EP3040783B1 - Sub-assembly for a mechanism for adjusting a speed in a clock movement and such a mechanism - Google Patents

Description

Technical field of the invention

The present invention relates to the field of watchmaking and is more particularly concerned with the function that an escapement and an oscillator together perform together in a watch movement and which is to adjust an average speed at the base of the different speeds in this field. watch movement. More specifically, the invention relates to a subassembly for a mechanism for adjusting a mean angular velocity in a watch movement, as well as such a mechanism.

State of the art

In a watchmaking movement, a driving member provides the driving energy, which a finishing gear transmits to the wheel of an escapement interacting with a mechanical oscillator. The speeds of the gears in the work train are all proportional to a rotational speed, which is the speed of rotation of the escape wheel and which is imposed by the oscillations of the mechanical oscillator. These oscillations are maintained by the energy supplied by the motor unit.

In known clock movements, the oscillation amplitude of the oscillator decreases as the torque supplied by the motor member decreases, which is particularly the case when the drive member is a spring which disarms progressively. In other words, the known watch movements perform a count whose accuracy changes with the degree of arming of the motor unit. A relevant notion in this regard is called isochronism. In the field of watchmaking, isochronism is the ability of an oscillator to oscillate at a frequency that does not vary as a function of the oscillation amplitude of this oscillator. Anisochronism refers to a deficiency of an oscillator to possess this ability.

In the European patent EP 2,037,335 it is described several anchors, each of which is provided with a pair of flexible arms to ensure its support in a watch movement. Among these anchors, the one represented in Figures 7 and 8 patent EP-2,037,335 can be made bistable, thanks to a winding spring able to induce a force on the flexible support arms. When this force is sufficient, the anchor is biased away from an intermediate position of unstable equilibrium, in a direction that reverses when the anchor passes this intermediate position of unstable equilibrium.

In addition, the European patent application EP1122617A1 proposes a locking device in which a circular plate of a mobile is surrounded by a skirt. This skirt has a notch arranged to be traversed by a finger fixed on a second mobile. This second mobile is immobilized in a first position when its finger adjoins the inner wall of the skirt. The second mobile is immobilized in a second position when its finger adjoins the outer wall of the skirt.

Summary of the invention

• un balancier d'oscillateur pivotant de manière à pouvoir osciller autour d'un axe de pivotement,
• une ancre pour mettre en interaction le balancier d'oscillateur et une roue d'échappement de manière qu'une fréquence du balancier d'oscillateur règle une vitesse de rotation moyenne de la roue d'échappement,
• des lames flexibles de support qui soutiennent l'ancre de manière que, moyennant une flexion de ces lames flexibles de support, l'ancre puisse basculer entre une première position, dans laquelle une levée d'entrée de l'ancre est en prise avec la roue d'échappement, et une deuxième position, dans laquelle une levée de sortie de l'ancre est en prise avec la roue d'échappement.

Any of the anchors represented at Figures 1 to 8 of the European patent EP 2,037,335 mentioned above may be associated with an oscillator beam. This results in a subset for a mechanism for adjusting an average angular velocity in a watch movement. Thus, a type of subassembly for a mechanism for adjusting an average angular speed in a watch movement comprises:

• an oscillator rocker pivoting so as to be able to oscillate about a pivot axis,
• an anchor for interacting the oscillator beam and an escape wheel so that a frequency of the oscillator balance adjusts an average rotational speed of the escape wheel;
• flexible support blades which support the anchor so that, by flexing these flexible support blades, the anchor can to switch between a first position, in which an anchor entry lift is engaged with the escape wheel, and a second position, in which an emergence lift of the anchor is engaged with the wheel of exhaust.

In the subset of the type specified above, an absence of frictional wear of the support means of the anchor can be obtained. Such absence of wear is advantageous compared to the case where the anchor is mounted via a pivot where frictional wear can occur.

The subassembly according to the invention is of the aforementioned type. In addition, it comprises at least one anti-rollover locking pin and at least one anti-rollover locking ring which form complementary anti-rollover means opposing an accidental rollover of the anchor between the first and second positions. The anchor carries the anti-rollover locking pin which is outside the anti-rollover locking ring, when the anchor is in one of its first and second positions, and which is at the inside the anti-rollover locking ring, when the anchor is in its other position among the first and second positions. The anti-rollover locking ring is open at a passage for the anti-rollover locking pin. It is integral with the oscillator pendulum. It is able to prevent a passage of the anti-rollover locking pin between the inside and the outside of the anti-rollover locking ring except when the passage is positioned so that it can be used by the blocking pin roll-over.

The subset defined above may incorporate one or more other advantageous features, alone or in combination, in particular from those defined below.

Advantageously, the subassembly comprises a support arm which is integral with the oscillator beam and which carries the anti-rollover locking ring.

Advantageously, the support arm comprises a bulge provided for exchanging thrusts with a fork of the anchor.

Advantageously, the anchor comprises at least one finger which carries the anti-rollover locking pin.

Advantageously, the subassembly comprises elastic means tending to return the anchor towards the first position when this anchor is between this first position and an intermediate position of unstable equilibrium, the elastic means tending to return the anchor towards the second position. position when this anchor is between this second position and the intermediate position of unstable equilibrium.

Advantageously, each lift comprises an active profile intended to be traversed from upstream to downstream by teeth of the escape wheel. Each active profile has a resting surface of which at least a portion is provided to temporarily block each tooth downstream. Each active profile comprises a reset ramp configured to be pushed in the direction opposite to the escape wheel by each tooth when the tooth runs down this ramp downstream. At each lift, the reset ramp is arranged upstream of the resting surface so that before stopping any of the teeth downstream, each lift is pushed by this tooth. When this is so and that the subset comprises elastic means as specified above, the elastic means can adjust at a substantially constant level the amount of energy that receives the oscillator at each of its oscillations. Because of this, the amplitude of these oscillations is substantially constant over time. It follows that the eventual anisochronism of the oscillator has little or no adverse influence on the accuracy of the count of time.

