EP1718846B1 - Dispositif de reglage electrique d'arbre a cames - Google Patents

Dispositif de reglage electrique d'arbre a cames Download PDF

Info

Publication number
EP1718846B1
EP1718846B1 EP05701151A EP05701151A EP1718846B1 EP 1718846 B1 EP1718846 B1 EP 1718846B1 EP 05701151 A EP05701151 A EP 05701151A EP 05701151 A EP05701151 A EP 05701151A EP 1718846 B1 EP1718846 B1 EP 1718846B1
Authority
EP
European Patent Office
Prior art keywords
sleeve
ring
camshaft adjuster
ring gear
adjuster according
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.)
Revoked
Application number
EP05701151A
Other languages
German (de)
English (en)
Other versions
EP1718846A1 (fr
Inventor
Jens Schäfer
Martin Steigerwald
Jonathan Heywood
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=34853652&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1718846(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP1718846A1 publication Critical patent/EP1718846A1/fr
Application granted granted Critical
Publication of EP1718846B1 publication Critical patent/EP1718846B1/fr
Revoked legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • 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
    • F01L2001/3521—Harmonic drive of flexspline type
    • 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
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/04—Camshaft drives characterised by their transmission means the camshaft being driven by belts
    • 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
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/06—Camshaft drives characterised by their transmission means the camshaft being driven by gear wheels

