EP3599514A1 - Hemmungsmechanismus mit bistabilen und monostabilen federn - Google Patents

Hemmungsmechanismus mit bistabilen und monostabilen federn Download PDF

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Publication number
EP3599514A1
EP3599514A1 EP18185387.0A EP18185387A EP3599514A1 EP 3599514 A1 EP3599514 A1 EP 3599514A1 EP 18185387 A EP18185387 A EP 18185387A EP 3599514 A1 EP3599514 A1 EP 3599514A1
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EP
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Prior art keywords
lever
winding
exhaust
bistable
elastic
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EP18185387.0A
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English (en)
French (fr)
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EP3599514B1 (de
Inventor
Nicolas Déhon
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Sowind SA
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Sowind SA
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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
    • G04B15/10—Escapements with constant impulses for the regulating mechanism
    • 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

Definitions

  • the present invention relates to the field of watchmaking and relates, more particularly, to a bistable spring escape mechanism formed by a blade working in buckling around a central point of inflection in cooperation with a winding rocker. and an expansion lever for transmitting pulses of mechanical energy from a motor source to an oscillating regulator of a timepiece.
  • the Demand WO 2018/002773 proposed an escape mechanism comprising a bistable leaf spring and a single escape mobile to drive a winding rocker during the winding phases, the escape mobile comprising a coaxial winding member arranged for cooperate with the winding rocker like a gear to rotate the winding rocker alternately in opposite directions.
  • the aim of the present invention therefore consists in providing a solution to the functional defects of the structural approach of a bistable spring exhaust mechanism proposed in WO 2018/002773 while retaining the advantages of the latter in terms of efficiency and compactness of construction.
  • the mechanism of the invention is further characterized in that it comprises a monostable elastic member dimensioned in such a way that it compensates for the variation in the driving torque of the winding lever by the exhaust mobile depending on the direction of rotation of said winding lever.
  • the mechanism of the invention thus makes it possible, by virtue of the provision of a monostable elastic member for compensating for bearing, the variations in winding torque applied to the winding rocker by the escape wheel according to the direction of rotation of this last in a configuration as proposed in WO 2018/002773 , and thus, by adapting the return force of the monostable elastic compensation member according to the dimensions of the other elements of the exhaust mechanism and the characteristics of the bistable elastic blade, to guarantee the alternating tilting of the winding lever perfectly balanced, without unnecessary energy loss or risk of blockage, with increased efficiency compared to similar exhaust mechanisms. This makes the exhaust mechanism more reliable and reliable.
  • the monostable elastic compensation member is coupled to the winding lever and arranged to exert on the latter a restoring torque in a single direction of rotation.
  • the mechanism of the invention comprises two identical escapement mobiles each provided with peripheral teeth and capable of meshing with a mobile the work train of a clockwork movement to pivot simultaneously in the same direction around d '' a proper axis of rotation and meshing each with a winding lug formed on an internal field of first and second eyelets formed symmetrically on the winding rocker.
  • the monostable elastic compensation member can be chosen as a leaf spring working in bending, a leaf spring working in buckling, or even a spiral spring.
  • the monostable elastic compensation member may be integral at a first end with a stud formed on the armature rocker and at a second end with an anchoring member to a frame element of a so-called watch movement or a timepiece.
  • anchoring points of said bistable elastic blade are also preferably located on said anchoring member to a frame element of a timepiece movement or of a timepiece.
  • the monostable elastic compensation member is a leaf spring made of material in monolithic form with a fixing frame to a frame element of a watch movement or a timepiece.
  • the bistable elastic blade is also preferably made in one piece in monolithic form with said fixing frame to a frame element of a watch movement or a timepiece and the elastic compensation member.
  • the bistable elastic blade and the monostable elastic compensation member are made of silicon. More particularly, the elastic blade and the monostable elastic compensating member, as well as the fixing frame from which they have come, if necessary, can be obtained by deep silicon etching processes.
  • the escape mechanism of the invention also advantageously comprises a locking lever arranged in kinematic connection with the trigger lever and configured to block the cocking lever in a first and a second extreme position outside the blade trigger phases elastic.
  • the locking lever comprises a bar provided at one end with a fork connecting to said trigger lever and two locking arms extending symmetrically from one another from said bar and each provided at its free end of a locking pallet arranged to cooperate with a complementary locking member on said winding lever.