Advantageously, the unstable equilibrium intermediate position is a third position, the anchor having a fourth position, in which the anchor is retained by any of the teeth of the escape wheel when this tooth abuts against the the resting surface and the ramp for rearranging the entrance lift. The fourth position is between the first position and the intermediate position of unstable equilibrium. Advantageously, the anchor has a fifth position, in which the anchor is retained by any of the teeth of the escape wheel when the tooth is in abutment against the resting surface and the rearming ramp of the lift. exit. The fifth position is between the second position and the intermediate position of unstable equilibrium.

Advantageously, the elastic means comprise at least one elastically flexible return blade. When this is the case, a compact solution can be obtained. In addition, the same technology can be used to manufacture resilient means and flexible support blades.

Advantageously, the flexible support blades and the resiliently flexible blade (s) return (s) form part of a piece in one piece. When this is the case, a compact solution can be obtained. It can be at a reduced cost, the flexible support blades and the elastically flexible blade (s) can be realized in one and the same step. In addition, a reduction of the components to be assembled can also be obtained. In addition, the single piece in question can be made of a monocrystalline material.

Advantageously, the piece in one piece defines a support frame to which the flexible support blades connect the anchor. When this is the case, the assembly of the mechanism is facilitated to the extent that it is easier to mount a single frame than to mount two frames to each of which would be connected a single flexible support plate. In addition, increased accuracy can be achieved in the geometry of the assembly, particularly when the integral part is made by means of the DRIE process or a similar process such as the LiGA process.

Advantageously, the piece in one piece is a first piece in one piece. The mechanism comprises a second integral piece which is part of the anchor and which is attached and fixed on a mounting portion constituting the first piece in one piece. One end of each flexible support strip is connected to this mounting portion. When such is the case, the anchor can extend in a first plane and the flexible support blades which support this anchor can extend in a second plane shifted from the first plane. In this way, there is great freedom of construction as to the solution for the support of the anchor.

Advantageously, the subassembly comprises a device for adjusting the elastic means.

Advantageously, the elastic means realize a compression of the flexible support blades, so as to flamber these flexible support blades except in the unstable equilibrium position. In other words, the flexible support blades are prestressed in compression. Advantageously, the mechanism comprises a device for adjusting the compression of the flexible support blades by the elastic means.

• un oscillateur,
• une roue d'échappement prévue pour interagir avec l'oscillateur selon un fonctionnement répétant un cycle, et
• un dispositif intermédiaire pour mettre en interaction l'oscillateur et la roue d'échappement de manière qu'une quantité d'énergie soit transmise de la roue d'échappement à l'oscillateur à chaque cycle et qu'une fréquence de l'oscillateur règle une vitesse de rotation moyenne de la roue d'échappement,
• un sous-ensemble tel que défini précédemment.

The invention also relates to a mechanism for adjusting a mean angular speed in a watch movement. This mechanism includes:

• an oscillator,
• an escape wheel provided to interact with the oscillator in a repeating cycle operation, and
• an intermediate device for interacting the oscillator and the escape wheel so that a quantity of energy is transmitted from the escape wheel to the oscillator at each cycle and a frequency of the oscillator rules an average rotation speed of the escape wheel,
• a subset as defined above.

In this mechanism for adjusting an average speed, the oscillator balance of the subassembly is part of the oscillator. The anchor of the subassembly is part of the intermediate device. In addition, the device intermediate comprises elastic means arranged to store substantially completely, by elastic deformation, said amount of energy, the intermediate device being configured so that its elastic means provide each cycle substantially the same amount of energy to the oscillator.

In the mechanism defined above, the elastic means regulate at a substantially constant level the amount of energy that the oscillator receives at each of its oscillations. Because of this, the amplitude of these oscillations is substantially constant over time. It follows that the eventual anisochronism of the oscillator has little or no adverse influence on the accuracy of the count of time.

Advantageously, the elastic means of the subassembly are the elastic means of the intermediate device

Brief description of the drawings

• la figure 1 est une vue en perspective d'un mécanisme qui est selon un premier mode de réalisation de l'invention et qui est plus précisément un mécanisme de réglage d'une vitesse moyenne dans un mouvement horloger,
• la figure 2 est un schéma où sont symbolisées plusieurs positions que l'ancre du mécanisme de la figure 1 occupe successivement au cours du fonctionnement de ce mécanisme,
• la figure 3 est une vue en perspective où seules une ancre, une roue d'échappement et une portion de balancier du mécanisme de la figure 1 sont représentées et où elles le sont telles que vues d'un autre angle, par rapport à cette figure 1,
• les figures 4a à 4h représentent les mêmes composants que la figure 2 et montrent des positions successives que l'ancre, la roue d'échappement et le balancier du mécanisme de la figure 1 occupent au cours du fonctionnement de ce mécanisme,
• la figure 5 est un graphique comprenant deux courbes qui sont les représentations graphiques de la valeur d'un couple de rappel exercé sur l'ancre 23 du mécanisme de la figure 1, en fonction de la position angulaire de cette ancre 23, pour deux réglages différents,
• la figure 6 est un graphique double où deux courbes réalisées avec des données expérimentales représentent les évolutions, sur plusieurs jours, de deux grandeurs mesurées, à savoir l'amplitude du balancier du mécanisme de la figure 1 et la marche d'un mouvement horloger intégrant ce mécanisme
• la figure 7 est une vue en plan d'une ancre pour un mécanisme selon un deuxième mode de réalisation de l'invention,
• la figure 8 est une vue en plan d'une ancre pour un mécanisme selon un troisième mode de réalisation de l'invention,
• la figure 9 est un agrandissement de la loupe IX de la figure 8,
• la figure 10 est un agrandissement de la loupe X de la figure 8, et
• la figure 11 est une vue en perspective d'une pièce d'un seul tenant pour un mécanisme selon un quatrième mode de réalisation de l'invention.

