EP3273308B1 - Hemmungsmechanismus - Google Patents

Hemmungsmechanismus Download PDF

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Publication number
EP3273308B1
EP3273308B1 EP16179989.5A EP16179989A EP3273308B1 EP 3273308 B1 EP3273308 B1 EP 3273308B1 EP 16179989 A EP16179989 A EP 16179989A EP 3273308 B1 EP3273308 B1 EP 3273308B1
Authority
EP
European Patent Office
Prior art keywords
lever
locking
escapement
winding
wheel
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
EP16179989.5A
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English (en)
French (fr)
Other versions
EP3273308A1 (de
Inventor
Stéphane OES
Matthieu Kummer
Sébastien LOPEZ
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.)
Sowind SA
Original Assignee
Sowind 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 Sowind SA filed Critical Sowind SA
Priority to EP16179989.5A priority Critical patent/EP3273308B1/de
Priority to PCT/EP2017/066689 priority patent/WO2018015146A1/fr
Priority to JP2019501474A priority patent/JP2019521344A/ja
Priority to CN201780043798.XA priority patent/CN109478037B/zh
Publication of EP3273308A1 publication Critical patent/EP3273308A1/de
Application granted granted Critical
Publication of EP3273308B1 publication Critical patent/EP3273308B1/de
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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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension
    • G04B17/045—Oscillators acting by spring tension with oscillating blade springs
    • 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
    • G04B15/10—Escapements with constant impulses for the regulating mechanism