  • said complementary locking member on said winding lever comprises a locking lug of shape and orientation suitable for hooking a said locking pallet of the locking lever.
  • the fork of the locking lever comprises two horns delimiting a space between horns into which is inserted an unlocking peg secured to the trigger rocker.
  • This exhaust mechanism comprises a first and a second escape wheel 4, 5 movable each in rotation respectively about a first axis D and a second axis G.
  • the two escape wheels 4, 5 mesh a mobile of the clockwork of a watch movement (of which only the fifth wheel 8 and the pendulum 0 are shown in the figures), in this case a fifth wheel 8 movable in rotation about an axis H, by the intermediate a first and a second exhaust pinion 6, 7 respectively coaxially integral with said first and second exhaust wheels 4,5.
  • the escape wheels 4, 5 are arranged to transmit a portion of mechanical energy from a driving source of the watch movement, typically a or several barrel springs, with motion regulator, formed of a pendulum 0 arranged to be movable in rotation about an axis K and carrying, in a conventional manner, a double plate 1 provided on its large plate with a dowel pin 1a.
  • the escape wheels 4, 5 cooperate to do this with a winding lever 3 pivotally mounted about an axis F and a bistable leaf spring L.
  • the bistable leaf spring L is formed by an elastic blade initially straight whose ends A, B have been brought symmetrically with respect to a midpoint to constrain said blade in buckling such that the latter is able to pivot around said midpoint, forming the point of inflection of the bistable leaf spring L, this inflection point being situated on the axis F of rotation of the winding lever 3.
  • the bistable leaf spring L thus comprises on either side of its inflection point two half-blades 10a, 10b elastic, each having in a state of rest, said stable state, an opposite concavity of the other half-blade.
  • the ends A, B forming anchors of the bistable leaf spring L are advantageously secured to a frame 10e capable of being fixed on a frame, for example a plate, of the watch movement, said frame 10e thus providing by construction the necessary buckling stress on the bistable leaf spring L, therefore on the half-blades 10a, 10c.
  • the bistable leaf spring L, the two half-blades 10a, 10c and the frame 10e are advantageously formed as a monolithic piece of silicon by deep etching processes, which makes it possible to obtain extremely dimensioned pieces. precise in accordance with the constraints and performances calculated beforehand as a function of the dimensions of the other parts of the escapement but also of the timepiece movement in which said escapement mechanism is implemented.
  • Said bistable leaf spring L is intended, in a manner known per se, to accumulate the mechanical energy of the driving source of the movement transmitted by the escapement wheels 4, 5 to the winding lever 3 in the form of a torque d dextral drive M d ( Figure 2 , 3 ), respectively senestre M g ( Figure 6 , 7 ), of said winding lever 3 around the axis F, said winding lever 3 being integral with the bistable leaf spring L substantially at the midpoints of each half-leaf 10a, 10b located on either side of the inflection point of the bistable leaf spring L.
  • connection of the arm lever 3 to each half-blade 10a, 10b is advantageously carried out at the ends of two arms of said arm lever 3 by means of two arm pins 10, 3f inserted in eyelets 10e , 10f corresponding formed of material in the middle of each half-blade 10a, 10b.
  • the winding rocker 3 advantageously has symmetry along a median plane passing through the axes of rotation F, respectively K of the winding rocker, respectively of the oscillator, so that the connecting points of the connecting arms of the winding lever 3 to the bistable leaf spring L are equidistant from the axis of rotation F of said winding lever by a distance R e , and thus suitable for applying to the middle of each half-leaf 10a, 10b a winding force F e of the bistable leaf spring 10 providing a winding torque M e capable of passing each half-blade 10a, 10b from a stable state to a metastable state called winding (shown in the figures 2 , 3 , 6 , 7 by lines in strong solid lines of each half-blade) in which each half-blade 10a, 10b is charged with an elastic energy then discharged and transmitted to the balance 0 by means of a trigger lever 2.
  • the trigger lever 2 is arranged integral with the leaf spring L at its point of inflection and therefore movable in rotation itself also around the axis F, common to the winding lever 3. However, the trigger lever 2 is independent in rotation of the cocking lever 3.
  • the trigger lever 2 has ( Figure 1B ) conventionally a fork for cooperation with the plate pin 1a of the double plate 1 of pendulum 0, said fork comprising internal horns 2b, 2c and external 10i, 10j as well as a central dart 2a intended to prevent any overturning as in an anchor escapement.