Other advantages and features will emerge more clearly from the following description of a particular embodiment of the invention given by way of non-limiting example and shown in the accompanying drawings, among which:

• the figure 1 is a perspective view of a mechanism which is according to a first embodiment of the invention and which is more precisely a mechanism for adjusting an average speed in a watch movement,
• the figure 2 is a diagram where are symbolized several positions that the anchor of the mechanism of the figure 1 occupies successively during the operation of this mechanism,
• the figure 3 is a perspective view where only an anchor, an escape wheel and a balance portion of the mechanism of the figure 1 are represented and where they are as seen from another angle, in relation to this figure 1 ,
• the Figures 4a to 4h represent the same components as the figure 2 and show successive positions that the anchor, the escape wheel and the balance of the mechanism of the figure 1 occupy during the operation of this mechanism,
• the figure 5 is a graph comprising two curves which are the graphical representations of the value of a restoring torque exerted on the anchor 23 of the mechanism of the figure 1 , depending on the angular position of this anchor 23, for two different settings,
• the figure 6 is a double graph where two curves made with experimental data represent the evolution, over several days, of two measured magnitudes, namely the amplitude of the pendulum of the mechanism of the figure 1 and the march of a watch movement integrating this mechanism
• the figure 7 is a plan view of an anchor for a mechanism according to a second embodiment of the invention,
• the figure 8 is a plan view of an anchor for a mechanism according to a third embodiment of the invention,
• the figure 9 is an enlargement of the magnifying glass IX of the figure 8 ,
• the figure 10 is an enlargement of the magnifying glass X of the figure 8 , and
• the figure 11 is a perspective view of an integral piece for a mechanism according to a fourth embodiment of the invention.

Description of a preferred embodiment of the invention

On the figure 1 , a mechanism 1 according to a first embodiment of the invention is more precisely a mechanism for adjusting a mean angular speed in a watch movement. It has an assembly frame 2, which supports an oscillator 3 and an exhaust 4 interacting with each other. On the figure 1 , the balance bridge or cock has been omitted for the sake of clarity.

In the example shown, the mechanism 1 is intended to be part of a vortex. However, the invention can be implemented also in the case where the assembly frame 2 is immobilized on a plate not shown or on a bridge also not shown in a watch movement without tourbillon.

The assembly frame 2 is a rigid assembly, of which a part 5, a part 6 and a support frame 7 are held together by screws 8. The support frame 7 is only a portion of a part 9 .

In the oscillator 3, a spiral spring 10 is associated with a rocker 11, which is pivotally mounted so as to be able to oscillate about a pivot axis Z ₁ -Z ' ₁ . The spiral spring 10 has two ends, one of which is fixed while being secured to the assembly frame 2. The other end of this spiral spring 10 is a movable end which is secured to the rocker arm 11. The rocker arm 11 comprises a shaft 12 for its pivotal mounting, and a flywheel 13 and a plate 14 which are mounted on the shaft 12.

Although in one piece, the part 9 has several portions fulfilling different functions. One of these portions constitutes the support frame 7, as has already been explained. The other portions of the part 9 are two flexible support blades 20, elastic means 21 and a mounting portion 22, which the flexible support blades 20 connect to the support frame 7. An anchor 23 of the exhaust 4 is reported on the mounting portion 22, to which it is fixed by means of two rivets 24. The flexible support blades 20 support the anchor 23 through the mounting portion 22, so that the anchor 23 can switch in a plane perpendicular to the pivot axis Z ₁ -Z ' ₁ . The anchor 23 and the part 9, including its resilient means 21, form an intermediate device.

The elastic means 21 comprise two flexible return blades 25, which are bent and symmetrical to each other. Elastic means 21 are stretched elastically between the anchor 23 and two armature levers 27. They thereby exert a pull on the anchor 23. A device for adjusting the intensity of this traction comprises the two arming levers 27, of which the respective angular positions are adjustable by means of two bodies not shown for the sake of clarity. Each of these two members mates with an arming lever 27, in a square hole 28 of the arming lever 27, which can thus rotate between several adjustment positions. The angular positions of the arming levers 27 determine the degree of arming of the elastic means 21 and the degree of prestressing in compression of the flexible support strips 20. The shape and the structure of the elastic means 21 and the arming levers 27 may be different from those described above and represented at figure 1 .

Due to the traction they exert on the anchor 23, the resilient means 21 compress the flexible support blades 20 until they are flamed up. These elastic means 21 cause the anchor 23 to be bistable when the buckling of flexible support strips 20 is effective.

In the sense that we understand it here, a bistable anchor is an anchor having two stable positions towards each of which it is recalled elastically.

On the figure 2 , several lines each schematically represent one of several angular positions of the anchor 23 in a plane perpendicular to the pivot axis Z ₁ -Z ' ₁ .

The anchor 23 has two positions of stable equilibrium, which are the positions S1 and S2 at the figure 2 . The anchor 23 also has an intermediate position of unstable equilibrium B, which lies between the positions S1 and S2. When the anchor 23 is between the position S1 and the unstable equilibrium intermediate position B, the elastic means 21 produce an elastic return of this anchor 23 to the position S1. When the anchor 23 is between the position S2 and the unstable equilibrium intermediate position B, the elastic means 21 produce an elastic return of the anchor 23 to the position S2. In other words, in a plane perpendicular to the pivot axis Z ₁ -Z ' ₁ , the anchor 23 is subjected to an elastic return whose direction is reversed when the anchor 23 passes its intermediate position of unstable equilibrium B.

