WO2015051796A1 - Dispositif de déphasage d'arbre à cames - Google Patents

Dispositif de déphasage d'arbre à cames Download PDF

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Publication number
WO2015051796A1
WO2015051796A1 PCT/DE2014/200534 DE2014200534W WO2015051796A1 WO 2015051796 A1 WO2015051796 A1 WO 2015051796A1 DE 2014200534 W DE2014200534 W DE 2014200534W WO 2015051796 A1 WO2015051796 A1 WO 2015051796A1
Authority
WO
WIPO (PCT)
Prior art keywords
lubricant
adjusting
camshaft
end wall
rotation
Prior art date
Application number
PCT/DE2014/200534
Other languages
German (de)
English (en)
Inventor
Mike Kohrs
Jens Schäfer
Marco HILDEBRAND
Original Assignee
Schaeffler Technologies AG & 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 & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2015051796A1 publication Critical patent/WO2015051796A1/fr

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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
    • F01L1/352—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 bevel or epicyclic gear
    • 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
    • F01L1/352—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 bevel or epicyclic gear
    • F01L2001/3522—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 bevel or epicyclic gear with electromagnetic brake
    • 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
    • F01L2810/02—Lubrication
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors

Definitions

  • the invention relates to a Nockenwelleriverstellvoroplasty with the features of the preamble de »claim 1.
  • Camshaft Vervei vorrfchtache serve for relative adjustment of the Win- keteleüung between the crankshaft and the camshaft of an internal combustion engine.
  • Nockenweilverstelier usually have a Arrestnebsteil which is coupled to the crankshaft, for example via a chain or a belt.
  • an output member which is usually rotatably coupled to the camshaft and a Verstelweile, which makes it possible to adjust a Winketotellung the output member relative to the drive member.
  • the drive shaft, the adjusting shaft and the output shaft are operatively connected to each other in a gearbox, resulting in mechanical friction in the gearbox due to bearings and mutual interference.
  • a lubricant circuit of a camshaft adjuster which probably forms the next state of the art, a lubricant circuit of a camshaft adjuster.
  • a lubricant is supplied to the cam shifter 30 via the camshaft and redirected via radially outward exhaust ports.
  • a flow element in a flow passage. which acts as a throttle or orifice to adjust the lubricant flow.
  • the invention has for its object to provide a Nockenwellenverstellvorrich- device, which has an improved lubricant management. This object is achieved by a Nockenwellenverstellvonvorungung with the features of claim 1. Preferred or advantageous embodiments of the invention will become apparent from the dependent claims, the following description and the attached drawings.
  • a NocfcerwellenverstelrvoiTtehtung is proposed, which is in particular designed for an engine, in particular for an internal combustion engine, a vehicle.
  • the camshaft adjusting device comprises a camshaft, wherein the camshaft for controlling valves of the engine is formed.
  • the Nockenwellenverstellvorrlchtung has an adjusting. wherein the adjusting gear particularly preferably designed as a three-shaft gear.
  • the adjusting gear comprises an input shaft, an output shaft and an adjusting shaft.
  • the input shaft can be coupled to the crankshaft of the engine, for example via a chain or a belt.
  • the output shaft is preferably rotatably coupled to the camshaft or coupled.
  • the input shaft forms a drive part and the output shaft forms a driven part.
  • the adjusting shaft can be coupled or coupled to an actuator.
  • the actuator may be housed or co-rotating with respect to the motor.
  • the actuator may, for example, be realized as a motor, in particular an electric motor, or as a brake.
  • the camshaft adjusting device comprises the actuator.
  • the adjusting mechanism is designed to adjust an angular position of the camshaft.
  • the adjusting mechanism is designed to change the angular position of the camshaft relative to the angular position of a crankshaft of the engine.
  • the adjusting mechanism is designed to adjust the angular position between the input shaft and the output width.
  • the adjusting mechanism forms a transmission interior. wherein in the transmission interior, the input shaft, the output shaft and the adjusting shaft are operatively connected to each other.
  • the adjusting mechanism is designed as a summation gear, wherein particularly preferably a rotational movement of the Verstellwelte is added to the rotational movement of the input shaft and in this way the angular position is adjusted.
  • the camshaft adjusting device in particular the adjusting gear, has a lubricant supply for supplying the gearbox interior with a lubricant.
  • the lubricant is formed as an oil, in particular as a transmission oil.
  • the lubricant supply is designed as a continuous supply, so that the transmission interior steadily supplied lubricant and discharged therefrom.
  • the lubrication supply includes a lubricant supply, which has one or more outlet openings in an end wall of the interior of the transmission which is open towards the interior of the transmission.
  • the lubricant is guided from the lubricant supply into the interior of the gearbox via the outlet openings.
  • the end wall is aligned axially with respect to the axis of rotation.
  • the front wall forms a lubricating metal surface for guidance of the lubricant from the outlet ports due to centrifugal forces in the radial direction with respect to the axis of rotation.
  • the lubricant base surface extends in the radial direction, starting from the outlet openings, preferably up to a radially outer boundary.
