EP2539555A2 - Device for variably adjusting the control times of gas exchange valves of an internal combustion engine - Google Patents

Device for variably adjusting the control times of gas exchange valves of an internal combustion engine

Info

Publication number
EP2539555A2
EP2539555A2 EP11702165A EP11702165A EP2539555A2 EP 2539555 A2 EP2539555 A2 EP 2539555A2 EP 11702165 A EP11702165 A EP 11702165A EP 11702165 A EP11702165 A EP 11702165A EP 2539555 A2 EP2539555 A2 EP 2539555A2
Authority
EP
European Patent Office
Prior art keywords
recess
drive
internal combustion
combustion engine
shaped portion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP11702165A
Other languages
German (de)
French (fr)
Other versions
EP2539555B1 (en
Inventor
Jürgen Weber
Rainer Ottersbach
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2539555A2 publication Critical patent/EP2539555A2/en
Application granted granted Critical
Publication of EP2539555B1 publication Critical patent/EP2539555B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F01L2810/00—Arrangements solving specific problems in relation with valve gears
    • F01L2810/01—Cooling

Definitions

  • the invention relates to a device for variably adjusting the timing of gas exchange valves of an internal combustion engine with a drive element, which is drivably connectable to a crankshaft of the internal combustion engine, an output element, which can be brought into drive connection with a camshaft of the internal combustion engine and pivotable to the drive - Is arranged element, and at least one side cover disposed on an axial side surface of the output element or the drive member and rotatably connected to the drive element or the driven element and having a disc-shaped portion, wherein the disc-shaped portion is open to the input or the output member Sliding recess has, in which a stop element is arranged, and wherein the slide recess and the stop element form a backdrop into which a locking element can engage.
  • devices for variable adjustment of the timing of gas exchange valves are used to set 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 rotatable. firmly connected to a camshaft and may, 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 known for example from DE 10 2006 020 314 A1.
  • the device has a drive element, an output element and two side covers, wherein the drive element is in drive connection with a crankshaft and the output element is non-rotatably attached to a camshaft.
  • the output element is arranged pivotable in a defined angular interval 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.
  • bores are introduced into the output element, which extend in the radial direction starting from a central opening of the output element and open into the pressure chambers.
  • the device has a locking mechanism comprising a gate and a spring-loaded locking element.
  • the scenery is formed by a depression in the formed as a solid casting side cover and arranged in the recess, hardened insert element.
  • the recess In order to ensure a flush conclusion between the axial side surface of the side cover and the insert element, the recess must be reworked by machining.
  • the locking element is disposed axially displaceable within a receptacle which is formed within the driven element. If the slide and the locking element face each other in the axial direction, then the locking element can engage in the slide and the driven element can mechanically engage with the drive element. PelN. To release the locking of the backdrop pressure medium is supplied, which pushes back the locking element into the receptacle.
  • the insert element provides a stop surface for the locking element, so that only the insert element must have a high strength and the Sode- disgust can be made of less expensive materials.
  • the introduction of force from the insert element to the side cover succeeds over a two-dimensional contact, so that the load at this point is lower than in the line contact between the locking element and the insert element.
  • the present invention has for its object to provide a cost-effective and weight-optimized device. Summary of the invention
  • a bottom of the slot recess has a flat contact surface against which abuts the stop element, wherein the contact surface spaced from an edge of the slot recess and the depth of the contact surface is designed to be less than a maximum depth of the slot recess.
  • 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.
  • the output element is pivotable in a predetermined angular interval to the drive element.
  • the device may for example have a hydraulic actuator with at least one pressure chamber.
  • a side cover is provided which is rotatably connected to one of these components.
  • the side cover has a disk-shaped section, optionally with a central opening, which, for example, seals the pressure chambers in the axial direction.
  • the disc-shaped portion has a slot recess, in which a separately manufactured stop element is fixed.
  • the gate recess and the stop element form a backdrop, in which a locking element can engage, which is arranged in a pivotable to the side cover component of the device.
  • the output element is mechanically coupled to the drive element.
  • the drive torque of the crankshaft is transmitted via the locking element and the stop element from the drive element to the output element.
  • the introduction of force is on the one hand between the locking element and the stop element, usually via a line contact, and the stop element and an axially extending boundary wall of the slot recess over a flat contact.
  • the bottom of the slot recess has a flat contact surface, against which the stop element.
  • the contact surface is arranged at a distance from an edge of the slot recess, wherein the depth of the contact surface is made smaller than a maximum depth of the slot recess. It can be provided that the depth of the contact surface is formed less than a depth in the edge region of the slot recess.
  • the edge of the slot recess is to be understood as the area of the slot recess which adjoins the axially extending boundary walls of the groove depression. Under the depth of the axial distance between the output member and the drive element or facing side surface of the disc-shaped Section and the respective point of the bottom of the gate recess.
  • the abutment surface can be formed in the manufacturing process of the disc-shaped portion with high dimensional accuracy.
  • it may be provided to produce the disc-shaped section by means of a deep-drawing method, by means of which the slot recess and the contact surface are simultaneously formed.
  • the disc-shaped portion can be produced by means of a deep-drawing process, by means of which at the same time the slide recess is formed and subsequently form the contact surface by means of an embossing method.
  • the dimensions can be reliably realized during the manufacturing process, so that costly machining post-processing steps of the slide recess can be omitted and the stop element nevertheless terminates flush with the side surface of the first side cover.
  • the abutment surface which is at a distance from the edge of the slot recess and protrudes from its bottom, ensures that the stop element does not dive into the region of a radius formed in the transition area between the base and the axially extending boundary wall of the slot recess.
  • a frictional connection between the axially extending boundary wall and the stop element can be produced.
  • fabric or form-fitting connections In comparison to solid (cast) side covers, such a thin-walled sheet-metal lid or a plastic lid can be used, whereby the weight and the manufacturing costs are reduced.
  • the slide recess on the side facing away from the drive element of the disc-shaped portion forms a bulge.
  • the cooling of the side cover is improved, thus reducing the thermal load.