  • the trigger lever 2 thus pivots about the axis F only under the action of the plate pin 1a in its detent horns 2b, 2c during the alternations of the balance 2, thus transmitting to the latter the accumulated elastic energy in the armored state of the bistable leaf spring L.
  • the trigger lever 2 can be formed monolithically with the bistable leaf spring L, so that the axis of rotation F of the trigger lever 2 coincides at the point of inflection Median of the bistable leaf spring L.
  • the movements of the trigger lever 2 are limited by stops in the form of pins or locks I, J for example integrated in monolithic form also with the 10th frame and the leaf spring L, the whole constituting a single piece 10 fixed on the plate of the watch movement.
  • said trigger lever 2 comprises an unlocking pin 2d, inserted into a link fork of a locking lever 9 of the arm lever 3.
  • This locking lever 9 is intended to operate the locking of said winding lever 3 in the dextral (clockwise rotation of said winding lever 3) and senestre (counterclockwise rotation of said winding lever 3) arming positions of the bistable leaf spring L, in which each half-blade 10a, 10b of the latter are in their metastable state of reinforcement.
  • the locking lever 9 is mounted movable about an axis of rotation H, in the example presented common to the fifth wheel 8, but which could also be arranged otherwise.
  • a central bar 9e one free end of which, opposite the axis of rotation H, comprises first and second unlocking horns 9a, 9b defining the connection fork to the trigger lever 2, between which the release pin 2d.
  • the unlocking horns 9a, 9b extend symmetrically with respect to the axis of rotation H and the central bar 9e two locking arms carrying at their free end a right locking pallet 9c and a pallet left locking device 9d respectively, arranged to cooperate with locking pins 3c, 3d of the arm lever 3, formed on a locking tail 3k of said locking lever 3, said locking tail being visible in more detail on the figures 4 and 5 .
  • the winding of the bistable leaf spring L results, as mentioned above, from the transmission of the mechanical drive torque from the driving source of the watch movement to the winding lever 3.
  • This torque transmission takes place according to the exhaust mechanism of the invention by meshing the teeth of the escapement wheels 4,5 with reinforcement lugs 3a, 3b formed on an internal field of a first and a second winding ring 3i, 3j, equidistant from the median axis of the winding lever 3 like the arms connecting to the bistable leaf spring L, said winding rings 3i, 3j each delimiting an oblong opening in which is housed one of the escape wheels 4, 5.
  • the winding ring 3i comprises a winding lug 3a arranged on an internal field of the external edge of the ring 3i, that is to say the edge furthest from the axis of rotation F of the rocker armament 3, and the armament ring 3j has a armament lug 3b arranged on an internal field of the inner edge of the ring 3j, that is to say the edge closest to the axis of rotation F of the cocking lever 3.
  • This particular configuration of the cocking rings 3i, 3j and the arrangement of the escapement wheels 4, 5 in the openings thereof provides a decoupling of the dexter cocking functions and armamentary cocking of the cocking lever 3 on the escape wheel 4 in the cocking ring 3i for dextral cocking on the one hand, and on the escape wheel 5 in the ring d 3j armage for the main armament on the other hand, as will be described in detail below.
  • the escape wheel 4 meshes with said winding pin 3a of the winding ring 3i during dextrous winding phases of the bistable leaf spring L, the second escape wheel 5 then being devoid of contact with the cocking pin 3b of the cocking ring 3j.
  • the escape wheel 5 meshes with said winding lug 3b of the winding ring 3j during phases of winding the bistable leaf spring L, the first escape wheel 4 then being without contact with the cocking lug 3a of the cocking ring 3i.
  • the distances R d , R g of application of the winding forces F d , F g applied by the teeth of the escape wheels 4, 5 on the winding pins 3a, 3b relative to the axis F during the dexter and senestre arming phases of the arming lever 3, are different, and therefore the dexter arming couples M d and senestre M g applied by each escape wheel 4, 5 are necessarily different, the lever arm R g , and therefore the winding torque M g , senestre being in practice less than the lever arm R d and the dexter winding torque M g while the applied forces F d , F g are equal (the gear ratio of the escape wheels 4,5 with the fifth wheel 8 is preferably equal), which causes the same potential drawbacks as those identified of the previous mechanism described in WO 2018/002773 .