Definitions

  • the invention relates to an electric camshaft adjuster for adjusting and fixing the phase position of a camshaft of an internal combustion engine with respect to the crankshaft, with a non-rotatably connected to the crankshaft drive wheel, a camshaft fixed output member, and a corrugated transmission with at least one ring gear Stirnradcruung, one of the two components rotatably with the drive wheel is connected and the other component is at least in a torque transmitting connection to the output part, wherein the spur gear is designed as a flexurally elastic sleeve and at least partially disposed within the first ring gear, with a driven by an electric adjusting motor via a transmission-fixed adjusting wave wave generator, the means for elliptical deformation of the flexurally elastic sleeve, whereby the sleeve is deformed such that between the ring gear and the sleeve at two opposite locations of the sleeve a mosmomentüb is made of the compound.
  • the low torque of the electric variable speed motor must be converted into the high torque required to adjust the camshaft. Serve this so-called three-shaft gear (summing).
  • the adjusting power is coupled by the electric adjusting motor via an adjusting shaft in one or the other direction in the three-shaft gear.
  • the three-shaft transmission must be inexpensive to produce, in order to keep the system costs for an electric camshaft adjuster with adjusting gear, adjusting motor and control electronics low.
  • Double-shaft transmissions, double and single eccentric gearboxes as well as harmonic drives are considered as three-shaft transmissions. In particular, the latter appear to be suitable to meet the above requirements.
  • Two versions of the wave gear are known, namely the wave gear in pot design and the sleeve design.
  • WO 95/00748 is a camshaft adjuster disclosed with a corrugated transmission in sleeve design.
  • this design no axial thrust occurs because the tilting forces in the toothing of the sleeve due to the floating support of the wave generator compensate and protect the wave generator from tilting and jamming.
  • the sleeve design requires relatively little axial space.
  • elaborate thin-ring bearings are also used for the wave generator in the above example.
  • the arrangement of the drive wheel, driven part and ring gears in the example above requires considerable space.
  • the invention is therefore an object of the invention to provide an electric camshaft adjuster with the least possible axial space and low construction costs, the adjustment is designed as a wave gear in sleeve design, weight optimized and inexpensive to manufacture.
  • the object is achieved in that the means for elliptical deformation of the flexible elastic sleeve two attached to the adjusting shaft, on two opposite Areas of the sleeve bearing journals are on each of which a roller bearing is arranged.
  • the modification of the components relates to the wave generator and the sleeve, while the integration relate to the arrangement of the drive wheel and the driven part and the first and second ring gear.
  • the telescoping drive wheel and driven part is made possible by the storage of the former on the second.
  • the bearing used for this purpose is a four-point bearing. At this point, but also deep groove ball bearings, cylindrical roller bearings or plain bearings are conceivable.
  • the one-piece design of the gears of the corrugated transmission with the drive wheel and / or driven part of the camshaft adjuster reduces the number of components and thus the installation costs.
  • the production costs of the components can be reduced by using non-cutting production techniques. In this case, non-cutting forming processes, applied to a steel sheet suitable blank, as well as punching package.
  • the gears of the gears can be realized with these techniques.
  • the sleeve is cup-shaped.
  • the flexurally elastic sleeve cooperates with its outer circumferential surface with the inner circumferential surface of a ring gear in such a way that a torque-transmitting connection is formed between these surfaces.
  • the torque-transmitting connection between the ring gear and the sleeve can be realized by engaging in an internal toothing of the ring gear outer toothing of the sleeve, wherein the number of teeth of the internal toothing of the ring gear deviates from the number of teeth of the external toothing of the sleeve.
  • the torque-transmitting connection between the ring gear and the sleeve is frictionally realized by the interaction of a smooth inner circumferential surface of the ring gear and a smooth outer surface of the sleeve. To improve the function is also provided to provide the coming into contact surfaces with friction linings.
  • the reduction of the wave gear we realized by the small number of teeth difference or the small difference of the radii of the ring gear and the sleeve.
  • the sleeve is connected directly to the camshaft via the bottom extending radially inward from an axial end of the sleeve.
  • the connection can be realized via a screw or positive-locking elements.
  • a second ring gear is arranged, the sleeve is at least partially disposed within the second ring gear and enters at two opposite points a torque transmitting connection with the second ring gear.
  • the sleeve in the axial direction at least partially and at least one ring gear are provided with a toothing.
  • the teeth mesh with each other in the areas of the two points of intersection of the ellipse circumference with the major axis of the ellipse, whereby a torque-transmitting connection is made.
  • the second spur ring pairing can be designed as Reibradcruung or also as a gear pair.
  • the electric variable motor is preferably designed as a bipolar brushless DC motor (BLDC motor) with rare-earth permanent magnets and cylinder-head fixed stator. But it is also conceivable, a DC motor with brushes or an asynchronous motor and a; Use electric motor with rotating stator.
  • BLDC motor bipolar brushless DC motor
  • a DC motor with brushes or an asynchronous motor and a Use electric motor with rotating stator.
  • the wave generator Since the wave generator is floatingly mounted in the toothing of the wave gear, it is necessary that the motor shaft of the BLDC motor and the adjusting shaft have a connection by a rotationally fixed, but radially movable or compliant coupling, which is designed for example as a polymer coupling.
  • teeth of the wave gear have a profile shift. This is necessary because the teeth of the sleeve and the teeth of the first and second ring gear must mesh with each other, both of which have a different number of teeth but the same, matching the sleeve inner diameter.
  • An advantageous variant of the wave gear according to the invention is characterized in that the translation stage is designed as a friction gear, which has smooth surfaces instead of the teeth of the ring gear and the associated portion of the sleeve. In this way, the consolidation of the teeth of the 1: 1 coupling stage are simplified and reduces the running noise and wear.
  • a fixing ring the outer diameter of which corresponds at least to the tooth tip diameter of the first ring gear, is pressed axially into the same and at its toothing.
  • the fixing ring serves for the axial securing of adjusting shaft, wave generator and sleeve.
  • the dynamics of the camshaft adjustment is increased by the fact that at least the adjusting shaft has recesses for the purpose of weight reduction and / or consists of light metal, plastic or a composite material.
  • at least one of, but possibly also all gear components for the purpose of weight reduction of light metal, plastic or a composite material is provided.
  • a corrugated ring with an elliptical outer circumference and an elliptically deformed rolling bearing mounted thereon are provided.
  • the corrugated gear with toothed spur gear is provided that the outer ring of the rolling bearing and the externally toothed sleeve are made in one piece, whereby the number of components and thus the installation costs can be reduced.
  • rolling bearings groove ball, roller or needle roller bearings come into question. But plain bearings are also conceivable.
  • the elliptical corrugated ring and the inner ring of the rolling bearing are made in one piece. If the elliptical surface of the wave generator serves as a running surface for the rolling elements, the inner ring of the standard rolling bearing is unnecessary. This saves another component of the wave gear.
  • a further embodiment of the invention provides for the use of two bearing journals mounted on the adjusting shaft and bearing against two opposite regions of the sleeve as a means for elliptical deformation of the bending-elastic sleeve instead of a solid or hollow shaft.
  • a rolling bearing is arranged on each journal.
  • the inner ring of the rolling bearing is supported on the bearing pin, while the sleeve is supported on the outer ring. If the adjusting shaft and the drive wheel rotate at different rotational speeds, then the outer ring of the roller bearing rolls on the inner lateral surface of the sleeve.
  • the bearing journals are mounted with an eccentric fastening means and rotatably mounted on the adjusting shaft and fixed thereto in any angle of rotation.
  • the two rolling bearings can be designed as ball bearings, preferably deep groove ball bearings, cylindrical roller or needle roller bearings. Due to the principle of the two standard bearings are not deformed during operation, so that they are not exposed to additional load. Compared to an elliptical wave generator, the sleeve is not supported on the entire circumference but only at the points of meshing.
  • FIG. 1 is a longitudinal section through a camshaft adjuster according to the invention shown.
  • This has a trained as a sprocket drive wheel 1, which is rotationally connected via a chain, not shown, with a crankshaft, not shown.
