EP2221677A1 - Riegelhemmung - Google Patents

Riegelhemmung Download PDF

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Publication number
EP2221677A1
EP2221677A1 EP09405029A EP09405029A EP2221677A1 EP 2221677 A1 EP2221677 A1 EP 2221677A1 EP 09405029 A EP09405029 A EP 09405029A EP 09405029 A EP09405029 A EP 09405029A EP 2221677 A1 EP2221677 A1 EP 2221677A1
Authority
EP
European Patent Office
Prior art keywords
balance
release
rocker
inertial
finger
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.)
Withdrawn
Application number
EP09405029A
Other languages
English (en)
French (fr)
Inventor
Fabiano Colpo
Benoît Boulenguiez
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 EP09405029A priority Critical patent/EP2221677A1/de
Priority to EP09405206.5A priority patent/EP2199875B1/de
Priority to US12/635,264 priority patent/US7927008B2/en
Priority to JP2009281686A priority patent/JP5406000B2/ja
Priority to CN200910259158XA priority patent/CN101750953B/zh
Publication of EP2221677A1 publication Critical patent/EP2221677A1/de
Withdrawn legal-status Critical Current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
    • G04B15/00—Escapements
    • G04B15/06—Free escapements

Definitions

  • the present invention relates to a detent escapement for a timepiece comprising a pendulum secured to a pulse element, an escape wheel whose toothing intersects the trajectory of the pulse element, a trigger rocker having a stop member and a release member, resilient biasing means for engaging the stop member in the path of the toothing of the escape wheel, and a finger or release pallet integral with the rotation of the rocker for engaging with the rocker release member once per swing period of the rocker arm to disengage the stop member of the toothing of the escape wheel.
  • the impulse of the escape wheel on the pendulum pulse finger can only occur in a direction of rotation of the pendulum, either once per oscillation period or alternately in half, the alternation corresponding to half a oscillation period.
  • This type of exhaust requires a release rocker which comprises firstly a stop element which cuts the path of the teeth of the escape wheel, and which further comprises a release element with which comes into engagement a release finger integral with the balance.
  • this release finger must come into engagement with the release element only during the alternation during which the rocker receives a pulse from the escape wheel, the stop element having to remain in engagement with the impeller. exhaust during the other alternation.
  • the release rocker comprises an elastic blade whose end free press against a stop of the rocker so that the blade causes the rocker in a direction of rotation of the rocker release finger, while in the opposite direction of rotation, the blade bends and lets the release finger without causing the release latch.
  • the sizing of the flexible parts of the trigger is clearly one of the critical points in the development of this exhaust. It requires sufficient rigidity to keep the stop in its natural position but, at the same time, it is not necessary that the energy to release the escape wheel or to perform the relaxation function is too high, the risk being a disturbance non-negligible balance-balance oscillator, associated with a significant drop in yield, or even the system shutdown.
  • the unlocking torque required for the release of the escape wheel also represents an operating safety (impact safety) which imposes a lower limit on the rigidity of the blade.
  • the object of the present invention is to overcome, at least in part, the aforementioned drawbacks.
  • this invention relates to a detent escapement for a timepiece according to claim 1.
  • this exhaust does not present certain risks of conventional expansion exhausts. If a shock moves the inertial organ to its other extreme position, the consequences will not be of an unfortunate nature. In one case, the release finger will meet the release member instead of fading and move the inertial member to its correct position with negligible effort. In the other case, instead of coming into contact with the release element, the finger will not meet it, which will lose an impulse to the pendulum and an increment to the gear, this having no impact on the good watchmaking as it is only an occasional event.
  • this exhaust reduces certain risks associated with the use of conventional expansion exhausts. Indeed, a shock applied to the timepiece may cause its balance to rotate beyond a normal operating angle, which leads, during the alternation where the pulse occurs, to a new release of the train of gear. There is a gallop, because two clearances and two pulses take place during the same alternation.
