Movable locking member for a watch escapement device

Abstract

A locking mechanism (4; 4') of an escapement device (10; 10') of a timepiece, comprising a fork (400; 400') with two first portions (411a, 421a; 411a', 421a'), called impulse portions, arranged opposite each other and arranged to transmit to an inertial element, during an impulse phase, at least a part of an impulse received from at least one escapement mechanism (1, 2; 1', 2'), characterized in that the fork (400; 400') comprises two second portions (411b, 421b; 411b', 421b'), called stop portions, arranged opposite each other and each arranged projecting from one of the first portions (411a, 421a; 411a', 421a'), and each arranged to come into contact with the inertial element, if a shock is received by the movement of the timepiece during the rest phase.

Description

Technical field of the invention

[0001] The present invention relates generally to escapement devices of a movement of a timepiece, and the invention relates in particular to a locking mechanism for such escapement devices. State of the art

[0002] In the prior art of escapement devices, we know of documents CH44855A and EP3754433A1, which disclose lever escapements with a lever without a tang and whose fork provides anti-overturning protection in cooperation with the balance wheel. However, these systems are bulky, particularly due to the dimensions of the lever, which must be quite long to ensure sufficient movement for the fork to engage and disengage from the balance wheel pin, even with the small angular deflection of the lever inherent in this type of escapement. Furthermore, it should be noted that these Swiss lever escapements are necessarily sensitive to friction during the impulse phase, as the lever and the escape wheel rotate in the same direction during this phase. Description of the invention

[0003] One object of the present invention is to address the disadvantages of the prior art mentioned above and in particular, first of all, to propose an escapement device with components which improve upon known escapement devices, i.e. to exhibit efficient operation, and / or good performance, and / or good operational safety, and / or good shock resistance, and / or reduced overall size.

[0004] To this end, a first aspect of the invention relates to a locking mechanism for the movement of a timepiece, the timepiece movement comprising: an escapement device comprising the locking mechanism and at least one escapement mechanism, an oscillator comprising at least one inertial element having a drive portion such as a tooth or a pin, and elastic return means coupled to the inertial element, the blocking mechanism including: blocking means, arranged to block, during a rest phase, said at least one escapement wheel of the escapement device; impulse receiving means, arranged to receive, during an impulse phase, an impulse from said at least one escapement wheel; a fork with two first portions, called impulse portions, arranged opposite each other and arranged to transmit to the drive portion of the inertial element, during the impulse phase, at least a part of the impulse received from said at least one escapement wheel. characterized in that the fork comprises two second portions, called stop portions, arranged opposite each other and each arranged in projection relative to one of the first portions, and each arranged to come into contact with the inertial element, if a shock is received by the movement of the timepiece during the rest phase.

[0005] The locking mechanism as described above comprises a fork that cooperates with the drive portion of the inertial element. This fork includes, projecting from the impulse portions (also called impulse surface portions or impulse surfaces), second portions known as thrust portions. These second projecting portions form bosses or protrusions extending from the first portions. Such second projecting portions allow for a butt joint with the inertial element, even if the locking mechanism has compact dimensions and / or significant angular displacements between two successive rest positions, as may be the case, for example, with a tangential drive escapement.

[0006] The blocking mechanism can be defined by the following characteristics, taken individually or in combination.

[0007] According to one embodiment, the fork comprises two elongated horns, each elongated along a respective longitudinal horn direction, and each horn, along a direction transverse to its respective longitudinal horn direction, has: a first width E1 at the level of the first portion, a second width E2 at the level of the second portion, and wherein E2>E1, preferably E2>1,1.E1, preferably E2>1,2.E1, preferably E2>1,3.E1. According to this configuration, the tines have a transverse dimension (relative to their longitudinal direction) that increases from the first to the second tines. In one embodiment, each second tine projects or protrudes inward from the frog. In other words, each projecting second tine can optionally cause a reduction in the width of the frog opening separating two tines, or can cause a reduction in the width of the frog opening separating two tines, typically known from the prior art.

[0008] According to one embodiment, each of the second portion comprises at least: a distal stop end, formed at a free end of the fork, in particular at a free end of the fork horn, a radial surface, oriented essentially in a direction normal to a pivoting direction of the locking mechanism, in which: the distal end of the stop is arranged to come into contact with the inertial element if a shock is applied to the movement of the timepiece during a travel of an additional upward or downward angle made by the inertial element, preferably during a travel of an additional upward or downward angle made by the inertial element during which the driving portion is not in the engagement or disengagement phase with the fork, and / or the radial surface is arranged to come into contact with the driving portion of the inertial element if a shock is applied to the movement of the timepiece during a travel of an additional upward or downward angle made by the inertial element, preferably during a travel of an additional upward or downward angle made by the inertial element during which the driving portion is in the engagement or disengagement phase with the fork.According to this implementation, two functional parts can be distinguished on each second portion. A first functional part is a distal or extremal portion that can abut the inertial element (and not the drive portion) if a shock is received while the drive portion of the inertial element is disengaged from the fork. A second functional part is a radial, lateral, or internal portion, located between the first functional part and the first portion, and which can abut the drive portion of the inertial element if a shock is received while the drive portion of the inertial element is engaging or disengaging from the fork.