  • the drive wheel 1 it is also conceivable, of course, to design the drive wheel 1 as a toothed belt wheel or spur gear, which is driven by a toothed belt or a spur gear.
  • the drive wheel 1 and a first ring gear 2 are integrally formed, wherein the first ring gear 2 has a first internal toothing 3.
  • An output part 4, which is designed in one piece with a second ring gear 5, is rotationally connected to a camshaft, not shown.
  • the second ring gear 5 has a second internal toothing 6 and is adjacent in the axial direction and coaxial with the first Ring gear 2 arranged.
  • the drive wheel 1 is mounted together with the first ring gear 2 by means of a four-point bearing 7, which is arranged radially and axially within the drive wheel 1, via the second ring gear 5 and the output part 4 on the camshaft, not shown.
  • the four-point bearing can, as shown, be designed as a separate component with inner ring, rolling elements, cage and outer ring.
  • the WälzSystemterrorismbahnen are formed directly on the drive wheel 1 and the second ring gear 5, whereby the inner and the outer ring of the rolling bearing omitted and the number of components is reduced.
  • a stop ring 22 for example, by means of screws 23, rivets, welded joints or caulking attached.
  • This carries a flag 8, which engages in a corresponding ring-segment-shaped, the adjustment angle limiting recess 9 of the driven part 4.
  • the adjustment angle limiting recess 9 is introduced into the drive wheel 1, in which engages a rotatably connected to the output member 4 element.
  • An adjusting shaft 10 has a toothed coupling 24 for an electric adjusting motor, not shown.
  • Other couplings such as polymer clutches or magnetic clutches are conceivable that can compensate occurring between the transmission shaft and the electric motor shaft axial and radial offset.
  • the adjusting shaft 10 is connected to a corrugated ring 11, which has an elliptical outer contour 12.
  • a roller bearing 13 On this is a roller bearing 13, the inner ring 14 and outer ring 15 of the same take on the elliptical shape of the corrugated ring 11 when pressing.
  • preferably deep groove ball bearings and other rolling bearing designs are conceivable, such as cylindrical roller or needle roller bearings.
  • an elastic sleeve 18 is pressed with external teeth 28, wherein the sleeve 18 also takes on the elliptical shape during pressing.
  • the sleeve 18 can be secured by means of positive locking means against axial wandering on the rolling bearing 13. This can be realized for example by radially inwardly directed curls of the axial ends of the sleeve 18.
  • the wave generator 17 and the sleeve 18 are designed such that they can be arranged radially within the ring gears 2, 5. In this case, the wave generator 17 abuts the output part 4 in the axial direction.
  • a fixing ring 20 is pressed into the first ring gear 2 on the side remote from the stripping section 4, whose outer diameter corresponds to at least the Zahnfuß devismesser the first ring gear 2 and the same rests on the inner toothing 3 thereof.
  • the wave generator 17 and the sleeve 18 are now in the axial direction between the driven part 4 and the fixing ring 20.
  • the elliptically deformed sleeve 18 engages with its external teeth 28 in the areas of the two intersection points of the ellipse circumference with the main axis of the ellipse in the first and second internal teeth 3, 6 of the ring gears 2, 5 a.
  • each ring gear 2, 5 is thus in engagement with the external teeth 28 of the sleeve 18 in two areas. Due to the elliptical deformation of the sleeve 18 ensures that these areas are located at opposite locations with respect to the center of the respective ring gear 2, 5 at this.
  • FIG. 2 is the wave gear 19 with the sleeve 18 and the ring gears 2, 5 shown in a simplified side view. It can be clearly seen that the outer toothing 28 of the elliptically deformed sleeve 18 engages in two areas of the first and second internal toothing 3, 6 of the ring gears 2, 5.
  • One of the ring gears 2, 5 has the same number of teeth as the sleeve 18, the other ring gear 2, 5 has z. B. two more teeth.
  • Profile displacement makes it possible that the external teeth 28 of the elliptical sleeve 18 with both ring gears 2, 5 despite their different number of teeth at the same time engaged, and at two opposite points of the same.
  • the ring gear 2 or 5 with the same number of teeth as the sleeve 18 acts as a 1: 1 gear coupling, the ring gear 2 or 5 with the increased number of teeth as a translation stage.
  • Which of the two ring gears 2 or 5 the same and which has the larger number of teeth, depends on the direction in which the wave gear 19 is to adjust when the adjusting shaft 10 is stationary, ie, whether it should work as a plus or a minus gear. It is also conceivable that the numbers of teeth of all gears 3, 6 and 28 differ. In this way, the size of the profile displacement on a toothing 3, 6 and 28 are limited to a minimum.
  • the external toothing 28 of the sleeve 18 can be carried out as a split external toothing, with one part of the toothing engaging in the first internal toothing, 3 and the second part of the toothing engaging in the second internal toothing 6.
  • the two external teeth can be designed differently.
  • the number of teeth or tooth module should be mentioned here. In this way, the profile displacements can be reduced or different modules can be used for a better load capacity
  • the drive wheel 1, which is designed in one piece with the first ring gear 2, the output part 4, which is designed in one piece with the second ring gear 5 and the sleeve 18 are preferably produced in non-cutting shaping process.
  • the use of chip removal techniques reduces both the weight of the individual components and their production costs in mass production.
  • the individual components including the teeth 3, 6, 28 can be advantageously made of sheet steel in a chipless forming process. It is also conceivable to produce the components by stamped packetizing.
  • the wave gear 19 after the FIGS. 1 and 2 works in the following way: With one revolution of the adjusting shaft 10, the wave generator 17 also makes one revolution. In this case, the external toothing 28 of the elliptical sleeve 18 is simultaneously rolled on the internal teeth 3, 6 of the first and second ring gear 2, 5.
  • the output tooth of the sleeve 18 again engages in its initial tooth gap after one revolution of the adjusting shaft 10.
  • the position of the sleeve 18 relative to the first ring gear 2 has not changed and there is a 1: 1 gear coupling before.
  • the spur-Hohlradcruung which is responsible for the reduction is designed as Reibradcruung, while the other spur Hohlradcruung cooperates via gears and is preferably designed as a 1: 1 clutch.
  • the outer toothing 28 of the sleeve 18 extends in the axial direction only in the region in which, the sleeve 18 is within the other ring gear 2 or 5.
  • the other area is smooth and cooperates with the also smooth running inner surface of the corresponding ring gear 2 together.
  • Both the toothings 6, 28 of the first spur ring gear pairing and the smooth surfaces of the second spur ring gear pair act together due to the elliptically deformed sleeve 18 at two opposite areas.
  • Another embodiment of the invention provides only a spur gear pair. Conceivable torque transmission is again about teeth 2, 28 or friction.
  • the drive wheel 1 is formed integrally with the ring gear 2.
  • the sleeve 18 is cup-shaped, wherein the camshaft is mounted rotationally fixed at the bottom.
  • the geometry of the ellipse of the wave generator 17 may according to the FIGS. 3a, 3b, 3c be determined:
  • FIG. 3a an undeformed standard rolling bearing 13 is shown.
  • FIG. 4 is a longitudinal section through a further embodiment of a deep groove ball bearing designed roller bearing 13 'is shown, the outer ring: 15' carries the outer teeth 28 of the sleeve 18 and thus can take their place.
  • FIG. 5 shows a front view of the rolling bearing 13 'from FIG. 4 with the one-piece with the outer ring 15 'running external teeth 28th
  • FIG. 6 is a longitudinal section through a wave generator 17 'with an adjusting shaft 10' and an outer toothing 28 is shown.
  • the corrugated generator 17 ' has a corrugated ring 11' and a roller bearing 13 "designed as a cylindrical roller bearing
  • the cylindrical roller bearing consists of a plurality of cylindrical rollers 26 which are arranged between an inner ring 14 'and an outer ring 15" and for relative movements between the rolling bearing rings 14', 15
  • the inner ring 14 ' is embodied in one piece with the corrugated ring 11'
  • the cylindrical rollers 26 of the rolling bearing 13 "run directly on the elliptical outer contour 12 'of the correspondingly enlarged corrugated ring 11'.
  • the external toothing 28 is formed directly on the outer ring 15 "of the rolling bearing 13". As compared to the first embodiment, the cyclic deformation of the inner ring 14 'and the sleeve 18 is omitted, the power of the electric adjusting motor can be correspondingly lower.
  • FIG. 7 is a longitudinal section through a wave gear 19 ', a variant of the wave gear 19 of FIG. 1
  • an adjusting shaft 10 "instead of a corrugated ring has two axial bearing journals 29 with two standard roller bearings 13"'designed as deep groove ball bearings 29, while the sleeve 18 is supported on the outer rings 15 "'.
  • the bearing journals 29 are offset by 180 ° and arranged at the same distance from the axis 30 of the adjusting shaft 10". The distance is chosen so that the sleeve 18 in the same manner as by the corrugated ring 11 of FIG. 1 is deformed elliptical.
  • the inner rings 25 of the roller bearings 13 "'can be formed as eccentric inner rings 25. By installing the same with corresponding rotation angle, the backlash between the teeth of the sleeve 18 and the ring gears 2, 5 can be adjusted.