  • the stop element projects beyond the contact surface in the direction of the backdrop. The stop element is positioned by the system on the contact surface, wherein the contact surface does not extend into the contact region between the stop element and the locking element. This ensures that the locking element comes exclusively to the stop element to the plant and the power transmission does not take place directly between the side cover and the locking element.
  • the stop element may have at least one groove for guiding the pressure medium on the side surface resting against the contact surface, so that, for example, the slide or a pressure medium line to one of the pressure chambers can be supplied with pressure medium.
  • FIG 1 only very schematically an internal combustion engine
  • FIG. 2 shows a longitudinal section through an inventive device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
  • Figure 3 shows a cross section through the device according to the invention along the line III-III in Figure 2
  • Figure 4 is a plan view of a voltage applied to the drive element
  • FIG. 5 shows a perspective view of the outside of the side cover from FIG. 4,
  • FIG. 6 shows a longitudinal section through the side cover along the line VI-VI in FIG. 4,
  • Figure 7 is an illustration of the side cover according to Figure 4 without stop element.
  • FIG. 1 schematically shows 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, with a first and a second device 1 1 for 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 an inventive device 1 1 in L Lucass, Cross-section.
  • the device 1 1 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 element 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.
  • 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 vane 18 thus divides the respective pressure chamber 23 into two counteracting pressure chambers 24, 25.
  • 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.
  • 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.
  • phase position can be kept constant become.
  • 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.
  • FIG. 4 to 6 show the first side cover 15 in different views.
  • the first side cover 15 has a disk-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 bulge 35a extends annularly around the central opening 34.
  • five second bulges 35b are provided, which are rib-shaped and extend radially outward from the first bulge 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 increase the surface area of the first side cover 15 so that the cooling of the device 11 is improved. Moreover, during the operation of the internal combustion engine 1, the bulges 35a-c generate air turbulences in the area of the first side cover 15, as a result of which the cooling thereof is further improved. Overall, this leads to a lower thermal Loading of the first side cover 15 and more effective cooling of the present in the device 1 1 pressure fluid, 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 sealing of the pressure chambers 24, 25 can be improved or the first side cover 15 can be made thinner walled.
  • a corresponding first depressions 36a, corresponding second depressions 36b and a slide recess 36c are formed on the side surface of the disk-shaped portion 33 facing the driven element 14 (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.
  • 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.
  • pressure medium reaches the control unit (not shown). Erventil 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 25. At the same time pressure fluid from the first pressure chambers 24 via the radial bores 39, the paraxial pressure medium lines 29 and the Annular groove 30 a discharged 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 supply of pressure medium to or the removal of pressure medium from the second pressure chambers 25 thus takes place via the first and second depressions 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 1 1 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 sliding recess 36c is made with an excess of the locking element 38 and receives a stop element 40.
  • the stop element 40 and the guide recess 36c delimit a slotted link into which the locking element 38 can engage when the latter projects in the axial direction.
  • the mechanical coupling between the output member 14 and the drive member 13 is produced. If the coupling is to be released, the backdrop pressure medium is supplied, which pushes the locking member 38 into the receptacle 37.
  • the bottom of the cup-shaped slot recess 36c has a plane bearing surface 43 ( Figure 7).
  • the abutment surface 43 is at a distance from the edge of the slot recess 36c, that is, spaced from the axially extending boundary walls of the slot recess 36c.
  • the depth of the contact surface 43 that is, the axial distance from the side facing the driven element 14 side surface of the disk-shaped portion 33, designed to be smaller than the depth of the slide recess 36c in the adjacent edge regions, so that a circumferential groove 35 around the contact surface is formed.
  • the stop element 40 is non-positively connected to the slide recess 36 c, wherein an axial side surface of the stop element 40 bears against the contact surface 43.
  • the plateau-shaped contact surface 43 ensures that the stop member 40 does not engage in the edge region of the guide recess 36c, which typically has a radius.
  • the contact surface 43 advantageously projects beyond the radius region, so that the stop element 40 can be fitted flush with the side surface of the disk-shaped portion 33 without damaging the slide recess 36c, producing a frictional connection between the stopper member 40 and the axially extending walls of the slide recess 36c can be.
  • the stop element 40 projects beyond the contact surface 43 in the direction of the slide, so that the locking element 38 can only come into contact with the stop element 40 and not with the contact surface 43. If the locking element 38 engages in the gate, the introduction of force usually takes place via line contact. In the illustrated embodiment, this line contact between the locking member 38 and the stopper member 40 is made, which has a higher strength than the disc-shaped portion 33. From the stop member 40, the force is applied to the disc-shaped portion 33 via a flat contact, so that the load is lower at this point. Thus, the disk-shaped portion 33 can be made of a less expensive material and only the stopper member 40 is to be provided with a higher strength.
  • the stop element 40 projects beyond the abutment face 43 in the direction of the link ensures that the force of the locking element 38 is transmitted exclusively to the stop element 40.
  • the stop element 40 has two grooves 41, 42 on a side face facing the contact surface 43.
  • the first groove 41 connects the first recess 36a with the second recess 36b, which adjoins the slot recess 36c 40, so that the pressure medium supply of this second recess 36b and thus the corresponding pressure chamber 25 via the first groove 41.
  • the second groove 42 connects the first groove 41 with the gate and thus provides their pressure medium supply, for releasing the mechanical connection between the drive member 13 and the output member 14, safe.
  • the grooves 41, 42 may alternatively or additionally be formed in the slot depression 36c in the region of the stop element 40.
  • the bulges 35a-c and the corresponding recesses 36a-c can be manufactured cost-neutral.
  • the first side cover 15 can be produced, for example, by means of a deep-drawing method from a sheet-metal blank, wherein the guide recess 36c and the contact surface 43 can be formed simultaneously with this method.