[0009] In one embodiment, each first portion is connected to a second portion by a third portion, called the connecting portion, preferably with a change in slope and / or a trough arranged at the level of the third portion. In particular, at the level of the third portion, called the connecting portion, a change of sign of the derivative may be provided (i.e., there is a turning point or a local extremum), or a change in the direction of the slope when moving from the first portion to the second portion. In another embodiment, each first portion is adjacent to a second portion, and the transition between each first portion and the respective second portion forms or defines the third portion.

[0010] In one embodiment, a first tangent to a first portion forms an angle δ of less than 180° with a second tangent to the second portion projecting from the first portion when the first portion and the second projecting portion are viewed from inside the fork. In particular, the first tangent may be tangent to the first portion at the point of intersection of the second tangent with the first portion. More specifically, a plane of symmetry of the fork may be defined, and the second tangent may be parallel or substantially parallel to the plane of symmetry of the fork.

[0011] According to one embodiment, each first portion comprises, preferably moving away from an axis of rotation of the locking device, at least one flat surface and at least one curved surface. Preferably, said at least one curved surface may comprise a circular or arcuate cross-section, a circular profile, or an arc of a circle.

[0012] In one embodiment, each second portion comprises at least one curved surface. In another embodiment, each second portion comprises a circular or arcuate cross-sectional surface or a circular or arcuate profile.

[0013] According to one embodiment: The locking means and / or the impulse receiving means are arranged at a radial distance R41 from an axis of rotation of the locking mobile; the second portions, called stop portions, are arranged at a radial distance R4 from the axis of rotation of the locking mobile. in which R4>R41, preferably R4>1.4.R41, preferably R4>1.8.R41.

[0014] In particular, the radial distance R41 is between: a first radial distance Ra41 from an axis of rotation of the blocking mobile, from which the pulse receiving means extend, and a second radial distance Ra43 from an axis of rotation of the blocking mobile, to which a terminal end of the blocking means are arranged.

[0015] According to one embodiment, the blocking mechanism is characterized: in that it is planar or formed by a planar component, and / or in that it is sting-free, and / or in that it comes from a single piece or formed by an assembly of at least two components, in that it can be made of silicon and manufactured by etching from a wafer, or in that it can be manufactured by metal growth in an electroplating mold, or in that it can be manufactured by traditional cutting in a metal plate, or in that it can be manufactured of metallic glass or amorphous material, in that it can be free of added paddles.

[0016] According to one embodiment, the impulse receiving means are arranged to receive a tangential impulse from said at least one escapement mobile.

[0017] According to one embodiment, the locking mechanism is symmetrical or substantially symmetrical with respect to a mid-plane, passing between the two horns or in the opening separating two horns and through the axis of rotation of the locking mechanism.

[0018] According to one embodiment, the blocking mechanism is arranged to cooperate with two escape mechanisms.

[0019] A second aspect may relate to a regulator device for a timepiece movement, comprising: an escapement device comprising a locking mechanism according to the first aspect and at least one escapement mechanism arranged to be engaged with a gear of the clockwork movement, such as a driving gear, to receive a driving force, an oscillator comprising an inertial element having a driving portion such as a tooth or a pin, and elastic return means coupled to the inertial element, two external stops, formed for example by limiting pins or by stops, in which, during the rest phase, the locking fork is arranged to come into contact with one of the two external stops and with the drive portion in the event of a re-beat or rebound of the oscillator. In particular, in the event of a re-beat or rebound of the oscillator, a first horn of the fork is arranged to come into contact with the drive portion, and a second horn of the fork is arranged to come into contact with one of the two external stops.

