EP2015147B2 - Stoßdämpfer-Gleitlager für eine Uhr - Google Patents

Stoßdämpfer-Gleitlager für eine Uhr Download PDF

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Publication number
EP2015147B2
EP2015147B2 EP08160043.9A EP08160043A EP2015147B2 EP 2015147 B2 EP2015147 B2 EP 2015147B2 EP 08160043 A EP08160043 A EP 08160043A EP 2015147 B2 EP2015147 B2 EP 2015147B2
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EP
European Patent Office
Prior art keywords
central portion
pivot
arms
annular
hole
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.)
Not-in-force
Application number
EP08160043.9A
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English (en)
French (fr)
Other versions
EP2015147A2 (de
EP2015147B1 (de
EP2015147A3 (de
Inventor
Michel Vermot
Loïc Pellation
Pierre Gygax
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.)
Manufacture et Fabrique de Montres et Chronometres Ulysse Nardin Le Locle SA
Original Assignee
Manufacture et Fabrique de Montres et Chronometres Ulysse Nardin Le Locle SA
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Application filed by Manufacture et Fabrique de Montres et Chronometres Ulysse Nardin Le Locle SA filed Critical Manufacture et Fabrique de Montres et Chronometres Ulysse Nardin Le Locle SA
Publication of EP2015147A2 publication Critical patent/EP2015147A2/de
Publication of EP2015147A3 publication Critical patent/EP2015147A3/de
Application granted granted Critical
Publication of EP2015147B1 publication Critical patent/EP2015147B1/de
Publication of EP2015147B2 publication Critical patent/EP2015147B2/de
Not-in-force 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
    • G04B31/00—Bearings; Point suspensions or counter-point suspensions; Pivot bearings; Single parts therefor
    • G04B31/02—Shock-damping bearings

