EP3929666A1 - Mobiles drehsystem eines uhrwerks - Google Patents

Mobiles drehsystem eines uhrwerks Download PDF

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Publication number
EP3929666A1
EP3929666A1 EP20182650.0A EP20182650A EP3929666A1 EP 3929666 A1 EP3929666 A1 EP 3929666A1 EP 20182650 A EP20182650 A EP 20182650A EP 3929666 A1 EP3929666 A1 EP 3929666A1
Authority
EP
European Patent Office
Prior art keywords
pivot
cavity
contact
axis
mobile system
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
EP20182650.0A
Other languages
English (en)
French (fr)
Inventor
M. Jean-Luc HELFER
M. Dominique LECHOT
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.)
ETA SA Manufacture Horlogere Suisse
Original Assignee
ETA SA Manufacture Horlogere Suisse
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 ETA SA Manufacture Horlogere Suisse filed Critical ETA SA Manufacture Horlogere Suisse
Priority to EP20182650.0A priority Critical patent/EP3929666A1/de
Priority to US17/341,536 priority patent/US11886151B2/en
Priority to JP2021099958A priority patent/JP7266637B2/ja
Priority to KR1020210081070A priority patent/KR20220000835A/ko
Priority to CN202110708425.8A priority patent/CN113848692B/zh
Publication of EP3929666A1 publication Critical patent/EP3929666A1/de
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
    • G04B31/06—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
    • 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
    • G04B31/008—Jewel bearings
    • G04B31/0087—Jewel bearings with jewel hole only
    • 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
    • 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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/06—Oscillators with hairsprings, e.g. balance
    • G04B17/063—Balance construction
    • 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
    • G04B31/004—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor characterised by the material used
    • G04B31/008—Jewel 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
    • G04B31/008—Jewel bearings
    • G04B31/0082—Jewel 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
    • G04B33/00—Calibers