Definitions

  • the present invention relates to the field of mechanical watchmaking. It relates, more particularly, to an escapement mechanism arranged to transmit mechanical energy pulses from a driving source to an oscillating timepiece regulator by means of a leaf spring working in buckling around a inflection point.
  • the leaf spring is capable of accumulating energy from the power source between two pulses and transmit it to said oscillating regulator at each pulse via a first and a second latch.
  • Such a mechanism is described in particular in the document WO 99/64936 .
  • the latter more generally discloses a method for transmitting pulses of mechanical energy from a power source to an oscillating regulator, by means of a leaf spring working in buckling mode. More particularly, this method is implemented in particular by an escape mechanism illustrated in FIG. figure 1 , intended to maintain the oscillations of a regulator, composed for example by a balance 1 associated with a spiral, by delivering energy received from a driving source, such as a barrel for example, not visible on the figure 1 , via a leaf spring 2, whose ends are positioned such that it occupies a stable position corresponding to a second mode buckling.
  • a driving source such as a barrel for example
  • the leaf spring 2 is capable, by means of an armature rocker 3 and a trigger rocker 4, of accumulating the energy coming from the driving source during a winding phase, to remain in an armed state during a rest phase and to restore the energy accumulated to said oscillating regulator during a pulse phase.
  • the trigger rocker 4 is kinematically connected to the leaf spring 2 substantially at its central point of inflection.
  • the trigger rocker 4 comprises, at one end, a fork intended to cooperate with a plate 6 and a plate pin 7 that includes the rocker 1.
  • the armature rocker 3 comprises a central portion and two symmetrical wings whose ends are kinematically connected to the leaf spring 2.
  • the central portion comprises a first 8 and a second 9 pallets of rest, intended to cooperate respectively with a first 10 and a second 11 escape wheel.
  • the two flip-flops 3 and 4 are mounted free to rotate with respect to each other.
  • the wheels 10 and 11 each comprise a pinion meshing with the last wheel 12 of the work train so that the wheels 10 and 11 pivot in a synchronized manner.
  • the wheels 10 and 11 have a particular toothing, the shape of which is adapted to cooperate with the first 8 and second 9 pallets of rest of the rocker arm 3, on the one hand to transmit energy to this rocker d ' arming 3 and, secondly, to block the rotation of the escape wheels 10 and 11, according to the phases of operation which will be summarized below. For more details, it is possible to refer to the document cited in the introduction.
  • the figure 1 represents an exhaust mechanism of the prior art immediately after a pulse phase and at the beginning of a winding phase, the rocker 1 rotates counterclockwise, the plateau pin 7 comes out of the fork, the first pallet rest 8 has just disengaged from the wheel 10 and the spring 2 is in a stable position corresponding to a second mode buckling.
  • the first escape wheel 10 rotates freely and the second escape wheel 11 cooperates with the second pallet of rest 9 of the rocking lever 3 to rotate the latter counterclockwise until a tooth of the second wheel 11 bears on the second pallet rest 9.
  • the leaf spring 2 has left its initial stable state corresponding to a second mode buckling and deformed under the action of the armature rocker 3 to a metastable state close to an unstable state corresponding to a fourth mode buckling.
  • the armature of the leaf spring 2 is then maximal.
  • the trigger rocker 4 pivots by acting on the leaf spring 2 which then suddenly switches from its unstable position to a stable state corresponding to a reverse second mode buckling of the previous one.
  • This change of state rotates the armature lever 3, causing the release of the second pallet of rest 9 of the second escape wheel 11.
  • the armature rocker 3 pivots until the first pallet of rest 8 when the spring wheel 2 is being changed, the latter also acts on the trigger rocker 4, thus communicating with the balance 1 the energy accumulated during the winding of the spring -lame 2, through the fork.
  • the draw of the escape wheels 10 and 11 on the first 8 and second 9 pallets of rest of the rocker arm 3 makes it possible to ensure the locking function of the escape wheels.
  • the pulling force must be sufficient to avoid unwanted unlocking which could, for example, result from accelerations experienced by the timepiece in everyday use and which would lead to an advance of the timepiece's running and an overconsumption of time. 'energy.
  • the pulling force must be as small as possible in order to limit the energy required to achieve the clearance and thus optimize the power reserve. It has been found that it is not possible to adjust the draft of the escape wheels 10 and 11 satisfactorily so as to together, to obtain a sufficient locking force and a moderate energy consumption.
  • the present invention aims to overcome this disadvantage.
  • the escapement mechanism of the invention is designed to transmit pulses of mechanical energy from a driving source to an oscillating timepiece regulator via a leaf spring working in buckling around a point of inflection, said leaf spring being capable of accumulating energy from the power source between two pulses and to transmit it to said oscillating regulator at each pulse by means of a cooperating armature latch with the leaf spring and a trigger rocker adapted to cooperate with at least one escapement mobile receiving energy from the drive source to block its rotation intermittently.
  • the escape mobile comprises a pinion adapted to kinematically bind said mobile escape to the power source.
  • the escape wheel comprises a locking wheel comprising a plurality of functional zones each having a locking plane intended to cooperate with a lug of the trigger rocker to block the escape wheel during the rest phases.
  • the escapement mobile also includes a winding cam.
  • the armature rocker comprises at least one lever adapted to cooperate with the arming cam of said at least one escapement mobile.
  • the exhaust mechanism comprises at least one said mobile escapement and the armature rocker comprises at least one lever, optionally associated with a return spring for example, which cooperates with the arming cam of said mobile exhaust, the arming cam comprising N functional areas and being indexed with an offset of 360 / N °.
  • the lever or levers are dimensioned and positioned to always be in contact with said arming cam.
  • the lever or levers are arranged on an arm integral with the armature rocker, and the lever or levers are sized and positioned to always be in contact with at least one arming cam.
  • the lever or levers and the arming cam are shaped to limit unintentional angular displacements of the armature rocker once it has reached one of its extreme positions in rotation about its axis.
  • the leaf spring 2 constrained in buckling at its ends by any appropriate means, for example integral with a frame sized to constrain said leaf spring and adapted to be fixed on a bridge or the plate of a timepiece or simply fixed directly on a said bridge or the turntable of a timepiece, is capable of accumulating energy from the power source between two pulses and transmit it to the oscillating regulator at each pulse via of a trigger rocker 25 pivotally mounted about an axis X1 coincides with the point of inflection of the leaf spring 2.