Definitions

  • the present invention relates to bearings for timepieces, and more particularly of the type for damping shocks.
  • Such bearings are, most frequently, used to ensure the pivoting of the rockers. Indeed, the latter are provided with small diameter pivots, that is to say, delicate. Since, moreover, the mass of the balance is relatively large, the risk is high that a pivot breaks under the effect of a shock.
  • shock absorbing bearings There are many types of shock absorbing bearings. The most frequently used include a body provided with positioning and sliding surfaces, a pierced stone and a counter-pivot stone together forming a pivot member, these stones being disposed in the body and positioned on the positioning and sliding surfaces. A spring maintains the stones in the rest position, while allowing them to move within a certain limit under the effect of a shock, the axis of the balance then arriving against stops.
  • Such bearings have, for example been sold under the trademark Incabloc ®.
  • Shock absorbing bearings are also known in which the elastic members and the pivot members form a whole. They have the advantage of being less expensive.
  • the document US 3,942,848 describes a shock-absorbing bearing comprising an annular body intended to be driven in a bridge or a plate.
  • a spring formed to define a conical housing is attached to the body.
  • This housing forms a truss inside which a conical pivot of the balance comes to engage.
  • the pivoting conditions are unfavorable, metal-to-metal pivoting generating significant friction.
  • a bearing type crapaudine cooperating with a conical pivot is poorly suited for a timepiece quality, the positioning of the balance is not very accurate.
  • the document CH 235 315 proposes a similar device with the same disadvantages.
  • the body is cup-shaped pierced in its bottom, and provided with a rim and a conical portion.
  • the elastic and pivoting members are made of a piece made of self-lubricating plastic.
  • the central portion forms a cylindrical housing in which can engage a pendulum pivot. It is further shaped to cooperate with the conical portion, so as to ensure the centering of the central portion.
  • Arms, forming the elastic member, start from the central part and engage under the rim.
  • the diameter of the rocker shafts must be relatively large, since the self-lubricating plastics do not support very high specific pressures.
  • shock-absorbing bearings comprising a central piece provided with a stone and surrounded by a rosette formed in a plate of rigid elastic material.
  • the rosette consists of springs extending radially, their central end cooperating with the central part.
  • the present invention is intended to provide a shock absorbing bearing ensuring a good positioning of the balance and a good protection of the axis. It relates more particularly to a shock absorber bearing for a timepiece according to claim 1.
  • the material used is of monocrystalline type, it is possible to machine it by chemical processes, in particular photo-lithographic methods to ensure substantially vertical walls, which is desirable to ensure good consistency in industrial production.
  • the bearing further comprises an annular housing part, arranged to be driven into a hole in the frame of the timepiece and to receive and fix the ends of the arms. elastic.
  • the annular piece has a truncated cone wall against which the pivot member bears in its outer part. In this way, it is possible to make the elastic arms more rigid and even to define a pre-arming of these arms.
  • the bearing further comprises first and second annular pieces arranged to be driven into a hole in the frame of the timepiece, the pivoting member being interposed between the two annular pieces.
  • a simple structure can be obtained with a bearing whose pivoting member comprises a solid annular portion and at least two resilient arms, said arms being secured by their outer end of said solid annular portion.
  • the bearing comprises elastic portions with annular orientation, integral with the outer end of said arms.
  • the elastic arms may have various shapes. However, a spiral structure seems to have advantages of simplicity and homogeneity of the structure, while providing a small footprint.
  • FIG. 1 to 4 A first embodiment is shown in Figures 1 to 4 .
  • the figures 1 and 2 illustrate a portion of timepiece provided with bearings according to the invention, respectively seen in section and from above, while the Figures 3 and 4 show a portion of a bearing viewed in perspective, respectively from above and from below.
  • the timepiece partially represented in figures 1 and 2 comprises a frame comprising a plate 10 and a balance bridge 12, bearings 14 and 16 respectively mounted in holes in the plate 10 and the bridge 12.
  • the bearing 14 comprises two annular pieces 26 and 27, the piece 27 being in the form of a cup pierced at its center with a hole 28, and a pivoting member 30 interposed between the two annular pieces 26 and 27.
  • the pivoting member 30 is thus maintained radially by the walls of the hole made in the plate 10 and axially on either side by the annular parts 26 and 27.
  • the bearing 16 comprises an annular piece 31 in the form of a cup, which defines a housing having an inner cylindrical wall 32 and a flat bearing surface 34 defined in the bottom of the cup. It is pierced with a central hole 35. It further comprises a pivoting member 30 disposed in the housing formed by the cylindrical wall 32 and the bearing surface 34. This member 30 is advantageously bonded to the annular piece.
  • a truncated cone portion 36 forms the free end of the cup. It holds and positions a mobile bolt carrier 38.
  • the pivoting members 30, better visible on the Figures 3 and 4 are in the form of pellets comprising a solid annular portion 30a, a central portion 30b provided with a cylindrical blind hole 30c and three spirally wound elastic arms 30d connecting the central portion 30b to the annular portion 30a. They are mounted one in the annular piece 31, the other in the hole of the plate 10, held radially by the wall of the hole and axially by the annular pieces 26 and 27.
  • the blind hole 30c extends over approximately half the thickness of the central portion 30b. Its diameter is chosen so that the pivot 24 which is engaged can rotate freely with a minimum of frolicking. The depth of the hole 30c is approximately equal to twice its diameter.
  • the rocker 18 is pivotally mounted by engagement of the pivots 24 in the blind holes 30c.
  • the tigers 22 are engaged in the holes 28 and 35.
  • the balance 18 In case of impact, the balance 18 is subjected to a force proportional to the acceleration. This force is transmitted to the bearings by means of the pivots 24. It has the effect of deforming the elastic arms 30d until the axis 20 comes to bear, by the rods 22, against the wall of the holes 28 and 35 The balance is then blocked, but by a part of its axis having dimensions much larger than those of the pivots 24.