Definitions

  • the present invention relates to a rotating mobile system of a watch movement, in particular a resonator mechanism.
  • the invention also relates to a watch movement provided with such a mobile system.
  • the axes of the rotating wheels In watch movements, the axes of the rotating wheels generally have pivots at their ends, which rotate in bearings mounted in the plate or in bridges of a watch movement.
  • the bearings For certain mobiles, in particular the balance, 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 absorbing bearing 1 is represented by the figure 1 .
  • a domed olive stone 2 is driven into a bearing support 3 commonly called chaton, on which is mounted a counter-pivot stone 4.
  • the chaton 3 is held in abutment 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 chaton 3 further comprises a conical outer wall arranged in correspondence with a conical inner wall disposed at the periphery of the bottom of the bearing block 5.
  • the kitten has an outer wall having a convex surface, that is to say convex.
  • the friction torque on the axis due to the weight of the mobile varies as a function of the orientation of the mobile with respect to the direction of gravity.
  • These variations in the friction torque can in particular cause a variation in the amplitude of oscillation for the balance.
  • the weight of the mobile rests on the stones with holes, and the friction force generated by the weight has a lever arm relative to the axis, which is equal to the radius of the pivot.
  • the axis of the mobile is parallel to the direction of gravity, it is the end of the pivot on which the weight of the mobile rests.
  • the bearing comprises a counter-pivot 7 of the crapaudine type, comprising a cavity 8 for receiving a pivot 12 of the axis 9 of the rotating mobile.
  • a cavity may have the shape of a pyramid, the bottom of the cavity being formed by the top 11 of the pyramid.
  • the pivot 12 is tapered to fit into the cavity 8, but the solid angle of the pivot 12 is smaller than that of the cavity 8.
  • An aim of the invention is therefore to provide a mobile system of a watch movement which avoids the aforementioned problem.
  • the invention relates to a mobile system comprising a rotating mobile, for example a balance, a first and a second bearing, in particular shock absorbers, for a first and a second pivot of the axis of the rotating mobile, the system comprising a center of mass in a position of its axis, the first bearing comprising a counter-pivot comprising a main body provided with a pyramidal cavity configured to receive the first pivot of the axis of the rotating mobile, the first pivot being able to cooperate with the cavity of the counter-pivot in order to be able to rotate in the cavity, at least one contact zone between the first pivot and a face being generated, the normal to the contact zone or zones forming a contact angle relative to the plane perpendicular to the pivot axis.
  • a rotating mobile for example a balance
  • a first and a second bearing in particular shock absorbers
  • the system is remarkable in that the contact angle is less than 45 °, preferably less than or equal to 30 °, or even less than or equal to arctan 1 2 , which is substantially equal to 26.6 °.
  • the variation in friction between the horizontal and vertical positions with respect to gravity is reduced.
  • a contact angle less than or equal to 45 °, preferably less than or equal to 30 °, or even less than or equal arctan 1 2
  • the friction torque due to the weight in contact between the pivots and the cavities of the bearings is substantially the same regardless of the direction of gravity.
  • such an angle makes it possible to compensate for the variations in contact force due to the change in orientation with respect to gravity by lever arms of the different friction force on the two bearings.
  • this configuration of the counter-pivot makes it possible to keep a small variation in the friction torque of the pivots inside the counter-pivots, whatever the position of the axis with respect to the direction of gravity, which is by important example for a balance axis of a movement of a timepiece.
  • the pyramid shape of the cavity, as well as that of the pivot minimize the difference in friction torque between the different positions of the axis with respect to the direction of gravity.
  • the second bearing cooperates with the second pivot to allow the rotating mobile device to rotate about its axis
  • the second bearing comprising a second pyramidal cavity comprising at least three faces
  • the first contact angle ( ⁇ h ) is less than or equal to arctan 1 2 and the second contact angle ( ⁇ b ) is greater than or equal to arctan 1 2 .
  • the cavity comprises three or four faces.
  • the faces are at least partly concave or convex.
  • the first pivot the first pivot has a conical shape.
  • the two minimum contact angles are equal.
  • the end of the pivot is defined by the intersection between the normal in contact and the axis of the pivot.
  • the pivots have a rounded end.
  • the rounded ends of the two pivots have identical radii.
  • the invention also relates to a watch movement comprising a plate and at least one bridge, said plate and / or the bridge comprising such a mobile system.
  • the bearing serves to maintain an axis of a rotating mobile, for example a balance 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 mobile and a bearing inserted in the orifice.
  • the figures 3 and 4 show a rotating mobile system provided with a balance 13 and a spiral spring 14, the balance 13 comprising an axis 16.
  • the axis 16 comprises a pivot 15, 17 at each end.
  • Each bearing 18, 20 comprises a cylindrical bearing block 83 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 15, 17 in the bearing up to the counter-pivot 22.
  • the counter-pivot 22 is mounted on a bearing support 23 and comprises a cylindrical main body provided with a cavity configured to receive the pivot 15, 17 of the axis 16 of the rotating mobile.
  • the pivots 15, 17 of the axis 16 are inserted into the housing 14, the axis 16 being maintained while being able to rotate to allow the movement of the rotating mobile.
  • the two bearings 18, 20 are shock absorbers, and further include an elastic support 21 of the counter-pivot 22 to absorb shocks and prevent the pin 16 from breaking.
