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EP3382472A1 - Führungslager einer unruhwelle einer uhr - Google Patents

Führungslager einer unruhwelle einer uhr Download PDF

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Publication number
EP3382472A1
EP3382472A1 EP17163973.5A EP17163973A EP3382472A1 EP 3382472 A1 EP3382472 A1 EP 3382472A1 EP 17163973 A EP17163973 A EP 17163973A EP 3382472 A1 EP3382472 A1 EP 3382472A1
Authority
EP
European Patent Office
Prior art keywords
bearing
shaft
elements
resonator
blades
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.)
Pending
Application number
EP17163973.5A
Other languages
English (en)
French (fr)
Inventor
Raphael Cettour-Baron
Olivier HUNZIKER
Léonard TESTORI
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.)
Rolex SA
Original Assignee
Rolex SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Rolex SA filed Critical Rolex SA
Priority to EP17163973.5A priority Critical patent/EP3382472A1/de
Priority to US15/935,609 priority patent/US11073798B2/en
Priority to CN202111395436.1A priority patent/CN114089616A/zh
Priority to JP2018063897A priority patent/JP7280018B2/ja
Priority to CN201810274357.7A priority patent/CN108693761B/zh
Publication of EP3382472A1 publication Critical patent/EP3382472A1/de
Priority to JP2023029267A priority patent/JP2023065540A/ja
Pending legal-status Critical Current

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Classifications

    • 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
    • G04B31/00—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor
    • G04B31/02—Shock-damping bearings
    • G04B31/04—Shock-damping bearings with jewel hole and cap jewel
    • 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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/06—Oscillators with hairsprings, e.g. balance
    • 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
    • G04B31/00—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor
    • 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
    • G04B31/00—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor
    • G04B31/02—Shock-damping bearings