  • the elastic arms 30d are dimensioned from in such a way that the spindle 20 comes into contact with the annular pieces 27 and 31 with its spurs 22 when the acceleration reaches approximately 500 g.
  • the diagram of the figure 5 shows how the displacement of the central organ varies according to the acceleration undergone. As shown in this figure, at first, there is proportionality between the acceleration and the displacement, then, for an acceleration of about 500 g, one and / or the other of the tigerons 22 comes into contact with the parts Annular 27 or 31. The balance is then blocked.
  • FIGS. 6, 7 and 8 represent a second embodiment of the invention.
  • the figure 6 shows a part of the timepiece provided with such a bearing seen from above while the Figures 7 and 8 show a part of this bearing seen in perspective, respectively from above and from below.
  • the same parts bear the same references as those appearing on the Figures 1 to 4 .
  • This embodiment differs from that previously described by the structure of the pivot members 30. More specifically, the annular portion 30a is replaced by three annular 30e shoes, each connected to an elastic arm 30d. The sole of these shoes has a diameter greater than the diameter of the hole in which the member 30 must be engaged. In this way, during installation, the elastic arms 30d are radially armed, which has the effect of improving the centering of the hole 30c.
  • FIG. 9 A variant of this embodiment is shown in Figures 9 and 10 . It can be seen a pivot member 30 respectively free and disposed in the annular part 31.
  • the member 30 comprises a central portion 30b in which is formed a blind hole, as explained above, not visible in these figures, three elastic arms 30d extending from the central portion 30b outwards, two fingers 30f with an annular orientation and extending on either side of the end of each of the elastic arms 30d, and three fingers 30g extending radially from the central portion 30b outwardly.
  • the distance between the center of the central portion 30b and the free ends of the fingers 30f is greater than the inside diameter of the annular piece 31. Moreover, the distance between the center of the central portion 30b and the end arms 30d is smaller than the inside diameter of the annular part 31. In this way, when the member 30 is put in place, the fingers 30f are armed.
  • the displacement is relatively important for small impacts, the fingers 30f participating in the deformation.
  • the active length of the spring is reduced and the restoring force is increased.
  • the displacement is practically blocked when one of the fingers 30g comes into contact with the annular part 31.
  • the variation of the displacement as a function of the accelerations is represented on the figure 11 .
  • the lateral displacement (X and Y axes) is defined by the thickness of the elastic arms, while the axial displacement (Z axis) is defined by the height of these arms, while the length of the arms contributes to the definition of the one and the other of these displacements.
  • the two bearings 14 and 16 are identical and very close, in their structure, of the bearing 16 of the figure 1 .
  • the elastic arms are curved and the central portion 30b is adjacent to the drop 44, touching or not depending on the desired purpose.
  • Such a construction ensures a pre-arming, insofar as the central portion 30b touches the drop 44.
  • the bearing has a pre-winding of the springs along the three axes, facilitating the return of the central portion 30b in its rest position. If the central portion 30b does not touch the drop 44, the deformation caused by the engagement of the member 30 against the wall 42 of frustoconical stiffens the elastic arms 30d.
  • the pivoting members 30 comprise two plates 301 and 302.
  • the plates 301 comprise a solid annular portion 301a, a central portion 301b provided with a hole 301c passing right through them and spirally wound elastic arms 301 connecting the central portion 301b to the annular portion 301a.
  • the central portion 301c is thinner than the rest of the plate 301, thus forming a recess 301e.
  • the plates 302 comprise a solid annular portion 302a, a solid central portion 302b and spirally wound elastic arms 302d connecting the central portion 302b to the annular portion 302a.
  • the central portion 302b comprises a cylindrical protuberance 302e engaged in the recess 301 e.
  • the pivots 24 are engaged in the holes 301c and in abutment against the central portions 302b, which provide a counter pivot function.
  • the plates 301 and 302 are mounted on the annular pieces 31 in a manner similar to the pivot member 30 described with reference to the Figures 1 to 4 however, the latter comprising two bearing surfaces and two cylindrical walls one for each of the plates 301 and 302.
  • the bearings do not include oiler. This is made possible by the fact that the steel-silicon pair has tribological characteristics such that the presence of oil is not necessary. Under certain conditions, however, it would be possible to maintain oil in the space between the bottom of the hollow 301e and the protrusion 302e.
  • pivot members 30 could be attached directly to frame members, without having to use an intermediate annular piece.
  • the latter facilitates the establishment of the bearing on the frame.
  • pivot members 30 Other materials such as diamond could also be used to manufacture the pivot members 30. It is simply necessary that the selected material is machinable by photo-lithographic processes and that they have good tribological conditions.
  • the friction should affect the mobility of the pivot member only within an acceptable limit for the refocusing of the central portion 30b.
  • the friction implies that a minimum force must be applied on the pivot to cause a displacement of the central portion 30b. In other words, a disturbance generating a force less than this minimum force, would not overcome the forces related to friction and the device would not be disturbed.
  • the figure 14 proposes an example illustrating such a friction element.
  • the central portion 30b of the pivot member 30 comprises, around the blind hole 30c, a flange 30h whose walls define a first truncated cone.
  • the annular piece 27 comprises, around the hole 28 through which the pivot 24 passes, a cup 50 whose walls define a second truncated cone.
  • the walls of the first and second truncated cones are arranged so that, when the resilient arms are in their rest position, they are flush with each other.
  • a slight prestress in the axis of pivoting supports the walls of the flange 30h against that of the cup 50.
  • the walls are substantially parallel, to avoid shocks between the two truncated cone.
  • the angle of the truncated cones may be relatively open, that is to say between about 120 and 180 degrees.
  • the value of the angle defines the friction generated between the two truncated cone and therefore the minimum force to be applied to cause a displacement of the central portion 30b.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Sliding-Contact Bearings (AREA)
  • Support Of The Bearing (AREA)