  • An elastic support 21 is for example a flat spring with axial 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 the housing 14. Thus, when the timepiece is subjected to a violent impact, the elastic support 21 absorbs the shock and preserves the impact. axis 16 of the rotating mobile.
  • the pivot 15, 17 has the shape of a first substantially circular cone 26 having a first opening angle 31.
  • the opening angle 31 is the half-angle formed inside the cone by its outer wall.
  • the cavity 28 of the counter-pivot 22 has a pyramidal shape provided with several faces 24.
  • the pyramidal cavity 28 has four faces 24.
  • the pyramidal cavity has three faces. In other embodiments the number of faces of the pyramid may be greater (5, 6, etc.).
  • the bottom of the cavity 28 is flat truncated, but it can be pointed or rounded truncated, according to other embodiments.
  • the cavity 28 has a second opening angle 32 at the top. So that the pivot 15, 17 can rotate in the cavity 28, the second opening angle 32 is greater than the first opening angle 31 of the first cone 26.
  • the faces 24 of the cavity 28 have the same orientation with respect to to the pivot axis. In other words, the half-opening angle of the cavity 28 is identical for all the faces.
  • the pivot 15, 17 and the faces of the cavity 28 cooperate to form at least one contact zone 29.
  • the pivot is in contact with all the faces 24 of the cavity 28, thus creating a contact zone with each face. 24, that is to say four for the first embodiment or three for the second embodiment.
  • a contact zone 29 is defined by the part of the face 24 of the cone pyramid in contact with the pivot 15, 17.
  • the normals to each contact zone 29 are straight lines perpendicular to each contact zone 29.
  • the normals form a angle, called the contact angle, with respect to the plane perpendicular to the axis of the pivot.
  • the normal corresponds to the line perpendicular to the face of the cavity 28.
  • the contact angle is equivalent to the half-opening angle of the pyramid of the cavity 28.
  • the contact angle is less than or equal to 45 °, preferably less than or equal to 30 °, or even less than or equal to arctan 1 2 .
  • N is the number of faces of the two pyramids
  • BH is the distance between the ends of the two pivots
  • GH is the distance between the end of the first pivot (17) in contact with the first bearing (18) and the center of mass (G) of the balance
  • GB is the distance between the end of the second pivot (15) in contact with the second bearing (20) and the center of mass (G) of the balance 2.
  • the first cones of the two pivots 15, 17 can have different opening angles. But if they meet this relationship, the variation in friction between the vertical and horizontal positions is reduced compared to other geometries of pivots and cavities.
  • the graph of the figure 8 shows the optimum contact angles for the two bearings and pivots for each position of the center of mass on the balance axis.
  • the center of mass is one third of the length of the axis of a first pivot
  • the optimum contact angle of that first pivot is 45 °
  • the second pivot has a contact angle optimal equal to 30 °.
  • the cavities have an opening angle equal to 90 °
  • the other pyramid of opening angle equal to 60 °.
  • Each optimum contact angle is within a range of 20 ° to 90 °.
  • the smallest contact angle is that of the pivot closest to the center of mass.
  • the graph of the figure 9 shows the difference in the optimal radii of the ends of the two pivots as a function of the position of the center of mass.
  • the radii are preferably equal for both ends.
  • the graph of the figure 10 shows the optimum contact angles for the two bearings and pivots for each position of the center of mass on the balance axis.
  • the desirable opening angle for cones is about 90 °.
  • the contact angles of the two bearing-pivot pairs are different. It is thus noted that there is always one of the two contact angles with a value less than or substantially equal to 45 ° and the other angle with a value greater than or substantially equal to 45 °.
  • the optimum contact angle of this first pivot is substantially 65 °, while the second pivot has an angle of optimum contact substantially equal to 35 °.
  • Each optimum contact angle is within a range of 27 ° to 90 °.
  • the smallest contact angle is that of the pivot closest to the center of mass.
  • the graph of the figure 11 shows the difference in the optimal radii of the ends of the two pivots as a function of the position of the center of mass.
  • the radii are preferably equal for both ends.
  • the graphics of figures 12 and 13 show how the optimum angles and the variation ⁇ vary as a function of the relative position of the center of mass for the first embodiment with four faces.
  • the graphics of figures 14 and 15 show how the optimal angles and the variation ⁇ vary as a function of the relative position of the center of mass for the second three-sided embodiment.
  • there is always one of the two angles with a value less than or equal to arctan 1 2 26 , 6 approximately, and the other angle with a value greater than or equal to arctan 1 2 .
  • FIG. 16 Examples of variation of the friction torque as a function of the orientation ⁇ are shown in FIG. 16 for the first embodiment, and in FIG. 17 for the second embodiment.
  • the curves are symmetrical for a value greater than 90 °.
  • the point of symmetry of the curve is offset with respect to 90 °.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Sliding-Contact Bearings (AREA)
  • Electromechanical Clocks (AREA)
  • Rolling Contact Bearings (AREA)
  • Telephone Set Structure (AREA)
EP20182650.0A 2020-06-26 2020-06-26 Mobiles drehsystem eines uhrwerks Pending EP3929666A1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP20182650.0A EP3929666A1 (de) 2020-06-26 2020-06-26 Mobiles drehsystem eines uhrwerks
US17/341,536 US11886151B2 (en) 2020-06-26 2021-06-08 Rotary wheel set system of a horological movement
JP2021099958A JP7266637B2 (ja) 2020-06-26 2021-06-16 計時器用ムーブメントのロータリー車セットシステム
KR1020210081070A KR20220000835A (ko) 2020-06-26 2021-06-22 측시 무브먼트의 회전 휠 세트 시스템
CN202110708425.8A CN113848692B (zh) 2020-06-26 2021-06-25 钟表机芯的旋转轮组***