Definitions

  • the invention relates to a rotational guide bearing for a timepiece shaft, in particular a guide bearing for a shaft portion or a pivot of a timepiece resonator, in particular a guide bearing for a timepiece pendulum tigeron.
  • the invention also relates to a watch shock absorber or anti-shock device comprising such a bearing.
  • the invention also relates to a clock mechanism comprising such a bearing or such a damper.
  • the invention also relates to a watch movement comprising such a bearing or such a damper or such a mechanism.
  • the invention also relates to a timepiece comprising such a bearing or such a damper or such a mechanism or such a movement.
  • the pivoting devices or conventional guide bearings balancer induce more or less significant friction on the pivots of the balance depending on the position of the oscillator.
  • the friction is higher in the vertical position of the watch, still called “hanging" position, than in the horizontal position of the watch or "flat” position, so that the oscillation amplitude of the balance is more weak in the vertical positions than in the horizontal positions of the watch.
  • a difference in amplitude may in particular result in a difference in operation, hence the importance for the accuracy of the timepiece of minimizing the "flat-hung", that is to say the difference between walk between the "flat” position and the "hanging" position.
  • the friction in the different positions varies because the configurations of the contact between the rocker pins and the guide stones change.
  • a horizontal watch position the balance shaft is vertical and the end of the pivot of the shaft comes to rest on a stone called against pivot. In general, this stone is flat and the end of the pivot is rounded, so that the radius of the friction surface is low and the resulting friction is low.
  • the balance shaft In a vertical watch position, the balance shaft is in a horizontal position and rubs on the edge of a hole, usually an olive hole and / or rounded edges formed in a stone. The friction is greater and the oscillation amplitude of the balance is therefore lower than horizontal watch position.
  • the document CH239786 discloses a pivoting device combining an olive stone and a counter-pivot abutment inclined relative to the shaft. This makes it possible to permanently induce a friction of the cylindrical portion of the shaft against the olive stone in the horizontal watch position, and therefore to increase the friction in this position.
  • US2654990 discloses a flat-end pivot and slightly rounded edges rubbing against a counter-pivot provided with a hemispherical depression. The goal is also to increase the friction in horizontal watch position by maximizing the radius of friction of the contact surface of the pivot in such a position.
  • Monobloc dampers are also known in which the pivoting means of the balance pivot are manufactured in one piece with return means.
  • the document CH700496 relates to a simplified monobloc damper, the guide means of the rocker pivot bearing are implemented by elastic return means of the damper body.
  • these elastic return means press the pivot bearing against a stop formed by the body of the damper so that they have no effect on the pivot of balance.
  • no indication is given on the chronometric performance of such a device.
  • the document CH701995 relates to a bearing which has the particularity of being pressed against a rocker pivot under the effect of a spring arranged to apply a force directed axially relative to the shaft of the rocker pivot.
  • the bearing and the spring are preassembled within a pivot structure ready to be mounted on the watch movement. The purpose is to remove the movements of the pivot, and thus the contact configuration variations between the pivot and the bearing, due to changes in position of the watch.
  • the spring is prestressed so that it can act on the balance pivot, unlike a lyre of a conventional damper which acts only by reaction in case of a shock under the effect of the longitudinal displacement of the pendulum pivot.
  • the spring has a geometry close to that of a lyre.
  • the spring may be in the form of a coil spring.
  • the bearing and the spring can be monobloc.
  • Such a solution is not optimal insofar as the preload of the spring is dependent on the axial location of the pivot structure, and therefore in particular many assembly tolerances.
  • the document CH701995 discloses besides means for adjusting the prestressing of the spring by the axial displacement of the pivoting structure, for example by means of a bearing body whose outer periphery is threaded so that it can cooperate with a tapping formed on a pendulum bridge.
  • the force produced by the spring is dimensioned such that it allows appropriate behavior of the pivot device in case of impact. Pivoting and damping functions are therefore dependent on each other.
  • the patent application CH709905 discloses different embodiments of blade pivots.
  • two blades supported by a beam are held in abutment in the groove bottom under the effect of elastically deformable arms.
  • Such a structure requires a complex construction, defining two distinct virtual pivot trees.
  • blades biased by elastically deformable arms can define the same virtual pivot axis, but must be arranged in separate planes.
  • Such embodiments are also not suitable for a conventional balance beam structure. In particular, the amplitude of oscillation on such pivots is very limited.
