EP3623875B1 - Uhrhemmungsmechanismus mit bistabiler blattfeder - Google Patents

Uhrhemmungsmechanismus mit bistabiler blattfeder Download PDF

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Publication number
EP3623875B1
EP3623875B1 EP18193657.6A EP18193657A EP3623875B1 EP 3623875 B1 EP3623875 B1 EP 3623875B1 EP 18193657 A EP18193657 A EP 18193657A EP 3623875 B1 EP3623875 B1 EP 3623875B1
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Prior art keywords
winding
locking
lever
rocker
pin
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EP18193657.6A
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English (en)
French (fr)
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EP3623875A1 (de
Inventor
Matthieu Kummer
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Sowind SA
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Sowind SA
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Priority to EP18193657.6A priority Critical patent/EP3623875B1/de
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    • 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
    • G04B15/08—Lever escapements
    • 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
    • G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape wheel

Definitions

  • the present invention relates to the field of mechanical watchmaking. It relates, more particularly, to an escapement mechanism arranged to transmit pulses of mechanical energy from a driving source to an oscillating regulator of a timepiece by means of a leaf spring working in buckling around a inflection point.
  • an escapement mechanism arranged to transmit pulses of mechanical energy from a driving source to an oscillating regulator of a timepiece by means of a leaf spring is well known. working in buckling around a point of inflection. Mention may be made here by way of example of the various patents of the Applicant WO 2009118310 A1 , CH 710925 A1 or WO 2018015146 A1 .
  • Such an escapement mechanism makes it possible in particular to maintain the oscillations of the balance constantly over the entire duration of the power reserve independently of the source of energy.
  • these escapement mechanisms result in a drawback linked to the alternating locking of the winding wheels by hooking a peripheral hook of the winding wheels onto the winding pegs of the winding rocker at the end of the winding phases.
  • armament Indeed, such picking tends to provide rebound effects between winding wheels and winding rocker with corresponding energy losses and untimely unlocking.
  • such a mode of locking the winding wheels is more sensitive, and therefore less reliable, in the event of accelerations undergone by the escapement mechanism during impacts.
  • the object of the present invention is to remedy these drawbacks and to make the locking of the winding wheels more reliable in a bistable leaf spring escapement mechanism working in buckling.
  • this escapement mechanism is arranged to transmit pulses of mechanical energy from a driving source to an oscillating regulator of a timepiece by means of a leaf spring working in buckling around a point of inflection, said leaf spring being capable, via a winding rocker, of accumulating the energy from the driving source during a winding phase, of then remaining in a metastable state close to instability during a locking phase, then to restore the energy accumulated to said oscillating regulator during a pulse phase by means of a detent rocker.
  • the winding rocker is arranged to cooperate with at least one winding wheel so as to wind the leaf spring during the winding phases, the or each winding wheel comprising on a periphery a plurality of winding cams each defining a cam surface.
  • the winding rocker further comprises at least one winding peg forming a cam follower such that each winding peg slides on the cam surface of one of the winding cams during the winding phases of the spring -blade.
  • the escapement mechanism of the invention finally comprises a locking rocker arranged to lock said winding rocker in a locking position at the end of each winding phase.
  • the locking rocker comprises two locking pallets arranged to cooperate with locking members complementary, in particular lugs, on said winding rocker and in that the at least one said winding wheel and said winding rocker are arranged respectively such that the or each winding wheel is stopped by wedging between a winding peg and a cam surface of a said winding cam and between a said locking pallets and a said complementary locking member at the end of each winding phase and during the locking phases.
  • the mechanism according to the invention makes it possible to eliminate the risk of accidental unlocking of a winding wheel and of the winding rocker during all the phases of locking, unlocking and relaxation, and to position in an identical manner and repeatable the winding rocker at each locking by eliminating all the rebounds.
  • this arrangement makes it possible to increase the energy transmitted to the balance because the blade no longer needs to unlock the winding rocker.
  • This mechanism also makes it possible to have distinct unlocking and relaxation phases.