  • the system object of the invention does not present this kind of problem because the release finger is at that moment already erased from the path of the unlocking element and does not cause the displacement of the blocker and therefore by a second pulse .
  • the detent escapement comprises an escape wheel 1 connected to a mainspring (not shown) by a finishing train (not shown) which tends to rotate the escapement wheel 1 ( Figures 1 to 7 ) in the opposite direction to clockwise.
  • a tooth of the escape wheel 1 bears against a stop element 2a, advantageously formed by a ruby paddle, of a release rocker 2.
  • This release rocker 2 is biased by a spring 3 which tends to to hold it against a stop 4, position in which the stop pallet 2a is engaged in the path of the teeth of the escape wheel, so that a tooth of this wheel bears against the stop pallet 2a as illustrated by the figure 1 .
  • the pulse and disengagement device associated with the pendulum pivot shaft is represented in detail by the Figures 8-10 . It comprises a circular plate 6 provided with a tubular element 6a designed to be driven on the balance shaft. This tubular element 6a has a partially circular outer section cut by two parallel outer flat faces 6b ( figure 8 ) on which is engaged a pulse ring 7, provided with an opening 7a ( figure 10 ) of complementary section to that of the outer section of the tubular element 6a.
  • the impulse ring 7 is retained axially between two retaining rings 8a, 8b driven.
  • the impulse ring 7 has a finger or impulse face 7b projecting from the outer lateral face of the impulse ring 7.
  • the finger of the impulse ring may be an insert such as a pallet.
  • Two pins 9 and 10, of semicircular sections in this example, are driven into two diametrically opposed openings 6c, 6d respectively and of corresponding sections, formed in the plate 6.
  • An inertial member 11, elliptical in this example, is provided with three openings 11a, 11b, 11c, two openings 11a, 11b are off center and preferably symmetrical and diametrically opposed.
  • One of these openings 11b is semicircular limited by two radii forming an angle greater than 180 ° to receive the pivot pin 10 of the inertial member 11 allowing it an angular displacement.
  • the other opening is elongated 11a to receive the pin 9.
  • the third opening is a central opening 11c for the clearance passage of the tubular portion 6a of the plate 6 and can be used, in the absence of the opening 11a and the ankle 9, to limit the displacement angular of the inertial member 11.
  • a release finger 11d protrudes from the outer lateral face of the inertial member 11.
  • This release finger 11d is of triangular shape in the example under consideration, with a radially oriented drive face. relative to the center of the inertial member 11 and an inclined face, as illustrated by the figure 8 .
  • the release finger could also be formed by a palette reported ruby, as the finger 7b.
  • the inclined face of the release finger 11d is used to push the inertial element 6 in the event that a shock would have moved to the projecting position when it should be in the retracted position.
  • the inertial member 11 is disposed at the base of the tubular portion 6a.
  • the openings 11a, 11b, 11c are arranged, dimensioned and shaped to allow the inertial member 11 to perform a limited angular displacement around the axis of the pin 10, which is parallel to the axis of the tray 6 driven on the pivot shaft of the balance, and which constitutes the pivoting member of the inertial member 11.
  • the elongate opening 11a extends symmetrically to a diameter of the inertial element 11 passing through the respective axes of the openings 11b , 11c, so that the two limit positions of the inertial member 11 are respectively symmetrically on either side of the axis of pivoting of the balance.
  • the axes of the two openings 11a, 11b occupy diametrically opposite and symmetrical positions relative to the center of the inertial member 11.
  • the pins 9, 10 also occupy diametrically opposite positions and symmetrical relative to the center of the circular plate 6 to cooperate with the respective openings 11a, 11b.
  • the angular position occupied by the inertial member 11 corresponds to that in which the release finger 11d protrudes outside the periphery of the circular plate 6.