  • the object of the invention is to provide a guide bearing to overcome the drawbacks mentioned above and improve the watch bearings known from the prior art.
  • the invention proposes a guide bearing of simple structure and making it possible to minimize the gap existing between the oscillating resistant torques of a resonator in the different horological positions.
  • a guide bearing according to the invention is defined by claim 1.
  • a damper according to the invention is defined by claim 12.
  • a mechanism according to the invention is defined by claim 13.
  • a movement according to the invention is defined by claim 15.
  • a timepiece according to the invention is defined by claim 16.
  • the timepiece is for example a watch, in particular a wristwatch.
  • the timepiece comprises a watch movement 120, including a mechanical watch movement.
  • the movement comprises a clock mechanism 110, in particular an oscillator connected to an energy source, such as a cylinder, by a finishing gear.
  • the oscillator comprises a resonator, in particular a resonator of the spring-balance type.
  • the resonator comprises a shaft 2 (shown, for example, schematically on the Figures 3 and 4 ), for example a balance shaft.
  • the mechanism comprises at least one guide bearing, in particular at least one bearing 1a; 1b; 1a '; 1b '; 1c 'of rotation guide of the resonator, at a shaft portion.
  • This at least one bearing is advantageously part of a damper 100 forming part of the mechanism.
  • the mechanism comprises two dampers 100 each comprising a guide bearing of the resonator.
  • the resonator is pivoted on both sides of the shaft 2 by two bearings.
  • the mounting of the resonator shaft in the guide bearing causes the elastic deformation of at least a portion of the bearing. It follows that after mounting the shaft in the guide bearing, the latter is prestressed.
  • the damper or dampers 100 comprise a counter-pivot stone biased into a stable position by the action of a spring and capable of being displaced axially relative to the axis of the resonator against the action of the spring in case of shock or acceleration moving the resonator against this counter-pivot stone.
  • the spring known as the lyre is intended to take up the efforts of the resonator shaft via the counter-pivot stone, the function of which is to delimit the frost, in particular the axial frustum, of the resonator shaft. In case of shock, the forces suffered by the shaft are taken up by the lyre via the counter-pivot stone.
  • the lyre plates the counter-pivot stone and the pivot stone against a stop defined by the body of the damper so that the lyre has no effect axial on the resonator shaft.
  • the resonator shaft is mounted axially within the damper.
  • the damper (s) 100 may comprise a pivot stone.
  • the resonator may, in case of shock or acceleration moving the resonator radially relative to the axis of the resonator against the action of the guide bearing, abut against this pivot stone, after the bearing has been deformed to a certain degree.
  • the damper (s) 100 may not include pivot stone.
  • the guide bearing 1a; 1b; 1a '; 1b '; 1c ' may come instead of the pivot stone of a shock absorber known from the prior art.
  • the bearing comprises at least one support element 13a; 13b; 131a; 132a; 13a '; 13b '; 13c 'arranged so as to exert, on the radial axis or substantially radially to the axis, an action on the shaft, in particular a force on the shaft, permanently.
  • the action may however be inclined relative to the radial direction to the axis 21 because of the coefficient of friction at the shaft-bearing element interface.
  • the action or actions are exerted perpendicular to the axis 21 of the shaft.
  • the rotational guidance function can therefore be dissociated from the axial force recovery function.
  • the direction of the action or actions forms an angle less than 20 ° or less than 10 ° or less than 5 ° with a plane perpendicular to the axis 21.
  • a support element By “exercising permanently”, it is intended to carry out the action or actions constantly in time, when the resonator is put in place in the rest of the movement, whatever the position of the movement in space, in particular whatever the position of the resonator in space.
  • the contact between a support element and the shaft can nevertheless be broken momentarily when the movement is subjected to an acceleration greater than a predefined threshold, for example a threshold of the order of 1 g which corresponds to the intensity of the field of view. terrestrial gravitation, especially a threshold between 0.1g and 1g.
  • a threshold gap advantageously makes it possible to better dimension the bearing with respect to energy considerations, especially with regard to the friction induced by the bearing against the shaft.
  • the acceleration threshold may nevertheless be set at any other value, in particular in preference to any other value greater than or equal to 1 g, in particular of the order of 2 g.
  • the intensity of the torque resisting the movement of the resonator due to the action or actions exerted by the at least one bearing element on the shaft is constant or substantially constant, particular constant in time, when the resonator is set up in the rest of the movement and when the resonator is in motion, regardless of the position of the movement in space, especially regardless of the position of the resonator in space .