  • the winding mobiles of the inventive mechanism are stopped by jamming a winding cam on a pin of the winding rocker, which is at the end of the winding phase and in the locking phase therefore “sandwiched” between a winding mobile and the locking rocker.
  • the winding cams of the winding mobiles of the mechanism of the invention are therefore configured to have a sufficient length to push the winding rocker into abutment against the locking rocker thus determining the end of the winding phase, the driving torque of the driving source sufficient to operate the wedging of a winding mobile on a winding peg once the winding rocker is in abutment.
  • this arrangement makes it possible to have a positioning of the winding rocker which is identical and very repeatable from one locking to another because the moving parts which form the abutment are rockers whose parts forming the wedging are always the same from lock to lock.
  • each pulse in turn becomes identical, providing a perfectly balanced operation of the mechanism and optimization of the energy consumed and transmitted to the balance wheel, and therefore of the efficiency of the escapement.
  • the escapement mechanism of the invention thus avoids all the rebounds of the winding wheels, of the winding rocker and of the locking rocker by mutual wedging of the latter and guaranteeing an identical positioning of the winding rocker. , backlash-free and perfectly repeatable on each locking.
  • This arrangement makes it possible to position the blade in its state closest to instability and also prevents any untimely unlocking of the escapement, this in a repetitive and identical manner at each locking even during external shocks.
  • the locking rocker intervenes only as a safety device in the event of failure of the hooking between the winding mobile and the winding rocker.
  • the mechanism of the invention secures the locking of the winding rocker and the winding mobiles and solves the dynamic problems encountered during rebounds of the winding wheels on the winding pegs as proposed in the prior art. .
  • the energy necessary for unlocking the winding rocker and the winding mobiles is also reduced by the inventive mechanism, which restores a greater part of the available energy transmitted to the regulator during the pulses.
  • the pendulum by its kinetic energy, triggers the unlocking phases of the driving force due to the kinematic connection of the detent rocker to the bistable leaf spring and the locking rocker.
  • each winding wheel comprises at least three identical winding cams regularly distributed over the periphery of said winding wheels.
  • the mechanism of the invention comprises two winding wheels arranged mobile in rotation around an individual pivot axis in a symmetrical position on either side of a straight line passing through the axis of rotation of the regulator and the point of inflection of the bistable leaf spring and are indexed in rotation with respect to each other so that the winding rocker is in contact on a said winding pin only 'with a single winding wheel alternating on one of the regulator and the other.
  • the locking rocker of the winding rocker is rotatable on a pivot axis and kinematically connected to the trigger rocker.
  • the locking rocker comprises a bar provided at a first end with a fork for connection to said trigger rocker and two locking arms extending symmetrically from each other from said bar and provided each at its free end of a locking pallet arranged to cooperate with a complementary locking member on said winding rocker.
  • the locking pallets are arcs of a circle concentric with the pivot point of the locking rocker. No pulling is thus caused on the locking rocker.
  • the complementary locking member on said winding rocker comprises one or two locking lugs of shape and orientation suitable for hooking a said locking pallet of the locking rocker.
  • This locking lug is advantageously arranged contiguous to the spouts supporting the winding pegs, between said spouts and the pallets of the locking rocker.
  • the fork of the locking rocker may comprise two horns defining a space between the horns with which an unlocking pin integral with the trigger rocker cooperates.
  • the locking rocker is arranged so that a locking pallet hooks a said locking lug of the winding rocker arranged on a first beak of the winding rocker following the displacement winding rocker pushed by a winding wheel thus causing jamming of a winding wheel on a winding peg arranged on the second beak of the winding rocker.
  • the invention also relates, according to a second aspect, to a timepiece comprising an escapement mechanism as defined above.
  • an escapement mechanism 1 in a preferred embodiment.
  • This mechanism in a conventional way, makes it possible to maintain the oscillations of an oscillating regulator, composed for example of a balance wheel 4 associated with a hairspring, by delivering to it energy received from a driving source, such as a barrel by example, not visible on the figure 1 , via a bistable leaf spring 2 working in buckling around a central point of inflection I, and whose ends are secured to a frame 9 for fixing to a watch movement frame such that it occupies a stable position corresponding to a first mode buckling.