  • the radial face the triangular finger meets a clearance member 2b located at the free end of the release rocker 2, so that the release finger 11d raises the release rocker 2 against the pressure of the return spring 3, as illustrated by the figure 2 .
  • the figure 4 illustrates the return of the release lever 2 under the pressure of the spring 3 against the stop 4 after the release of the rocker by the release finger 11d, so that when the tooth of the escape wheel is released by the finger d 7b impulse, another tooth of the escape wheel is stopped by the pallet 2a of the release lever 2, as illustrated by the figure 5 .
  • This figure 5 also illustrates the reversal of the direction of rotation of the balance which passes from the rotation in the direction of clockwise to a rotation of opposite direction.
  • the balance shaft is integral in rotation with the pulse finger 7b and the release finger 11d.
  • the balance is braked by the spiral spring, and passes through a zero speed before being driven in the opposite direction of rotation.
  • the inertial member 11 has two stable positions, each dependent on the direction of rotation of the balance.
  • the Tests carried out show that the inertial member 11 moves before the pendulum has completed each of the two alternations making up its oscillation period, but its rotation around the ankle 10 begins around the neutral point of the pendulum (angle 0 of its position ).
  • the pendulum In neutral, the pendulum has the maximum speed and thus passes from a positive acceleration to a negative acceleration (it starts to decelerate) and that is when the inertial effects begin to be felt.
  • This behavior depends on the inertia of the inertial member 11, (material, geometry, in particular), of the friction between the inertial member 11 and the surfaces with which it is in contact, but it is also influenced by the effect of the centrifugal force acting on the center of mass of the inertial member 11 (offset relative to the axis of rotation of the balance) and which is added to the initial acceleration due to the balance.
  • the inertial member 11 is moved clockwise about the axis of the pin 10. In this position, the release finger 11d is retracted inside the peripheral edge of the circular plate 6.
  • the release finger 11d does not cooperate with the disengagement latch 2 as it passes opposite the disengagement member 2b, as illustrated by FIG. figure 6 .
  • the clearance finger 11d has no elastic element to overcome to pass the obstacle of the element 2b of the trigger rocker 2 during the alternation of the balance where this one does not receive a maintenance pulse of its oscillating movement, since the finger disappears inside the circular periphery of the plate 6. There is therefore no loss of energy or disturbance of the pendulum swing period.
  • the figure 11 is a diagram of the angular displacement of the balance during a period of oscillation. It is to be compared with the diagram of the figure 12 which shows the angular displacement of the inertial member 11 between its two limit positions determined by the two radial edges of the opening 11a alternately abutting against the pin 9 secured to the plate 6.
  • the angular displacement of the inertial member 11 between its two limit positions is only a few degrees, typically of the order of 5 ° to 10 °, these two limit positions being located symmetrically on either side of the pivoting axis of the balance.
  • This inertial member 11 may be made of a low specific mass material, the inertial effect being always sufficient to guarantee the function.
  • the freedom of choice of the outer geometrical shape makes it possible to produce an inertial element of symmetrical shape, which guarantees a weak added imbalance.
  • a sparse material such as silicon, the influence on the equilibrium of the balance is negligible.
  • the inertial member 11 made of nickel can be produced by the LIGA technique with a small thickness, typically of the order of 0.10 to 0.15 mm, so that the influence on the equilibrium of the balance can be considered as being negligible.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Micromachines (AREA)
EP09405029A 2008-12-16 2009-02-16 Riegelhemmung Withdrawn EP2221677A1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP09405029A EP2221677A1 (de) 2009-02-16 2009-02-16 Riegelhemmung
EP09405206.5A EP2199875B1 (de) 2008-12-16 2009-11-26 Chronometerhemmung
US12/635,264 US7927008B2 (en) 2008-12-16 2009-12-10 Detent escapement
JP2009281686A JP5406000B2 (ja) 2008-12-16 2009-12-11 戻止脱進機
CN200910259158XA CN101750953B (zh) 2008-12-16 2009-12-15 天文钟擒纵机构

