EP3208663B1 - Kugellager und anschlusssystem, das ein solches kugellager umfasst - Google Patents

Kugellager und anschlusssystem, das ein solches kugellager umfasst Download PDF

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Publication number
EP3208663B1
EP3208663B1 EP17155835.6A EP17155835A EP3208663B1 EP 3208663 B1 EP3208663 B1 EP 3208663B1 EP 17155835 A EP17155835 A EP 17155835A EP 3208663 B1 EP3208663 B1 EP 3208663B1
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EP
European Patent Office
Prior art keywords
rotation
segment
ball
notch
ball bearing
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EP17155835.6A
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English (en)
French (fr)
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EP3208663A1 (de
Inventor
Alain Laager
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Mps Micro Precision Systems AG
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Mps Micro Precision Systems AG
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    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B5/00—Automatic winding up
    • G04B5/02—Automatic winding up by self-winding caused by the movement of the watch
    • G04B5/18—Supports, suspensions or guide arrangements, for oscillating weights
    • G04B5/19—Suspension of the oscillating weight at its centre of rotation

Definitions

  • the present invention relates to a ball bearing and a coupling system comprising a ball bearing.
  • the present invention relates in particular to a clock-bearing ball bearing for a winding system in an automatic watch movement.
  • the document EP1134626 discloses a device for coupling an oscillating weight to a reduction gear in an automatic watch for the purpose of simplifying and compacting the winding system of the mainspring.
  • the coupling device used comprises two unidirectional coupling elements with superposed ball bearings. Each element makes it possible to transmit the bidirectional rotation movement of an oscillating mass unidirectionally to the mainspring.
  • the two elements are arranged to transmit the rotation of the oscillating mass each in an opposite direction so that the movement of the winding mass is always transmitted to the mainspring regardless of its direction of rotation.
  • the disadvantage of this construction lies in the large thickness of the coupling device due to the superposition of two ball bearing devices.
  • CH701343 discloses a device for damping radial movements during an impact of an annular oscillating mass.
  • Damping members support rollers in contact with the oscillating ring, these rollers are rotatably placed in a ball bearing.
  • the damping members are in contact with elastic means connected to the plate and allow a radial play of the mass during an impact. This damping device acts neither on the amplitude nor on the rotational power of the annular oscillating mass.
  • EP2110719 describes a damping device for the oscillating weight of a self-winding watch comprising a plate whose one end is fixed to the ground and whose other end is fixed to a tube arranged to turn about a shaft constituting the axis of rotation of said mass.
  • the plate has at least one flexible zone capable of flexing in the event of shocks to the oscillating mass.
  • a ball bearing is disposed between the shaft and the tube. This damping device does not limit the speed of rotation of the oscillating mass.
  • CH332550 discloses a self-winding watch in which an oscillating mass has on its underside two recesses in which is disposed a U-shaped leaf spring whose free ends abut against a pillar in turn so that the branches of the spring are deformed elastically to the extent permitted by the width of the clearances, thereby limiting the amplitude of the oscillations of the mass.
  • This device has the disadvantage of limiting the stroke of the oscillating mass in both directions of rotation and thus the efficiency of reassembly.
  • US3901021 discloses a ball bearing disengaging device in which a clutch spring is provided with inclined elastic pawls. These are oriented to engage in openings of a reduction gear whose teeth can engage with a ratchet so as to rotate in the winding direction of the barrel. In the opposite direction, of non-winding of the barrel, the elastic pawls slide with a slight resistance due to friction.
  • This device has a disadvantage associated with the size of the pawls facing upwards in the thickness of a watch movement.
  • EP0924579 has a device for limiting the mechanical power of an oscillating weight mounted elastically on a holding mobile to be braked by touching a bearing path and thus limit the power supplied when the latter substantially exceeds the powers provided in normal use.
  • WO15193400 discloses a transmission clock device comprising a ball bearing for binding a first ring with an outer ring.
  • a brake serves to slow the rotation of the first ring relative to the outer ring.
  • the braking is provided by a preload spring washer-type fixed or attached to the first ring, and having a flat surface acting on a flat surface of the outer ring.
  • the brake washer acts axially and its thickness is added to that of the other elements of the bearing, which becomes thicker. This device is therefore not suitable for fine watch movements.
