EP3671368B1 - Palier, notamment amortisseur de choc, et mobile tournant d'un mouvement horloger - Google Patents

Palier, notamment amortisseur de choc, et mobile tournant d'un mouvement horloger Download PDF

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Publication number
EP3671368B1
EP3671368B1 EP18214830.4A EP18214830A EP3671368B1 EP 3671368 B1 EP3671368 B1 EP 3671368B1 EP 18214830 A EP18214830 A EP 18214830A EP 3671368 B1 EP3671368 B1 EP 3671368B1
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EP
European Patent Office
Prior art keywords
pivot
bearing
cone
curvature
radius
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.)
Active
Application number
EP18214830.4A
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German (de)
English (en)
French (fr)
Other versions
EP3671368A1 (fr
Inventor
Jean-Jacques Born
Dominique Lechot
Yves Winkler
Christophe Vincent
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.)
Swatch Group Research and Development SA
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Swatch Group Research and Development 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 Swatch Group Research and Development SA filed Critical Swatch Group Research and Development SA
Priority to EP18214830.4A priority Critical patent/EP3671368B1/fr
Priority to JP2019224233A priority patent/JP2020101539A/ja
Priority to US16/713,079 priority patent/US11592784B2/en
Priority to CN201911329064.5A priority patent/CN111352332B/zh
Publication of EP3671368A1 publication Critical patent/EP3671368A1/fr
Priority to JP2022149179A priority patent/JP7411040B2/ja
Application granted granted Critical
Publication of EP3671368B1 publication Critical patent/EP3671368B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • G04B37/00—Cases
    • G04B37/04—Mounting the clockwork in the case; Shock absorbing mountings
    • 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
    • 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
    • G04B13/00—Gearwork
    • G04B13/02—Wheels; Pinions; Spindles; Pivots
    • 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
    • G04B29/00—Frameworks
    • G04B29/02—Plates; Bridges; Cocks
    • 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
    • G04B31/004—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor characterised by the material used
    • 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
    • G04B31/004—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor characterised by the material used
    • G04B31/012—Metallic bearings
    • 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
    • G04B31/004—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor characterised by the material used
    • G04B31/016—Plastic bearings
    • 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
    • G04B31/06—Manufacture or mounting processes
    • 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
    • G04B33/00—Calibers