  • the first side cover 15 including the slide recess 36c can be produced by a deep-drawing process and the contact surface 43 can be formed by embossing in a further work step.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

The invention relates to a device (11) for variably adjusting the control times of gas exchange valves (9, 10) of an internal combustion engine (1), comprising a drive element (13) that can be brought into driving connection with a crankshaft (2) of the internal combustion engine (1), an output element (14) which can be brought into driving connection with a camshaft (6, 7) of the internal combustion engine (1) and which is arranged in a pivotable manner with respect to the drive element (13), and at least one lateral cover (15) which lies on an axial lateral surface of the output element (14) or of the drive element (13), which is connected to the drive element (13) or to the output element (14) in a rotationally fixed manner and which has a disk-shaped portion (33). The disk-shaped portion (33) has a slotted recess (36c) which is open to the drive or output element (13, 14), said slotted recess being equipped with a stop element (40), and the slotted recess (36c) and the stop element (40) form a slot into which a locking element (38) can engage.

Description

Bezeichnung der Erfindung  Name of the invention
Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
Beschreibung Gebiet der Erfindung 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 Antriebs- element 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 der scheibenförmige Abschnitt eine zu dem An- oder dem Abtriebselement offene Kulissenvertiefung aufweist, in der ein Anschlagelement angeordnet ist, und wobei die Kulissenvertiefung und das Anschlagselement eine Kulisse ausbilden, in die ein Verriegelungselement eingreifen kann. Description Field of the Invention The invention relates to a device for variably adjusting the timing of gas exchange valves of an internal combustion engine with a drive element, which is drivably connectable to a crankshaft of the internal combustion engine, an output element, which can be brought into drive connection with a camshaft of the internal combustion engine and pivotable to the drive - Is arranged element, and at least one side cover disposed on an axial side surface of the output element or the drive member and rotatably connected to the drive element or the driven element and having a disc-shaped portion, wherein the disc-shaped portion is open to the input or the output member Sliding recess has, in which a stop element is arranged, and wherein the slide recess and the stop element form a backdrop into which a locking element can engage.
Hintergrund der Erfindung Background 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 Spätpo- sition, 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 dreh- fest 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 set 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 rotatable. firmly connected to a camshaft and may, 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 2006 020 314 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 Nockenwel- le 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 einge- bracht, die ausgehend von einer zentralen Öffnung des Abtriebselements in radialer Richtung verlaufen und in die Druckkammern münden. Such a device is known for example from DE 10 2006 020 314 A1. The device has a drive element, an output element and two side covers, wherein the drive element is in drive connection with a crankshaft and the output element is non-rotatably attached to a camshaft. The output element is arranged pivotable in a defined angular interval 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 medium to the pressure chambers, bores are introduced into the output element, which extend in the radial direction starting from a central opening of the output element and open into the pressure chambers.
Die Vorrichtung weist einen Verriegelungsmechanismus auf, der eine Kulisse und ein federbeaufschlagtes Verriegelungselement umfasst. Die Kulisse wird durch eine Vertiefung in dem als massives Gussteil ausgebildeten Seitendeckel und ein in der Vertiefung angeordnetes, gehärtetes Einlegeelement gebildet. Um einen bündigen Abschluss zwischen der axiale Seitenfläche des Seitendeckels und dem Einlegeelement zu gewährleisten muss die Vertiefung spanend nachbearbeitet werden. 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 kop- peln. Zum Lösen der Verriegelung wird der Kulisse Druckmittel zugeführt, das das Verriegelungselement in die Aufnahme zurückdrängt. Das Einlegeelement stellt eine Anschlagfläche für das Verriegelungselement bereit, so dass lediglich das Einlegelement eine hohe Festigkeit aufweisen muss und der Seitende- ekel aus kostengünstigeren Materialien gefertigt werden kann. Die Krafteinleitung von dem Einlegeelement auf den Seitendeckel erfolg über einen flächigen Kontakt, so dass die Belastung an dieser Stelle geringer ausfällt als bei dem Linienkontakt zwischen dem Verriegelungselement und dem Einlegeelement. Aufgabe der Erfindung The device has a locking mechanism comprising a gate and a spring-loaded locking element. The scenery is formed by a depression in the formed as a solid casting side cover and arranged in the recess, hardened insert element. In order to ensure a flush conclusion between the axial side surface of the side cover and the insert element, the recess must be reworked by machining. The locking element is disposed axially displaceable within a receptacle which is formed within the driven element. If the slide and the locking element face each other in the axial direction, then the locking element can engage in the slide and the driven element can mechanically engage with the drive element. PelN. To release the locking of the backdrop pressure medium is supplied, which pushes back the locking element into the receptacle. The insert element provides a stop surface for the locking element, so that only the insert element must have a high strength and the Seitende- disgust can be made of less expensive materials. The introduction of force from the insert element to the side cover succeeds over a two-dimensional contact, so that the load at this point is lower than in the line contact between the locking element and the insert element. Object of the invention
Der vorliegenden Erfindung liegt die Aufgabe zugrunde, eine kostengünstige und gewichtsoptimierte Vorrichtung vorzuschlagen. Zusammenfassung der Erfindung The present invention has for its object to provide a cost-effective and weight-optimized device. Summary of the invention
Die Aufgabe wird erfindungsgemäß dadurch gelöst, dass ein Boden der Kulissenvertiefung eine plane Anlagefläche aufweist, an der das Anschlagelement anliegt, wobei die Anlagefläche von einem Rand der Kulissenvertiefung beabstandet angeordnet und die Tiefe der Anlagefläche geringer als eine maximale Tiefe der Kulissenvertiefung ausgeführt ist. The object is achieved in that a bottom of the slot recess has a flat contact surface against which abuts the stop element, wherein the contact surface spaced from an edge of the slot recess and the depth of the contact surface is designed to be less than a maximum depth of the slot recess.
Die Vorrichtung weist ein Antriebselement und ein Abtriebselement auf, wobei das Antriebselement von einer Kurbelwelle der Brennkraftmaschine angetrie- ben wird und das Abtriebselement eine Nockenwelle der Brennkraftmaschine antreibt. Das Antriebselement kann beispielsweise mittels eines Zugmittel- o- der Zahnradtriebs in Antriebsverbindung mit der Kurbelwelle stehen. Das Abtriebselement kann beispielsweise drehfest mit der Nockenwelle verbunden sein. 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.