Claims (9)

  1. Stoßdämpferlager für eine Uhr, das ein Drehorgan (30; 301) aufweist, das mindestens einen elastischen Arm (30d; 301d, 302d) und einen zentralen Abschnitt (30b; 301b) umfasst, der ein Loch (30c; 301c) aufweist, in dessen Inneren ein Drehzapfen (24) bestimmt ist, im Kontakt zu sein, dadurch gekennzeichnet, dass der mindestens eine elastische Arm und der zentrale Abschnitt aus einem einzigen Teil in Plättchenform aus einem monokristallinem Material gebildet sind, dass das Drehorgan (30; 301) aus Silizium ist und dass das Loch blind ist.
  2. Stoßdämpferlager für eine Uhr, dadurch gekennzeichnet, dass es zwei übereinanderliegende Platten (301, 302), die eine innen, die andere außen, aufweist, wobei jede mit elastischen Armen (301d, 302d) und einem zentralen Abschnitt (301b, 302b) ausgestattet ist, wobei der zentrale Abschnitt (301b) der inneren Platte (301) mit einem Loch ausgestattet (301c), in dessen Inneren ein Drehzapfen bestimmt ist, im Kontakt zu sein, und die äußere Platte (302) einen Deckstein bildet, und dass die elastischen Arme (301d, 302d) und der zentrale Abschnitt (301b, 302b) jeder Platte aus einem einzigen Teil in Plättchenform aus monokristallinem Material gebildet sind.
  3. Lager nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass es ferner ein eine Aufnahme bildendes ringförmiges Teil (31, 40) aufweist, das ausgebildet ist, um in ein Loch des Gestells der Uhr eingepresst zu sein und um die Enden der Arme (30d; 301d, 302d) aufzunehmen und zu befestigen.
  4. Lager nach Anspruch 3, dadurch gekennzeichnet, dass das ringförmige Teil (40) eine kegelstumpfförmige Wand (42) aufweist, an der sich das Drehorgan (30) mit seinem Außenabschnitt abstützt.
  5. Lager nach Anspruch 1, dadurch gekennzeichnet, dass es ferner ein erstes (26) und ein zweites (27) ringförmiges Teil aufweist, die ausgebildet sind, um in ein Loch des Gestells (10, 12) der Uhr eingepresst zu sein, wobei das Drehorgan (30) zwischen den zwei ringförmigen Teilen (26, 27) zwischengestellt ist.
  6. Lager nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass das Drehorgan (30b) einen gefüllten ringförmigen Abschnitt (30a) und mindestens zwei elastische Arme (30d) umfasst, wobei die Arme mit ihrem äußeren Ende mit dem gefüllten ringförmigen Abschnitt (30a) fest verbunden sind.
  7. Lager nach Anspruch 1, dadurch gekennzeichnet, dass es mindestens zwei elastische Arme (30d) und ringförmig ausgerichtete elastische Abschnitte (30e, 30f) umfasst, die mit dem äußeren Ende der Arme (30d) fest verbunden sind.
  8. Lager nach einem der Ansprüche 6 und 7, dadurch gekennzeichnet, dass die elastischen Arme (30d) eine Spiralstruktur aufweisen.
  9. Lager nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass es ein Reibungs- oder Dämpfungselement aufweist, das dazu neigt, sich einer Störkraft entgegenzustellen, die derart ausgerichtet ist, eine Verschiebung des Drehorgans hervorzurufen.
EP08160043.9A 2007-07-12 2008-07-09 Stoßdämpfer-Gleitlager für eine Uhr Not-in-force EP2015147B2 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH01122/07A CH704739B1 (fr) 2007-07-12 2007-07-12 Palier amortisseur de chocs pour pièce d'horlogerie.