Definitions

  • the present invention relates to a bearing of a watch movement, in particular a shock absorber, for an axis of a rotating mobile.
  • the invention also relates to a rotating mobile of a watch movement.
  • the invention also relates to a watch movement provided with such a bearing and such a rotating wheel set.
  • the axes of revolving mobiles In watch movements, the axes of revolving mobiles generally have pivots at their ends, which turn in bearings mounted in the plate or in bridges of a watch movement.
  • the bearings For certain mobiles, in particular the balance wheel, it is customary to equip the bearings with a shock-absorbing mechanism. Indeed, as the pivots of the axis of a balance are generally thin and the mass of the balance is relatively high, the pivots can break under the effect of a shock in the absence of a damping mechanism.
  • the configuration of a conventional shock absorber bearing 1 is represented by the figure 1 .
  • a domed olive-shaped stone 2 is driven into a bearing support 3 commonly called a chaton, on which is mounted a counter-pivot stone 4.
  • the chaton 3 is held against the bottom of a bearing block 5 by a damping spring 6 arranged to exert an axial stress on the upper part of the counter-pivot stone 4.
  • the bezel 3 further comprises a conical outer wall arranged in correspondence with a conical inner wall arranged at the periphery of the bottom of the bearing block 5.
  • the kitten comprises an outer wall having a surface of convex shape, that is to say domed.
  • the bearing 10 comprises a counter pivot 7 of the center plate type, comprising a cavity 8 in the shape of a cone to receive a pivot 12 of the axis 9 of the rotary wheel set, the bottom of the cavity being formed by the top 11 of the cone.
  • Pivot 12 is also tapered to fit into cavity 8, but the solid angle of pivot 12 is smaller than that of the cone of cavity 8.
  • this type of bearing has a significant drawback concerning the centering of the axis with respect to the bearing plates. Indeed, it is not possible to achieve good centering in the current configurations of this type of shock absorber. Thus, there is a high risk of having the shaft jammed by jamming between the clamps holding the shaft of the rotating mobile on either side.
  • a counter-pivot comprising a main body provided with a cavity configured to receive a pivot having the shape of a first cone having a first solid angle, the apex of the first cone being rounded with a first predefined radius of curvature included in a range from 0.2 ⁇ m to 50 ⁇ m, the cavity having a shape of a second cone having a second solid angle greater than the first solid angle, so that the pivot can rotate in the cavity, the top of the second cone being rounded and having a second predefined radius of curvature.
  • An object of the invention is, therefore, to provide a bearing, in particular a shock absorber, for an axis of a rotating mobile of a watch movement, for example an axis of a balance wheel, which avoids the aforementioned problem.
  • a bearing makes it possible to correctly center the axis in the center plate.
  • the invention relates to a bearing comprising a bearing block provided with a housing and a counter-pivot arranged in the housing, the counter-pivot comprising a main body provided with a cavity configured to receive a pivot of the axis of the rotating mobile, the pivot having the shape of a first cone having a first solid angle, the apex of the first cone being rounded with a first predefined radius of curvature comprised in an interval ranging from 5 ⁇ m to 50 ⁇ m, the cavity having a shape of a second cone having a second solid angle greater than the first solid angle, so that the pivot can rotate in the cavity, the apex of the second cone being rounded and having a second predefined radius of curvature, characterized in that the second radius of curvature is less than the first radius of curvature.
  • the bearing is remarkable in that the second radius of curvature is less than the first radius of curvature.
  • the pivot is well maintained in the cavity of the counter-pivot to prevent the axle from jamming in the bearing, while leaving it free to rotate.
  • the pivot can decenter in the bottom of the cavity and risks causing the shaft to jam, so that the balance is braked, or even completely blocked. Thanks to a radius of curvature of the bottom of the cavity smaller than that of the pivot of the axis, the pivot remains centered in the cavity, whatever the movement or the position of the timepiece.
  • this configuration of the counter-pivot makes it possible to keep a constant friction of the pivot inside the counter-pivot, whatever the position of the axis with respect to the direction of gravity, which is for example important for a balance shaft of a movement of a timepiece.