  • EP1134626 relates to a clutch device comprising a ball bearing type of wedging pads. In a direction of rotation, the oscillating mass drives the output wheel; in the other direction, the torque exerted on the output wheel is zero. This device does not allow braking the oscillating weight.
  • An object of the present invention is to provide a ball bearing for a mechanical watch free from the limitations of known devices.
  • Another object of the invention is to provide a ball bearing for oscillating weight that can be used to reduce noise in the direction of free rotation of the oscillating mass.
  • Another object is to provide a ball bearing for oscillating weight of reduced thickness.
  • a ball bearing comprising an outer ring, an inner ring, balls and at least one segment intended to separate said balls from each other, the segment being placed in the radial direction between said inner ring with which it is in contact and the outer ring, the segment comprising a braking element, at least some of the balls can move relative to the segment so as to occupy a different relative position depending on the direction of rotation of said rings, so that, in the first direction of rotation only, one of the rings can rotate independently of the other ring but being braked by the braking element.
  • Such a bearing can be used to brake the oscillating mass when one of the rings drives the segments in the first direction of rotation. It is thus possible to design an automatic winding cylinder system in which the oscillating mass can rotate in one of the two directions of rotation without reloading the barrel, but still being braked by the ball bearing. This avoids the disadvantages of an oscillating weight rotating completely free in a direction of rotation, often causing a disturbing noise.
  • the braking system can also be used to brake the gear between the bearing and the barrel. This avoids unwanted rotation of the elements of this wheel when the gear is not driven by the oscillating weight.
  • the braking system is integrated in the ball bearing so that the assembly has a small footprint.
  • the bearing is thus designed to exert a different braking according to the direction of rotation.
  • Braking has the effect of preventing one of the rings and the segments from rotating freely relative to the other ring.
  • the braking system exerts friction on one of the rings, for example on the inner ring.
  • the braking is obtained by a portion of the separation segment of the balls. It does not require additional thickness.
  • the braking torque exerted by the bead separation segment therefore depends on the direction of rotation.
  • the braking element of the ball bearing according to the invention may comprise a flexible blade in contact with one of the rings of the bearing, for example with the inner ring.
  • the bearing force of this flexible blade against the ring may be constrained by a ball of the bearing, called the brake ball.
  • the ball bearing may comprise several segments, for example an odd number of segments, each having a flexible blade acting as a braking system.
  • Each segment may comprise an outer face facing the outer ring and an inner face in contact with the inner ring.
  • the different segments are placed between the inner and outer rings of the ball bearing, and thus serve as a cage for separating the balls from the bearing.
  • Each segment may extend between a first end and a second end on a segment angular sector, for example on an angular segment less than 120 °.
  • Each braking element may extend from the second end to a first angular sector smaller than the segment angular sector.
  • the configuration of the braking element ensures the necessary friction to slow down the braked ring without exerting too much friction that would lead to premature wear of the inner or outer ring.
  • Each segment may have at least one notch in which a ball may move between a first position when the outer ring rotates in a first direction of rotation and a second position when the outer ring rotates in the second direction of rotation.
  • One or more brake beads may be mounted in one or more brake notches on the outer face of each segment.
  • the brake balls may bear against the outer ring.
  • the brake notch may be located against the inner ring, the brake ball thus being able to roll against the inner ring.
  • the invention also relates to a coupling system comprising a ball bearing type unidirectional reducing noise in the direction of free rotation of the oscillating mass.
  • the bearing is arranged in such a way that the rotation of one of the rings in the second direction of rotation is transmitted without sliding, or practically without sliding, to the segments and to the other ring.
  • the second direction of rotation is opposite to the first direction.
  • the rotation of one of the rings in the first direction of rotation is not transmitted to the other ring; the ball bearing merely curbs a ring, or both rings.
  • the rotation of one of the rings in the second direction is however transmitted to the segments and to the other ring.
  • the ball bearing is therefore of unidirectional type ("one-way"), the braking element however creating a friction which prevents the free and unbraked rotation of the driving ring and / or the ring driven in the first direction of rotation.