  • this compensatory device consisting essentially of the provision of an elastic member monostable 10c for compensating for a variation in the driving torque of the winding lever 3 by the exhaust mobiles 4, 5 according to the dexter and senestre winding rotations.
  • the elastic compensation member advantageously consists of a monostable leaf spring 10c arranged to exert a restoring force complementary to the winding force applied by the escape wheel 5 on the lug 3b of the rocking arm 3 during the phases of the armament, said monostable leaf spring 10c preferably working in buckling.
  • said monostable leaf spring 10c preferably working in buckling.
  • it could also provide a compensating leaf spring 10c working in bending, or even a spiral spring arranged between the frame of the movement for example and the winding lever 3.
  • the compensating leaf spring 10c preferably extends from a first anchor point C on the frame 10e and a second anchor point on the tail 3k of the arm lever 3, formed for example in the form presented by an eyelet 10g at the end of the compensating leaf spring 10c adjusting with play in a stud secured to a tail 3k of the arm lever 3, at the base of the release horns 9a, 9b of the fork of locking lever 9.
  • the compensating leaf spring 10c can also be obtained in monolithic form with the frame 10e and its bistable leaf spring L, which comprises two half-blades 10a, 10b connected together by a part 10d of the trigger rocker.
  • This monolithic assembly can in particular be made of silicon, by deep etching processes, well known in the field of watchmaking and microtechnology in general.
  • the figures 2 to 5 represent a first alternation of the pendulum 0 with arming and locking during the additional arc of the pendulum 0 then an unlocking and dexter trigger operating during its angle of lift, the arm 3 and trigger 2 rockers successively rotating in one direction dextral rotation, that is to say with a rotation in direction.
  • the dextral arming phase ( Figure 2 ) is initiated when a tooth of the escapement wheel 4, driven by the fifth wheel 8 in a clockwise movement, meshes the winding lug 3a of the winding ring 3i, thus applying to the point of meshing a force F d with a lever arm R d relative to the axis F of rotation of the winding lever 3, providing a dexter winding torque M d .
  • This dextrous winding torque M d rotates the winding lever 3 around its axis F clockwise, which imposes what requires the two half-blades 10a, 10b to leave a stable state for a metastable state and therefore to cause, by reaction of the bistable elastic blade L, forces F e acting on the winding lever 3 by means of the eyelets 10e, 10f acting on the tenons 3e, 3f (represented by the lines in strong lines ), without the trigger lever 2 moving.
  • the dextral rotation of the winding lever 3 also constrains the compensating leaf spring 10c which also undergoes buckling.
  • the monostable compensation leaf spring 10c thus applies a reaction force F c to the winding lever 3 by its eyelet 3g on the lug 3g of the winding lever 3
  • the locking pin 3d of the tail 3k of the lever rocker 3 engages the locking pallet 9d of the lever lever 9 and hooks with it, operating the dexter lock of the lever lever 3, and then blocking the leaf spring bistable L in a metastable state, the monostable compensation spring 10c being in turn in a state close to its maximum arming state.
  • the trigger lever 2 is substantially stationary, in stable support by the right outer horn 10j against the bar J, the pendulum 0 finishing traversing its additional ascending dexter arc or begins its additional descending arch.
  • the pendulum 0 begins its return to neutral and its second alternation in counterclockwise rotation on its axis, that is to say its additional descending sinister arc.
  • the dexter unlocking phase begins when the plate pin 1a comes into contact with the left inner horn 2b of the trigger lever 2 and ends when this pin is substantially on the center line.
  • This unlocking analogous to the release of the anchor in a Swiss anchor escapement, induces an inflection of the bistable leaf spring L around its inflection point I which leaves its metastable state to reach its unstable state proper, this thanks to the dexter rotation of the trigger lever 2 about its axis F.
  • the rotation of the trigger lever 2 undergoes the relaxation of the bistable leaf spring L which transmits the elastic energy accumulated in its unstable state of armament at pendulum 0 and then goes into a second stable state of rest, in which the concavity of the half-blades 10a, 10b is reversed with respect to that of the start of arming, shown in the figure 1 or 2 .