Das Abtriebselement ist in einem vorgegebenen Winkelintervall verschwenkbar zu dem Antriebselement. Zu diesem Zweck kann die Vorrichtung beispielsweise einen hydraulischen Stellantrieb mit zumindest einem Druckraum aufweisen. 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, gege- benenfalls mit einer zentralen Öffnung, auf, der beispielsweise die Druckräume in axialer Richtung abdichtet. Der scheibenförmige Abschnitt weist eine Kulissenvertiefung auf, in der ein separat gefertigtes Anschlagelement fixiert ist. Die Kulissenvertiefung und das Anschlagelement bilden eine Kulisse aus, in die ein Verriegelungselement eingreifen kann, das in einem zu dem Seitendeckel verschwenkbaren Bauteil der Vorrichtung angeordnet ist. Greift das Verriegelungselement in die Kulisse ein, ist das Abtriebselement mechanisch mit dem Antriebselement gekoppelt. Dabei wird das Antriebsmoment der Kurbelwelle über das Verriegelungselement und das Anschlagelement von dem Antriebselement auf das Abtriebselement übertragen. Die Kraftein leitung erfolgt einer- seits zwischen dem Verriegelungselement und dem Anschlagelement, in der Regel über einen Linienkontakt, und dem Anschlagelement und einer axial verlaufenden Begrenzungswand der Kulissenvertiefung über einen flächigen Kontakt. Somit sind lediglich das Verriegelungselement und das Anschlagselement zu härten, der Seitendeckel kann aus kostengünstigeren Materialien gefertigt werden, da die Belastung auf Grund des flächigen Kontaktes zwischen dem Anschlagelement und dem Seitendeckel geringer ist. The output element is pivotable in a predetermined angular interval to the drive element. For this purpose, the device may for example have a hydraulic actuator with at least one pressure chamber. 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 has a disk-shaped section, optionally with a central opening, which, for example, seals the pressure chambers in the axial direction. The disc-shaped portion has a slot recess, in which a separately manufactured stop element is fixed. The gate recess and the stop element form a backdrop, in which a locking element can engage, which is arranged in a pivotable to the side cover component of the device. Engages the locking element in the backdrop, the output element is mechanically coupled to the drive element. In this case, the drive torque of the crankshaft is transmitted via the locking element and the stop element from the drive element to the output element. The introduction of force is on the one hand between the locking element and the stop element, usually via a line contact, and the stop element and an axially extending boundary wall of the slot recess over a flat contact. Thus, only the locking element and the stop element to harden, the side cover can be made of less expensive materials, since the load is lower due to the surface contact between the stop element and the side cover.
Der Boden der Kulissenvertiefung weist eine plane Anlagefläche auf, an der das Anschlagelement anliegt. Die Anlagefläche ist beabstandet zu einem Rand der Kulissenvertiefung angeordnet, wobei die Tiefe der Anlagefläche geringer als eine maximale Tiefe der Kulissenvertiefung ausgeführt ist. Dabei kann vorgesehen sein, dass die Tiefe der Anlagefläche geringer als eine Tiefe im Randbereich der Kulissenvertiefung ausgebildet ist. Unter dem Rand der Kulissenvertiefung ist der sich an die axial erstreckenden Begrenzungswände der Ku- lissenvertiefung angrenzende Bereich der Kulissenvertiefung zu verstehen. Unter der Tiefe ist der axiale Abstand zwischen der dem Abtriebselement und oder dem Antriebselement zugewandten Seitenfläche des scheibenförmigen Abschnitts und dem jeweiligen Punkt des Bodens der Kulissenvertiefung zu verstehen. The bottom of the slot recess has a flat contact surface, against which the stop element. The contact surface is arranged at a distance from an edge of the slot recess, wherein the depth of the contact surface is made smaller than a maximum depth of the slot recess. It can be provided that the depth of the contact surface is formed less than a depth in the edge region of the slot recess. The edge of the slot recess is to be understood as the area of the slot recess which adjoins the axially extending boundary walls of the groove depression. Under the depth of the axial distance between the output member and the drive element or facing side surface of the disc-shaped Section and the respective point of the bottom of the gate recess.
Durch die plateauartig aus dem Boden der Kulissenvertiefung herausragende Anlagefläche ist sichergestellt, dass das Anschlagelement bündig mit der Seitenfläche des scheibenförmigen Abschnitts abschließt. Die Anlagefläche kann in dem Herstellungsprozess des scheibenförmigen Abschnitts mit hoher Maßgenauigkeit ausgebildet werden. Beispielsweise kann vorgesehen sein den scheibenförmigen Abschnitt mittels eines Tiefziehverfahrens herzustellen, mit- tels dem gleichzeitig die Kulissenvertiefung und die Anlagefläche ausgebildet sind. Alternativ kann der scheibenförmige Abschnitt mittels eines Tiefziehverfahrens hergestellt werden, mittels dem gleichzeitig die Kulissenvertiefung ausgebildet ist und die Anlagefläche anschließend mittels eines Prägeverfahrens auszubilden. Die Maße können während des Herstellungsverfahrens prozess- sicher realisiert werden, so dass aufwändige spanende Nachbearbeitungsschritte der Kulissenvertiefung entfallen können und das Anschlagelement trotzdem bündig mit der Seitenfläche des ersten Seitendeckels abschließt. Durch die zu dem Rand der Kulissenvertiefung beabstandete und aus deren Boden hervorstehende Anlagefläche ist gewährleistet, dass das Anschlagele- ment während dessen Montage nicht in den Bereich eines Radius eintaucht, der im Übergangsbereich zwischen dem Boden und der axial verlaufenden Begrenzungswand der Kulissenvertiefung ausgebildet ist. Somit ist eine exakte Positionierung des Anschlagelements in der Kulissenvertiefung möglich, wobei eine Schädigung der Wandung vermieden wird. Gleichzeitig kann eine kraft- schlüssige Verbindung zwischen der axial verlaufenden Begrenzungswand und dem Anschlagelement hergestellt werden. Ebenfalls denkbar sind stoff- oder formschlüssige Verbindungen. Im Vergleich zu massiv ausgebildeten (Guss-) Seitendeckeln kann so ein dünnwandiger Blechdeckel oder ein Kunststoffde- ckel Einsatz finden, wodurch das Gewicht und die Herstellungskosten reduziert werden. By the plateau-like protruding from the bottom of the slot recess contact surface ensures that the stop element is flush with the side surface of the disc-shaped portion. The abutment surface can be formed in the manufacturing process of the disc-shaped portion with high dimensional accuracy. For example, it may be provided to produce the disc-shaped section by means of a deep-drawing method, by means of which the slot recess and the contact surface are simultaneously formed. Alternatively, the disc-shaped portion can be produced by means of a deep-drawing process, by means of which at the same time the slide recess is formed and subsequently form the contact surface by means of an embossing method. The dimensions can be reliably realized during the manufacturing process, so that costly machining post-processing steps of the slide recess can be omitted and the stop element nevertheless terminates flush with the side surface of the first side cover. The abutment surface, which is at a distance from the edge of the slot recess and protrudes from its bottom, ensures that the stop element does not dive into the region of a radius formed in the transition area between the base and the axially extending boundary wall of the slot recess. Thus, an exact positioning of the stop element in the slot recess is possible, with damage to the wall is avoided. At the same time, a frictional connection between the axially extending boundary wall and the stop element can be produced. Also conceivable are fabric or form-fitting connections. In comparison to solid (cast) side covers, such a thin-walled sheet-metal lid or a plastic lid can be used, whereby the weight and the manufacturing costs are reduced.