  • a driving source such as a barrel by example
  • the leaf spring 2 cooperates with a winding rocker 3, a trigger rocker 5 and a locking rocker 8 in order to accumulate the energy from the driving source during winding phases, to remain in an armed state during locking phases and to restore the energy accumulated to said oscillating regulator 4 during pulse phases.
  • the trigger rocker 5 is kinematically linked to the leaf spring 2 substantially at its central point of inflection and thus pivots around this point of inflection. It comprises, at one end, a fork 51 and a stinger 53 intended to cooperate with a double plate 41, 42 of the rocker arm 4 and a plate pin 43 driven onto the large plate 41 of the double plate. It also comprises an unlocking pin 52 which cooperates with the fork 83 of a locking rocker 8 presented below.
  • the winding rocker 3 comprises a central portion 33 and two symmetrical winding arms 31, 32 whose ends are kinematically linked to the leaf spring 2, in particular in the example represented by winding tenons 31a, 32a inserted with sufficient clearance in the eyelets 2a, 2b of the bistable leaf spring 2.
  • the winding rocker 3 is rotatable around a coincident axis passing through the point of inflection I.
  • the winding rocker 3, the rocker trigger 5 and leaf spring 2 therefore all pivot around the same axis perpendicular to the plane of the figures 1 to 7 .
  • the winding 3 and trigger 4 rockers are mounted free to rotate with respect to their common axis of rotation.
  • the central portion 33 of the winding rocker 3 comprises at a rear end or tail two beaks 34a, 34b or projections symmetrical to each other with respect to a median axis of said central portion 33, each beak 34a, 34b carrying a winding pin 35a, 35b integral with said beak 34a, 34b and intended to cooperate with a winding wheel 6, 7.
  • the winding wheels 6, 7 each comprise a winding pinion 62, 72 meshing with a mobile end of the going train (not shown) so that the winding wheels 6, 7 pivot in a synchronized manner.
  • the winding wheels 6, 7 each comprise on their periphery a plurality of winding cams 61, 71, in this case three winding cams, angularly distributed in a regular manner with respect to the center of the winding wheels, these winding cams 61, 71 being identical to one another on the two wheels 6, 7 and each defining a cam surface 611, 711 whose shape and length are adapted to cooperate with the winding pins 35a, 35b of the rocker winding 3 in order to transmit the driving energy to the winding rocker 3 on the one hand and to block the rotation of the winding wheels 6, 7 during the locking phases on the other hand, according to the operation described above -After.
  • each winding pin 35a, 35b is made of a material with a low coefficient of friction such as ruby, corundum or even silicon and has a contact surface 351 with the cam track of the winding cams 61, 71 adapted to slide with reduced friction on said cam tracks.
  • the mechanism 1 further comprises a locking rocker 8 of the winding rocker 3, represented individually in figure 9 .
  • This locking rocker 8 is rotatably mounted on a pivot axis 86 on the frame of the watch movement and kinematically connected to the trigger rocker 5.
  • it comprises a bar 84 extending from a central body 85 , said bar 84 being provided at its free end with a connecting fork 83 to said trigger lever 5 by means of an unlocking pin 52 cooperating with the two horns 83a, 83b of the fork 83.
  • the locking lever 8 also comprises two locking arms extending symmetrically l each other from the central body 85 and each provided at its free end with a locking pallet 81, 82 in the form of a circular hook concentric with the axis of rotation of the locking rocker arranged to cooperate with a lug locking 36a, 36b of the winding rocker 3. This is so as not to cause pulling on the locking rocker and thus not inducing any geometric and dynamic recoil on the winding rocker and the winding wheels.
  • the locking lugs 36a, 36b and the pallets 81, 82 of the locking rocker are of shape and orientation suitable for hooking together when the winding rocker reaches one of its two locking positions, respectively dexter ( fig. 1 ) or sinister ( fig. 7 ), at the end of the winding phase of the bistable leaf spring 2 corresponding to the extreme positions occupied by the winding rocker 3 and the trigger rocker 4 as will be described later and so as not to cause pulling on the lock toggle.