  • the compensating leaf spring 10c itself remains in the armed state and in fact even more constrained due to the complementary rotation of the winding lever 3 clockwise following the expansion of the bistable leaf spring L, up to 'so that the trigger lever 2 comes into abutment on the left outer horn 10i against the bar I, the plate pin 1a then leaves the trigger fork and starts its additional arc on the second half-wave of the pendulum 0 ( figures 6 and 7 ).
  • the pallet 9d of the locking lever 9 detaches from the hook 3d, thereby releasing the cocking lever 3, which is free to pursue a small dexter unlocking angle sufficient for its cocking pin. 3a frees the tooth of the armament mobile 4 hitherto engaged.
  • the two winding wheel, both meshing with their winding pinion 6, 7 at the wheel fifth 8 rotate in concert until a tooth of the winding wheel 5 meets the winding lug 3b of the winding lever 3, then initiating the phase of winding the bistable leaf spring 10 ( figure 6 ).
  • the compensating leaf spring 10c then compensates for the lack of arming torque M g of the escape wheel 5 by the progressive release of the elastic energy accumulated during the arming and dexter expansion phases, which induces a thrust F c on the tail 3k of the winding lever 3, and therefore a compensation torque M e which, added to the winding torque M g , is able to overcome the feedback torque 2 x F e x R e necessary to produce the armature of the bistable leaf spring L.
  • the locking pin 3c of the tail 3k of the rocking lever 3 engages the locking pallet 9c of the locking lever 9 and hooks with it, operating the senestrial locking of the lever lever 3, and then blocking the bistable leaf spring L in a metastable state.
  • the trigger lever 2 is substantially stationary, in stable support by its left outer horn 10i against the bar I, the pendulum 0 traversing all of its additional ascending semester arc and possibly a part of its additional descending dexter arc.
  • the pendulum 0 finishes its additional dexter arc descending towards the angel next lift, itself consisting of an unlocking and a senestre trigger.
  • the compensating leaf spring 10c is practically discharged, close to rest ( figure 8 )
  • the senestre unlocking phase begins when the plateau pin 1a comes into contact with the right inner horn 2c of the trigger lever 2 and ends when this pin is substantially on the center line.
  • This unlocking analogous to the release of the anchor in a Swiss anchor escapement, induces an inflection of the leaf spring L around its inflection point I which leaves its metastable state to reach its unstable state proper, this thanks to the rotation of the trigger flip-flop 2 around its axis F. ( figures 8 and 9 ).
  • the pallet 9c of the locking lever 9 detaches from the locking pin 3c, thereby releasing the winding lever 3.
  • the rotation of the trigger lever 2 causes the bistable leaf spring 10 to relax.
  • the bistable leaf spring L is again in a stable state, ready for a new dextral winding and so on.
  • the exhaust mechanism of the invention can also be declined in a second embodiment comprising a single escape wheel 4, like the proposal made in WO 2018/002773 .
  • This second embodiment is shown in a preferred embodiment in figures 10 to 18 .
  • the dextral arming phase ( figure 11 ) is initiated when a tooth of the escapement wheel 4, integral with its pinion 6, itself meshing with the fifth wheel 8 in a dextrous rotation, meshes with the winding pin 3a located on the upper arm ( with reference to the figure) of the winding ring 3i, thus applying to the point of engagement a force F d with a lever arm R d relative to the axis F of rotation of the winding rocker 3, providing a dextral winding torque M d .
  • This dexter winding torque M d rotates the winding lever 3 around its axis F clockwise, which makes it possible to overcome the force couple 2 x F e x R e coming from the feedback produced by the bistable elastic spring L by its two eyelets 10e, 10f formed in its two half-blades 10a, 10b acting on the lugs 3e, 3f of the winding lever 3, without the trigger lever 2 not moving.
  • the dextral rotation of the winding lever 3 also constrains the compensating leaf spring 10c which in this case undergoes simple bending.
  • the compensating leaf spring 10c thus applies a force to the armature lever. of reaction F c by its tenon 3g with a lever arm R c , inducing a torque opposite to the dexter winding torque M d .
  • the locking lug 3d of the latch 3 located on the right external field of the letting ring 3i, engages the locking pallet 9d of the latch 9 and hooks with it, operating the locking dexter of the winding lever 3, and then blocking the bistable leaf spring 10 in a metastable state and the compensating leaf spring 10c in bending.
  • the trigger lever 2 is substantially stationary, in stable support by its right outer horn 10j against the bar J, the pendulum 0 finishing traversing its additional ascending dexter or beginner arc its additional descending arch.