  • Such a bearing can for example be used in watchmaking in the gear train between the oscillating weight and the barrel of an automatic winding system; it then makes it possible to transmit to the barrel the rotations of the oscillating mass in the second direction of rotation, and to allow this oscillating mass to rotate in the first direction of rotation without acting on the barrel, but nevertheless being braked.
  • each segment has a second notch, said locking notch.
  • the locking notch may be arranged in such a way that in the second direction of rotation at least one ball, called the locking ball, occupies a second position in the locking segment and is wedged between the outer ring of the bearing and the segment, making the outer ring rotate and the inner ring.
  • the locking ball can move between two positions of the locking notch.
  • the locking ball is wedged between the outer ring and the segment, and can therefore neither roll on itself nor move in the notch.
  • the segment is then wedged between the two inner rings, thus allowing the inner ring to drive the outer ring in rotation at the same speed or vice versa.
  • the outer ring thus cause the inner ring to rotate at the same speed.
  • the locking groove of the ball bearing according to the invention can be arranged so that in the first direction of rotation (direction of braking), the locking ball occupies a first position in which it is free to roll on it -even. In this position, the braking element is pressed against the inner ring, so as to slow down its speed of rotation. The inner ring rotating in the first direction of rotation is then braked by the segment.
  • the braking element for example a blade connected to the segment, causes friction on the inner ring tending to slow its rotation.
  • the locking groove of the ball bearing according to the invention may have a first inclined portion extending from the first end towards the second end to a second portion forming a stop and substantially radial in the plane of the bearing.
  • the first portion is at an angle less than 90 ° with the second portion.
  • the segment may have at least one first notch, called the brake notch, close to the second end, wherein a brake ball can move between a first position and a second position while in contact with the outer ring.
  • the brake notch may have a first substantially radial portion, near the locking notch and a second substantially radial portion near the second end of the segment.
  • a brake ball can move between these two portions.
  • the brake ball is placed in the brake notch so as to provide braking of the inner race.
  • the brake notch may have a first inclined portion, so as to change the braking intensity according to the position of the brake ball in the notch.
  • the inclined portion may extend towards the second end of the segment, so as to increase the pressure of the brake ball when the brake ball is in the first position, in the braking direction.
  • the invention also relates to a unidirectional coupling system comprising a ball bearing according to the first embodiment of the invention, an integral input in rotation of the inner ring, an output integral in rotation with the outer ring, so that in a first direction of rotation, the rotational movement of the input is not transmitted to the output and the speed of rotation of the inner ring and the outer ring is reduced by the braking element while in a second direction of rotation, the rotational movement of the input is transmitted to the output.
  • Such a coupling system can be used to couple an oscillating mass to a reduction gear so as to slow down the rotation of the oscillating weight and / or the gear in one direction of rotation, while in the other direction the inner ring connected to the oscillating weight and the teeth of the outer ring of the bearing meshing with a reduction gear rotate at the same speed of rotation.
  • An automatic watch according to the invention may comprise the unidirectional coupling system described above, the input being kinematically connected to an oscillating mass and the output being kinematically connected to a mainspring, the kinematic connection with the output possibly comprising a train gear.
  • the coupling system of such a watch makes it possible to brake the oscillating mass, in a direction of rotation, when it does not take part in reassembling the barrel. This braking avoids generating noise that becomes awkward for the wearer of the watch when the oscillating mass rotates too fast.
  • the coupling system makes it possible to transmit the energy supplied by the rotation of the oscillating mass to the barrel.
  • the ball bearing is arranged so that, in a first direction of rotation, the braking element is pressed against the inner ring to create friction with the segment, while that in the second direction of rotation, the stress on the brake element is released so that the segment is free to rotate with respect to the inner ring.
  • each segment in this second embodiment comprises a first notch, called a brake notch, in which a brake ball moves in the direction of rotation, so as to modify the braking intensity in the direction of rotation. (Without blocking the relative movement of the segment against the inner ring).
  • the brake ball occupies a first position bearing against the outer ring, which causes a rotation of the segment on itself, and the support of the braking element against the inner ring.
  • the brake ball occupies a second position without contact with the outer ring, or with a lower support.
  • the release of this support causes a relaxation of the braking against the inner ring.