  • the armature rocker 3 comprises two connecting arms 31 to the leaf spring 2 extending from the X1 axis and each having between their end opposite said axis X1 pins 13a cooperating with eyelets 13b integral with the leaf spring 2.
  • the latch 20 advantageously cooperates via anterior pins 26a and 26b rear with an escapement mobile 28 of the leaf spring 2 to block the rotation of the escapement mobile 28 intermittently, said mobile of exhaust 28 is in kinematic connection with the driving source.
  • the latch 20 is integral with the pulse rocker 4, and the dart 22 and they are assembled by pins or any other means, which ensure their respective angular positioning around the axis X1 in a safe way.
  • the latch 20, the pulse rocker 4 and the dart 22 respectively extend in longitudinal directions located in the same vertical plane passing through the axis X1.
  • the armature rocker 3, on the one hand, and the trigger rocker 25, on the other hand, are rotatably mounted one with reference to the other on a pivoting material axis coinciding with the axis X1 , the leaf spring 2 not participating in a virtual pivoting of the armature and trigger rockers 25.
  • the escape wheel 28 comprises a pinion 32 by which it is kinematically connected to the finishing gear of the timepiece comprising the exhaust mechanism for receiving energy from the energy source, for example consisting of one or more barrels.
  • the escapement wheel 28 further comprises, stacked on the same axis, a winding cam 36, for example a triangular cam with convex cam planes, the role of which will appear below, as well as a locking wheel 38.
  • the arming cam 36 and the locking wheel 38 each comprise a plurality of functional zones, the angular position of which is adjusted with reference to each other.
  • Each functional zone of the locking wheel 38 comprises a locking plane 40 intended to cooperate with the latch 20.
  • the locking plane 40 is preferably located in the plane of the locking wheel 38, which can thus be manufactured easily.
  • the latch 20 comprises a fork 24.
  • This fork 24 is adapted to cooperate with the regulator 1, and more particularly with a plate pin 7 as shown in FIGS. Figures 2 to 6 of the regulator 1, as in the case of a regulating system cooperating with a conventional Swiss anchor escapement.
  • the latching lever 20 also comprises anterior locking lugs 26a and posterior 26b arranged to lock the escape wheel 28 during the rest phases, by working with the locking planes 40 of the locking wheel 38.
  • the mechanism is illustrated when the trigger rocker 25 has been positioned by the change of buckling mode of the leaf spring 2.
  • the trigger rocker 25 and the rocker arm 3 are then in the input or anterior position, side mobile exhaust 28, under the action of the previous locking pin 26a and the locking wheel 38, which transmits the torque provided by the energy source.
  • This torque provides a pull on the trigger rocker 25 via the front lug 26a, against which a locking plane 40 is supported.
  • the pair presses the fork of the pulse rocker 4 against one of the stars E, in order to always definitively define the position of the pulse rocker 25.
  • the armature rocker 3 is also positioned directly by the cam of the armature 36 and not by the leaf spring 2.
  • the escape wheel 28 is stopped.
  • the plate pin 7 that it comprises enters the fork 24 of the latch 20.
  • the leaf spring 2 then leaves its unstable mode of second order and repositioned in buckling of 1 st order, thus providing all its energy to the regulator through the fork 24 of the latch 20 and the plate pin 7 of the regulator.
  • the trigger rocker 25 pivots around the axis X1 and moves from a first position in abutment against a first star E to a second position abutting against the second star E ( Figures 3 to 6 ). This movement releases the latch 20 from its support against the locking wheel 38 at the front pin 26a, thus releasing the escapement wheel 28 which then rotates.
  • the latch 20 is then positioned to receive, in abutment against the output or rear locking pin 26b at a locking plane 40 of the locking wheel 38.
  • the locking plane 40 of the locking wheel 38 transmits the torque provided by the energy source to the trigger rocker via the rear lug 26b. This torque provides a pull on the latch 20 and the trigger rocker 25 and thus presses the pulse latch 4 against one of the star E, to always definitively determine the position of the trigger rocker 25.
  • the armature rocker 3 is also positioned directly via the arming cam 36. The leaf spring 2 is armed, close to its unstable position and waiting for the ankle 7 during the next alternation.
  • the armature rocker 3 also comprises, as represented on the Figures 2 to 6 and in detail at the figure 8 two levers 50 shaped to cooperate with the arming cam 36 of the escapement wheel 28.
  • the arming cam 36 visible on the figure 7 in particular comprises N functional areas consisting of cam segments 36a, 36b, 36c.
  • the cam 36 of the escapement wheel 28 is indexed with an offset of 360 ° / N.
  • the levers 50 are dimensioned and positioned to be in permanent contact with the arming cam 36, the angular position of said cam 36 thus making it possible to perfectly position the armature rocker 3, in synchronism with the locking wheel 38.
  • the cam 36 is essentially triangular, the 3 cam segments 36a, 36b, 36c being convex to define a point contact with the levers 50 of the armature rocker 3 and optimize the friction.
  • the levers 50 may be formed of the branches of a fork 52 in U carried at the end of an arm 53, the fork being shaped and dimensioned so that the arming cam 36 of the mobile 28 is inserted between the branches the U in permanent and punctual contact with the cam 36, which ensures a perfect positioning and an angular locking of the armature rocker 3.
  • each lever 50 allows, in cooperation with the arming cam 36 of the escapement wheel 28 on the one hand and the pins 13a of the connection of the armature rocker 3 to the leaf spring 2 in the corresponding eyelets 13b on the other hand to reset the leaf spring 2 to a defined optimum point and angularly locked by the geometry of the arming cam 36 and levers 50 for the next pulse.
  • the exhaust mechanism of the invention has been described here with reference to the appended figures in an embodiment comprising a single exhaust mobile 28 cooperating with the trigger rocker 25 via the latch 20 incorporated in the latter.
  • those skilled in the art can easily make a similar exhaust mechanism comprising two symmetrical armoring mobiles 28 cooperating alternately with each alternation with the trigger rocker 25 by adjusting differently the pins 26a, 26b on the latch and by providing a kinematic connection of the two armoring mobiles between them to ensure synchronization in rotation, for example by means of a toothed gear coaxial with the locking wheels and arming cams of each of the armoring mobiles, identical. It will then be ensured to ensure a geometry of the levers 50 of the armature rocker allowing an alternating contact with the winding cams of each of the two symmetrical armoring mobiles while ensuring a locked position angularly of this rocker.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Measurement Of Unknown Time Intervals (AREA)
  • Transmission Devices (AREA)
  • Springs (AREA)
  • Braking Arrangements (AREA)