Landscapes

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

Claims (18)

  1. Dispositif électrique de réglage d'arbre à cames pour le réglage et la fixation de la position de phase d'un arbre à cames d'un moteur à combustion interne par rapport à son vilebrequin, comprenant
    - une roue d'entraînement (1) qui est connectée de manière solidaire en rotation au vilebrequin,
    - une partie de prise de force (4) fixée à l'arbre à cames et
    - une transmission harmonique
    - comprenant au moins une paire couronne-pignon droit,
    - l'un des deux composants étant connecté de manière solidaire en rotation à la roue d'entraînement (1) et l'autre composant étant au moins en liaison de transfert de couple par rapport à la partie de prise de force (4),
    - le pignon droit étant réalisé sous forme de manchon élastique en flexion (18) et
    - étant disposé au moins en partie à l'intérieur de la première couronne (2, 5),
    - comprenant un générateur d'ondes (17") entraîné par un moteur de réglage électrique par le biais d'un arbre de réglage fixé à la transmission (10", 10"'),
    - qui possède des moyens pour la déformation elliptique du manchon élastique en flexion (18),
    - de sorte que le manchon (18) soit déformé de telle sorte qu'entre la couronne (2, 5) et le manchon (18), en deux endroits opposés du manchon (18), une liaison de transfert de couple soit établie,
    caractérisé en ce que
    - les moyens pour la déformation elliptique du manchon élastique en flexion (18) sont deux tourillons (29) montés sur l'arbre de réglage (10", 10"'), s'appliquant contre deux zones opposées du manchon (18), sur desquelles est disposé à chaque fois un palier à roulement (13"').
  2. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce que le manchon (18) est réalisé en forme de pot.
  3. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce qu'une deuxième couronne (5) est disposée dans la direction axiale à côté de et coaxialement à la première couronne (2), le manchon (18) est disposé au moins en partie à l'intérieur de la deuxième couronne (5) et entre en liaison de transfert de couple avec la deuxième couronne (5) en deux endroits opposés.
  4. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce que la liaison de transfert de couple entre la couronne (2,5) et le manchon (18) est réalisée par une denture extérieure (28) du manchon (18) venant en prise dans une denture intérieure (3, 6) de la couronne (2, 5), et le nombre de dents de la denture intérieure (3, 6) de la couronne (2, 5) est différent du nombre de dents de la denture extérieure (28) du manchon (18).
  5. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce que la liaison de transfert de couple entre la couronne (2, 5) et le manchon (18) est réalisée par engagement par friction par coopération de la surface d'enveloppe intérieure de la couronne (2, 5) réalisée sous forme lisse et de la surface d'enveloppe extérieure du manchon (18) réalisée sous forme lisse.
  6. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce que le moteur de réglage électrique est réalisé de préférence sous forme de moteur à courant contenu sans balai, à commande bipolaire (moteur BLDC), avec un stator fixé à la culasse et avec de préférence un aimant terres rares.
  7. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce que l'arbre de moteur du moteur BLDC et l'arbre de réglage (10, 10', 10", 10"') présentent une liaison par accouplement fixée en rotation, mais mobile radialement ou flexible, qui est réalisée par exemple sous forme d'accouplement polymére (26).
  8. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce qu'une bague de butée (22) est fixée sur la roue d'entrainement (1), qui présente un fanion (8) qui vient en prise dans un évidement (9) correspondant de la partie de prise de force (4), en forme de segment annulaire, limitant l'angle de réglage.
  9. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce qu'une bague de fixation (20) dont le diamètre extérieur correspond au moins au diamètre de tête des dents de la première couronne (2), peut être pressée dans celle-ci.
  10. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce qu'au moins l'arbre de réglage (10, 10', 10", 10"'), aux fins de réduire le poids, présente des évidements et/ou se compose de métal léger, de plastique ou d'un matériau composite.
  11. Dispositif de réglage d'arbre à cames selon la revendication 4, caractérisé en ce qu'au moins l'un des composants de denture (3, 6, 28), aux fins de réduire le poids, se compose d'un métal léger, de plastique ou d'un matériau composite.
  12. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce que tous les composants ou des composants individuels, de préférence les composants de denture (3, 6, 28) de la transmission harmonique (19, 19'), sont fabriqués sans enlèvement de copeaux.
  13. Dispositif de réglage d'arbre à cames selon la revendication 4, caractérisé en ce que les composants de la transmission harmonique (19, 19') sont fabriqués sans enlèvement de copeaux et les dentures (3, 6, 28) sont subséquemment trempées ou nitrurées.
  14. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce que le moyen pour la déformation elliptique du manchon élastique en flexible (18) est une bague ondulée (11, 11') de périphérie extérieure elliptique (12) et un palier à roulement (13, 13', 13") monté sur celle-ci et déformé elliptiquement.
  15. Dispositif de réglage d'arbre à cames selon la revendication 4, caractérisé en ce que le moyen pour la déformation elliptique du manchon élastique en flexion (18) est une bague ondulée (11, 11') de périphérie extérieure elliptique (12) et un palier à roulement (13' 13") monté sur celle-ci et déformé elliptiquement, et la bague extérieure (15") du palier à roulement (13', 13") et le manchon à denture extérieure (18) sont réalisés d'une seule pièce.
  16. Dispositif de réglage d'arbre à cames selon la revendication 14, caractérisé en ce que la bague ondulée elliptique (11') et la bague intérieure (14') du palier à roulement (13") sont réalisées d'une seule pièce.
  17. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce que les tourillons de palier (29') sont montés avec un moyen de fixation excentrique de manière rotative sur l'arbre de réglage (10"') et peuvent être fixés dans une position d'angle de rotation quelconque.
  18. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce que les palmiers à roulement (13"') présentent des bagues intérieures (25) réalisées de manière excentrique, qui peuvent être pressées dans une position d'angle de rotation quelconque sur les tourillons (29).
EP05701151A 2004-02-25 2005-01-25 Dispositif de reglage electrique d'arbre a cames Revoked EP1718846B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004009128A DE102004009128A1 (de) 2004-02-25 2004-02-25 Elektrischer Nockenwellenversteller
PCT/EP2005/000672 WO2005080757A1 (fr) 2004-02-25 2005-01-25 Dispositif de reglage electrique d'arbre a cames

Publications (2)

Publication Number Publication Date
EP1718846A1 EP1718846A1 (fr) 2006-11-08
EP1718846B1 true EP1718846B1 (fr) 2013-03-13

Family

ID=34853652

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05701151A Revoked EP1718846B1 (fr) 2004-02-25 2005-01-25 Dispositif de reglage electrique d'arbre a cames

Country Status (6)