  • the brake notch may have an inclined portion against which the ball moves according to the direction of rotation, so as to modify the bearing against the outer ring.
  • the segment according to this second embodiment may have at least one second notch, said guide notch, to accommodate a guide ball for guiding the segment between the inner and outer rings, and to allow the outer ring to rotate relative to to the segment.
  • the guide segment can move in the guide slot without modifying its support against the outer ring.
  • An oscillating mass suspension may comprise a ball bearing according to this second embodiment of the invention.
  • a bearing allows the oscillating mass to rotate completely freely in a second direction of rotation while in the first direction of rotation, the oscillating mass is braked.
  • An automatic watch may comprise an oscillating weight carried by the suspension according to this second embodiment of the invention.
  • Such a watch makes it possible to reduce the speed of rotation of the oscillating mass when it does not take part in winding the barrel, in the corresponding direction of rotation, thus reducing the noise generated by the oscillating weight. In the other direction of rotation, the speed of rotation of the oscillating mass is not slowed down, it can thus provide a maximum energy for the winding of the barrel.
  • the braking of one of the rings is therefore maximum in one of the directions of rotation, and zero or at least reduced in the other direction of rotation. It would indeed be counterproductive to slow the oscillating mass when, in one of the directions of rotation, it contributes to the winding of the barrel.
  • the braking is further obtained by the action of the separation segment of the balls, which is in the same plane as the balls.
  • the thickness of the braking element is therefore not superimposed on the balls, which makes it possible to maintain a reduced thickness.
  • the braking is obtained by friction of this segment and / or balls in a radial direction, which avoids the need for additional rigid structures in the radial direction in order to absorb the braking torque.
  • FIGS 1 to 3 illustrate a first embodiment of the invention.
  • This bearing is intended to transmit the rotations of an oscillating mass to the cylinder when the oscillating mass rotates in a second direction of rotation, and to brake the oscillating mass without transmitting its movements when it turns in opposite direction. It can be mounted in the gear train between the oscillating weight and the cylinder of an automatic watch.
  • the ball bearing 1 presented to the figures 1 and 2 comprises three identical segments 2 placed between an outer ring 11 and an inner ring 12 of the bearing.
  • the number of segments 2 shown is not limiting, one could imagine a bearing 1 comprising a smaller or greater number of segments 2. An odd number of segments is however desirable to balance the loads.
  • the figure 1 represents a sectional view of a bearing according to this first embodiment.
  • the segments 2 and the balls 10a, 10b occupy a second position, called the locking position, which is reached when the bearing is driven by the inner ring 12 rotating in a second direction of rotation, in this case the clockwise direction .
  • the inner ring 12 rotates the segments 2 and the outer ring 11.
  • Each segment 2 comprises a first notch 201b, said brake notch, and a second notch 200a, or locking notch.
  • a locking ball 10a is housed in each locking notch 200a and a brake ball 10b is housed in each brake notch 201b.
  • each locking notch 200a has a first portion 2000 inclined near the first end 21 of the segment 2 and a second portion 2001 forming a substantially radial stop.
  • the locking balls 10a rise along the inclined portion 2000 and become wedged between the outer ring 11 of the bearing 1 and the segment 2. In this position, the segment 2 and the outer ring 11 rotate integrally.
  • Each segment 2 further comprises a braking element 240.
  • This element is pressed by the brake ball 10b against the inner ring 12, making the segments 2 and the inner ring 12 rotationally integral.
  • the rotation in the clockwise direction of the inner ring 12 causes the rotation in the same direction and at the same speed of each segment 2 and therefore the outer ring 11.
  • the outer ring 11 and the inner ring 12 are thus integral in rotation.
  • the brake balls 10b roll against the first portion 2010 of the brake notch. They push the second end 22 of the corresponding segment 2 against the inner ring, so as to press the brake element 240 against the inner ring.
  • the slot 243 between the brake member 240 and the segment body 2 provides some resilience to the brake member 240 to compensate for machining tolerances.
  • the figure 2 represents the position of the segments 2 and the balls 10a, 10b when the inner ring 12 rotates in the first direction of rotation, in this case the counterclockwise direction.
  • Each locking ball 10a of the locking notch 200a occupies a first position, against the portion 2001.
  • each brake ball 10b occupying a first position, against the portion 2011 of the second notch 201.
  • the braking element 240 is pressed against the inner ring 12 by the pressure exerted by the brake ball 10b, so that the rotation of the inner ring 12 in the clockwise direction is braked.