Publications (4)

Publication Number Publication Date
EP2015147A2 EP2015147A2 (de) 2009-01-14
EP2015147A3 EP2015147A3 (de) 2009-09-02
EP2015147B1 EP2015147B1 (de) 2010-11-24
EP2015147B2 true EP2015147B2 (de) 2015-07-08

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ID=39294139

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08160043.9A Not-in-force EP2015147B2 (de) 2007-07-12 2008-07-09 Stoßdämpfer-Gleitlager für eine Uhr

Country Status (3)

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EP (1) EP2015147B2 (de)
CH (1) CH704739B1 (de)
DE (1) DE602008003621D1 (de)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103124935B (zh) * 2010-06-22 2015-05-13 斯沃奇集团研究和开发有限公司 钟表抗震***
CH705861A2 (fr) 2011-12-12 2013-06-14 Swatch Group Res & Dev Ltd Palier antichoc pour pièce d'horlogerie.
EP2607971A1 (de) * 2011-12-22 2013-06-26 The Swatch Group Research and Development Ltd. Verfahren zur Herstellung eines Bauteils
CH707809B1 (fr) * 2013-03-19 2017-05-31 Nivarox Far Sa Palier pour mécanisme d'horlogerie.
EP2806314A1 (de) 2013-05-24 2014-11-26 The Swatch Group Research and Development Ltd. Stoßdämpfer mit Bajonett
CH709867B1 (fr) 2014-07-14 2018-12-14 Mft Et Fabrique De Montres Et Chronometres Ulysse Nardin Le Locle Sa Palier antichoc pour pièce d'horlogerie.
CH709908A1 (fr) 2014-07-22 2016-01-29 Richemont Int Sa Palier amortisseur de choc pour pièce d'horlogerie.
CH710905A1 (fr) 2015-03-20 2016-09-30 Mft Et Fabrique De Montres Et Chronomètres Ulysse Nardin Le Locle S A Palier antichoc pour pièce d'horlogerie.
CH716041A1 (fr) * 2019-04-04 2020-10-15 Csem Ct Suisse Delectronique Microtechnique Sa Rech Developpement Dispositif antichoc et oscillateur mécanique horloger à guidage flexible disposant d'un tel dispositif antichoc.

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH237812A (fr) † 1943-12-30 1945-05-31 Erismann Schinz Sa Pare-choc pour paliers de pièces d'horlogerie.
CH244883A (fr) † 1944-05-15 1946-10-15 Erismann Schinz S A Palier amortisseur de chocs pour pièces d'horlogerie.
CH546975A (de) † 1971-12-23 1974-03-15
FR2279140A1 (fr) † 1973-12-18 1976-02-13 Epsilon Sarl Palier amortisseur de chocs
CH577202B5 (de) † 1973-10-26 1976-06-30 Parechoc Sa

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH235315A (fr) * 1942-09-30 1944-11-30 Erismann Schinz Sa Pare-choc pour pièce d'horlogerie.
CH495673A4 (fr) 1973-04-06 1976-10-29 Seitz Sa Dispositif de pivotement de l'ace d'un mobile d'horlogerie
CH697017A5 (fr) 2003-03-26 2008-03-14 Franck Muller Watchland S A Dispositif anti-chocs pour mobile tournant sur un axe.
DE602005025585D1 (de) * 2005-02-23 2011-02-10 Eta Sa Mft Horlogere Suisse Stoßdämpfende Uhrenlagerung

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH237812A (fr) † 1943-12-30 1945-05-31 Erismann Schinz Sa Pare-choc pour paliers de pièces d'horlogerie.
CH244883A (fr) † 1944-05-15 1946-10-15 Erismann Schinz S A Palier amortisseur de chocs pour pièces d'horlogerie.
CH546975A (de) † 1971-12-23 1974-03-15
CH577202B5 (de) † 1973-10-26 1976-06-30 Parechoc Sa
FR2279140A1 (fr) † 1973-12-18 1976-02-13 Epsilon Sarl Palier amortisseur de chocs

Also Published As

Publication number Publication date
CH704739B1 (fr) 2012-10-15
DE602008003621D1 (de) 2011-01-05
EP2015147A2 (de) 2009-01-14
EP2015147B1 (de) 2010-11-24
EP2015147A3 (de) 2009-09-02

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