We refer again to the figure 1 . With axis of rotation Z ₂ -Z ' ₂ , an escape wheel 30 of the exhaust 4 is intended to be subjected to a unidirectional motor torque C from a motor member such as a spring not shown. This driving torque C is exerted only in one direction, in which it tends to rotate the escape wheel 30. In the present description and in the appended claims, the terms "upstream", "downstream", "entry", "Output", as well as similar terms, refer to the direction of progression of a tooth of the escape wheel 30 in the vicinity of the anchor 23.

On the figure 3 only the plate 14, the anchor 23 and the escape wheel 30 are shown. The plate 14 is thus called by reference to its function and not by reference to its shape. This plate 14 comprises a mounting hub 35, which carries an arm 36 for supporting an anti-tilt locking ring 37 open at a passage 38. This arm 36 has a bulge 39 designed to interact with the fork 40. anchor 23. This bulge 39 fulfills the function of what is called an "ellipse" or a "plateau pin" in conventional Swiss anchor escapements.

During a complete oscillation of the oscillator 3, the bulge 39 passes twice in the range 40, once in one direction, once in the opposite direction. At each of its passages in the range 40, the bulge 39 causes a crossing of the intermediate position of unstable equilibrium B by the anchor 23, as will be explained later.

Instead of a stinger, the anchor 23 comprises an anti-rollover locking pin 41, which carries a finger 42 located at the same end as the fork 40. The anti-rollover locking ring 37 and the Anti-rollover locking pin 41 together prevents a shock or other parasitic phenomenon from causing an untimely crossing of the unstable equilibrium intermediate position B by the anchor 23, while the bulge 39 is at a distance from the fork 40. In the example shown, the Anti-rollover locking pin 41 has come from material with the finger 42. Instead, it can be attached to this finger 42. In addition, its shape may not be cylindrical. Moreover, the anti-rollover locking pin 41 can be worn on the symmetrical finger of the finger referenced 42, by means of a displacement of the position of the passage 38 with respect to the bulge 39.

Opposite the fork 40, the anchor 23 comprises two arms, namely an upstream arm 43 having an inlet lift 45 and a downstream arm 44 having an outlet lift 46. In the example shown, the lifts 45 and 46 are integral with the arms 43 and 44 of the anchor 23. Alternatively, they may be reported pallets which are fixed on these arms and which may, for example, be made of rubies.

Each of the lifts 45 and 46 comprises a rearming ramp 47 intended to be traversed downstream and then pushed by each tooth 48 of the escape wheel 30. Each of the lifts 45 and 46 further comprises a stopper 49 which has the shape of a protrusion at the downstream end of a reset ramp 47 and a resting surface 50 is provided to temporarily stop each tooth 48 after it has traveled the corresponding reset ramp 47.

The teeth 48 of the escape wheel 30 are identical to each other. Each tooth 48 is elongated radially. At its free end, each tooth 48 curves downstream so as to end with a spout 51 projecting both downstream and in the opposite direction to the axis of rotation Z ₂ -Z ' ₂ . Each spout 51 terminates in a rounded tip 52 provided to slide from upstream to downstream on the active profile, a rearming ramp 47 and a resting surface 50 forming together on each of the lifts 45 and 46.

In the example shown, three and a half teeth 48 are embraced between the lifts 45 and 46. The number of teeth embraced between the lifts 45 and 46 can be increased or decreased according to the needs of the construction.

In the example shown, the teeth 48 of the escape wheel 30 are twenty in number. According to the needs of the construction (frequency of the oscillator, etc.), the escape wheel 30 could also have more than twenty teeth 48 or less than twenty teeth 48.

Preferably, the part 9, the plate 14, the anchor 23 and the escape wheel 30 are each an integral part made of a monocrystalline material including silicon-based or quartz-based. Such a part can be manufactured by means of, for example, the "DRIE" method (acronym for "Deep Reactive Ion Etching"). Using the process "LiGA" (acronym for "Lithography, Galvanoformung und Abformung"), any of the parts 9, 14, 23 and 30 can also be made of nickel or any other material that can be made by galvanic growth.

During the operation of the mechanism 1, the plate 14, the anchor 23 and the escape wheel 30 occupy successive positions, some of which are shown in FIGS. Figures 4a to 4h . On these Figures 4a to 4h S arrows each indicate the direction of movement of the plate 14 at a given instant, while the teeth 48a and 48b are two of the teeth 48 of the escape wheel 30.

On the figure 4a the phase represented is the rest. The stopper 49 of the inlet lift 45 retains the tooth 48a downstream, so that the escape wheel 30 is stationary although subjected to the engine torque C. The nose 51 of the tooth 48a is located at the downstream end of the resetting ramp 47 of the inlet lift 45 so that, acting against the return produced by the elastic means 21, this tooth 48a keeps the anchor 23 away the nearest stable equilibrium position, which is the S1 position. More precisely, the tooth 48a holds the anchor 23 in the position which is referenced R1 to the figure 2 and which is a momentary stopping position. Always on the figure 4a , the bulge 39 is engaged in the fork 40 and approaches the horn 40b among the two horns 40a and 40b forming this fork 40.

Once it has reached the horn 40b, the bulge 39 exerts on this horn 40b a thrust P1 because of the angular speed of the balance 11, which is the case at the figure 4b .

On this figure 4b , the passage 38 is positioned so as to be able to be borrowed by the anti-rollover locking pin 41 and thus to allow this anti-rollover locking pin 41 to pass inside the anti-rollover locking ring 37, which allows tilting of the anchor 23 to its position of unstable equilibrium B.