  • the lubricant base surface terminates at an end limit, such as a hollow cylindrical surface.
  • the end wall on the Schmiemrilttelleitflache has additional structures for distribution and / or Verwirbe- treatment, in particular vaporizing the lubricant.
  • the additional structures are designed in particular as elevations or depressions in the end wall on the Schmie rmrtteltert Design. It is a consideration of the invention that the lubricant entering through the outlet openings in the gearbox interior is guided substantially along the Schmierstofelleit Chemistry to the radial outer region or the radially outer boundary of the Schmierstoffleit Structure and vorzuuhrt in this way at friction-relevant areas in the adjusting.
  • the swirling of the lubricant comprises a lifting of the lubricant from the Schmierstoffelleit Structure.
  • the lifting off of the lubricant from the lubricant base not only takes place earlier in the radial outer or end region of the lubricant base surface, but in the radial direction, in order to achieve a distributed or homogeneous supply of lubricant.
  • the advantage of the invention can be seen in particular in the fact that the lubricant management in the adjusting mechanism is significantly reduced by a comparatively small and cost-effective structural change of the end wall.
  • the end wall in the region of the lubricant base surface is formed as an active fluidic component which lifts the lubricant in the axial direction from the end wall.
  • the Zueatz Quiltung of the invention which are arranged concentrically and / or coaxially to the axis of rotation in the direction of rotation extend The ring structures may be interrupted depending on the Ausgestartung of the invention in circulation direction or continuously formed.
  • the structural structures are formed, in particular, by height differences in the radial direction, so that a profile with a height profile is formed in the radial direction. Any increase in the course of the height profile can lead to a swirling and thus lift-off of lubricant, so that each ring structure supports the distribution and the swirling of the lubricant.
  • the additional structures comprise sector structures which extend in the radial direction to the axis of rotation.
  • the sector structures may also be interrupted or formed in a continuous manner.
  • the sector structures divide the lubricant surface area into sectors, in particular in circular sectors.
  • the lubricant is distributed more evenly in the circumferential direction by the sector structures, and on the other hand, the sector structures form a height profile in the direction of rotation, so that upon rotation of the end wall with the lubricant base surface and the sector structures, the lubricant can be fluidized at each elevation and thus lifted off the lubricant surface ,
  • the ring structures and / or the sector structures z. B as waves. Grooves, open channels, grooves, grooves and / or webs are formed.
  • the lubricant base surface comprises at least three ring structures in order to achieve a sufficient distribution and / or turbulence.
  • the Schmierstoffleit S at least two, preferably at least four sector structures comprises, which are particularly «preferably evenly distributed in the circumferential direction to counteract an imbalance in the end wall.
  • the additional structures may also comprise surface pattern structures, wherein the surface pattern structures are formed, for example, as corrugations, knobs and / or honeycombs. These surface pattern structures also form, with each elevation, a possibility for distributing and / or swirling the lubricating oil by lifting off the lubricating oil at the elevation
  • a hybrid of ring structures, sector structures and / or surface pattern structures is provided.
  • annular structures running in the direction of rotation are cut through by radially extending sector structures.
  • the ring structures can be designed as shafts in these developments, for example, or the sector structures as grooves or channels.
  • partial surfaces or the entire lubricant surface are additionally provided with surface pattern structures.
  • the Schmieremitelleitflache may be formed as a radial plane surface which is aligned perpendicular to the axis of rotation.
  • the basic shape of the Schmierstoflegit Structure is designed as a Konusmantetftache, which extends around the axis of rotation, wherein the T chterform the Konus lateral surface, the distribution of the lubricant on the Schmierstoffleit Structure is further improved.
  • the additional structures establish a height offset in the axial direction to the axis of rotation relative to the two alternative basic basic forms of Schmierstoffleitfleche, the height offset has at least 0.5 millimeters, preferably at least 1 millimeter.
  • each of the sector structures and / or each of the ring structures forms such a height offset.
  • the additional structures are formed as coarse structures, which allow an effective lifting of the lubricant from the Schmierstoffelleitflache.
  • the additional structures form cut-off edges for the lubricant in order to achieve the turbulence, in particular the lift-off, in particular the nebulization of the lubricant.
  • the tear-off edges may be rounded off in some embodiments, wherein blocking of the lubricant in the radial direction is already for In the event that a stronger lift-off of the lubricant is desired.
  • the tear-off edges or portions thereof are formed as a sharp edge without Kantenrundung.
  • the lubricant supply comprises a lubricant outlet for removing the lubricant from the interior of the transmission, wherein the lubricant outlet is preferably formed radially on the outside of the transmission interior. The removal of lubricant ensures that, for example, interfering particles or other impurities in the lubricant do not permanently deposit in the interior of the transmission, but are removed from the radially outer bottom of the transmission interior via the lubricant discharge from the interior of the transmission, in particular flushed out.