Claims (7)

  1. Hemmungsmechanismus, der so angeordnet ist, dass er die mechanischen Energieimpulse einer Antriebsquelle an einen oszillierenden Regler eines Zeitmessgeräts über eine Blattfeder (2) überträgt, die um einen geknickten Wendepunkt arbeitet, wobei besagte Blattfeder (2) in der Lage ist, die von der Antriebsquelle zwischen zwei Impulsen freigesetzte Energie zu speichern und sie bei jedem Impuls über eine mit der Blattfeder (2) zusammenwirkende Spannwippe (3), und über eine Riegelwippe (25), welche in der Lage ist, mit zumindest einem Hemmungsdrehteil (28), welches die Energie der Antriebsquelle empfängt, zusammen zu wirken, um dessen Drehung intermittierend zu blockieren, an besagten oszillierenden Regler zu übertragen, dadurch gekennzeichnet, dass die Riegelwippe (25) eine Sperrwippe (20) umfasst, welche folgendes umfasst:
    - eine Gabel (24), die in der Lage ist, mit dem Regler (1) zusammenzuarbeiten, und
    - zumindest zwei Schließzapfen (26), die so angeordnet sind, dass sie das Hemmungsdrehteil (28) in den Ruhephasen blockieren, sodass das Freisetzen der Sperrwippe (20) beim Übergang der Freisetzungsenergie durch Einwirken des Reglers auf besagte Gabel unabhängig von der Feder (2) ausgelöst wird, wobei die Verriegelungs- und Entriegelungsfunktionen des besagten Hemmungsdrehteils (28) einerseits, und die Spannfunktionen der Blattfeder (2) andererseits voneinander getrennt sind.
  2. Hemmungsmechanismus nach Anspruch 1, dadurch gekennzeichnet, dass das Hemmungsdrehteil (28) ein Zahnrad (32) umfasst, dass so angepasst ist, dass es besagtes Hemmungsdrehteil kinematisch mit der Antriebsquelle verbindet.
  3. Hemmungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Hemmungsdrehteil (28) ein Verriegelungsrad (38) umfasst, welches eine Vielzahl an funktionalen Bereichen mit jeweils einer Verriegelungsebene (40) umfasst, die dazu bestimmt ist, mit einem Zapfen (26a, 26b) der Sperrwippe (20) zusammen zu wirken, um das Hemmungsdrehteil (28) in den Ruhephasen zu blockieren.
  4. Hemmungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Spannwippe (3) zumindest einen Hebel (50) umfasst, der in der Lage ist, mit einer Spannnocke des besagten Hemmungsdrehteils (28) zusammenzuwirken.
  5. Hemmungsmechanismus nach Anspruch 4, dadurch gekennzeichnet, dass der zumindest eine Hebel (50) mit einer Spannnocke (36) des Hemmungsdrehteils (28) zusammenwirkt, wobei besagte Spannnocke (36) N funktionale Bereiche umfasst, und mit einer Verschiebung von 360/N° indexiert ist, und dadurch, dass der Hebel (50) so bemessen und positioniert ist, dass er immer mit besagter Spannocke (36) in Berührung ist.
  6. Hemmungsmechanismus nach Anspruch 4 oder 5, dadurch gekennzeichnet, dass der zumindest eine Hebel (50) auf einem Arm angeordnet ist, der mit der Spannwippe verbunden ist, und dadurch, dass besagter Hebel (50) so bemessen und positioniert ist, dass er immer mit der Spannnocke (36) in Berührung ist.
  7. Hemmungsmechanismus nach Anspruch 4 bis 6, dadurch gekennzeichnet, dass der Hebel (50) und die Spannnocke (36) so ausgebildet sind, dass sie die unbeabsichtigten Winkelverschiebungen der Spannwippe (3) beschränken.
EP16179989.5A 2016-07-18 2016-07-18 Hemmungsmechanismus Active EP3273308B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP16179989.5A EP3273308B1 (de) 2016-07-18 2016-07-18 Hemmungsmechanismus
PCT/EP2017/066689 WO2018015146A1 (fr) 2016-07-18 2017-07-04 Mecanisme d'echappement
JP2019501474A JP2019521344A (ja) 2016-07-18 2017-07-04 エスケープメント・メカニズム
CN201780043798.XA CN109478037B (zh) 2016-07-18 2017-07-04 擒纵机构