  • the cone shape of the cavity, as well as that of the pivot minimizes the difference in friction between the different positions of the axis with respect to the direction of gravity.
  • the second radius of curvature is less than 40 ⁇ m.
  • the second radius of curvature is less than 30 ⁇ m.
  • the second radius of curvature is less than 20 ⁇ m.
  • the second radius of curvature is less than 10 ⁇ m.
  • the second radius of curvature is substantially equal to 4 ⁇ m.
  • the second radius of curvature is at least equal to 0.1 ⁇ m.
  • the second radius of curvature is at least equal to 1 ⁇ m.
  • the main body of the counter-pivot is formed of a material to be chosen from the following list: an at least partially amorphous metal alloy, an electro-formed material, or a synthetic material.
  • the cavity can be obtained by a process of hot deformation of an at least partially amorphous metal alloy by a tool whose diameter is less than the first radius of curvature of the first cone.
  • the second solid angle is within a range ranging from 60 to 120°, or even 80 to 100°, preferably equal to 90°.
  • the at least partially amorphous metal alloy can be crystallized in order to create phases favorable to friction.
  • the at least partially amorphous metal alloy is ceramized to harden the surface of the main body, in particular in the second cone of the cavity.
  • the main body of the counter-pivot can be produced by a process of galvanic growth, such as electroforming on a corresponding cavity.
  • the main body of the counter-pivot made of synthetic material, for example of the POM type, and can be obtained by molding.
  • the main body of the counter-pivot made of composite material for example of the POM type loaded with particles of a material that lowers friction, for example PTFE, and can be obtained by molding.
  • it comprises an elastic support for the counter-pivot, such as a spring, to absorb shocks.
  • the main body of the counter-pivot and the elastic support are formed from the same piece.
  • the resilient support may be formed by a LIGA type lithography, electrodeposition and forming process.
  • the main body of the counter-pivot is molded onto the elastic support.
  • the first radius of curvature is within an interval ranging from 0.2 ⁇ m to 35 ⁇ m.
  • the first solid angle of the first cone is within an interval ranging from 0.2 ⁇ m to 25 ⁇ m.
  • the first solid angle of the first cone is within an interval ranging from 0.2 to 15 ⁇ m.
  • the invention also relates to a rotating mobile of a watch movement, such as a pendulum, for a bearing according to the invention, the mobile being provided with an axis with at least one pivot having the shape of a first cone having a first predefined solid angle, the vertex of the first cone being rounded and having a first predefined radius of curvature.
  • the mobile is remarkable in that the first radius of curvature is included in an interval going from 0.2 ⁇ m to 50 ⁇ m.
  • the first radius of curvature is within an interval ranging from 0.2 ⁇ m to 35 ⁇ m.
  • the first radius of curvature is within an interval ranging from 0.2 ⁇ m to 25 ⁇ m.
  • the first radius of curvature is within an interval ranging from 0.2 to 15 ⁇ m.
  • a particular shape of the rotary wheel set is defined in claim 17, in which the apex of the first cone of the pivot is cut to form a third circular cone, presenting a third solid angle greater than the first solid angle.
  • the third solid angle is substantially equal to the second angle of the counter-pivot.
  • the invention also relates to a watch movement comprising a plate and at least one bridge, said plate and/or the bridge comprising an orifice.
  • the movement is remarkable in that it comprises a bearing according to the invention inserted in the orifice and a rotating mobile according to the invention.
  • a bearing and an axle of a rotary wheel set will be described according to two embodiments, the same numbers being used to designate identical objects.
  • the bearing is used to maintain an axis of a rotating mobile, for example a pendulum axis, by allowing it to perform rotations around its axis.
  • the watch movement generally comprises a plate and at least one bridge, not shown in the figures, said plate and/or the bridge comprising an orifice, the movement further comprising a rotating wheel set and a bearing inserted in the orifice.
  • the picture 3 shows part 15 of a watch movement comprising two bearings 18, 20 and an axis 16 of a balance held at each end by two bearings 18, 20.