  • the intensity of the action or actions exerted by the at least one support element on the shaft is constant or substantially constant, in particular constant over time, once the resonator has been put in place in the rest movement, whatever the position of the movement in space, especially whatever the position of the resonator in space.
  • the shaft portion guided by the bearing may be a pivot or a tigeron.
  • the pivot may in particular have a cylindrical or frustoconical section.
  • the bearing comprises at least one element 12a; 12b; 12a '; 12b '; 12c 'cooperating with the at least one support element.
  • it is the at least one element 12a; 12b; 12a '; 12b '; 12c 'reminder that recalls the at least one support element 13a; 13b; 131a; 132a; 13a '; 13b '; 13c 'in contact on the shaft 2.
  • This at least one return element is advantageously elastically deformable.
  • the return force of the at least one bearing element on the shaft is produced by the elastic deformation of the at least one return element.
  • the at least one return element is defined or dimensioned so as to ensure the permanence of the contact as long as the acceleration experienced by the timepiece remains below the acceleration threshold described above.
  • the blades are curved in the form of a spiral.
  • the spiral may in particular be such that it is defined by a polar equation in which the radius is proportional to the angle or in which the radius is proportional to the angle raised to a power.
  • the blades can have any shape as long as they have adequate stiffness. They can have a zigzag shape, straight, curved.
  • the blades can be bent more than 180 °, in particular about 270 °, between their two ends.
  • the curved shapes of the blades optimize their size for a given dimensioning so as to obtain mechanical stress characteristics in the blades and rigidity characteristics of the blades that are adequate for the application.
  • the shapes of the blades can be flat (especially in a plane perpendicular to the axis of the bearing).
  • the shapes of the blades can also be non-planar. Thus, it is possible to increase the active lengths of the blades.
  • the bearing mainly comprises a frame 11a, in particular an annular frame, and blades 14a extending towards the inside of the frame, in particular three blades.
  • the blades extend for example from an inner surface of the annular frame.
  • Each blade has a convex face and a concave face.
  • a first end of each blade is attached or attached to the frame.
  • a second end of each blade is free.
  • the concave faces can form the support elements on the shaft.
  • Each support element is for example a portion of a concave face in the vicinity of a free end of a blade.
  • the support elements are formed at the level of the portions of faces by concave surfaces.
  • the radii of curvature of these concave surfaces are greater than the radius of the shaft 2 that the bearing is intended to receive.
  • the radii of curvature of these concave surfaces at the level of the support elements are greater than 5 times the radius of the shaft 2 that the bearing is intended to receive.
  • the diameter of the internal face of the frame can be 30 times, even 40 times, the diameter of the shaft 2.
  • the bearing differs from the bearing described in the first variant of the first embodiment in that the bearing elements 131a extend perpendicularly or substantially perpendicular to the free ends of the blades in a plane perpendicular to the axis 21.
  • Bearing elements 131a are, in this variant, cylinder portions disposed perpendicularly or substantially perpendicularly to the free ends of the blades. Such a conformation particularly promotes the positioning and stability of the pivot relative to the bearing. Thus, it can be guaranteed that the axis 21 of the shaft 2 remains in a defined neighborhood of its centered position in the bearing even under the effect of significant efforts on the resonator.
  • the bearing differs from the bearing described in the second variant of the first embodiment in that the bearing elements 132a comprise abutments or hooks 133a arranged so as to limit the deformations of the return elements 12a.
  • the bearing elements 132a comprise abutments or hooks 133a arranged so as to limit the deformations of the return elements 12a.
  • the stops are for example formed by arms extending substantially perpendicularly to the surfaces of the bearing elements which bear against the shaft. These stops are intended to cooperate with another bearing element adjacent to the bearing.
  • the different elements are represented in a configuration where the stops are not active, that is to say a configuration where they do not cooperate by contact with an adjacent element.
  • the bearing differs from the bearing described in the first embodiment in that the blades 14b are straight or rectilinear (and not curved).
  • the surfaces of the bearing elements in contact with the shaft 2 are planar.
  • the flexible blades are therefore in the form of straight beams. Their sections can be constant.
  • the bearing comprises stops limiting the deformation of the return elements. Indeed, the blades remain close to surfaces 16 of the frame constituting stops. When a certain degree of deformation of a return element is reached, the blade comes into contact against this stop and its deformation is thus limited. This avoids any risk of breakage of the blades during assembly of the bearing, in particular during the introduction of the shaft 2 in the bearing, or during operation of the timepiece when the resonator is in motion , especially in case of shock.