  • the lubricant discharge can be realized as one or more outlet openings which extend in the radial direction and / or one or more outlet openings which extend in axial directions can each be realized as openings from the interior of the transmission.
  • the adjusting mechanism has a plurality of outlet openings as lubricant outlets, which are preferably distributed regularly in the circumferential direction about the axis of rotation.
  • an intermediate angle between the outlet openings of the lubricant outlet is less than 60 degrees, in particular less than 50 degrees granted. Due to the distribution in the direction of rotation, it is achieved that when the variable speed gear is at a standstill Lubricant can run off automatically through the lubricant removal.
  • this has the advantage that after a longer standstill of the variable speed gear no uncooled and thus tough or sticky lubricant remains in the adjusting gear and / or that the lubricant does not accumulate in an angular segment of the variable gear and in this way an imbalance at a restart of the Verstellgetriebes generated.
  • the lubricant supply is dimensioned such that a volume flow QZ of the lubricant of the lubrication mitterzuschreibung preferably medium on average is less than or equal to a volume flow QA of the lubricant discharge, so that QA ⁇ QZ gil In this way it is ensured that during operation of the Nockerrwellenverstellvorrichlung the lubricant in the transmission interior does not jam. With another dimensioning, excess lubricant would flow out unused during lubricant removal, resulting in unnecessary hydraulic losses. On the other hand, the moving mass of the variable speed is increased by the jamming lubricant, which is also disadvantageous.
  • the preferred Voiumenstromlie can be achieved by the fact that the total area of the openings of the lubricant discharge from the transmission interior larger, preferably more than twice as large as the total area of the outlet openings of the lubricant supply lines are designed. In this case, it is preferably assumed that the total areas are in each case the volume flow-determining size of the lubricant supply or the lubricant removal.
  • the lubricant supply in particular the Outlet openings, a radius RZ and the Schmierstoffab Adjust «be assigned in radius RA with respect to the axis of rotation.
  • RZ ⁇ RA.
  • a common radius is used, which can be calculated, for example, according to the following formula.
  • R is a moderate radius, ie RZ bz RA
  • the adjusting gear is designed as a wave gear, wherein the wave gear has a bearing and a deformable steel bushing with external teeth, wherein the steel bushing is arranged on a non-circular, in particular elliptical generator portion of the Versteltwelle.
  • the input shaft and the output shaft each have internal teeth that mesh with the external teeth.
  • the one or more outlet ports of the lubricant supply are disposed in the output shaft, with the end wall forming part of the output shaft and facing the lubricant base surface on the bearing and / or steel sleeve bulkhead the output shaft is arranged.
  • the bearing is designed as a rolling bearing having a rolling body space, wherein the rolling body space is open in the direction of the end wall and thus in the direction of the Schmierstoffleit- surface. orzugswelse the rolling bearing comprises a cage for rolling elements in the rolling bearing, wherein the cage particularly preferably has only one side ring, which is arranged on the side facing away from the end wall of the rolling elements.
  • the Wälz stressesraum is open in the direction of Schmierstoffleit Structure.
  • the lubricant entering the outlet openings in the transmission interior is deflected radially outward to a larger radius.
  • the distribution of the lubricant on the Schmierstofelleitflä- it is swirled or atomized by the relative speed depending on the design of the additional structures, so that also adjacent functional surfaces are supplied with the lubricant.
  • FIG. 1 is a schematic overview of a cam adjusting device as an embodiment of the invention
  • FIG. 2 is a sectional view of the variable speed transmission of the camshaft closure device in FIG. 1, FIG. 3a. b is a three-dimensional representation and a Schnrttdarstel- ment of the end wall in the Nockenwellenverste lvorraum in Figure 2;
  • the camshaft adjuster 1 includes a camshaft 2 having a plurality of cams 3 configured to actuate valves of the engine.
  • a crankshaft (not shown) of the engine.
  • an adjusting 5 is intercalated, which makes it possible, controlled an angular displacement of the camshaft 2 relative to the drive wheel 4 and thus implement relative to the crankshaft, not shown.
  • this is coupled to an electric motor 6 via a motor shaft 13, which is arranged stationary, that is to say non-rotating, relative to the adjusting mechanism 5
  • the Nockenwellenverstellvorrlchtung 1 has a Schmiermrttetments 7, which, starting from an oil sump or an oil tank 8 via an engine oil pump 9 and optionally an engine grille 10 via an oil rotary transformer (not shown) introduces gear oil as a lubricant in the camshaft 2.
  • the lubricant is conducted via a lubricant supply 11 from the camshaft 2 into the adjusting gear 5 in order to lubricate the adjusting gear 5 and is subsequently removed from the adjusting gear 5 via a lubricant removal 12, so that the lubricant supply 7 is designed as a lubricant circuit , FIG.
  • the adjusting mechanism 5 in a sectional view along an axis of rotation D, which is defined, for example, by the camshaft 2 or the motor shaft 13 (FIG. 1).
  • the adjusting 5 is called a so-called wave gear - also harmony - Drive - called - trained.
  • the wave gear 5 is also called Gleitkeilgetriebe, stress wave gear or English strain wave gear (SWG).