  • the axis 16 comprises a pivot 17 at each end, the pivots being formed in a hard material, preferably ruby.
  • Each bearing 18, 20 comprises a cylindrical bearing block 13 provided with a housing 14, a counter-pivot 22 arranged in the housing 14, and an opening 19 made in one face of the bearing 18, 20, the opening 19 leaving a passage for inserting the pivot 17 in the bearing as far as the counter-pivot 22.
  • the counter-pivot 22 comprises a main body provided with a cavity configured to receive the pivot 17 of the axis of the rotary wheel set. The pivots 17 of the shaft 16 are inserted into the housing 14, the shaft 16 being held while being able to rotate to allow the movement of the rotating mobile.
  • the two bearings 18, 20 are shock absorbers, and further comprise an elastic support 21 of the counter-pivot 22 to absorb shocks and prevent the axis 16 from breaking.
  • An elastic support 21, represented on the figure 4 is for example a flat spring with axial and radial deformation on which the counter-pivot 22 is assembled.
  • the elastic support 21 is fitted into the housing 14 of the bearing block 13 and it maintains the counter-pivot 22 in suspension in the housing 14.
  • the elastic support 21 has the shape of a spiral with several strands 25, here three, each strand 25 connecting a rigid central ring 24 to a rigid peripheral ring 23.
  • the peripheral ring 23 is fitted into the housing 14 of the bearing block 13 and held by one or more internal faces of the bearing block 13 of the picture 3 .
  • the counter-pivot 22 is fitted into the central ring 24 of the elastic support 21.
  • the material of the elastic support and its thickness is chosen to allow its deformation by a strong force, for example following an impact which can generate a force of 100G or 200G, one G being the force of earth's attraction due to gravity.
  • the pivot 17 has the shape of a substantially circular first cone 26 having a first solid angle 31.
  • the solid angle 31 is the angle formed inside the cone by its outer wall.
  • the vertex 29 of the first cone 26 is also rounded with a first predefined radius of curvature to allow rotation of the pivot 17.
  • the first radius of curvature is included in an interval ranging for example from 0.2 ⁇ m to 40 ⁇ m, or even 0.2 ⁇ m to 25 ⁇ m, preferably from 0.2 ⁇ m to 15 ⁇ m. On the picture 3 , the first radius of curvature is equal to 10 ⁇ m.
  • the cavity of the counter-pivot 22 has the shape of a second cone 28 having a second solid angle 32 at the apex.
  • second solid angle 32 is greater than first solid angle 31 of first cone 26. , or even 80 to 100°.
  • the second solid angle 32 is substantially equal to 90° on the picture 3 , because it is the angle which makes it possible to have a substantially equal friction between the different positions of the axis with respect to the direction of gravity, as explained previously.
  • the apex 27 of the second cone 28 is also rounded and has a second predefined radius of curvature. The curvatures of the vertices 27, 29 of the two cones 26, 28 facilitate the rotation of the pivot 17 in the counter-pivot 22.
  • the second radius of curvature 27 of the second cone 28 of the counter-pivot 22 is less than the first radius of curvature 29 of the first cone 26 of the pivot 19.
  • the second radius of curvature is for example less than 40 ⁇ m, or less than 30 ⁇ m, or even less than 20 ⁇ m, or even less than 10 ⁇ m.
  • the second radius of curvature is preferably at least equal to 0.1 ⁇ m, or even greater than 1 ⁇ m.
  • the second radius of curvature is equal to 4 ⁇ m, while the first radius of curvature is 10 ⁇ m.
  • Such radii of curvature improve the centering of the pivot 17 in the cavity and further avoid the risk of the axis being off-centered between the bearings 22.
  • the second radius of curvature of the counter-pivot is equal to 10 ⁇ m, while the first radius of curvature is 15 ⁇ m.
  • the counter-pivot 22 is the same as that of the first embodiment, but the pivot 30 is different.
  • the vertex 40 of the first cone 33 of the pivot 30 is recut to form a third circular cone 35, having a third solid angle 42 substantially equal to the second solid angle 32 of the second cone 28 of the counter-pivot 22.
  • the second solid angle 32 and the third solid angle 42 are 90°.
  • the third cone 35 is restricted around the vertex 40 of the pivot 30.
  • the third cone 35 has an average diameter 37 of 29 ⁇ m and a lateral radius 38 of 21 ⁇ m, while the height of the first cone is for example 500 ⁇ m.
  • the first cone 33 forms the body of the pivot 30, but it is truncated at its apex by the third cone 35 whose solid angle 42 is different to adapt to the cavity of the counter-pivot 22.