Country Link
US (1) US7673598B2 (fr)
EP (1) EP1718846B1 (fr)
JP (1) JP2007527968A (fr)
KR (1) KR20060129029A (fr)
DE (1) DE102004009128A1 (fr)
WO (1) WO2005080757A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016216667A1 (de) 2015-09-10 2017-03-16 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102016111546A1 (de) 2016-06-23 2017-12-28 Pierburg Gmbh Wellgetriebe für eine Verbrennungskraftmaschine
DE102019102264A1 (de) 2019-01-30 2020-07-30 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Montage eines Nockenwellenverstellers
DE102022109041A1 (de) 2022-04-13 2023-10-19 Bayerische Motoren Werke Aktiengesellschaft Verbrennungskraftmaschine für ein Kraftfahrzeug, insbesondere für einen Kraftwagen, sowie Kraftfahrzeug
DE112013007274B4 (de) 2013-07-25 2024-01-18 Harmonic Drive Systems Inc. Spannungswellengetriebe

Families Citing this family (116)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004038681B4 (de) * 2004-08-10 2017-06-01 Schaeffler Technologies AG & Co. KG Elektromotorischer Nockenwellenversteller
DE102005018956A1 (de) * 2005-04-23 2006-11-23 Schaeffler Kg Vorrichtung zur Nockenwellenverstellung einer Brennkraftmaschine
DE102005048570A1 (de) * 2005-10-10 2007-04-12 Ortloff-Technologie Gmbh Motorgetriebe mit Torquemotor und Spannungswellgetriebe
DE102006010649A1 (de) * 2006-03-06 2007-09-13 Ovalo Gmbh Vorrichtung zur Nockenwellenverstellung
US7421990B2 (en) * 2006-08-22 2008-09-09 Delphi Technologies, Inc. Harmonic drive camshaft phaser
EP2006501A1 (fr) * 2007-06-22 2008-12-24 Delphi Technologies, Inc. Appareil déphaseur à came variable
DE102007034091A1 (de) 2007-07-21 2009-01-22 Schaeffler Kg Wellgenerator für ein Wellgetriebe
DE102008010645A1 (de) 2008-02-22 2009-08-27 Schaeffler Kg Nockenwellenversteller und Nockenwelle für eine Brennkraftmaschine
DE102008010638B4 (de) 2008-02-22 2022-01-27 Schaeffler Technologies AG & Co. KG Elektromechanisches Nockenwellenverstellsystem und Verfahren zur Verstellung einer Nockenwelle mittels eines solchen Nockenwellenverstellsystems
DE102008010644A1 (de) 2008-02-22 2009-08-27 Schaeffler Kg Nockenwellenversteller und Nockenwelle für eine Brennkraftmaschine
DE102008019586A1 (de) 2008-04-18 2009-10-22 Schaeffler Kg Nockenwellenverstellvorrichtung
JP5064300B2 (ja) * 2008-05-28 2012-10-31 株式会社ハーモニック・ドライブ・システムズ 波動歯車式直動機構
DE102008039009A1 (de) 2008-08-21 2010-02-25 Schaeffler Kg Nockenwellenversteller
DE102008039007A1 (de) 2008-08-21 2010-02-25 Schaeffler Kg Verfahren zur Verstellung einer Kurbelwelle eines Verbrennungsmotors, Nockenwellenverstellsystem und Verbrennungsmotor mit verstellbarer Kurbelwelle
DE102008039008A1 (de) 2008-08-21 2010-02-25 Schaeffler Kg Verfahren zur Verstellung einer Nockenwelle eines Verbrennungsmotors, Nockenwellenverstellsystem und Verbrennungsmotor mit verstellbarer Nockenwelle
DE102008053913B4 (de) * 2008-10-30 2017-05-18 Ovalo Gmbh Spannungswellengetriebe sowie Vorrichtung zum Überlagern von Bewegungen
DE202008016005U1 (de) 2008-12-01 2009-08-06 Ortloff, Helene Kunststoff-Getriebe-Motor
EP2194241A1 (fr) * 2008-12-05 2010-06-09 Delphi Technologies, Inc. Déphaseur à came variable
DE102009006957A1 (de) * 2009-01-31 2010-08-05 Sbs Feintechnik Gmbh & Co.Kg Verstelleinrichtung für Nockenwellen von Verbrennungsmotoren von Fahrzeugen, wie Kraftfahrzeuge, Boote, Schiffe oder dergleichen
DE102009009523A1 (de) 2009-02-18 2010-08-19 Schaeffler Technologies Gmbh & Co. Kg Phasenstellanordnung einer Brennkraftmaschine
EP2282021B1 (fr) * 2009-08-06 2012-05-09 Delphi Technologies, Inc. Déphaseur d'arbre à cames à commande harmonique avec ressort de rappel
US8584633B2 (en) * 2009-08-06 2013-11-19 Delphi Technologies, Inc. Harmonic drive camshaft phaser with bias spring
DE102009037403B4 (de) * 2009-08-13 2018-01-11 Schaeffler Technologies AG & Co. KG Elektrischer Nockenwellenversteller
EP2360358A1 (fr) 2010-02-24 2011-08-24 Delphi Technologies, Inc. Déphaseur d'arbre à cames électrique avec récupération d'énergie
EP2561189B1 (fr) * 2010-04-23 2017-10-25 Borgwarner Inc. Plaque flexible de synchronisateur de phase d'arbre à cames concentrique
US8322318B2 (en) * 2010-07-28 2012-12-04 Delphi Technologies, Inc. Harmonic drive camshaft phaser with phase authority stops
JP5741893B2 (ja) 2010-09-03 2015-07-01 株式会社ジェイテクト カムシャフト装置
DE102010050814A1 (de) 2010-11-09 2012-05-10 Schaeffler Technologies Gmbh & Co. Kg Getriebeeinrichtung und Nockenwellenversteller mit einer solchen Getriebeeinrichtung
DE102010051051A1 (de) * 2010-11-11 2012-05-16 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller für eine Brennkraftmaschine
US8555836B2 (en) * 2010-12-10 2013-10-15 Delphi Technologies, Inc. Electric drive camshaft phaser with torque rate limit at travel stops
DE102011004071A1 (de) * 2011-02-14 2012-08-16 Schaeffler Technologies Gmbh & Co. Kg 3-Wellen-Verstellgetriebe mit integrierter Überlastkupplung
DE102011004075A1 (de) * 2011-02-14 2012-08-16 Schaeffler Technologies Gmbh & Co. Kg Wellgetriebe mit seitlicher Führung des Stirnrades
DE102011004070A1 (de) 2011-02-14 2012-08-16 Schaeffler Technologies Gmbh & Co. Kg 3-Wellen-Verstellgetriebe mit zwei mechanischen Anschlägen
DE102011004066A1 (de) 2011-02-14 2012-08-16 Schaeffler Technologies Gmbh & Co. Kg 3-Wellen-Verstellgetriebe mit veränderter Masseverteilung und Verfahren zur Herstellung eines Wellgenerators
DE102011004069A1 (de) 2011-02-14 2012-08-16 Schaeffler Technologies Gmbh & Co. Kg 3-Wellen-Verstellgetriebe mit elastischem Koppelglied
US8726865B2 (en) * 2011-06-08 2014-05-20 Delphi Technologies, Inc. Harmonic drive camshaft phaser using oil for lubrication
CN104822909A (zh) * 2012-12-10 2015-08-05 博格华纳公司 分离的环齿轮行星式凸轮相位器
DE102013215816B3 (de) * 2013-04-22 2014-10-16 Magna Powertrain Ag & Co. Kg Nockenwellenversteller
US9016250B2 (en) 2013-06-18 2015-04-28 Delphi Technologies, Inc. Camshaft phaser
US20150033906A1 (en) * 2013-08-01 2015-02-05 Delphi Technologies, Inc. Axially compact electrically driven camshaft phaser
JP5968528B2 (ja) * 2013-09-11 2016-08-10 株式会社ハーモニック・ドライブ・システムズ 波動発生器および波動歯車装置
US9664073B2 (en) * 2014-02-25 2017-05-30 Delphi Technologies, Inc. Modular electrically actuated camshaft phaser
JP5878196B2 (ja) * 2014-03-10 2016-03-08 上銀科技股▲分▼有限公司 中空型減速器
US9151191B1 (en) 2014-04-01 2015-10-06 Delphi Technologies, Inc. Electrically actuated camshaft phaser
DE102014209312B4 (de) 2014-05-16 2020-12-03 Schaeffler Technologies AG & Co. KG Nockenwellenverstellanordnung, umfassend eine axiale Sicherung mittels einer Spannhülse
US9677657B2 (en) 2014-05-30 2017-06-13 Spectrum Diversified Designs, Llc Circular wave drive
US9494224B2 (en) * 2014-05-30 2016-11-15 Ohio State Innovation Foundation Circular wave drive
DE102014214125B4 (de) 2014-07-21 2018-01-04 Schaeffler Technologies AG & Co. KG Stelleinrichtung zur Verstellung von Steuerzeiten einer Brennkraftmaschine