In einer vorteilhaften Weiterbildung der Erfindung kann vorgesehen sein, dass die Kulissenvertiefung auf der dem Antriebselement abgewandten Seite des scheibenförmigen Abschnitts eine Ausbuchtung ausbildet. Durch die Erhöhung der (Außen-) Fläche wird die Kühlung des Seitendeckels verbessert und damit die thermische Belastung gesenkt. Vorteilhafterweise überragt das Anschlagselement die Anlagefläche in Richtung der Kulisse. Das Anschlagelement wird durch die Anlage an der Anlagefläche positioniert, wobei die Anlagefläche sich nicht bis in den Kontaktbereich zwischen dem Anschlagelement und dem Verriegelungselement erstreckt. Somit ist sichergestellt, dass das Verriegelungselement ausschließlich an dem Anschlagelement zur Anlage kommt und die Kraftübertragung nicht direkt zwischen dem Seitendeckel und dem Verriegelungselement erfolgt. In an advantageous embodiment of the invention can be provided that the slide recess on the side facing away from the drive element of the disc-shaped portion forms a bulge. By increasing the (outer) surface, the cooling of the side cover is improved, thus reducing the thermal load. Advantageously, the stop element projects beyond the contact surface in the direction of the backdrop. The stop element is positioned by the system on the contact surface, wherein the contact surface does not extend into the contact region between the stop element and the locking element. This ensures that the locking element comes exclusively to the stop element to the plant and the power transmission does not take place directly between the side cover and the locking element.
Das Anschlagselement kann an der an der Anlagefläche anliegenden Seitenfläche zumindest eine Nut zur Druckmittelführung aufweisen, so dass bei- spielsweise die Kulisse oder eine Druckmittelleitung zu einer der Druckräume mit Druckmittel versorgt werden können. The stop element may have at least one groove for guiding the pressure medium on the side surface resting against the contact surface, so that, for example, the slide or a pressure medium line to one of the pressure chambers can be supplied with pressure medium.
Kurze Beschreibung der Zeichnungen Brief 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: 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:
Figur 1 nur sehr schematisch eine Brennkraftmaschine Figure 1 only very schematically an internal combustion engine
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 anliegende2 shows a longitudinal section through an inventive device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine Figure 3 shows a cross section through the device according to the invention along the line III-III in Figure 2, Figure 4 is a plan view of a voltage applied to the drive element
Seitenfläche des Seitendeckels Figur 5 eine perspektivische Darstellung der Außenseite des Seitendeckels aus Figur 4, 5 shows a perspective view of the outside of the side cover from FIG. 4,
Figur 6 einen Längsschnitt durch den Seitendeckel entlang der Linie VI- VI in Figur 4, FIG. 6 shows a longitudinal section through the side cover along the line VI-VI in FIG. 4,
Figur 7 eine Darstellung des Seitendeckels gemäß Figur 4 ohne Anschlagelement. Figure 7 is an illustration of the side cover according to Figure 4 without stop element.
Ausführliche Beschreibung der Zeichnungen Detailed 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 1 1 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. 1 schematically shows 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, with a first and a second device 1 1 for 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 1 1 im Längsbzw. Querschnitt. Die Vorrichtung 1 1 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. Figures 2 and 3 show an inventive device 1 1 in Längsbzw. Cross-section. The device 1 1 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 element 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 1 1 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 Druck- kammern 24, 25. Within the device 1 1 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 vane 18 thus divides the respective pressure chamber 23 into two counteracting pressure chambers 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. 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.
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. 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 become.
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. 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.
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. 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.
Die Figuren 4 bis 6 zeigen den ersten Seitendeckels 15 in verschiedenen Ansichten. 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 rip- penförmig 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 Küh- lung der Vorrichtung 1 1 verbessert wird. Darüber hinaus erzeugen die Ausbuchtungen 35a-c während des Betriebs der Brennkraftmaschine 1 Luftverwir- belungen 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 1 1 vorhandenen Druckmittels, in der Regel Motoröl der Brennkraftmaschine 1 . Gleichzeitig erhöhen die Ausbuchtungen 35a-c die Steifigkeit des ersten Seitendeckels 15, wodurch die Abdichtung der Druckkammern 24, 25 verbessert oder der erste Seitendeckel 15 dünnwandiger ausgebildet werden kann. Figures 4 to 6 show the first side cover 15 in different views. The first side cover 15 has a disk-shaped portion 33 with a central opening 34 and consists of a steel sheet. On the disk-shaped portion 33, a plurality of recesses 35a-c are formed on the side surface facing away from the output element 14 (FIG. 5). A first bulge 35a extends annularly around the central opening 34. In addition, five second bulges 35b are provided, which are rib-shaped and extend radially outward from the first bulge 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 increase the surface area of the first side cover 15 so that the cooling of the device 11 is improved. Moreover, during the operation of the internal combustion engine 1, the bulges 35a-c generate air turbulences in the area of the first side cover 15, as a result of which the cooling thereof is further improved. Overall, this leads to a lower thermal Loading of the first side cover 15 and more effective cooling of the present in the device 1 1 pressure fluid, 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 sealing of the pressure chambers 24, 25 can be improved or the first side cover 15 can be made thinner walled.