Always on the figure 4b , the thrust P1 tilts the anchor 23 from its position R1 to its intermediate position of unstable equilibrium B. The anchor 23 then executes the movement M1 symbolized by an arrow at the figure 2 .

Still on the figure 4b the resting surface 50 of the inlet lift 45 still retains the tooth 48a, while sliding on the nose 51 of this tooth 48a in the opposite direction to the escape wheel 30, towards a release position of this tooth 48a.

The thrust P1 continues to cause the anchor 23 to cross its intermediate unstable equilibrium position B. After the anchor 23 has passed its unstable equilibrium position B towards its position S2, the elastic means 21 take the relay push P1 and in turn actuate the anchor 23 to the position S2. This is what happens at the figure 4c .

On this figure 4c the horn 40a exerts a thrust P2 on the bulge 39, so that the rocker 11 then receives one of the pulses maintaining its oscillatory movement. Enter here figure 4b and the figure 4c , there was a reversal in the interaction between the bulge 39 and the fork 40, since the thrust P1 was exerted by the bulge 39 on the fork 40 (clearance), while the thrust P2 is exerted by the fork 40 on the bulge 39 (pulse). Furthermore, it will be noted that the movement of the anchor 23 at the origin of the thrust P2 is produced by the elastic means 21 and not by a thrust by a tooth 48 on one of the lifts 45 and 46. The movement of the anchor 23 due to the actuation thereof by the elastic means 21 is referenced M2.

During the movement M2 of the anchor 23, the entry lift 45 withdraws from the trajectory of the tooth 48a. After that, the engine torque C causes a rotation of the escape wheel 30. The movement M2 continues a few times after the rotation of the escape wheel 30.

The rotation of the escape wheel 30 causes the tooth 48b to meet the re-arming ramp 47 of the exit lift 46, which causes the direction of progression of the anchor 23 to be reversed. figure 2 , the reference It designates the position where this inversion of the direction of progression of the anchor 23 occurs.

The rotation of the escape wheel 30 continues after the encounter of the tooth 48b with the rearming ramp 47 of the exit lift 46, which is the case at the figure 4d where this rotation is referenced R.

On this figure 4d the nose 51 of the tooth 48b slides along the rearing ramp 47 of the exit lift 46. When this, this tooth 48b exerts a thrust P3 on the output lift 46 and thus actuates the anchor 23 in the direction opposite position S2. The movement of the anchor 23 due to the thrust P3 is the movement M3 at the figure 2 .

Always on the figure 4d , the rounded back of the spout 51 of the tooth 48a is not in the path of the stopper 49 of the entry lift 45 as it returns to the escape wheel 30.

The movement M3 continues until the nose 51 of the tooth 48b meets the stopper 49 of the exit lift 46. After this stopper 49 has stopped the tooth 48b, the exhaust 4 and the tray 14 are as shown in FIG. figure 4e .

On this figure 4e , the stopper 49 of the output lift 46 retains the tooth 48b downstream, so that the escape wheel 30 is stationary although subject to the engine torque C. The nose 51 of the tooth 48b is located at the downstream end of the rearming ramp 47 of the output lift 46 so that, acting against the return produced by the elastic means 21, this tooth 48b keeps the anchor 23 in the position which is referenced R2 to the figure 2 and which is a momentary stopping position.

On the figure 4d as on the figure 4e , the anti-rollover locking ring 37 forms a barrier for the anti-rollover locking pin 41. This barrier prevents passage of the anti-rollover locking pin 41 between the inside and the outside of the locking ring anti-rollover 37, which eliminates the possibility of an accidental rollover in case of shock.

The movement of the balance 11 has changed direction S between the state represented at figure 4e and the state shown in the figure 4f which is the counterpart of the state illustrated in figure 4b . After reversing the direction S of the movement of the balance 11, the return to the state of the figure 4a includes a succession of steps and actions that are similar to those described above that have led to the state of the figure 4a up to the state of the figure 4e .

On the figure 4f , the passage 38 is positioned to allow the anti-rollover locking pin 41 to pass outside the anti-rollover locking ring 37, thereby allowing the anchor 23 to tilt to its position. unstable balance B.

Always on the figure 4f , a thrust P4 of the bulge 39 on the horn 40a of the fork 40 tilts the anchor 23 from its position R2 towards its unstable equilibrium intermediate position B. The movement of the anchor 23 due to the thrust P4 is the M4 movement at the figure 2 .

Still on the figure 4f , the rest surface 50 of the outlet lift 46 still holds the tooth 48b, while sliding on the nose 51 of the tooth 48b in the opposite direction to the escape wheel 30, towards a release position of this tooth 48b .

The thrust P4 continues until the anchor 23 passes its intermediate instable equilibrium position B. After the anchor 23 has passed its unstable equilibrium position B towards its position S1, the elastic means 21 take the relay P4 thrust and in turn actuate the anchor 23 to the position S1. This is what happens at the figure 4g .

The state represented on the figure 4g is the counterpart of the state represented on the figure 4c . On this figure 4g the horn 40b exerts a thrust P5 on the bulge 39, so that the rocker 11 then receives one of the pulses maintaining its oscillatory movement. The movement of the anchor 23 due to the actuation thereof by the elastic means 21 is referenced M5.

During the movement M5 of the anchor 23, the tooth 48b comes off the exit lift 46. After that, the engine torque C causes a rotation R of the escape wheel 30. The movement M5 continues after the implementation. rotation of the escape wheel 30. As can be seen at figure 2 , the movement M5 brings the anchor 23 to a position 12, where there is a reversal of the direction of progression of this anchor 23.