  • the Figures 4 and 5 illustrate a variant of the first embodiment differing in the configuration of the brake notch 201a.
  • the brake notch 201a is arranged to vary the pressure exerted by the brake ball 10b against the segment 2; the pressure is greater in the second direction of rotation (locking direction) than in the first direction of rotation (direction of braking), so as to increase the braking torque and further reduce the risk of sliding in the blocking direction .
  • the brake notch 201a has a first inclined portion 2010 along which the brake ball rises in the blocking direction.
  • the figure 6 illustrates a unidirectional coupling system 6 comprising a ball bearing 1 according to the first embodiment, driven by an oscillating mass 4 whose axis is connected to the outer ring 11 of the bearing.
  • the outer ring 11 of the unidirectional coupling system is intended to mesh a reduction gear (not shown) of a gear train or kinematic chain (not shown) connecting the oscillating mass 4 to the barrel (not shown).
  • the figure 7 is a sectional view of the unidirectional coupling device 6 according to a first embodiment of the invention.
  • the balls 10a, respectively 10b, placed in the notches 200a, respectively 201a or 201b of the segments 2, are held between on the one hand the outer ring 11 and on the other hand the inner ring 12 and the cone 13.
  • the balls 10a, 10b thus have four points of contact with the rings and the cone 13 of the bearing.
  • the cone makes it possible to close the bearing after the placement of the balls.
  • FIG. 8 to 12 A second embodiment of the invention is shown in Figures 8 to 12 .
  • This embodiment may for example be implemented with an inner ring 12 fixed with respect to the watch movement plate, and an oscillating weight 4 connected to the outer ring 11.
  • the bearing 1 allows the oscillating weight 4 to rotate freely. in one direction (second direction), to raise the barrel, and to be braked in the first direction.
  • the ball bearing 1 presented on the figures 8 and 9 comprises a plurality of identical segments 2, for example three segments 2, placed between the outer ring 11 and the inner ring 12 of the bearing 1.
  • the figure 8 represents the position of the segments 2 and the balls 10b, 10c when the outer ring 11 rotates in a second direction of rotation, in this case the counterclockwise direction, and that the inner ring 12 is fixed.
  • Each segment 2 is provided with a brake notch 200b and a guide notch 201c.
  • a brake ball 10b occupies a second position at the bottom of the brake notch 200b; it bears against a first notch portion 2000 substantially radial, and can turn on itself.
  • a guide ball 10c occupies a first position in the guiding notch 201c, bearing against a first portion (2010) substantially radial, in which it can rotate on itself.
  • the two balls 10b and 10c roll on themselves and the segment 2 is configured so that the braking element 240 does not rub against the inner ring 12 of the bearing 1. Therefore, the outer ring 11 and the segments 2 can rotate freely in the second direction (counterclockwise), without being braked.
  • the figure 9 represents the position of the segments 2 and the balls 10b, 10c when the inner ring 12 is fixed while the outer ring 11 rotates in a first direction of rotation, in this case the clockwise direction.
  • Each brake ball 10b in the first notch 200b rises along the second inclined portion 2001 towards a position bearing against the radial portion 2002.
  • the brake ball 10b is then bearing against the outer ring 11 and pushes the segment 2 into position. pivoting it about itself in the direction of the inner ring 12.
  • the brake member 240 then bears more against the inner ring 12, creating friction.
  • the braking torque is adjusted automatically due to the deformation of the braking element 240 that allows the slot 243, reducing the gap 242 between the free end of the blade 240 and the end 22 of the segment.
  • the rotation of the segments 2 and the outer ring 11 are thus braked.
  • the guide ball 10c is free to roll on itself in the guide notch 201c.
  • the figure 10 illustrates a segment 2 according to the second embodiment of the invention.
  • the figure 11 illustrates in section a suspension of oscillating mass 5 containing a ball bearing 1 according to the second embodiment of the invention.
  • the braking element 240 rests against a portion of the inner ring 12 which is not in contact with the balls 10b, 10c.
  • the oscillating mass 4 is for example screwed onto a thread 110 at the periphery of the outer ring 11.
  • the figure 12 illustrates in perspective a suspension with an oscillating mass 4 mounted directly on the outer ring 11 of a ball bearing according to the second embodiment of the invention.
  • the balls 10a, 10b, 10c of the bearing 1 according to the invention may be replaced by rollers, cylinders or any type of element used in bearings.
  • the balls 10a, 10b, and 10c are placed in notches 200a, 200b, 201b, 201c located on the outer face 20 of the segment 2, in contact with the outer ring 11, however, these notches 200a, 200b, 201b, 201c could be located on the inner face 24 of the segment 2, the balls 10a, 10b, and 10c then being in contact with the inner ring 12 of the bearing 1.
  • This ball bearing may be applied to a watch movement, as described, or to any mechanical apparatus requiring to transmit rotation in a single direction of rotation.