Im Bereich der Ausbuchtungen 35a-c sind an der dem Abtriebselement 14 zu- gewandten Seitenfläche des scheibenförmigen Abschnitts 33 eine korrespondierende erste Vertiefungen 36a, korrespondierende zweite Vertiefungen 36b und eine Kulissenvertiefung 36c 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. In the region of the bulges 35a-c, a corresponding first depressions 36a, corresponding second depressions 36b and a slide recess 36c are formed on the side surface of the disk-shaped portion 33 facing the driven element 14 (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.
Während des Betriebs der Brennkraftmaschine 1 wird über eine nicht darge- stellte 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. 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.
Wird von der Motorsteuerung eine Phasenverstellung in Richtung später Steuerzeiten angefordert, so gelangt Druckmittel von dem nicht dargestellten Steu- erventil 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. If a phase adjustment in the direction of later control times is requested by the engine control unit, then pressure medium reaches the control unit (not shown). Erventil 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 25. At the same time pressure fluid from the first pressure chambers 24 via the radial bores 39, the paraxial pressure medium lines 29 and the Annular groove 30 a discharged 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 supply of pressure medium to or the removal of pressure medium from the second pressure chambers 25 thus takes place via the first and second depressions 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 1 1 weist des Weiteren einen Verrieglungsmechanismus auf, mittels dem eine lösbare mechanische Verbindung zwischen dem Abtriebsele- ment 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. The device 1 1 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.
Die Kulissenvertiefung 36c ist mit Übermaß zu dem Verriegelungselement 38 gefertigt und nimmt ein Anschlagelement 40 auf. Das Anschlagelement 40 und die Kulissenvertiefung 36c begrenzen eine Kulisse, in die das Verriegelungselement 38 eingreifen kann, wenn dieses der Kulisse in axialer Richtung gege- nübersteht. Somit wird die mechanische Kopplung zwischen dem Abtriebselement 14 und dem Antriebselement 13 hergestellt. Soll die Kopplung gelöst werden, wird der Kulisse Druckmittel zugeführt, das das Verriegelungselement 38 in die Aufnahme 37 zurückdrängt. Der Boden der topfförmigen Kulissenvertiefung 36c weist eine plane Anlagefläche 43 (Figur 7) auf. Die Anlagefläche 43 ist von dem Rand der Kulissenvertiefung 36c, d.h. von den axial verlaufenden Begrenzungswänden der Kulissen- Vertiefung 36c, beabstandet ausgeführt. Dabei ist die Tiefe der Anlagefläche 43, d.h. der axiale Abstand von der dem Abtriebselement 14 zugewandten Seitenfläche des scheibenförmigen Abschnitts 33, geringer ausgeführt als die Tiefe der Kulissenvertiefung 36c in den angrenzenden Randbereichen, so dass eine um die Anlagefläche 43 umlaufende nutförmige Einbuchtung ausgebildet ist. Das Anschlagelement 40 ist kraftschlüssig mit der Kulissenvertiefung 36c verbunden, wobei eine axiale Seitenfläche des Anschlagelements 40 an der Anlagefläche 43 anliegt. Durch die plateauförmige Anlagefläche 43 ist sichergestellt, dass das das Anschlagelement 40 nicht in den Randbereich der Kulissenvertiefung 36c eingreift, der typischerweise einen Radius aufweist. Dabei überragt die Anlagefläche 43 vorteilhafterweise den Radiusbereich, so dass das Anschlagelement 40 bündig zu der Seitenfläche des scheibenförmigen Abschnitts 33 gefügt werden kann, ohne die Kulissenvertiefung 36c zu beschädigen, wobei eine kraftschlüssige Verbindung zwischen dem Anschlagelement 40 und den axial verlaufenden Wänden der Kulissenvertiefung 36c hergestellt werden kann. The sliding recess 36c is made with an excess of the locking element 38 and receives a stop element 40. The stop element 40 and the guide recess 36c delimit a slotted link into which the locking element 38 can engage when the latter projects 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 pressure medium is supplied, which pushes the locking member 38 into the receptacle 37. The bottom of the cup-shaped slot recess 36c has a plane bearing surface 43 (Figure 7). The abutment surface 43 is at a distance from the edge of the slot recess 36c, that is, spaced from the axially extending boundary walls of the slot recess 36c. In this case, the depth of the contact surface 43, that is, the axial distance from the side facing the driven element 14 side surface of the disk-shaped portion 33, designed to be smaller than the depth of the slide recess 36c in the adjacent edge regions, so that a circumferential groove 35 around the contact surface is formed. The stop element 40 is non-positively connected to the slide recess 36 c, wherein an axial side surface of the stop element 40 bears against the contact surface 43. By the plateau-shaped contact surface 43 ensures that the stop member 40 does not engage in the edge region of the guide recess 36c, which typically has a radius. In this case, the contact surface 43 advantageously projects beyond the radius region, so that the stop element 40 can be fitted flush with the side surface of the disk-shaped portion 33 without damaging the slide recess 36c, producing a frictional connection between the stopper member 40 and the axially extending walls of the slide recess 36c can be.