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20182650.0A EP3929666A1 (de) 2020-06-26 2020-06-26 Mobiles drehsystem eines uhrwerks

Publications (1)

Publication Number Publication Date
EP3929666A1 true EP3929666A1 (de) 2021-12-29

Family

ID=71266363

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20182650.0A Pending EP3929666A1 (de) 2020-06-26 2020-06-26 Mobiles drehsystem eines uhrwerks

Country Status (5)

Country Link
US (1) US11886151B2 (de)
EP (1) EP3929666A1 (de)
JP (1) JP7266637B2 (de)
KR (1) KR20220000835A (de)
CN (1) CN113848692B (de)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1333053A (fr) * 1962-09-04 1963-07-19 Perfectionnement aux dispositifs de pivotement d'un arbre de balancier pour mouvement de montre
EP1986059A1 (de) * 2007-04-26 2008-10-29 ETA SA Manufacture Horlogère Suisse Schwenkenvorrichtung einer Welle in einer Uhr
WO2013087173A1 (fr) * 2011-12-12 2013-06-20 The Swatch Group Research And Development Ltd Palier antichoc pour piece d'horlogerie

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1907792A (en) * 1929-03-01 1933-05-09 Western Clock Co Bearing
US3080703A (en) * 1961-01-12 1963-03-12 United States Time Corp Watch lubrication system
JPS484508Y1 (de) * 1968-10-22 1973-02-05
NL7107454A (de) 1971-05-29 1972-12-01
CH495673A4 (fr) * 1973-04-06 1976-10-29 Seitz Sa Dispositif de pivotement de l'ace d'un mobile d'horlogerie
JP5455115B2 (ja) * 2009-10-07 2014-03-26 セイコーインスツル株式会社 時計用軸受、ムーブメントおよび携帯用時計
JP5657106B2 (ja) * 2010-06-22 2015-01-21 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 時計の衝撃吸収軸受
EP2757426B1 (de) * 2013-01-22 2017-11-08 Montres Breguet SA Führungsvorrichtung für Uhrwerkswelle
EP2884348A1 (de) * 2013-12-11 2015-06-17 The Swatch Group Research and Development Ltd. Stoßsicheres System aus zwei verschiedenen Materialien für Uhr
EP3671368B1 (de) * 2018-12-20 2022-11-23 The Swatch Group Research and Development Ltd Lager, insbesondere zur stossdämpfung, und drehteil eines uhrwerks

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1333053A (fr) * 1962-09-04 1963-07-19 Perfectionnement aux dispositifs de pivotement d'un arbre de balancier pour mouvement de montre
EP1986059A1 (de) * 2007-04-26 2008-10-29 ETA SA Manufacture Horlogère Suisse Schwenkenvorrichtung einer Welle in einer Uhr
WO2013087173A1 (fr) * 2011-12-12 2013-06-20 The Swatch Group Research And Development Ltd Palier antichoc pour piece d'horlogerie

Also Published As

Publication number Publication date
US11886151B2 (en) 2024-01-30
CN113848692A (zh) 2021-12-28
KR20220000835A (ko) 2022-01-04
CN113848692B (zh) 2023-11-17
US20210405587A1 (en) 2021-12-30
JP7266637B2 (ja) 2023-04-28
JP2022008178A (ja) 2022-01-13

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