  • the adjusting 5 has an input shaft 14 which is rotatably coupled to the drive wheel 4 or is formed by this.
  • the adjusting mechanism 5 has an output shaft 15, which is non-rotatably connected to the camshaft 2.
  • An adjusting shaft 16, however, is rotatably connected to the motor shaft 13.
  • the adjusting shaft 16 has a non-circular, in particular elliptical in cross-section perpendicular to the rotation axis D generator section 17 on which a roller bearing 18 is arranged, the inner ring 19 of the roller bearing 18 rests on a lateral surface of the generator section 17 and the outer ring 20 a deformable, cylindrical steel bushing 21 carries external teeth.
  • the steel sleeve 21 is also referred to as flex spline.
  • the steel bush 21 is also elliptical in cross-section perpendicular to the axis of rotation D.
  • the input shaft 14 carries an internal toothing 22, which meshes with the external toothing of the steel bush 21.
  • the output shaft 15 carries an internal toothing 23, which also meshes with the external toothing of the steel bush 21.
  • the adjusting 5 forms a Gereteinnenraum 25, which is formed by the input shaft 14, on one side by a support member 26 and on the other side by a cover 27, wherein in the Gereteinnenraum 25 Gleitlagerab church 24, the roller bearing 18 and the Wech - El Angels Scheme 28 of the external toothing of the steel sleeve 21 and the internal teeth 22 and 23 are arranged.
  • the Schmie rmrtte -zuzenung 11 includes one or more axially aligned Auslasslassö réelleen 29, which are arranged on an end wall S of the output shaft Je 15 at a distance RZ to the rotation axis D.
  • the exhaust ports 29 are supplied with lubricant through passages in the camshaft 2.
  • lubricant exits from the exhaust ports 29 and is distributed in the transmission interior due to the rotation of the output shaft 1, with the end wall S in the radial range between RZ and RG a SchmierstofffUhrungs constitutional acts.
  • the lubricant is supplied into the transmission interior 25.
  • the lubricant outlet 12 is arranged as one or more radial passage openings 30 at a distance RA from the axis of rotation D at the radially outer edge of the transmission interior 25.
  • the volume flow QZ of the lubricant supply 1 is adjusted by the design of the outlet openings 29 and other fluidically relevant components such that it is on average always less than or equal to the volume flow QA of the lubricant discharge 12. In this way, it is ensured during operation that no lubricant accumulates in the transmission interior 25. This can be achieved in particular by the fact that the total area AA of all the passage openings 30 is larger than the total area AZ of all the outlet openings 29 is formed. For example, AA ⁇ 2, Ü * AZ
  • FIGS. 3a. b show, in a schematic three-dimensional representation or sectional illustration, the end face S of the output shaft 15 in a first embodiment.
  • Four of the outlet openings 20 and a central through-opening 35 can be seen in the end face S.
  • the lubricant exits through the outlet openings 29.
  • the end wall S of FIG. 3a carries ring structures whose height profile is shown in a somatic sectional view in FIG. 3b.
  • the arrows in FIG. 3b illustrate the path of the lubricant. Starting from the outlet opening 29, the lubricant is transported radially outward, being guided to a first shaft 33a after a first groove 32a. where it is partly dropped in the axial direction and partly transported radially further.
  • a second groove 32b After a second groove 32b, the lubricant is guided onto a second shaft 33b, where it is again partly thrown off and partly continued in the radial direction. After passing through a third groove 32c, the lubricant comes to a third shaft 33c, where the remaining lubricant is completely thrown off.
  • a pair of grooves 32 a, b. c and a shaft 33 a. b, c form one of the ring structures.
  • the end wall in the coarse form forms a radial plane surface RE. which is aligned perpendicular to the axis of rotation D
  • the height difference in the axial direction to the axis of rotation D between the bottom of the grooves 32a, b, c and the tips of the shafts 33a, b, c amounts to at least 0.5 millimeters, in particular at least 1 millimeter to achieve an effective release of the lubricant.
  • FIG. 4 a shows an end wall S with sector structures 34, wherein the sector structures 34 are configured as twelve grooves running in the radial direction which cake-like segments are planar Leave areas on the front wall S.
  • the sector structures 34 the lubricant is uniformly distributed in the circumferential direction
  • the sharp edges of the grooves form as well as the tips of the waves 33 a.
  • b, c Fracture edges for the lubricant and thus also serve to confuse the lubricant.
  • the depth of the grooves as sector structures is more than 1 mm.
  • Figure 4b shows a furtherconstrusbeispiei the end wall S, but in this example, the basic shape of the end wall S is formed as a conical surface, which deviates with a small cone angle of less than 10 degrees, in particular less than five degrees from a radial plane.
  • this represents three to five circumferential steps 35 as ring structures, which technically the same effect as the ring structures formed by the grooves 32 a. b, c and waves 33 a. b. c in the figure 3a implement.
  • FIG. 2 shows an arrow 36 which illustrates the transition of the lubricant from the end wall S with the lubricant base surface in the direction of the roller body space of the roller bearing 18.
  • the roller bearing 18 is opened in the direction of the end wall S and this is facing the roller bearing 18, so that an adequate supply of the rolling bearing 18 is achieved with lubricant.
  • the interaction region 28 is at the same time lubricated by the running of the rolling bearing 18 lubricant and by lubricant, which is dropped from the Schmierstoffieitflache, the sliding bearing portion 24 is supplied by draining lubricant.