DE102015210707B3 (de) * 2015-06-11 2016-12-01 Schaeffler Technologies AG & Co. KG Drei-Wellengetriebe
DE102015222831A1 (de) 2015-11-19 2017-05-24 Schaeffler Technologies AG & Co. KG Verstelleinrichtung einer Brennkraftmaschine
DE102015223419A1 (de) 2015-11-26 2016-11-10 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE202015009214U1 (de) 2015-12-01 2016-11-29 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102015224897A1 (de) 2015-12-10 2017-06-14 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102015224901A1 (de) 2015-12-10 2017-01-19 Schaeffler Technologies AG & Co. KG Wellgetriebe
CN114576333A (zh) 2015-12-18 2022-06-03 舍弗勒技术股份两合公司 谐波传动机构的弹性齿轮
DE102016201536A1 (de) 2016-02-02 2017-08-03 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016204784A1 (de) 2016-03-23 2017-09-28 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102017105318A1 (de) 2016-04-20 2017-10-26 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016207046A1 (de) 2016-04-26 2017-02-23 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016207930B3 (de) * 2016-05-09 2017-08-10 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016207927B4 (de) 2016-05-09 2018-07-26 Schaeffler Technologies AG & Co. KG Stellantrieb
DE102016210700A1 (de) 2016-06-15 2017-05-18 Schaeffler Technologies AG & Co. KG Flexibles Getriebeelement
DE102016210703A1 (de) 2016-06-15 2017-05-24 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016210865A1 (de) 2016-06-17 2017-12-21 Schaeffler Technologies AG & Co. KG Stellvorrichtung
DE102016212841A1 (de) 2016-07-14 2018-01-18 Schaeffler Technologies AG & Co. KG Flexibles Getriebebauteil
DE102016214632A1 (de) 2016-08-08 2018-02-08 Schaeffler Technologies AG & Co. KG Stellantrieb für einen Verbrennungsmotor
DE102016216670B4 (de) 2016-09-02 2021-05-12 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102016216594B3 (de) * 2016-09-02 2017-11-02 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102016216817A1 (de) 2016-09-06 2018-03-08 Schaeffler Technologies AG & Co. KG Kugelgestrahlter elektrischer Nockenwellenversteller
DE102016217051A1 (de) 2016-09-08 2017-08-17 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
CN109690033B (zh) 2016-09-22 2021-10-29 舍弗勒技术股份两合公司 内燃机的调节单元
EP3299595A1 (fr) 2016-09-22 2018-03-28 Schaeffler Technologies GmbH & Co. KG Déphaseur d'arbre à cames
DE102016218192B3 (de) * 2016-09-22 2018-01-25 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102016218574B4 (de) 2016-09-27 2020-01-02 Schaeffler Technologies AG & Co. KG Stellgetriebe
DE102016218575A1 (de) 2016-09-27 2017-08-17 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016218927A1 (de) 2016-09-29 2017-11-02 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016219076A1 (de) 2016-09-30 2017-08-17 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102017119860A1 (de) 2016-09-30 2018-04-05 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016219915A1 (de) 2016-10-13 2018-04-19 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016219944A1 (de) 2016-10-13 2018-04-19 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016220631A1 (de) 2016-10-20 2017-08-31 Schaeffler Technologies AG & Co. KG Verstellvorrichtung
DE102016221839A1 (de) 2016-11-08 2018-05-09 Schaeffler Technologies AG & Co. KG Nockenwellenversteller zur variablen Ventilsteuerung einer Brennkraftmaschine
DE102016222406A1 (de) 2016-11-15 2018-05-17 Schaeffler Technologies AG & Co. KG Verstellgetriebe eines Verbrennungsmotors
DE102016222536B4 (de) * 2016-11-16 2020-02-06 Schaeffler Technologies AG & Co. KG Verstellgetriebevorrichtung für eine Welle sowie Fahrzeug mit der Verstellgetriebevorrichtung
DE102017126527A1 (de) 2016-11-16 2018-05-17 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016222833A1 (de) 2016-11-21 2018-05-24 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016222997B4 (de) 2016-11-22 2019-01-03 Schaeffler Technologies AG & Co. KG Flexibles Getriebebauteil
DE102016122826A1 (de) 2016-11-25 2018-05-30 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016223372A1 (de) 2016-11-25 2017-11-02 Schaeffler Technologies AG & Co. KG Verstellgetriebe
DE102016223796A1 (de) 2016-11-30 2018-03-29 Schaeffler Technologies AG & Co. KG Wellgetriebe
JP6685889B2 (ja) 2016-12-16 2020-04-22 住友重機械工業株式会社 撓み噛合い式歯車装置
KR102225568B1 (ko) * 2017-01-21 2021-03-08 가부시키가이샤 하모닉 드라이브 시스템즈 파동기어장치
KR101943757B1 (ko) 2017-04-21 2019-04-17 강성순 긴급상황 대피 또는 화재진압용 리프트장치
DE102017109305B4 (de) 2017-05-02 2024-05-16 Schaeffler Technologies AG & Co. KG Elektrischer Nockenwellenversteller
US10253864B2 (en) * 2017-07-03 2019-04-09 Optimal Actuation Inc. Bearing wave generator assembly
CN109653828B (zh) * 2017-10-10 2022-02-22 博格华纳公司 轴承跨距缩小的偏心齿轮
JP6939397B2 (ja) * 2017-10-19 2021-09-22 株式会社デンソー バルブタイミング調整装置
DE102017130062B4 (de) 2017-12-15 2024-01-18 Schaeffler Technologies AG & Co. KG Flexibles Getriebebauteil
DE102017130063B4 (de) 2017-12-15 2019-07-11 Schaeffler Technologies AG & Co. KG Wellgetriebe und dessen Verwendung
CN108006167A (zh) * 2017-12-31 2018-05-08 无锡凯涵科技有限公司 一种智能机器人减速器结构
JP6953326B2 (ja) * 2018-02-23 2021-10-27 住友重機械工業株式会社 減速装置
EP3537004A1 (fr) * 2018-03-08 2019-09-11 Ovalo GmbH Dispositif de montage des paliers de roulement flexibles dans le sens radial sur les générateurs de ligne d'arbre
WO2019170198A1 (fr) 2018-03-08 2019-09-12 Schaeffler Technologies AG & Co. KG Transmission à ondulations et procédé de fabrication d'un composant de transmission élastique
JP6734001B2 (ja) * 2018-03-30 2020-08-05 三菱電機株式会社 バルブタイミング調整装置
US10371241B1 (en) * 2018-06-22 2019-08-06 Baoxiang Shan Stress-wave actuator and reducer
DE102018117950A1 (de) * 2018-07-25 2020-01-30 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102018124571A1 (de) 2018-10-05 2020-04-09 Schaeffler Technologies AG & Co. KG Flexibles Getriebebauteil
DE102018126439A1 (de) * 2018-10-24 2020-04-30 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Montage eines Wellgetriebes
DE102018128028B3 (de) 2018-11-09 2020-03-05 Schaeffler Technologies AG & Co. KG Wellgetriebe für einen elektromechanischen Nockenwellenversteller
JP2020133445A (ja) * 2019-02-15 2020-08-31 株式会社ミクニ バルブタイミング変更装置
DE102019109131A1 (de) * 2019-04-08 2020-10-08 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Herstellung eines Wellgetriebes
CN114341524A (zh) 2019-06-13 2022-04-12 圆波驱动合作伙伴公司 一种圆形波驱动器
DE102019132995A1 (de) * 2019-12-04 2021-06-10 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Herstellung eines Innenrings eines Wellgenerators
JP2023526882A (ja) 2020-03-31 2023-06-26 サーキュラー ウェーブ ドライブ パートナーズ インコーポレイテッド 円形波動ドライブ
CN112128342A (zh) * 2020-10-15 2020-12-25 重庆金山医疗器械有限公司 谐波减速机连接结构和胶囊内窥镜控制器
JP2023138174A (ja) * 2022-03-18 2023-10-02 株式会社リケン 軸受