Succeeding the state represented on the figure 4g , the state represented on the figure 4h is the counterpart of the state represented on the figure 4d . On this figure 4h , the spout 51 of a tooth 48 slides along the reset ramp 47 of the entry lift 45. At this point, this tooth 48 exerts a thrust P6 on the entry lift 45 and thus actuates the anchor 23 to position R1. The movement of the anchor 23 due to the thrust P6 is the movement M6 at the figure 2 .

Always on the figure 4h , the rounded back of the spout 51 of the tooth 48b is not in the path of the stopper 49 of the exit lift 46 as it returns to the escape wheel 30.

On the figure 4h , the anti-rollover locking ring 37 forms a barrier preventing passage of the anti-rollover locking pin 41 between the inside and the outside of the anti-rollover locking ring 37, eliminating the possibility of accidental spilling in case of shock.

The movement M6 continues until the exhaust 4 is as shown in FIG. figure 4a . A go from the state represented to the figure 4a in the state shown in figure 4e and a return from the state represented to the figure 4e at the state represented in figure 4a together form a complete cycle, which is repeated immediately in a succession of substantially identical cycles. Each complete cycle corresponds exactly to a complete oscillation of the balance 11.

When a rest surface 50 slides on a tooth 48 as is the case on the figure 4b or on the figure 4f there is slight friction. Each resting surface 50 is oriented so that the force then applied by the tooth 48 on the resting surface 50 can then comprise a driving component in addition to the component due to the friction and that these two components compensate each other in the sense that their addition passes through the center of the anchor 23 and is substantially without effect on the tilting of this anchor 23.

On the figure 5 , the curve C1 is a graphical representation of the torque exerted by the elastic means 21 and the flexible support blades 20 on the anchor 23, as a function of the angle at which this anchor 23 is offset from its intermediate equilibrium position. unstable B. The X axis and the C1 curve delimit between them a surface that lines parallel to the ordinate axis can divide into several slices. Each of these slices has an area proportional to the variation that the amount of energy stored in both the elastic means 21 and the flexible support strips 20 is known to change the angular position of the anchor 23.

In what follows, we neglect the few losses occurring during energy exchanges between the anchor 23 and the oscillator 3. In addition, it is assumed that the exhaust 4, including the elastic means 21, has a functioning symmetrical with respect to the intermediate position of unstable equilibrium B.

During the movement M6, a first quantity of energy Q1 is transferred from the driving member at the origin of the torque C, to the elastic means 21. During the movement M1, a second quantity of energy Q2 passes from the oscillator 3 to the elastic means 21. During the movement M2, the first quantity of energy Q1 and the second quantity of energy Q2 pass elastic means 21 to the oscillator 3. On this occasion, this oscillator 3 thus covers the second quantity of energy Q2 and receives in addition the first quantity of energy. energy Q1.

Similarly, the first quantity of energy Q1 is again transferred from the motor unit at the origin of the torque C to the elastic means 21 during the movement M3. During the movement M4, the second quantity of energy Q2 passes from the oscillator 3 to the elastic means 21. During the movement M5, the first quantity of energy Q1 and the second quantity of energy Q2 pass through the elastic means 21. oscillator 3.

It will be noted that the reloading of the elastic means 21 by the escape wheel 30 takes place only once the contact between the anchor 23 and the oscillator 3 has ended.

During a complete cycle, that is to say during a complete oscillation of the balance 11, the oscillator 3 receives substantially twice the first quantity of energy Q1. During the transfer of a quantity of energy equal to twice Q1 from the escape wheel 30 to the oscillator 3, the elastic means 21 store entirely or substantially entirely, by elastic deformation, this quantity of energy .

It follows from the above that all the energy that the oscillator 3 receives is temporarily stored in the elastic means 21 before reaching this oscillator 3. In other words, the oscillator 3 receives only the energy it derives from the elastic means 21. However, the amount of energy that the elastic means 21 provide to the oscillator 3 is substantially the same at each cycle. In particular, the amount of energy that the elastic means 21 provide to the oscillator 3 at each cycle is independent of the degree of arming of the motor unit, provided that the torque C at the escape wheel has allowed the tooth 48 to have been able to bring the anchor in position R1 or R2 by the thrust P3 or P6 on one of the ramps 47. It follows that the oscillations of the oscillator 3 are constant over time, although that it is the same the accuracy of the counting of the time whatever the degree of isochronism of the oscillator 3.

In a way, the elastic means 21 play the role of a metering energy transmitted to the oscillator 3, thanks to which it has a very stable operation.

The operation described above is maintained as it is as long as the degree of arming of the drive member remains above a certain threshold. When the degree of arming of the drive member passes below this threshold, the engine torque C no longer manages to bring the teeth 48 back to the stops 49. The operation is therefore degraded, since the positions R1 and R2 are further away from B and a decrease of Q1 then occurs in parallel with an increase of Q2. This results in a loss of the amplitude of the oscillations, until a stop of the oscillator 3.

Like the curve C1, the curve C2 is a graphical representation of the torque exerted by the elastic means 21 and the flexible support blades 20 on the anchor 23, as a function of the angle at which this anchor 23 is offset with respect to its position. unstable equilibrium intermediate B. The curve C1 is obtained in the case where the elastic means 21 are set so that the positions S1 and S2 are offset from each other by 20 °. The curve C2 is obtained in the case where the elastic means 21 are set so that the positions S1 and S2 are shifted from one another by 15 °. The amount of energy transmitted to the oscillator 3 in the case corresponding to the curve C1 is different from that transmitted to the oscillator 3 in the case corresponding to the curve C2. As a result, the amplitude of the oscillations of the balance 11 can be adjusted by means of an adjustment of the elastic means 21 by means of the arming levers 27.