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09405029A EP2221677A1 (de) 2009-02-16 2009-02-16 Riegelhemmung

Publications (1)

Publication Number Publication Date
EP2221677A1 true EP2221677A1 (de) 2010-08-25

Family

ID=40937584

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09405029A Withdrawn EP2221677A1 (de) 2008-12-16 2009-02-16 Riegelhemmung

Country Status (1)

Country Link
EP (1) EP2221677A1 (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2199875A2 (de) * 2008-12-16 2010-06-23 Rolex Sa Chronometerhemmung
WO2011120180A1 (fr) 2010-04-01 2011-10-06 Rolex S.A. Dispositif de blocage pour roue dentée
EP2450755A1 (de) 2010-11-04 2012-05-09 Nivarox-FAR S.A. Synchronhemmung für Uhrwerk
EP2645189A1 (de) * 2012-03-29 2013-10-02 Nivarox-FAR S.A. Flexibler Uhrhemmungsmechanismus
WO2013144237A1 (fr) 2012-03-29 2013-10-03 Nivarox-Far S.A. Mecanisme d'echappement flexible sans ancre
WO2013144238A1 (fr) 2012-03-29 2013-10-03 Nivarox-Far S.A. Mécanisme d'échappement flexible à balancier sans plateau
WO2013144236A1 (fr) 2012-03-29 2013-10-03 Nivarox-Far S.A. Mécanisme d'échappement flexible à cadre mobile
RU2749943C2 (ru) * 2016-10-18 2021-06-21 Эта Са Мануфактюр Орложэр Сюис Резонатор для механических часов

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1538490A1 (de) 2003-12-04 2005-06-08 Montres Breguet S.A. Chronometerhemmung für Armbanduhren

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1538490A1 (de) 2003-12-04 2005-06-08 Montres Breguet S.A. Chronometerhemmung für Armbanduhren

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2199875A3 (de) * 2008-12-16 2011-07-27 Rolex Sa Chronometerhemmung
EP2199875A2 (de) * 2008-12-16 2010-06-23 Rolex Sa Chronometerhemmung
EP2818941A1 (de) 2010-04-01 2014-12-31 Rolex Sa Blockiervorrichtung für Zahnrad
WO2011120180A1 (fr) 2010-04-01 2011-10-06 Rolex S.A. Dispositif de blocage pour roue dentée
EP2450755A1 (de) 2010-11-04 2012-05-09 Nivarox-FAR S.A. Synchronhemmung für Uhrwerk
US8439556B2 (en) 2010-11-04 2013-05-14 Nivarox-Far S.A. Synchronous escapement for a timepiece mechanism
EP2645189A1 (de) * 2012-03-29 2013-10-02 Nivarox-FAR S.A. Flexibler Uhrhemmungsmechanismus
WO2013144237A1 (fr) 2012-03-29 2013-10-03 Nivarox-Far S.A. Mecanisme d'echappement flexible sans ancre
WO2013144238A1 (fr) 2012-03-29 2013-10-03 Nivarox-Far S.A. Mécanisme d'échappement flexible à balancier sans plateau
WO2013144236A1 (fr) 2012-03-29 2013-10-03 Nivarox-Far S.A. Mécanisme d'échappement flexible à cadre mobile
US9075394B2 (en) 2012-03-29 2015-07-07 Nivarox-Far S.A. Flexible escapement mechanism with movable frame
US9207640B2 (en) 2012-03-29 2015-12-08 Nivarox-Far S.A. Flexible escape mechanism with no pallet lever
US9304493B2 (en) 2012-03-29 2016-04-05 Nivarox-Far S.A. Flexible escapement mechanism having a balance with no roller
RU2749943C2 (ru) * 2016-10-18 2021-06-21 Эта Са Мануфактюр Орложэр Сюис Резонатор для механических часов

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