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3427898A (en) 1963-05-20 1969-02-18 Ferdy Mayer Production of low velocity motion
US3471913A (en) * 1967-02-24 1969-10-14 Usm Corp Method of making a roller bearing and an elliptoidal inner ring therefor
US3789700A (en) * 1972-04-04 1974-02-05 Usm Corp Positive drive roller planetary wave generator
JPS50155822A (fr) * 1974-06-10 1975-12-16
JPH0267405A (ja) * 1988-08-31 1990-03-07 Aisin Seiki Co Ltd 弁開閉時期制御装置
US5417186A (en) * 1993-06-28 1995-05-23 Clemson University Dual-acting apparatus for variable valve timing and the like
DE19520555A1 (de) 1995-06-06 1996-12-12 Fickelscher Kurt G Dipl Ing Elastische Steckwellenverbindung für Planetengetriebe mit flexiblem Planetenrad
DE19708310A1 (de) 1997-02-28 1998-09-17 Ims Morat Soehne Gmbh Untersetzungsgetriebe
US6257186B1 (en) 1999-03-23 2001-07-10 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
US6328006B1 (en) * 1999-03-23 2001-12-11 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
AT409786B (de) * 1999-03-23 2002-11-25 Tcg Unitech Ag Vorrichtung zur verstellung einer nockenwelle einer brennkraftmaschine mit innerer verbrennung
US6155220A (en) 1999-09-13 2000-12-05 General Motors Corporation Piezoelectric differential cam phaser
JP4807689B2 (ja) 2001-05-23 2011-11-02 株式会社ハーモニック・ドライブ・システムズ 無潤滑型波動歯車装置
US7144468B2 (en) * 2002-09-05 2006-12-05 Metglas, Inc. Method of constructing a unitary amorphous metal component for an electric machine