For tests, the mechanism 1 has been coupled to a motor unit in a watch movement. The operation of this mechanism 1 was observed as the motor unit disarmed from a maximum armature. The tests were carried out with the watch movement placed in the position known as HH (Horizontal High), in which this watch movement is horizontal and oriented so that the dial side is on the top, considering the direction of gravity. The results of the tests are reported on the figure 6 , where the zero time on the abscissa axis corresponds to the start time while the arming of the motor member is maximum. On the figure 6 , the curve C4 is a graphical representation of the average amplitude of the oscillations of the balance 11 as a function of time, during a running time of several days without arming action of the motor member. Always on the figure 6 , curve C3 is a graphical representation of daytime running (in seconds per day), that is the number of seconds gained or lost each day, as a function of time, during the same operating period of several days without arming action of the motor unit. Over a period of more than six days without arming the motor unit, the diurnal step deviated no more than one second per day from its average value, which is a very good result in terms of chronometric accuracy. As the anchor 23 is supported by the flexible support blades 20 and not by a pivot shaft, there is no friction at such a pivot shaft, while there is infinitely little friction at the level of the flexible support blades 20 (it is possible to neglect the friction internal to the material at these blades). Mechanism 1 maintains its stable operation over a long period of time, as shown by the results of the tests outlined above.

According to a second embodiment of the invention, a mechanism for adjusting an average angular speed in a watch movement is obtained by replacing the anchor 23 with an anchor 123 in the mechanism 1. The anchor 123 can replace the anchor 23 is represented alone at the figure 7 . In what follows, only that which distinguishes it from the anchor 23 is described. In addition, when a part of the anchor 123 is identical or equivalent to a referenced part of the anchor 23, it is designated by the same reference as that part of the anchor 23.

On the anchor 123, each rearming ramp 47 has an upstream portion 160 and a downstream portion 161 which succeed one another without having the same slope. The upstream portion 160 is more difficult to push back by a tooth 48 than the downstream portion 161. As a result, when a tooth 48 reaches any portion upstream 160 after the engine torque C has passed below a certain threshold, it stops before reaching the downstream portion 161 which follows this upstream portion 150. This accelerates the stop of the oscillator, so that or there is no degraded operation between the stable operation of the mechanism for adjusting an average speed and its stopping, or the degraded operation is only of short duration.

According to a third embodiment of the invention, a mechanism for adjusting a mean speed in a watch movement is obtained by replacing the anchor 23 with an anchor 223 in the mechanism 1. The anchor 223 can replace the anchor 23 is represented alone at the figure 8 . In what follows, only that which distinguishes it from the anchor 23 is described. Moreover, when a part of the anchor 223 is identical or equivalent to a referenced part of the anchor 23, it is designated by the same reference as that part of the anchor 23.

As can be seen better on the Figures 9 and 10 each re-arming ramp 47 of the anchor 223 comprises a transverse rib 262, as well as an upstream portion 260 and a downstream portion 261 that this transverse rib 262 separates from one another. The transverse rib 262 forms an obstacle to be crossed. When a tooth 48 reaches the upstream portion 260 of any rearrangement ramp 47 after the engine torque C has fallen below a certain threshold, it stops while abutting the transverse rib 262 of this ramp. resetting 47, without ever reaching the downstream portion 161 of this reset ramp 47. This accelerates the stop of the oscillator, so that there is no degraded operation between the stable operation of the adjustment mechanism of an average speed and its stopping, the degraded operation is only of short duration.

The figure 11 represents a single piece 300 provided for a fourth embodiment of the invention. As long as part of the part 300 is identical or equivalent to a referenced part of the mechanism 1, it is designated by the same reference as this part of the mechanism 1.

In the fourth embodiment of the invention, the anchor 23, the flexible support blades 20, the elastic means 21 and the support frame 7 are part of the same piece in one piece, which is the piece 300. The resiliently flexible return blades 25 meet at a fastening portion 370 which terminates in a fastener bulge 371. This fastener bulge 371 is retained in a hole 372. In the manufacture of 300, the fastener bulge 371 is remote from the hole 372. Upon placement, the fastener bulge 371 is pulled to the hole 372 before being inserted therein. This arms the elastic means 21. The fastener formed by the insertion of the fastener bulge 371 into the hole 372 can be obtained in various other ways, for example by means of a clip or a snap-in device.

The piece 300 in one piece can be made of a monocrystalline material, in particular based on silicon or quartz-based. Its manufacture can, for example, use the "DRIE" method. With the aid of the "LiGA" process, the part 300 can also be made of nickel or of any other material that can be produced by galvanic growth.

The invention is not limited to the embodiments described above. For example, it can be incorporated in the exhaust described in the Swiss patent application CH-703 333 mentioned above, in particular by means of a replacement of the lifts of this exhaust by the lifts 45 and 46.

Claims (14)

1. Subassembly for a mechanism for regulating an average angular speed in a horological movement, this subassembly comprising:

   - an oscillator balance (11) pivoting in a manner so as to be able to oscillate about a pivot axis (Z₁-Z'₁),

   - a pallet fork (23 ; 123 ; 223) for putting in interaction the oscillator balance (11) and an escape wheel (30) in a manner such that a frequency of the oscillator balance (11) regulates an average rotational speed of the escape wheel (30),