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

Abstract

L'objectif de cette invention est de concevoir un dispositif de déphasage d'arbre à cames à gestion de lubrifiant améliorée. Cette invention concerne un dispositif de déphasage d'arbre à cames (1) comprenant un mécanisme de déphasage, ce mécanisme de déphasage (5) formant un espace interne de mécanisme (25), un arbre d'entrée (14), un arbre de sortie (15), et un arbre de déphasage (16) étant reliés de manière à coopérer dans cet espace interne de mécanisme (25), ledit mécanisme de déphasage (5) comprenant un système d'alimentation en lubrifiant (7) destiné à alimenter l'espace interne de mécanisme (25) en lubrifiant, ce système d'alimentation en lubrifiant (25) comportant une amenée de lubrifiant (11) qui comprend une ou plusieurs ouvertures de sortie (29) dans une paroi frontale (S) de l'espace interne de mécanisme (25), cette paroi frontale (S) présentant une surface de guidage de lubrifiant conçue pour guider le lubrifiant dans la direction radiale par rapport à l'axe de rotation (D) lors d'un mouvement de rotation de la paroi frontale (S), cette paroi frontale (S) présentant en outre sur ladite surface de guidage de lubrifiant des structures supplémentaires (32, 33, 34, 35) destinées à répartir et/ou faire tourbillonner le lubrifiant.
PCT/DE2014/200534 2013-10-08 2014-10-06 Dispositif de déphasage d'arbre à cames WO2015051796A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013220221.0A DE102013220221B4 (de) 2013-10-08 2013-10-08 Nockenwellenverstellvorrichtung
DE102013220221.0 2013-10-08