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP16179989.5A EP3273308B1 (de) 2016-07-18 2016-07-18 Hemmungsmechanismus

Publications (2)

Publication Number Publication Date
EP3273308A1 EP3273308A1 (de) 2018-01-24
EP3273308B1 true EP3273308B1 (de) 2019-06-12

Family

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Application Number Title Priority Date Filing Date
EP16179989.5A Active EP3273308B1 (de) 2016-07-18 2016-07-18 Hemmungsmechanismus

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Country Link
EP (1) EP3273308B1 (de)
JP (1) JP2019521344A (de)
CN (1) CN109478037B (de)
WO (1) WO2018015146A1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3599514B1 (de) 2018-07-25 2023-06-07 Sowind S.A. Hemmungsmechanismus mit bistabilen und monostabilen federn
EP3623875B1 (de) 2018-09-11 2023-04-26 Sowind S.A. Uhrhemmungsmechanismus mit bistabiler blattfeder
CN112859566A (zh) * 2019-11-28 2021-05-28 福州市闽侯夫达工艺品有限公司 一种石英钟机芯

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1084459A1 (de) 1998-06-08 2001-03-21 Manufacture des Montres Rolex S.A. Verfahren zur übertragung von mechanischen energieimpulsen von einer antriebsquelle zu einem schwingungsregler
DE60135977D1 (de) * 2000-04-11 2008-11-13 Detra Sa Hemmung für uhr
EP1544689B1 (de) * 2003-12-16 2010-02-24 Montres Breguet S.A. Chronometerhemmung für Uhren
ATE449985T1 (de) * 2007-04-18 2009-12-15 Eta Sa Mft Horlogere Suisse Hemmung, die zwei hemmungsräder umfasst
EP2105806B1 (de) * 2008-03-27 2013-11-13 Sowind S.A. Hemmungsmechanismus
WO2013144236A1 (fr) * 2012-03-29 2013-10-03 Nivarox-Far S.A. Mécanisme d'échappement flexible à cadre mobile
EP2706416B1 (de) * 2012-09-07 2015-11-18 The Swatch Group Research and Development Ltd Flexibler Anker mit konstanter Kraft
WO2016113704A2 (de) * 2015-01-16 2016-07-21 Creaditive Ag Uhr, regelorgan und verfahren zum betreiben eines regelorgans mit hoher regelgüte
CH710685B1 (fr) * 2015-01-30 2019-07-15 Sowind S A Mécanisme d'échappement.

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
JP2019521344A (ja) 2019-07-25
WO2018015146A1 (fr) 2018-01-25
CN109478037B (zh) 2021-04-06
CN109478037A (zh) 2019-03-15
EP3273308A1 (de) 2018-01-24

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