  • the winding wheels 6, 7 and said winding rocker 3 are arranged respectively such that each winding mobile 6, 7 is stopped by jamming of a winding pin 35a, 35b on a cam surface of a winding cam 61, 71 of one of the winding wheels during the locking phases of the escapement mechanism, the locking rocker 8 further being arranged so that the locking pallets 81 , 82 hook a said locking pin 36a and 36b of the winding rocker 3 following the jamming of a winding wheel 6, 7 on a said winding peg 35a, 35b.
  • This combined locking mode of the winding wheels 6, 7 and the winding rocker 3 at the end of the winding of the bistable leaf spring 2 and during the locking phases is described below with reference to the figures 1 to 7 .
  • the configuration of the figure 1 corresponds to a locking phase subsequent to a dextral winding phase, in which the leaf spring 2 is armed in a state close to instability.
  • the stopping of the winding wheel 6 at the end of the winding takes place without rebound because the geometry of the winding cam surface 61 causes wedging between the left hand winding pin 35a of the winding rocker 3 and the winding cam surface 61 of the winding wheel 6 of a either side between the dexter locking lug 36b of the winding rocker and the pallet 82 of the locking rocker 8 on the other hand.
  • Pendulum 4 completes its ascending arc clockwise.
  • the leaf spring 2 transmits the energy accumulated during the previous winding to the balance and changes from a state close to instability to a stable state.
  • the locking rocker 8 is still in contact with the winding rocker 3 and the winding wheels 6, 7, and therefore the going train, are still stopped.
  • the trigger rocker 5 pivots around the point of inflection and drives the locking rocker 8 in rotation around its axis 86, which releases the locking pallet 82 from the lug 36 and thus releases the winding rocker 3 this without causing geometric recoil of the winding rocker.
  • the plate pin 43 has left the fork 52 of the trigger rocker 5 and the leaf spring 2 has transmitted all its energy to the rocker arm 4, and the winding rocker 3 is free.
  • the winding wheel 6 is also released from its support on the pin 35 of the winding rocker but has not yet started to rotate because of its inertia which is non-zero.
  • Pendulum 4 begins its ascending anti-clockwise arc.
  • the locking rocker 8 is already in the sinister locking position for the next winding. This is followed by the rotation of the winding wheels under the driving torque of the going train transmitted to the pinions 62, 72, as shown in figure 4 .
  • the pendulum 4 continues its anti-clockwise ascending arc during this interval.
  • the left arming phase is shown in figures 5 to 7 .
  • the initial phase is represented in the figure 5
  • the final winding and sinister locking phase being shown at figure 7 .
  • the initial phase of the left winding begins when a winding cam 71 of the winding wheel 7 comes into contact with the dexter winding pin 35b of the winding rocker 3.
  • the two winding wheels armature 6, 7 are then in rotational motion in a clockwise direction.
  • the engagement of the winding cam 71 against the pin 35b causes a pivoting of the winding rocker 3 counterclockwise, which induces a force of the arms 31, 32 on the leaf spring 2 on either side of its point of inflection, and the elastic loading thereof.
  • the balance wheel 4 is still continuing its ascending arc in the counterclockwise direction.
  • the device according to the invention thus makes it possible to eliminate the effects of contact rebound between the winding rocker 3 and the winding wheels such as encountered with the configurations of the prior art.
  • unlocking is also simplified because there is no longer any picking between the winding rocker and the winding wheel.
  • the jamming between the winding rocker and the locking rocker is easily released by the unlocking effect of the winding rocker during the relaxation phase, following the rotation of the trigger rocker 5, which suffices to pivot the locking rocker 8 and therefore release the winding rocker 3 from its counter-bearing force on the winding cams 61, 71.
  • This support being substantially punctual and the mutual friction forces being reduced because the wheels winding 6, 7 only have to overcome their own inertia to resume their rotation once the locking rocker is released, without the winding rocker 3 opposing an additional resistance force.