  • the escape wheel 4 then disengages from the winding lug 3a when a tooth from the escape wheel 4 in turn engages the lug 3b from the winding ring 3i, which corresponds substantially to the moment.
  • unlocking ( figure 13 ) effective either after the moment when the plateau pin 1a comes into contact with the right horn 2b of the trigger lever 2 but substantially before the moment when the plateau pin 1a is on the center line, initiating the trigger phase dexter ( figure 13 and 14 ).
  • the pallet 9c of the locking latch 9 detaches from the locking lug 3c, thus releasing the arming latch 3 for the phase of arming the bistable leaf spring 10 ( figure 15 ).
  • the plateau pin 1a strikes the left horn 2b of the trigger lever 2, inducing the inflection of the bistable leaf spring 10 around its point of inflection on the axis F simultaneously with the rotation of the lever detent 2.
  • the rotation of the detent lever 2 is driving with respect to the bistable leaf spring L and allows it to leave its metastable state (close to its unstable state) to reach the unstable state proper.
  • the bistable leaf spring L becomes a motor vis-a-vis the trigger lever 2 and transmits its accumulated energy to the balance 0 and then passes into a second stable state of rest, in which the concavity of the half-blades 10a, 10b is reversed with respect to that of the start of winding up, shown in the figure 10 or 11 .
  • the compensating leaf spring 10c itself remains under maximum bending stress, the complementary dextral rotation of the winding lever 3 clockwise then being maximum, the trigger lever 2 abuts on its left outer horn 10i against the label I.
  • the dowel pin 1a then leaves the fork of the trigger lever 2 and begins its additional ascending arc on the second half-swing of pendulum 0 ( figures 15 and 16 ).
  • the compensating leaf spring 10c then compensates for the lack of arming torque M g of the escape wheel 4 by the progressive release of the elastic energy accumulated during the arming and dexter unlocking phases, which induces a thrust F c on the rocking arm 3, and therefore a compensation torque M c which, added to the earthly arm torque M g is able to overcome the feedback couple 2 x F e x R e necessary to produce reinforcement of the bistable leaf spring L.
  • the locking pin 3c of the cocking lever 3 located on the left external field of the cocking ring 3i engages the locking pallet 9c of the locking lever 9 and hooks with it, operating the senestrial locking of the rocking arm 3, and then blocking the bistable leaf springs L in a metastable state.
  • the trigger 2 is substantially stationary, in stable support by its right outer horn 10j against the label J, the pendulum 0 finishing to travel its additional ascending or beginning semester arc its additional dexter arc descending at the end from the locking phase, the pendulum 0 begins its return to neutral, ie its additional descending dexter arc.
  • the compensating leaf spring 10c is in a lower arming state than that which existed when the arming lever 3 was in the dextral locking position ( figure 13 ).
  • the senestre unlocking phase begins when the plateau pin 1a comes into contact with the right inner horn 2c of the trigger lever 2 and ends when this pin is substantially on the center line.
  • This unlocking analogous to the release of the anchor in a Swiss anchor escapement, induces an inflection of the leaf spring L around its inflection point I which leaves its metastable state to reach its unstable state proper, this thanks to the rotation of the trigger flip-flop 2 around its axis F. ( figures 17 and 18 ).
  • the pallet 9c of the locking lever 9 detaches from the locking pin 3c, thereby releasing the cocking lever 3.
  • the expansion phase begins when the trigger lever 2 becomes driven and therefore when its left horn 2b strikes the plateau pin 1a.
  • the rotation of the trigger lever 2 undergoes the relaxation of the bistable leaf spring L which transmits to it the elastic energy accumulated while it was in its unstable armament state in the balance wheel and then goes into its stable armament state, shown in the figure 17 or 18 .
  • the compensating leaf spring 10c is then also in a weakly armed state and therefore weakly stressed and only has a low state of elastic deformation energy.
  • the bistable leaf spring L is again in a state of rest, ready for a new dextral winding and so on.
  • the mechanism of the invention thus makes it possible, whatever the embodiment considered, to overcome the variations in winding torque applied to the rocking lever 3 by one or more wheels of escapements cooperating in engagement with said winding rocker in the direction of rotation, variations inherent in such a mode of driving the rocking rocker.