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112013007274B4 (de) 2013-07-25 2024-01-18 Harmonic Drive Systems Inc. Spannungswellengetriebe
DE102016216667A1 (de) 2015-09-10 2017-03-16 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
WO2017041799A1 (fr) 2015-09-10 2017-03-16 Schaeffler Technologies AG & Co. KG Déphaseur d'arbre à cames
DE102016111546A1 (de) 2016-06-23 2017-12-28 Pierburg Gmbh Wellgetriebe für eine Verbrennungskraftmaschine
DE102019102264A1 (de) 2019-01-30 2020-07-30 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Montage eines Nockenwellenverstellers
DE102019102264B4 (de) 2019-01-30 2024-04-18 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Montage eines Nockenwellenverstellers
DE102022109041A1 (de) 2022-04-13 2023-10-19 Bayerische Motoren Werke Aktiengesellschaft Verbrennungskraftmaschine für ein Kraftfahrzeug, insbesondere für einen Kraftwagen, sowie Kraftfahrzeug

Also Published As

Publication number Publication date
DE102004009128A1 (de) 2005-09-15
JP2007527968A (ja) 2007-10-04
US7673598B2 (en) 2010-03-09
EP1718846A1 (fr) 2006-11-08
KR20060129029A (ko) 2006-12-14
WO2005080757A1 (fr) 2005-09-01
US20080210182A1 (en) 2008-09-04

Similar Documents

Publication Publication Date Title
EP1718846B1 (fr) Dispositif de reglage electrique d'arbre a cames
EP1776513B1 (fr) Actionneur d'arbre a cames a moteur electrique
EP1715143B1 (fr) Déphaseur d'arbre à cames de moteur à combustion interne
EP2976551B1 (fr) Démultiplicateur harmonique à couronne de broches
WO2019170198A1 (fr) Transmission à ondulations et procédé de fabrication d'un composant de transmission élastique
WO2006034921A1 (fr) Transmission a excentrique presentant une denture en fuseaux cycloidaux
DE102017114175B3 (de) Wellgetriebe
WO2006024371A1 (fr) Ajusteur d'arbre a cames
DE102016219919A1 (de) Elastisches Zahnrad eines Wellgetriebes
DE102013018775A1 (de) Triebstock-Getriebeeinrichtung
WO2006074733A1 (fr) Dispositif pour transformer les temps de commande d'un moteur a combustion interne
WO2020125843A1 (fr) Réducteur harmonique et procédé de fabrication d'un réducteur harmonique
EP2676010A2 (fr) Mécanisme de réglage à trois arbres à répartition modifiée des masses et procédé de production d'un générateur d'onde
WO2006074732A1 (fr) Dispositif de modification des temps de commande d'un moteur a combustion interne
DE102013015843A1 (de) Taumelkörpergetriebe
DE102015204420A1 (de) Baugruppe für ein Wellgetriebe, Wellgetriebe und Antriebseinheit
WO2017174060A1 (fr) Mécanisme de réglage
WO2019185088A1 (fr) Engrenage à ondes de déformation
DE102016207927B4 (de) Stellantrieb
WO2015036401A1 (fr) Déphaseur d'arbre à cames
DE102013015844A1 (de) Übertragungsvorrichtung mit exzentrischer Triebstockkomponente
DE102010004579A1 (de) Ventiltrieb einer Brennkraftmaschine
DE102020129738A1 (de) Wellgetriebe, Verfahren zur Herstellung eines Wellgetriebes und Brennkraftmaschine mit Wellgetriebe aufweisenden Nockenwellenverstellern
WO2019115579A1 (fr) Arbre à cames rapportées et son procédé de fabrication
DE102019127672A1 (de) Wellgetriebe

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20060719

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR HU IT

RIN1 Information on inventor provided before grant (corrected)

Inventor name: HEYWOOD, JONATHAN

Inventor name: STEIGERWALD, MARTIN

Inventor name: SCHAEFER, JENS

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE FR HU IT

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG

17Q First examination report despatched

Effective date: 20120702

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR HU IT

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502005013541

Country of ref document: DE

Effective date: 20130508

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

26 Opposition filed

Opponent name: OVALO GMBH

Effective date: 20131211

PLAX Notice of opposition and request to file observation + time limit sent

Free format text: ORIGINAL CODE: EPIDOSNOBS2

REG Reference to a national code

Ref country code: DE

Ref legal event code: R026

Ref document number: 502005013541

Country of ref document: DE

Effective date: 20131211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130313

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005013541

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER KG, 91074 HERZOGENAURACH, DE

Effective date: 20130313

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005013541

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES AG & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20140218

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005013541

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES AG & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20140218

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005013541

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER KG, 91074 HERZOGENAURACH, DE

Effective date: 20130313

PLBB Reply of patent proprietor to notice(s) of opposition received

Free format text: ORIGINAL CODE: EPIDOSNOBS3

PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO

R26 Opposition filed (corrected)

Opponent name: OVALO GMBH

Effective date: 20131211

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20140930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140131

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005013541

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20150213

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20050125

APAH Appeal reference modified

Free format text: ORIGINAL CODE: EPIDOSCREFNO

APBM Appeal reference recorded

Free format text: ORIGINAL CODE: EPIDOSNREFNO

APBP Date of receipt of notice of appeal recorded

Free format text: ORIGINAL CODE: EPIDOSNNOA2O

APBM Appeal reference recorded

Free format text: ORIGINAL CODE: EPIDOSNREFNO

APBP Date of receipt of notice of appeal recorded

Free format text: ORIGINAL CODE: EPIDOSNNOA2O

APBQ Date of receipt of statement of grounds of appeal recorded

Free format text: ORIGINAL CODE: EPIDOSNNOA3O

PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20210319

Year of fee payment: 17

R26 Opposition filed (corrected)

Opponent name: OVALO GMBH

Effective date: 20131211

REG Reference to a national code

Ref country code: DE

Ref legal event code: R103

Ref document number: 502005013541

Country of ref document: DE

Ref country code: DE

Ref legal event code: R064

Ref document number: 502005013541

Country of ref document: DE

APBU Appeal procedure closed

Free format text: ORIGINAL CODE: EPIDOSNNOA9O

RDAF Communication despatched that patent is revoked

Free format text: ORIGINAL CODE: EPIDOSNREV1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: PATENT REVOKED

RDAG Patent revoked

Free format text: ORIGINAL CODE: 0009271

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: PATENT REVOKED

27W Patent revoked

Effective date: 20210701

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230522