  • the locking rocker 8 then pivots on its axis on a portion corresponding to the spur of the trigger rocker 5, during this movement, in normal training (by the plate pin 43 of the balance) or in the event of an external shock, the trigger rocker 5 has not yet reached its point of instability and the locking rocker 8 has not yet released the locking lugs 36a, 36b of the winding rocker 3. Continuing the rotation of the plate pin, it still pushes the trigger rocker 5 to its point of instability. At this moment, the leaf spring 2 tends to return to its first buckling mode and it is at this moment that the impulse of the detent rocker 5 begins. At this moment, the winding cam 6, 7 is still locked by the locking rocker 8.
  • the rocker arm 4 is the source of energy which must overcome the frictional forces which are between the locking rocker 8 and the lugs 36a, 36b of the winding rocker 3 as well that the pressing force of the trigger rocker 5 against the stokers caused by the buckling of the leaf spring 2.
  • the pallets 81, 82 of the locking rocker 8 are concentric at its pivot point, this in order not to cause any pulling and to take as little energy as possible from the rocker arm 4 when unlocking the the driving force.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Electromechanical Clocks (AREA)
  • Transmission Devices (AREA)

Claims (12)

  1. Hemmungsmechanismus (1), der angeordnet ist, um Impulse mechanischer Energie von einer Antriebsquelle an einen schwingenden Regler (4) einer Uhr mit Hilfe einer durch Knickung um einen Wendepunkt (I) arbeitenden Blattfeder (2) zu übertragen, wobei die besagte Blattfeder (2) mit Hilfe einer Spannwippe (3) und einer Auslösewippe (5) fähig ist, die aus der Antriebsquelle stammende Energie während einer Spannphase zu speichern, anschliessend während einer Sperrphase in einem gespannten Zustand zu bleiben, dann die gespeicherte Energie an den besagten schwingenden Regler (4) während einer Auslösephase zurückzugeben, wobei die Spannwippe (3) angeordnet ist, um mit mindestens einem Spannrad (6, 7) so zusammenzuwirken, dass die Blattfeder (2) während der Spannphasen gespannt wird, wobei das oder jedes Spannrad (6, 7) an einer Peripherie eine Vielzahl von Spannnocken (61, 71) aufweist, die jeder eine Nockenfläche definieren, und die Spannwippe (3) mindestens einen Spannstift (35a, 35b) aufweist, der einen Nockenmitnehmer bildet, dergestalt, dass jeder Spannstift (35a, 35b) auf der Nockenfläche (611, 711) eines der Spannnocken (61, 71) während der Spannphasen der Blattfeder gleitet, wobei der Mechanismus darüber hinaus eine Sperrwippe (8) der Spannwippe (3) mindestens während der Sperrphasen umfasst, Mechanismus, in dem die Sperrwippe (8) zwei Sperrpaletten (81, 82) umfasst, die angeordnet sind, um mit komplementären Sperrorganen (36a, 36b), insbesondere Dorne, auf der besagten Spannwippe (3) zusammenzuwirken, und dadurch gekennzeichnet, dass das mindestens eine besagte Spannrad (6, 7) und die besagte Spannwippe (3) jeweils so angeordnet sind, dass das oder jedes Spannrad (6, 7) durch Verkeilung zwischen einem Spannstift (35a, 35b) und einer Nockenfläche eines besagten Spannnocken (61, 71) und zwischen einer besagten Sperrpalette (81, 82) und einem besagten komplementären Sperrorgan (36a, 36b) am Ende jeder Spannphase und während der Sperrphasen gestoppt wird.
  2. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass jeder Spannstift (35a, 35b) eine Kontaktfläche (351) im Nockenweg der Spannnocken (61, 71) mit kreisförmigem Querschnitt aufweist, wobei jeder der besagten Stifte auf einem Schnabel(34a, 34b) der Wippe angeordnet ist.
  3. Mechanismus nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass jedes Spannrad (6, 7) mindestens drei identische Spannnocken (61, 71) umfasst, die gleichmässig an der Peripherie der besagten Spannräder verteilt sind.