  • the monostable compensating leaf spring 10c whether it is designed to work in buckling or in bending, or whether it is in a spiral, allows with an appropriate dimensioning according to known calculation principles.
  • the compensating leaf spring 10c knowing the mechanical characteristics of the bistable leaf spring L, determining the maximum winding moment necessary for the passage of the half-leaves 10a, 10b d '' a stable state of rest at their metastable state of arming, as well as the arms of dextral and senestrial arming determined by the distance of application of the arming force of the escape wheel (s) 4, 5 relative to the axis F of rotation of the winding lever 3.
  • the present invention has been described above with reference to two preferred particular embodiments making it possible to demonstrate the relevance of the implementation of a monostable elastic member compensating for winding torque of a bistable leaf spring in the frame of a bistable spring escapement with one or more exhaust mobiles cooperating in the manner of a gear with a lever for winding the bistable spring.
  • the arm lever 3 could take other forms than that presented, just as the monostable compensation spring could also be arranged differently from the form presented, provided that its return action on the arm lever 3 is consistent to the principles presented in the present invention.
  • the locking of the cocking lever 3 could also be carried out differently.

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EP18185387.0A 2018-07-25 2018-07-25 Hemmungsmechanismus mit bistabilen und monostabilen federn Active EP3599514B1 (de)

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EP3599514B1 EP3599514B1 (de) 2023-06-07

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4535089A1 (de) 2023-10-04 2025-04-09 Sowind S.A. Auspuffmechanismus mit bistabiler blattfeder
EP4535088A1 (de) 2023-10-04 2025-04-09 Sowind S.A. Auspuffmechanismus mit bistabiler blattfeder

Citations (8)

* Cited by examiner, † Cited by third party
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WO1999064936A1 (fr) 1998-06-08 1999-12-16 Manufacture Des Montres Rolex S.A. Procede pour transmettre des impulsions d'energie mecanique d'unesource motrice a un regulateur oscillant
WO2009118310A1 (fr) 2008-03-27 2009-10-01 Girard-Perregaux S.A. Mécanisme d'échappement
CH705674A2 (fr) 2011-10-27 2013-04-30 Sowind S A Mécanisme d'échappement.
CH710925A2 (fr) 2015-01-30 2016-09-30 Sowind S A Mécanisme d'échappement.
EP3208662A1 (de) * 2016-02-08 2017-08-23 Hepta Swiss SA Uhrwerk, das eine reguliervorrichtung umfasst
CH712631A1 (fr) * 2016-06-27 2017-12-29 Mft Et Fabrique De Montres Et Chronomètres Ulysse Nardin Le Locle S A Echappement pour mouvement d'horlogerie.
WO2018002773A1 (fr) 2016-06-27 2018-01-04 Patek Philippe Sa Geneve Echappement d'horlogerie
WO2018015146A1 (fr) 2016-07-18 2018-01-25 Sowind SA Mecanisme d'echappement

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999064936A1 (fr) 1998-06-08 1999-12-16 Manufacture Des Montres Rolex S.A. Procede pour transmettre des impulsions d'energie mecanique d'unesource motrice a un regulateur oscillant
WO2009118310A1 (fr) 2008-03-27 2009-10-01 Girard-Perregaux S.A. Mécanisme d'échappement
CH705674A2 (fr) 2011-10-27 2013-04-30 Sowind S A Mécanisme d'échappement.
CH710925A2 (fr) 2015-01-30 2016-09-30 Sowind S A Mécanisme d'échappement.
EP3208662A1 (de) * 2016-02-08 2017-08-23 Hepta Swiss SA Uhrwerk, das eine reguliervorrichtung umfasst
CH712631A1 (fr) * 2016-06-27 2017-12-29 Mft Et Fabrique De Montres Et Chronomètres Ulysse Nardin Le Locle S A Echappement pour mouvement d'horlogerie.
WO2018002773A1 (fr) 2016-06-27 2018-01-04 Patek Philippe Sa Geneve Echappement d'horlogerie
WO2018015146A1 (fr) 2016-07-18 2018-01-25 Sowind SA Mecanisme d'echappement

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4535089A1 (de) 2023-10-04 2025-04-09 Sowind S.A. Auspuffmechanismus mit bistabiler blattfeder
EP4535088A1 (de) 2023-10-04 2025-04-09 Sowind S.A. Auspuffmechanismus mit bistabiler blattfeder

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