  • the third cone 35 has the same rounded apex with the same radius of curvature as the first cone 26 of the first mode of realization of the figure 5 , to keep the same advantages.
  • the connection between the pivot 30 and the counter-pivot 22 is also improved by slightly increasing the friction zone, to avoid premature wear of the pivot 30 and the counter-pivot 22.
  • the material used to make the body of the tailstock must be specifically chosen. Indeed, the materials conventionally used to manufacture counter-pivots are too hard to obtain such a radius of curvature.
  • the machining of a ruby or steel material allows to obtain second radii of curvature in the cavity of the counter-pivot of more than 40 ⁇ m, because the tool used to hollow out the cavity must have a thickness enough not to break during the machining of the main body of the counter-pivot.
  • the main body of the counter-pivot is formed of a material to be chosen from the following list: an at least partially amorphous metal alloy, an electro-formed material, an synthetic, or a composite material.
  • the main body is formed from an at least partially amorphous metal alloy comprising a metal element.
  • This metallic element can be a conventional metallic element of the iron, nickel, zirconium, titanium or aluminum type or a precious metallic element such as gold, platinum, palladium, rhenium, ruthenium, rhodium, silver, iridium or osmium.
  • the material is able to solidify at least partially in the amorphous phase, that is to say that it is subjected to a rise in temperature above its melting temperature allowing it to locally lose any crystalline structure, said rise being followed by cooling to a temperature below its glass transition temperature allowing it to become at least partially amorphous.
  • the amorphous metal is for example chosen from the following compositions: Zr58.5Cu15.6Ni12.8Al10.3Nb2.8 based on Zirconium (Zr), Pd43Cu27Ni10P20 based on Palladium (Pd), or Pt57.5Cu14.7Ni5.3P22. 5 based on Platinum (Pt).
  • Other compositions of amorphous metals can of course be used, and the invention is in no way limited to these examples.
  • the cavity is then obtained by a hot deformation process.
  • the amorphous metal is heated to a temperature above its glass transition temperature, which considerably reduces its viscosity and therefore makes it possible to faithfully replicate the tool on which it is deformed.
  • the tool will have been previously machined to have a conical shape whose radius of curvature is substantially equal to the second desired radius of curvature.
  • the second radius of curvature is smaller than the first radius of curvature.
  • the amorphous metal can be ceramized to improve the tribological properties and thus harden the surface of the main body, in particular in the second cone of the cavity.
  • the surface treatment consists in forming a layer of ceramic nature on this surface.
  • routes chemical, thermal, plasma, etc.
  • the main body of the counter-pivot is formed by an electro-formed material, for example of the type Ni, Ni-P, Ni-Co, Pd, Pd-Co, Pt , Au750, Au9ct, or others.
  • the galvanic growth is operated on a corresponding imprint.
  • the imprint has the shape of a convex cone whose dimensions correspond to those of the second cone.
  • a third embodiment of the formation of the main body consists in forming the main body in a synthetic or composite material, such as a polymer material or a filled polymer material.
  • the polymer is chosen from the group comprising polyoxymethylene, polyamide, polyetheretherketone, polyphenylene sulfide.
  • the filler can be, for example, particles of PTFE or of graphite, making it possible to modify the tribological properties of the base polymer material.
  • Other types of fillers can be envisaged, such as for example silicon oxide nanoparticles or other ceramics to mechanically reinforce the base polymer. It is also of course possible to combine several types of fillers with a given polymer.
  • the material is molded on an imprint corresponding to the desired shape.
  • the imprint has the shape of a convex cone whose dimensions correspond to those of the second cone. The body is obtained by molding this material on the impression.
  • the main body of the counter-pivot and the elastic support are formed from the same piece.
  • the main body and the elastic support are made of the same material, for example of amorphous metal, to form a single piece.
  • the main body of the counter-pivot is molded onto the elastic support.
  • the elastic support is formed beforehand by a LIGA type lithography, electrodeposition and forming process (for “Rôntgenlithographie, Galvanoformung, Abformung” in German).