  4. Mechanismus nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass er mindestens ein Spannrad (6, 7) umfasst, das drehbeweglich um eine individuelle Schwenkachse angeordnet ist, die auf einer Geraden liegen kann, die durch die Drehachse des Reglers (4) und den Wendepunkt der bistabilen Blattfeder (2) verläuft, und dadurch, dass die Spannstifte (35a, 35b) an einer Innenwand eines mit der Spannwippe (3) fest verbundenen Rings angeordnet sind, in welchem das Spannrad so angeordnet ist, dass ein besagter Spannstift (35a, 35b) nur mit einem einzigen Spannnocken des Spannrads auf einer Halbschwingung des Reglers (4) in Kontakt kommt.
  5. Mechanismus nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass er zwei Spannräder (6, 7) umfasst, die drehbeweglich um eine individuelle Schwenkachse in symmetrischer Position auf beiden Seiten einer Geraden angeordnet sind, die durch die Drehachse des Reglers (4) und den Wendepunkt der bistabilen Blattfeder (2) verlaufen kann, und in Rotation zueinander indexiert sind, dergestalt, dass die Spannwippe (3) auf einem besagten Spannstift (35a, 35b) nur mit einem einzigen Spannrad auf einer Halbschwingung des Reglers (4) in Kontakt kommt.
  6. Mechanismus nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die Sperrwippe (8) der Spannwippe (3) drehbar auf einer Schwenkachse (86) ist und bewegungsverbunden mit der Auslösewippe (5) ist.
  7. Mechanismus nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass die Sperrwippe (8) eine Barrette aufweist, die an einem ersten Ende mit einer Verbindungsgabel an der besagten Auslösewippe (5) versehen ist, und zwei Sperrarme, die sich symmetrisch zueinander von der besagten Barrette erstrecken und jeder an seinem freien Ende mit einer besagten Sperrpalette (81, 82) versehen ist.
  8. Mechanismus nach Anspruch 7, dadurch gekennzeichnet, dass jede Sperrpalette aus einem zur Drehachse der Sperrwippe konzentrisch liegendem Kreissegment besteht.
  9. Hemmungsmechanismus nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass das komplementäre Sperrorgan auf der besagten Spannwippe (3) einen Sperrdorn (36a, 36b) umfasst, in Form und Ausrichtung so angepasst, um in eine besagte Sperrpalette (81, 82) der Sperrwippe einzuhaken.
  10. Hemmungsmechanismus nach einem der Ansprüche 7 bis 9, dadurch gekennzeichnet, dass die Gabel der Sperrwippe (8) zwei Hörner (83a, 83b) umfasst, die einen Raum zwischen den Hörnern begrenzen, in dem ein mit der Auslösewippe (5) fest verbundener Stift (52) zum Entriegeln zusammenwirkt.
  11. Hemmungsmechanismus nach einem der Ansprüche 5 und 9, dadurch gekennzeichnet, dass die Sperrwippe (8) so angeordnet ist, damit eine Sperrpalette (81,82) in einen besagten Sperrdorn (36a, 36b) der Spannwippe (3), der auf einem ersten Schnabel der Spannwippe angeordnet ist, einhakt, im Wesentlichen gleichzeitig zur Verkeilung eines Spannrads (6, 7) auf einem Spannstift (33), der auf dem zweiten Schnabel der Spannwippe angeordnet ist.
  12. Uhr mit einem Hemmungsmechanismus nach einem der Ansprüche 1 bis 11.
EP18193657.6A 2018-09-11 2018-09-11 Uhrhemmungsmechanismus mit bistabiler blattfeder Active EP3623875B1 (de)

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EP3623875B1 true EP3623875B1 (de) 2023-04-26

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Publication number Priority date Publication date Assignee Title
EP2105806B1 (de) 2008-03-27 2013-11-13 Sowind S.A. Hemmungsmechanismus
CH710685B1 (fr) 2015-01-30 2019-07-15 Sowind S A Mécanisme d'échappement.
EP3273308B1 (de) 2016-07-18 2019-06-12 Sowind S.A. Hemmungsmechanismus

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