  • the return elements are constituted by a portion of a flexible blade.
  • the various flexible blades are made of material of a single piece thus forming a one-piece bearing including the frame.
  • the resonator shaft can be pivoted between the flexible blades.
  • the blades in particular the support elements, are pressed against the shaft under the effect of their respective prestressing.
  • the blades, in particular the return elements are deformed elastically when the shaft is introduced into the bearing. This elastic deformation causes a return force tending to bring the blades back to their original position during the introduction of the shaft.
  • each of the blades exerts the same force, ideally minimized as far as possible, on the shaft.
  • This force is ideally suited to induce friction substantially equal to the friction acting in a vertical position.
  • the contact between the blades and the shaft can be broken momentarily when the movement is subjected to an acceleration greater than a predefined threshold.
  • a threshold which can be between 0.5 g and 1 g advantageously allows minimize as much as possible the friction of the blades against the shaft.
  • the weight of the shaft is theoretically not taken up by the bearing.
  • the weight is, for example, taken up by a counter-pivot stone.
  • the weight of the resonator is taken up by the blade or blades of the bearing. This causes a slight displacement (perpendicular to the axis 21). This displacement is advantageously similar or lower than those known within the conventional bearings. As a result of this movement, the blade or blades located above the shaft exert a lower force on the shaft than those below.
  • the sum of the intensities of the forces of the blades on the shaft remains essentially the same regardless of the position of the resonator.
  • the intensity of the friction torque resulting from the forces of the blades on the shaft then also remains essentially the same regardless of the position of the resonator. This has the effect of balancing the quality factors of the resonator between the different watch positions.
  • a bearing is partially shown in the absence of the shaft mounted in the bearing.
  • the three blades define an inscribed circle of radius r0.
  • the flexible blades When mounting the shaft in the bearing, the flexible blades are elastically deformed, or preloaded, over a distance rp-r0, rp being the radius of the shaft at the support of the blades on the shaft.
  • the static friction torque C regardless of the position of the resonator, is equal to or substantially equal to the static friction torque CH induced by the flexible blades against the resonator shaft when the watch is in the horizontal position. (shaft 2 and axis 21 oriented vertically).
  • This value C being constant or substantially constant regardless of the position of the watch, it has the effect of balancing the quality factors of the oscillator between the different positions.
  • the figure 18 illustrates a graph representing different FQ quality factors according to oscillator amplitude of an oscillator and the spatial position of a watch having an oscillator pivoted by two bearings such as that illustrated in FIG. figure 7 . It is observed that these FQ quality factors are homogenized regardless of the position of the resonator, and significantly in relation to the quality factors FQ of the same conventionally rotated resonator shown in FIG. figure 17 .
  • F0 can be minimized to the best possible extent so as to produce the lowest possible static friction torque while balancing the frictional moments in all the horizontal and vertical positions.
  • the stiffness k of each of the flexible blades must satisfy the criterion: k > 2. P / 3. rp - r 0
  • the sections of these blades may be constant or not.
  • Each of these blades may also consist of several blades, integral or not, so as to optimize and differentiate their stiffness according to the different displacements or positions of the resonator. For example, such an embodiment would make it possible to minimize the radial bearing force at against the shaft in order to minimize the frictional forces against the shaft while ensuring the centering of the shaft in the bearing.
  • the blades, and more generally the bearings may for example be made of nickel, a nickel-phosphorus alloy, or silicon and / or coated silicon (silicon oxide , silicon nitride, ).
  • Such components can be manufactured in a preferred manner by electroforming or etching. Alternatively, such components could be machined by electroerosion.
  • the bearing comprises a ring having a geometry including several protuberances or lobes directed towards the axis of the ring, in particular directed towards the axis of the ring and extending from a surface of the ring directed towards the inside of the ring.
  • the ring comprises at least two protuberances. It may include two or three or four or five or six protuberances.
  • the bearing comprises a ring of elastomeric material.
  • the bearing can be made of natural rubber or synthetic rubber such as neoprene, polybutadiene, polyurethane or silicone.
  • the ring may have a constant section.
  • it may have a bearing element comprising a continuous surface bearing on the shaft over its entire circumference or on the majority of its circumference, for example more than 240 ° or more than 270 ° or more than 300 ° .
  • the bearing therefore comprises a single bearing element on the shaft.