   - flexible support blades (20) which support the pallet fork (23; 123; 223) in a manner that, through a flexion of these flexible support blades (20), the pallet fork (23; 123; 223) is able to rock between a first position (I2), in which an entry pallet (45) of the pallet fork is engaged with the escape wheel (30), and a second position (I1), in which an exit pallet (46) of the pallet fork is engaged with the escape wheel (30),

   characterized in that it comprises at least one anti-overbanking locking pin (41) and at least one anti-overbanking locking ring (37) which form complementary anti-overbanking means opposing an accidental overbanking of the pallet fork between the first and second positions, the pallet fork (23; 123; 223) bearing the anti-overbanking locking pin (41) which is located on the exterior of the anti-overbanking locking ring (37), when the pallet fork (23; 123; 223) is in one of its first and second positions, and which is located on the inside of the anti-overbanking locking ring (37), when the pallet fork (23; 123; 223) is in its other position among the first and second positions, the anti-overbanking locking ring (37) being open at a passage (38) for the anti-overbanking locking pin (41), the anti-overbanking locking ring (37) being connected with the oscillator balance (11), the anti-overbanking locking ring (37) being able to prevent a passage of the anti-overbanking locking pin (41) between the interior and the exterior of the anti-overbanking locking ring (37) except when the passage (38) is positioned in a manner so as to be able to be taken by the anti-overbanking locking pin (41).
2. Subassembly according to claim 1, characterized in that it includes a support arm (36) which is connected with the oscillator balance (11) and which bears the anti-overbanking locking ring (37).
3. Subassembly according to claim 2, characterized in that the support arm (36) includes a swelling (39) provided to exchange thrusts with a fork (40) of the pallet fork (23).
4. Subassembly according to any one of the preceding claims, characterized in that the pallet fork comprises at least one finger (42) which bears the anti-overbanking locking pin (41).
5. Subassembly according to any one of the preceding claims, characterized in that it includes elastic means (21) tending to bring back the pallet fork (23; 123; 223) toward the first position (I2) when this pallet fork (23 ; 123; 223) is located between this first position (I2) and an intermediate position of unstable equilibrium (B), the elastic means (21) tending to bring back the pallet fork (23; 123; 223) towards the second position (I1) when this pallet fork (23; 123; 223) is located between this second position (I1) and the intermediate position of unstable equilibrium (B).
6. Subassembly according to claim 5, characterized in that each pallet (45, 46) includes an active profile (47, 50) provided to be travelled from the upstream to the downstream by the teeth (48) of the escape wheel (30), each active profile (47, 50) including a locking surface (50), at least one portion of which is provided to block temporarily each tooth (48) downstream, each active profile (47, 50) including a straining ramp (47) configured to be pushed back in the direction opposite to the escape wheel (30) by each tooth (48) when this tooth (48) crosses this straining ramp (47) downstream, and in that, at each pallet (45, 46), the straining ramp (47) is disposed upstream from the locking surface (50) in a manner that, before stopping any of the teeth (48) downstream, each pallet (45, 46) is pushed back by this tooth (48).
7. Subassembly according to claim 6, characterized in that the intermediate position of unstable equilibrium (B) is a third position, the pallet fork (23; 123; 223) having a fourth position (R1), in which the pallet fork (23; 123; 223) is retained by any of the teeth (48) of the escape wheel (30) when this tooth (48) abuts against the locking surface (50) and the straining ramp (47) of the entry pallet (45), the fourth position (R1) being located between the first position (I2) and the intermediate position of unstable equilibrium (B), the pallet fork (23; 123; 223) having a fifth position (R2), in which the pallet fork (23; 123; 223) is retained by any of the teeth (48) of the escape wheel (30) when this tooth (48) abuts against the locking surface (50) and the straining ramp (47) of the exit pallet (46), the fifth position (R2) being located between the second position (I1) and the intermediate position of unstable equilibrium (B).
8. Subassembly according to any one of the claims 5 to 7, characterized in that the elastic means (21) include at least one elastically flexible return blade (25).
9. Subassembly according to claim 8, characterized in that the flexible support blades (20) and the elastically flexible return blade (25) form part of an integrally formed piece (9).
10. Subassembly according to claim 9, characterized in that the integrally formed piece (9) defines a support frame (7) to which the flexible support blades (20) connect the pallet fork (23; 123; 223).
11. Subassembly according to any one of the claims 9 and 10, characterized in that the integrally formed piece is a first integrally formed piece (9), the mechanism comprising a second integrally formed piece (23; 123; 223) which forms part of the pallet fork (23; 123; 223) and which is added and fixed on a mounting portion (22) of the first integrally formed piece (9), an end of each flexible support blade (20) being connected on this mounting portion (22).
12. Subassembly according to any one of the claims 5 to 11, characterized in that it comprises a device (27) for adjustment of the elastic means (25).
13. Mechanism for regulating an average angular speed in a horological movement, comprising:

    - an oscillator (3),

    - an escape wheel (30) provided to interact with the oscillator (3) according to an operation repeating a cycle, and

    - an intermediate device (9, 23, 24; 9, 123, 24; 9, 223, 24; 300) for putting the oscillator (3) and the escape wheel (30) in interaction in such a way that a quantity of energy is transmitted from the escape wheel (30) to the oscillator (3) at each cycle and that a frequency of the oscillator (3) regulates an average speed of rotation of the escape wheel (30),

    characterized in that it comprises a subassembly (11, 20, 23, 37, 38, 41 ; 123; 223) according to any one of the claims 1 to 4, the oscillator balance (11) forming part of the oscillator (3), the pallet fork (23; 123; 223) forming part of the intermediate device (9, 23, 24; 9, 123, 24; 9, 223, 24; 300), this intermediate device (9, 23, 24; 9, 123, 24; 9, 223, 24; 300) comprising elastic means (21) designed to store substantially entirely, through elastic deformation, the said quantity of energy, the intermediate device (9, 23, 24; 9, 123, 24; 9, 223, 24; 300) being configured so that its elastic means (21) provide at each cycle substantially the same quantity of energy to the oscillator (3).
14. Mechanism according to claim 13, characterized in that the subassembly is according to any one of the claims 5 to 12, the elastic means (21) of this subassembly (11, 20, 23, 37, 38, 41; 123; 223) being the elastic means (21) of the intermediate device (9, 23, 24; 9, 123, 24; 9, 223, 24; 300).

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