Das Anschlagelement 40 überragt die Anlagefläche 43 in Richtung der Kulisse, so dass das Verriegelungselement 38 lediglich an dem Anschlagelement 40 und nicht an der Anlagefläche 43 zum Anliegen kommen kann. Greift das Ver- riegelungselement 38 in die Kulisse ein, so erfolgt die Krafteinleitung in der Regel über einen Linienkontakt. In der dargestellten Ausführungsform ist dieser Linienkontakt zwischen dem Verriegelungselement 38 und dem Anschlagelement 40 hergestellt, das eine höhere Festigkeit als der scheibenförmige Abschnitt 33 aufweist. Von dem Anschlagelement 40 erfolgt die Krafteinleitung auf den scheibenförmigen Abschnitt 33 über einen flächigen Kontakt, so dass die Belastung an dieser Stelle geringer ist. Somit kann der scheibenförmige Abschnitt 33 aus einem kostengünstigeren Material hergestellt werden und lediglich das Anschlagelement 40 ist mit einer höheren Festigkeit auszustatten. Da das Anschlagelement 40 die Anlagefläche 43 in Richtung der Kulisse überragt ist sichergestellt, dass die Kraft von dem Verriegelungselement 38 ausschließlich auf das Anschlagelement 40 übertragen wird. Das Anschlagelement 40 weist auf einer der Anlagefläche 43 zugewandten Seitenfläche zwei Nuten 41 , 42 auf. Die erste Nut 41 verbindet die erste Vertiefung 36a mit der zweiten Vertiefung 36b, die sich an die Kulissenvertiefung 36c 40 anschließt, so dass die Druckmittelversorgung dieser zweiten Vertiefung 36b und damit der korrespondierenden Druckkammer 25 über die erste Nut 41 erfolgt. Die zweite Nut 42 verbindet die erste Nut 41 mit der Kulisse und stellt somit deren Druckmittelversorgung, zum Lösen der mechanischen Verbindung zwischen dem Antriebselement 13 und dem Abtriebselement 14, sicher. Die Nuten 41 , 42 können alternativ oder zusätzlich in der Kulissenvertiefung 36c im Bereich des Anschlagselements 40 ausgebildet sein. The stop element 40 projects beyond the contact surface 43 in the direction of the slide, so that the locking element 38 can only come into contact with the stop element 40 and not with the contact surface 43. If the locking element 38 engages in the gate, the introduction of force usually takes place via line contact. In the illustrated embodiment, this line contact between the locking member 38 and the stopper member 40 is made, which has a higher strength than the disc-shaped portion 33. From the stop member 40, the force is applied to the disc-shaped portion 33 via a flat contact, so that the load is lower at this point. Thus, the disk-shaped portion 33 can be made of a less expensive material and only the stopper member 40 is to be provided with a higher strength. There the stop element 40 projects beyond the abutment face 43 in the direction of the link ensures that the force of the locking element 38 is transmitted exclusively to the stop element 40. The stop element 40 has two grooves 41, 42 on a side face facing the contact surface 43. The first groove 41 connects the first recess 36a with the second recess 36b, which adjoins the slot recess 36c 40, so that the pressure medium supply of this second recess 36b and thus the corresponding pressure chamber 25 via the first groove 41. The second groove 42 connects the first groove 41 with the gate and thus provides their pressure medium supply, for releasing the mechanical connection between the drive member 13 and the output member 14, safe. The grooves 41, 42 may alternatively or additionally be formed in the slot depression 36c in the region of the stop element 40.
Wird der erste Seitendeckel 15 mittels eines spanlosen Umformverfahrens o- der eines Metall- oder Kunststoffspritzgussverfahrens hergestellt, so können die Ausbuchtungen 35a-c und die korrespondierenden Vertiefungen 36a-c kostenneutral gefertigt werden. Der erste Seitendeckel 15 kann beispielsweise mittels eines Tiefziehverfahrens aus einem Blechrohling hergestellt werden, wobei mit diesem Verfahren gleichzeitig die Kulissenvertiefung 36c und die Anlagefläche 43 ausgebildet werden kann. Alternativ kann der erste Seitendeckel 15 inklusive der Kulissenvertiefung 36c durch einen Tiefziehprozess hergestellt werden und die Anlagefläche 43 mittels Prägen in einem weiteren Ar- beitsschritt ausgebildet werden. Bezugszeichen If the first side cover 15 is produced by means of a non-cutting shaping method or a metal or plastic injection molding method, then the bulges 35a-c and the corresponding recesses 36a-c can be manufactured cost-neutral. The first side cover 15 can be produced, for example, by means of a deep-drawing method from a sheet-metal blank, wherein the guide recess 36c and the contact surface 43 can be formed simultaneously with this method. Alternatively, the first side cover 15 including the slide recess 36c can be produced by a deep-drawing process and the contact surface 43 can be formed by embossing in a further work step. reference numeral
1 Brennkraftmaschine 1 internal combustion engine
2 Kurbelwelle  2 crankshaft
3 Kolben 3 pistons
4 Zylinder  4 cylinders
5 Zugmitteltrieb  5 traction drive
6 Einlassnockenwelle  6 intake camshaft
7 Auslassnockenwelle  7 exhaust camshaft
8 Nocken 8 cams
9 Einlassgaswechselventil  9 inlet gas exchange valve
10 Auslassgaswechselventil  10 outlet gas exchange valve
1 1 Vorrichtung  1 1 device
12 Schraube  12 screw
13 Antriebselement 13 drive element
14 Abtriebselement  14 output element
15 Seitendeckel  15 side covers
6 Seitendeckel  6 side covers
17 Nabenelement  17 hub element
18 Flügel 18 wings
19 Umfangswand  19 peripheral wall
20 Vorsprung  20 advantage
21 Riemenrad  21 pulley
22 Zentralschraube  22 central screw
23 Druckraum 23 pressure room
24 erste Druckkammer  24 first pressure chamber
25 zweite Druckkammer  25 second pressure chamber
26 Frühanschlag  26 early stop
27 Spätanschlag  27 Late stop
28 zentrale Druckmittelleitung 28 central pressure medium line
29 achsparallele Druckmittelleitung  29 axis-parallel pressure medium line
30ab Ringnut  30ab ring groove
31 Raum Verschlußstopfen scheibenförmiger Abschnitt31 room Stopper disc-shaped section
34 Öffnung 34 opening
35abc Ausbuchtungen  35abc bulges
36ab Vertiefung 36ab well
36c Kulissenvertiefung  36c backdrop recess
37 Aufnahme  37 recording
38 Verriegelungselement 38 locking element
39 radiale Bohrung 39 radial bore
40 Anschlagelement 40 stop element
41 erste Nut  41 first groove
42 zweite Nut  42 second groove
43 Anlagefläche  43 contact surface

Claims

Patentansprüche claims
1 . Vorrichtung (1 1 ) zur variablen Einstellung der Steuerzeiten von Gaswechselventilen (9, 10) einer Brennkraftmaschine (1 ) mit 1 . Device (1 1) for variably setting the control times of gas exchange valves (9, 10) of an internal combustion engine (1) with
- einem Antriebselement (13), das in Antriebsverbindung mit einer Kurbelwelle (2) der Brennkraftmaschine (1 ) bringbar ist, a drive element (13) which can be brought into drive connection with a crankshaft (2) of the internal combustion engine (1),
- einem Abtriebselement (14), das in Antriebsverbindung mit einer Nockenwelle (6, 7) der Brennkraftmaschine (1 ) bringbar und schwenkbar zu dem Antriebselement (13) angeordnet ist,  an output element (14) which is arranged in drive connection with a camshaft (6, 7) of the internal combustion engine (1) such that it can be brought and pivoted to the drive element (13),
- und mindestens einem Seitendeckel (15), der an einer axialen Seitenfläche des Abtriebselements (14) oder des Antriebselements (13) angeordnet und drehfest mit dem Antriebselement (13) oder dem Abtriebselement (14) verbunden ist und einen scheibenförmigen Abschnitt (33) aufweist, - And at least one side cover (15) disposed on an axial side surface of the output member (14) or the drive member (13) and rotatably connected to the drive element (13) or the output element (14) and a disc-shaped portion (33) .
