phaser

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19808619A1 (en) * 1998-02-28 1999-09-02 Schaeffler Waelzlager Ohg Locking device for a device for changing the control times of gas exchange valves of an internal combustion engine, in particular for a vane cell adjustment device
DE10038607B4 (en) 2000-08-08 2007-07-12 Schaeffler Kg Device for changing the timing of gas exchange valves of an internal combustion engine, in particular hydraulic camshaft adjusting device in rotary piston type
DE102004026865A1 (en) 2004-06-02 2006-05-04 Ina-Schaeffler Kg Device for changing the timing of an internal combustion engine
US7305949B2 (en) * 2005-08-18 2007-12-11 Delphi Technologies, Inc. Stamped target wheel for a camshaft phaser

Also Published As

Publication number Publication date
DE102010009392A1 (en) 2011-09-01
EP2362074A1 (en) 2011-08-31

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