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Claims (15)

  1. Kugellager (1) für mechanische Uhr mit einem Aussenring (11), einem Innenring (12), Kugeln (10a, 10b, 10c) und mindestens einem Segment (2) zum Trennen der besagten Kugeln (10a, 10b, 10c) voneinander, wobei das Segment (2) in radialer Richtung zwischen dem besagten Innenring (12), mit dem es in Kontakt steht, und dem besagten Aussenring (11) angeordnet ist,
    wobei zumindest einige der besagten Kugeln (10) in Bezug auf das besagte Segment (2) beweglich sind, um entsprechend der Drehrichtung der besagten Ringe eine unterschiedliche relative Position einzunehmen,
    dadurch gekennzeichnet, dass das Segment (2) ein Bremselement (240) aufweist, so dass, lediglich in einer ersten Drehrichtung, einer der besagten Ringe (11, 12) sich unabhängig vom anderen Ring (11, 12) drehen kann, jedoch durch das besagte Bremselement (240) gebremst wird.
  2. Kugellager (1) gemäss Anspruch 1, wobei das besagte Bremselement (240) eine flexible Klinge in Kontakt mit dem besagten Innenring (12) aufweist.
  3. Kugellager (1) gemäss dem vorhergehenden Anspruch, wobei das besagte Segment (2) mindestens eine erste Kerbe (200a, 200b, 201a, 201b) aufweist, in welcher sich eine Kugel (10a, 10b) zwischen einer ersten Position, wenn der Aussenring sich in einer ersten Drehrichtung dreht, und einer zweiten Position, wenn sich der Aussenring in der zweiten Drehrichtung dreht, bewegen kann.
  4. Kugellager (1) gemäss Anspruch 3, wobei jedes Segment eine erste besagte, als Bremskerbe bezeichnete Kerbe (200b, 201a, 201b) umfasst, so angeordnet, dass zumindest in einer ersten Drehrichtung eine besagte, als Bremskugel bezeichnete Kugel (10b) auf das Segment (2) drückt, um das Bremselement (240) gegen den Innenring (12) zu drücken, um eine Reibung zwischen dem Segment (2) und dem Innenring (12) zu erzeugen.
  5. Kugellager gemäss Anspruch 4, wobei die besagte Bremskerbe (200b, 201a, 201b) so angeordnet ist, dass sie das gegen den besagten Innenring (12) in Drehrichtung ausgeübte Bremsmoment verändert.
  6. Kugellager gemäss Anspruch 5, so angeordnet, dass sich jedes besagte Segment (2) um sich selbst dreht, wenn sich die Bremskugel (10b) in der Bremskerbe (201a, 200b) bewegt, so dass der durch das Bremselement (240) auf den Innenring (12) ausgeübte Druck variiert wird.
  7. Kugellager (1) gemäss einem der Ansprüche 3 bis 6, wobei jedes Segment (2) eine zweite besagte, als Verriegelungskerbe bezeichnete Kerbe (200a) aufweist, so angeordnet, dass in einer zweiten Drehrichtung eine besagte, als Sperrkugel bezeichnete Kugel (10a) zwischen dem Aussenring (11) des Lagers (1) und dem Segment (2) eingeklemmt ist, wodurch der Aussenring (11) und der Innenring (12) drehfest miteinander gemacht werden.
  8. Kugellager (1) gemäss dem vorhergehenden Anspruch, wobei jede Sperrkerbe (200a) so angeordnet ist, dass in der zweiten Drehrichtung die besagte Sperrkugel (10a) einen reduzierten Druck auf das Segment (2) ausübt, um den Aussenring (11) in Bezug auf das Segment (2) drehen zu lassen.
  9. Lager (1) gemäss einem der Ansprüche 7 oder 8, derart angeordnet, dass, wenn eine Sperrkugel (10a) gegen einen zweiten Abschnitt (2001) der Sperrkerbe (200a) rollt, eine Bremskugel (10b) gegen den zweiten Abschnitt (2011) der Bremskerbe (201a, 201b) rollt, wobei das Bremselement (240) gegen den Innenring (12) gedrückt wird und die Drehgeschwindigkeit des Innenrings (12) gebremst wird.
  10. Kugellager (1) gemäss einem der Ansprüche 3 bis 6, wobei jedes Segment (2) eine zweite besagte, als Führungskerbe bezeichnete Kerbe (201c) aufweist, welche es dem besagten Segment ermöglicht, sich in Bezug auf den besagten Aussenring (11) in der zweiten Drehrichtung frei zu drehen.
  11. Kugellager (1) gemäss einem der Ansprüche 1 bis 10, wobei das besagte Bremselement (240) durch eine Klinge gebildet ist, welche durch einen Schlitz (243) vom Körper des Segments (2) getrennt ist, wodurch sich die Klinge verformen kann, um Bearbeitungstoleranzen auszugleichen.
  12. Unidirektionales Kupplungssystem (6) mit einem Kugellager (1) gemäss einem der Ansprüche 1 bis 11, einem drehfest mit dem Innenring (12) verbundenen Eingang, einem drehfest mit dem Aussenring (11) verbundenen Ausgang, worin in einer ersten Drehrichtung die Drehbewegung des Eingangs nicht auf den Ausgang übertragen wird und die Drehgeschwindigkeit des Innenrings (12) und des Aussenrings (11) durch das Bremselement (240) verringert wird, während in einer zweiten Drehrichtung, die Drehbewegung des Eingangs auf den Ausgang übertragen wird.
  13. Automatische Uhr (7) mit einem unidirektionalen Kupplungssystem (6) gemäss dem vorhergehenden Anspruch, wobei der Eingang kinematisch mit einer oszillierenden Masse (4) verbunden ist und der Ausgang kinematisch mit einer Triebfeder verbunden ist.
  14. Aufhängung (5) für schwingende Masse mit dem Kugellager (1) gemäss einem der Ansprüche 1 bis 3 oder 10 bis 11.
  15. Automatische Uhr mit einer schwingenden Masse (4), die von der Aufhängung (5) gemäss dem vorhergehenden Anspruch getragen wird.
EP17155835.6A 2016-02-16 2017-02-13 Kugellager und anschlusssystem, das ein solches kugellager umfasst Active EP3208663B1 (de)