- wobei der scheibenförmige Abschnitt (33) eine zu dem An- oder dem Ab- triebselement (13, 14) offene Kulissenvertiefung (36c) aufweist, in der ein - Wherein the disc-shaped portion (33) has a to the arrival or the Ab- drive member (13, 14) open slot recess (36c) in which a
Anschlagelement (40) angeordnet ist, und wobei die Kulissenvertiefung (36c) und das Anschlagselement (40) eine Kulisse ausbilden, in die ein Verriegelungselement (38) eingreifen kann, dadurch gekennzeichnet, dassStop element (40) is arranged, and wherein the sliding recess (36c) and the stop element (40) form a link in which a locking element (38) can engage, characterized in that
- ein Boden der Kulissenvertiefung (36c) eine plane Anlagefläche (43) auf- weist, an der das Anschlagelement (40) anliegt, wobei die Anlagefläche- A bottom of the slot recess (36c) has a planar contact surface (43) has, against which the stop element (40) is applied, wherein the contact surface
(43) von einem Rand der Kulissenvertiefung (36c) beabstandet angeordnet und die Tiefe der Anlagefläche (43) geringer als eine maximale Tiefe der Kulissenvertiefung (36c) ausgeführt ist. (43) spaced from one edge of the slot recess (36c) and the depth of the abutment surface (43) is less than a maximum depth of the slot recess (36c) is executed.
2. Vorrichtung (1 1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass die Tiefe der Anlagefläche (43) geringer als eine Tiefe im Randbereich der Kulissenvertiefung (36c) ausgebildet ist. 2. Device (1 1) according to claim 1, characterized in that the depth of the abutment surface (43) is less than a depth in the edge region of the slot recess (36 c) is formed.
3. Vorrichtung (1 1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass die Ku- lissenvertiefung (36c) auf der dem Antriebselement (14) abgewandten Seite des scheibenförmigen Abschnitts (33) eine Ausbuchtung (35c) ausbildet. Vorrichtung (1 1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass das Anschlagselement (40) kraftschlüssig mit der Kulissenvertiefung (36c) verbunden ist. 3. Device (1 1) according to claim 1, characterized in that the lisse recess (36c) on the drive element (14) facing away from the disk-shaped portion (33) forms a bulge (35c). Device (1 1) according to claim 1, characterized in that the stop element (40) is non-positively connected to the slide recess (36 c).
Vorrichtung (1 1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass das Anschlagselement (40) die Anlagefläche (43) in Richtung der Kulisse überragt. Device (1 1) according to claim 1, characterized in that the stop element (40) projects beyond the contact surface (43) in the direction of the slide.
Vorrichtung (1 1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass das Anschlagselement (40) an der an der Anlagefläche (43) anliegenden Seitenfläche zumindest eine Nut (41 , 42) zur Druckmittelführung aufweist. Device (1 1) according to claim 1, characterized in that the stop element (40) has at least one groove (41, 42) for guiding the pressure medium on the side surface lying against the contact surface (43).
Vorrichtung (1 1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass der scheibenförmige Abschnitt (33) mittels eines Tiefziehverfahrens hergestellt ist, mittels dem gleichzeitig die Kulissenvertiefung (36c) und die Anlagefläche (43) ausgebildet sind. Device (1 1) according to claim 1, characterized in that the disc-shaped portion (33) is produced by means of a deep-drawing process, by means of which simultaneously the slot recess (36c) and the abutment surface (43) are formed.
Vorrichtung (1 1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass der scheibenförmige Abschnitt (33) mittels eines Tiefziehverfahrens hergestellt ist, mittels dem gleichzeitig die Kulissenvertiefung (36c) ausgebildet ist und die Anlagefläche (43) anschließend mittels eines Prägeverfahrens ausgebildet wird. Device (1 1) according to claim 1, characterized in that the disc-shaped portion (33) is produced by means of a deep-drawing process, by means of which the slide recess (36 c) is formed simultaneously and the contact surface (43) is subsequently formed by means of a stamping process.
EP11702165.9A 2010-02-26 2011-01-25 Device for variably adjusting the control times of gas exchange valves of an internal combustion engine Active EP2539555B1 (en)

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DE201010009393 DE102010009393A1 (en) 2010-02-26 2010-02-26 Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
PCT/EP2011/050970 WO2011104054A2 (en) 2010-02-26 2011-01-25 Device for variably adjusting the control times of gas exchange valves of an internal combustion engine

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CN102782263A (en) 2012-11-14
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US8978607B2 (en) 2015-03-17
DE102010009393A1 (en) 2011-09-01
CN102782263B (en) 2016-01-20
WO2011104054A3 (en) 2011-10-20
US20130047943A1 (en) 2013-02-28

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