  • This support element is constituted by the surface in contact with the shaft.
  • An annular portion of the ring located between the surface in contact with the shaft and the larger diameter surface of the ring constitutes a return element, in this case a single return element.
  • the bearing 1a ' comprises three protuberances 14a'.
  • Each protuberance comprises a support element 13a 'on the shaft and a return element 12a' of the support element in contact with the shaft.
  • the support elements are constituted by surfaces of the protuberances in contact with the shaft.
  • the return elements are constituted by the material of the protuberances connecting the support elements to the remainder of the ring 11a 'constituting a frame and having a constant section.
  • the protuberances are lobes or bosses filled with matter.
  • the bearing differs from the first variant of the third embodiment of the bearing in that the protuberances are lobes or bosses in which cutouts 91 have been made.
  • the bearing may comprise at least one radial or substantially radial protuberance, each protuberance comprising at least one bearing element on the shaft and a return element of at least one bearing element on the shaft, the or the return elements including cutouts.
  • the bearing differs from the first variant of the third mode or the second variant of the third embodiment in that the ring is mechanically connected to, in particular fixed to, in particular overmolded on a ring 11c 'constituting the frame.
  • the at least one return element and the at least one support element are preferably monobloc.
  • the bearing has three return elements and three support elements. However, whatever the embodiment and whatever the variant, the bearing may have a different number of three return elements and three support elements. In particular, whatever the embodiment and whatever either the variant, the bearing may have one or two or three or four or five or six return elements and one or two or three or four or five or six support elements. Preferably, the bearing has as many return elements as support elements.
  • the bearing surface bearing against the shaft 2 of each support element may be flat or concave or convex.
  • all the bearing surfaces may be flat or concave or convex.
  • the frame including the annular frame, can be manufactured in one piece or made of several independent parts, including as many independent parts as return elements.
  • the blades are made independently of each other, they are each fixed to a base 111a.
  • the bases are advantageously provided with positioning elements and possibly adjustment elements, in particular centering elements, such as holes. These positioning elements make it possible to define the axis of the bearing.
  • Such an embodiment with a base is represented on the figure 12 .
  • the positioning elements cooperate for example with pins.
  • the bearing can be provided with assembly means of the bearing.
  • the frame may comprise a split ring so as to allow its elastic deformation and thus allow adequate positioning of the blades during assembly as shown in FIG. figure 13 .
  • the frame may also comprise a continuous ring as shown on the figure 11 .
  • the bearing may comprise stops for limiting the deformation of the return elements.
  • the support elements and / or the return elements are preferably uniformly distributed angularly around the axis 21.
  • the solutions described are intended to remedy the problem of difference in position between positions by providing a shaped bearing so as to generate a substantially constant force on a shaft of a resonator, regardless of the position of the resonator.
  • the bearing has the particularity of being provided with at least one return means provided for applying a substantially radial force against a resonator shaft, and whatever the position of the resonator.
  • the bearing is provided with at least one return means which is provided to apply a substantially radial force against the shaft so as to induce a substantially constant force between the shaft and the bearing, and whatever the position of the watch.
  • the quality factor of the resonator can be constant or substantially constant regardless of the position of the resonator, and the chronometric performance of the movement optimized.
  • the biasing means preferably function to support and position, at least in the transverse plane of the bearing, the shaft of the resonator.
  • the bearing can be integrated within a damper, especially within a damper whose structure is conventional.
  • an axial damping function can be dissociated from the radial damping function.
  • the axial damping is mainly provided by a conventional counter-pivot stone and lyre.
  • a radial damping function can be provided by the bearings.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Support Of The Bearing (AREA)
  • Vibration Prevention Devices (AREA)
EP17163973.5A 2017-03-30 2017-03-30 Führungslager einer unruhwelle einer uhr Pending EP3382472A1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP17163973.5A EP3382472A1 (de) 2017-03-30 2017-03-30 Führungslager einer unruhwelle einer uhr
US15/935,609 US11073798B2 (en) 2017-03-30 2018-03-26 Guide bearing for a timepiece balance pivot
CN202111395436.1A CN114089616A (zh) 2017-03-30 2018-03-29 用于计时器摆轮枢轴的引导轴承
JP2018063897A JP7280018B2 (ja) 2017-03-30 2018-03-29 時計テンプピボット用案内軸受
CN201810274357.7A CN108693761B (zh) 2017-03-30 2018-03-29 用于计时器摆轮枢轴的引导轴承
JP2023029267A JP2023065540A (ja) 2017-03-30 2023-02-28 時計機構