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Sliding-Contact Bearings (AREA)
EP18214830.4A 2018-12-20 2018-12-20 Palier, notamment amortisseur de choc, et mobile tournant d'un mouvement horloger Active EP3671368B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP18214830.4A EP3671368B1 (fr) 2018-12-20 2018-12-20 Palier, notamment amortisseur de choc, et mobile tournant d'un mouvement horloger
JP2019224233A JP2020101539A (ja) 2018-12-20 2019-12-12 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
US16/713,079 US11592784B2 (en) 2018-12-20 2019-12-13 Bearing, particularly a shock absorber, and rotary wheel set of a timepiece movement
CN201911329064.5A CN111352332B (zh) 2018-12-20 2019-12-20 时计机芯的轴承、尤其是减震器和旋转轮组
JP2022149179A JP7411040B2 (ja) 2018-12-20 2022-09-20 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

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18214830.4A EP3671368B1 (fr) 2018-12-20 2018-12-20 Palier, notamment amortisseur de choc, et mobile tournant d'un mouvement horloger

Publications (2)

Publication Number Publication Date
EP3671368A1 EP3671368A1 (fr) 2020-06-24
EP3671368B1 true EP3671368B1 (fr) 2022-11-23

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EP18214830.4A Active EP3671368B1 (fr) 2018-12-20 2018-12-20 Palier, notamment amortisseur de choc, et mobile tournant d'un mouvement horloger

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Country Link
US (1) US11592784B2 (zh)
EP (1) EP3671368B1 (zh)
JP (2) JP2020101539A (zh)
CN (1) CN111352332B (zh)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3929666A1 (fr) * 2020-06-26 2021-12-29 ETA SA Manufacture Horlogère Suisse Système mobile tournant d'un mouvement horloger
EP3929667A1 (fr) * 2020-06-26 2021-12-29 ETA SA Manufacture Horlogère Suisse Système mobile tournant d'un mouvement horloger

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WO2011161139A1 (fr) 2010-06-22 2011-12-29 The Swatch Group Research And Development Ltd Systeme antichoc de piece d'horlogerie
JP6231264B2 (ja) * 2011-07-29 2017-11-15 ロレックス・ソシエテ・アノニムＲｏｌｅｘ Ｓａ 最適化された枢動支持（ｐｉｖｏｔｉｎｇ）を有するテンプ輪（ｂａｌａｎｃｅｗｈｅｅｌ）組立体
JP2013088179A (ja) 2011-10-14 2013-05-13 Seiko Instruments Inc てんぷの耐振軸受機構、これを備えたてんぷ及びこれを備えた時計
CH705861A2 (fr) 2011-12-12 2013-06-14 Swatch Group Res & Dev Ltd Palier antichoc pour pièce d'horlogerie.
JP2013170821A (ja) * 2012-02-17 2013-09-02 Seiko Instruments Inc 時計用軸受ユニット、ムーブメント及び時計
EP2781972B1 (fr) * 2013-03-19 2018-08-01 Nivarox-FAR S.A. Pivot pour mécanisme d'horlogerie
EP2884348A1 (fr) * 2013-12-11 2015-06-17 The Swatch Group Research and Development Ltd. Système antichoc bi-matiere pour piece d'horlogerie
CN203930351U (zh) 2013-12-20 2014-11-05 Eta瑞士钟表制造股份有限公司 减震轴承、包括该减震轴承的机芯及包括该机芯的钟表
EP2952971B1 (fr) * 2014-06-05 2016-10-12 Nivarox-FAR S.A. Ancre pour mécanisme d'échappement d'un mouvement de montre
EP2990883A1 (fr) 2014-08-29 2016-03-02 Nivarox-FAR S.A. Ensemble balancier-spiral d'horlogerie
EP3258325B1 (fr) 2016-06-13 2019-10-30 Rolex Sa Axe horloger
EP3291026B1 (fr) 2016-08-30 2020-01-01 ETA SA Manufacture Horlogère Suisse Palier amortisseur de chocs pour pièce d'horlogerie
EP3382472A1 (fr) * 2017-03-30 2018-10-03 Rolex Sa Palier de guidage d'un pivot de balancier de pièce d'horlogerie

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US11592784B2 (en) 2023-02-28
JP7411040B2 (ja) 2024-01-10
JP2020101539A (ja) 2020-07-02
EP3671368A1 (fr) 2020-06-24
US20200201259A1 (en) 2020-06-25
CN111352332B (zh) 2022-02-25
CN111352332A (zh) 2020-06-30
JP2022171887A (ja) 2022-11-11

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