Applications Claiming Priority (1)

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CH00206/16A CH712163A1 (fr) 2016-02-16 2016-02-16 Roulement à billes et système d'accouplement comportant un tel roulement à billes.

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EP3208663A1 EP3208663A1 (de) 2017-08-23
EP3208663B1 true EP3208663B1 (de) 2019-05-22

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CN109404435B (zh) * 2018-12-18 2023-09-05 屠申富 双向自动变速电机的传动机构

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Publication number Priority date Publication date Assignee Title
CH332550A (fr) 1956-08-09 1958-09-15 Nicolet Watch S A Montre à remontage automatique pour automobile
US3087300A (en) * 1959-01-28 1963-04-30 Elgin Nat Watch Co Self-winding watch and like device
US3901021A (en) 1973-06-25 1975-08-26 Citizen Watch Co Ltd Automatic winding watch
EP0924579B1 (de) 1997-11-24 2003-10-22 ETA SA Manufacture Horlogère Suisse Vorrichtung zur Begrenzung der durch eine Schwungmasse gelieferten Leistung in kleinen Instrumenten
CH694025A5 (fr) * 2000-03-17 2004-06-15 Soprod S A Dispositif d'accouplement pour transformer un mouvement de rotation dans les deux sens en un mouvement dans un sens.
ATE544098T1 (de) 2008-04-15 2012-02-15 Montres Jaquet Droz Sa STOßDÄMPFER FÜR SCHWUNGMASSE
CH703343B1 (fr) 2010-06-22 2019-08-15 Swatch Group Res & Dev Ltd Aiguille de pièce d'horlogerie.
EP3158401B1 (de) * 2014-06-19 2023-08-30 Rolex S.A. Übertragungsvorrichtung für uhr

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CH712163A1 (fr) 2017-08-31
EP3208663A1 (de) 2017-08-23

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