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17163973.5A EP3382472A1 (de) 2017-03-30 2017-03-30 Führungslager einer unruhwelle einer uhr

Publications (1)

Publication Number Publication Date
EP3382472A1 true EP3382472A1 (de) 2018-10-03

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EP17163973.5A Pending EP3382472A1 (de) 2017-03-30 2017-03-30 Führungslager einer unruhwelle einer uhr

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Country Link
US (1) US11073798B2 (de)
EP (1) EP3382472A1 (de)
JP (2) JP7280018B2 (de)
CN (2) CN114089616A (de)

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JP2020101539A (ja) * 2018-12-20 2020-07-02 ザ・スウォッチ・グループ・リサーチ・アンド・ディベロップメント・リミテッド 時計ムーブメントの軸受、とりわけ、ショック・アブソーバー、およびロータリー・ホイール・セット
EP4123394A1 (de) 2021-07-22 2023-01-25 Rolex Sa Ring zur mechanischen verbindung von zwei uhrenkomponenten
WO2023156201A1 (fr) * 2022-02-15 2023-08-24 Pierhor-Gasser Sa Pierre d'horlogerie et procede de fabrication d'une telle pierre
EP4242753A1 (de) 2022-03-11 2023-09-13 ETA SA Manufacture Horlogère Suisse Vorrichtung zum führen einer welle einer unruh mit spiralfeder
EP4242752A1 (de) 2022-03-11 2023-09-13 ETA SA Manufacture Horlogère Suisse Vorrichtung zum führen einer welle einer unruh mit spiralfeder
EP4471505A1 (de) * 2023-06-01 2024-12-04 Flexous Mechanisms IP B.V. Mechanisches teil für uhrwerk einer armbanduhr

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Publication number Priority date Publication date Assignee Title
EP3719583B1 (de) * 2019-04-03 2021-11-10 ETA SA Manufacture Horlogère Suisse Mechanische bremsvorrichtung für triebfeder einer uhr
EP3792702A1 (de) * 2019-09-13 2021-03-17 ETA SA Manufacture Horlogère Suisse Lager für uhrwerk, insbesondere stossdämpfer, für eine achse einer sich drehenden triebfeder
CH716957A2 (fr) * 2019-12-16 2021-06-30 Eta Sa Mft Horlogere Suisse Dispositif de guidage pour afficheur d'horlogerie.
EP4191346B1 (de) * 2021-12-06 2024-06-26 The Swatch Group Research and Development Ltd Stossdämpfungsschutz eines resonatormechanismus mit flexibler drehführung

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EP3396470B1 (de) 2017-04-24 2020-01-01 ETA SA Manufacture Horlogère Suisse Mechanische bremsvorrichtung für drehteil einer uhr
JP2020101539A (ja) * 2018-12-20 2020-07-02 ザ・スウォッチ・グループ・リサーチ・アンド・ディベロップメント・リミテッド 時計ムーブメントの軸受、とりわけ、ショック・アブソーバー、およびロータリー・ホイール・セット
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JP7280018B2 (ja) 2023-05-23
US20180284698A1 (en) 2018-10-04
US11073798B2 (en) 2021-07-27
JP2018200303A (ja) 2018-12-20
CN114089616A (zh) 2022-02-25
CN108693761B (zh) 2021-11-30
CN108693761A (zh) 2018-10-23

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