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WO2015051796A1 true WO2015051796A1 (fr) 2015-04-16

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Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11015692B2 (en) 2015-09-10 2021-05-25 Schaeffler Technologies AG & Co. KG Gearing having an elastic gear
US11226027B2 (en) 2015-09-10 2022-01-18 Schaeffler Technologies AG & Co. KG Gearing having an elastic gear
CN108474463A (zh) 2015-12-18 2018-08-31 舍弗勒技术股份两合公司 谐波传动机构的弹性齿轮
DE102016214917A1 (de) 2016-08-11 2018-02-15 Schaeffler Technologies AG & Co. KG Stirnradbüchseneinrichtung für ein Wellgetriebe sowie Wellenverstellanordnung mit dem Wellgetriebe
DE102017119611A1 (de) 2016-09-02 2018-03-08 Schaeffler Technologies AG & Co. KG Elektrischer Nockenwellenversteller und Vorrichtung zur Variation des Verdichtungsverhältnisses eines Hubkolbenmotors

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004035997A1 (fr) * 2002-10-17 2004-04-29 Ina-Schaeffler Kg Dispositif de reglage d'arbre a cames a entrainement electrique
US20050103299A1 (en) * 2002-07-11 2005-05-19 Ina-Schaeffler Kg Electrically driven camshaft
DE102004062067A1 (de) * 2004-12-23 2006-07-06 Schaeffler Kg Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102005018956A1 (de) 2005-04-23 2006-11-23 Schaeffler Kg Vorrichtung zur Nockenwellenverstellung einer Brennkraftmaschine
WO2007068576A1 (fr) * 2005-12-15 2007-06-21 Schaeffler Kg Dispositif de reglage d'un arbre a cames
DE102008043987A1 (de) * 2007-11-22 2009-05-28 Denso Corp., Kariya-shi Ventilzeitsteuergerät
DE102008010644A1 (de) * 2008-02-22 2009-08-27 Schaeffler Kg Nockenwellenversteller und Nockenwelle für eine Brennkraftmaschine

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10257706A1 (de) * 2002-07-11 2004-01-29 Ina-Schaeffler Kg Nockenwellenversteller mit elektrischem Antrieb
DE102010007668B4 (de) * 2009-02-12 2015-01-08 Ovalo Gmbh Getriebeelement für ein Spannungswellengetriebe, Nockenwellenversteller sowie Lenkkrafthilfe

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050103299A1 (en) * 2002-07-11 2005-05-19 Ina-Schaeffler Kg Electrically driven camshaft
WO2004035997A1 (fr) * 2002-10-17 2004-04-29 Ina-Schaeffler Kg Dispositif de reglage d'arbre a cames a entrainement electrique
DE102004062067A1 (de) * 2004-12-23 2006-07-06 Schaeffler Kg Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102005018956A1 (de) 2005-04-23 2006-11-23 Schaeffler Kg Vorrichtung zur Nockenwellenverstellung einer Brennkraftmaschine
WO2007068576A1 (fr) * 2005-12-15 2007-06-21 Schaeffler Kg Dispositif de reglage d'un arbre a cames
DE102005059860A1 (de) 2005-12-15 2007-07-05 Schaeffler Kg Nockenwellenversteller
DE102008043987A1 (de) * 2007-11-22 2009-05-28 Denso Corp., Kariya-shi Ventilzeitsteuergerät
DE102008010644A1 (de) * 2008-02-22 2009-08-27 Schaeffler Kg Nockenwellenversteller und Nockenwelle für eine Brennkraftmaschine

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