[0020] In one embodiment, a triangle whose vertices are the axis of rotation of the locking wheel, the axis of rotation of the first escapement wheel, and the axis of rotation of the second escapement wheel, has, at the vertex centered on the axis of rotation of the locking wheel, an angle of less than 120°, preferably less than 90°, and preferably less than 80°. In another embodiment, the locking wheel is not positioned between the axis of rotation of the first escapement wheel and the axis of rotation of the second escapement wheel. In yet another embodiment, the axis of rotation of the locking wheel lies within a triangle whose vertices are, respectively, the axes of rotation of the escapement wheels and the axis of rotation of the oscillator.In one embodiment, a circle centered on the axis of rotation of the locking wheel and passing through the axis of rotation of the first escape wheel and the axis of rotation of the second escape wheel, and passing through at least a portion of the oscillator or balance wheel, can be identified. In another embodiment, the locking wheel is not elongated or highly elongated, typically with a length less than twice its maximum width. In yet another embodiment, a portion of the locking wheel furthest from its center of rotation is arranged at a radius substantially equal to the maximum width of the locking wheel: the overall shape of the locking wheel is compact and homogeneous (without significant protrusions), which limits its moment of inertia (strongly influenced by the square of the distance to the axis of rotation).

[0021] In one embodiment, the escapement device is not of the direct impulse type. In other words, said at least one escapement element never cooperates directly with the inertial element. In another embodiment, the blocking element is the only component of the escapement device that cooperates directly with the inertial element. In yet another embodiment, the blocking element forms a single component of the escapement device, arranged between said at least one escapement element and the inertial element, from a functional point of view.

[0022] The second aspect may relate to a regulator device for a timepiece movement, comprising: an escapement device comprising a locking mechanism according to the first aspect and at least one escapement mechanism arranged to be engaged with a gear of the clockwork movement, such as a driving gear, to receive a driving force, an oscillator comprising an inertial element having a driving portion such as a tooth or a pin, and elastic return means coupled to the inertial element, in which the locking mechanism is pivotally mounted and exhibits, between two successive rest positions, a rocking motion of an amplitude greater than 30°, preferably greater than 40°, preferably greater than 45°. In such an escapement device, the impulse is typically tangential. In other words, during the impulse, the locking element and the escape element that transmits the impulse pivot in opposite directions. This reduces sensitivity to friction.

[0023] According to one embodiment, the escapement device comprises: a first escapement mobile, mounted pivoting about a first axis of rotation, arranged to be engaged with the gear train of the clock movement, and comprising a plurality of first locking surfaces to cooperate with the locking means of the locking mobile and a first drive toothing, a second escapement mobile, mounted pivoting about a second axis of rotation, comprising a plurality of second locking surfaces to cooperate with the locking means of the locking mobile and a second drive toothing engaged with the first drive toothing to transmit the motive force from the first escapement mobile to the second escapement mobile.

[0024] In one embodiment, during an impulse phase imparted by the first escapement mechanism to the blocking mechanism, the impulse is tangential. In another embodiment, during an impulse phase imparted by the second escapement mechanism to the blocking mechanism, the impulse is tangential. In yet another embodiment, the impulse phase imparted by the first escapement mechanism to the blocking mechanism occurs during the first half-cycle of an oscillation, and the impulse phase imparted by the second escapement mechanism to the blocking mechanism occurs during the second half-cycle of said oscillation.

[0025] According to one embodiment: The drive portion is arranged at a radial distance R5 from the axis of rotation of the inertial element; the second portions, called stop portions, are arranged at a radial distance R4 from the axis of rotation of the locking mechanism. in which 0.8.R5 <R4<1,2.R5 et de préférence 0,9.R5<R4<1,1.R5. Selon cette mise en oeuvre, le mobile de blocage est nettement plus compact qu'une ancre d'un dispositif d'échappement à ancre suisse.

[0026] According to one embodiment: the drive portion has a crescent shape, and / or the inertial element includes a cylindrical lateral surface forming a thrust wall arranged to come into contact with one of the two second portions, called thrust portions, if a shock is received by the movement of the timepiece during the rest phase, in which: the drive portion is arranged at a radial distance R5 from the axis of rotation of the inertial element in which, the thrust wall is arranged at a radial distance R6 from the axis of rotation of the inertial element, in which preferably R5>R6, preferably R5>1,2.R6, preferably R5>1,3.R6.

[0027] A third aspect may relate to a timepiece, including a regulator device according to the second aspect.

[0028] A fourth aspect of the invention, which may be independent of or combined with the above aspects, relates to an escapement device for a clockwork movement, comprising: a first escapement wheel, mounted to pivot about a first axis of rotation, arranged to engage with a gear train of the clockwork mechanism, such as a main gear train, to receive a motive force, and comprising a plurality of first locking surfaces and a first drive toothing; a second escapement wheel, mounted to pivot about a second axis of rotation, comprising a plurality of second locking surfaces and a second drive toothing engaged with the first drive toothing to transmit the motive force from the first escapement wheel to the second escapement wheel; an inertial element, mounted to pivot about a third axis of rotation, arranged to exhibit oscillations, each comprising a first alternation and a second alternation; a blocking wheel, mounted to pivot about a fourth axis of rotation, comprising: a first blocking surface portion,arranged to come into contact with one of the plurality of the first blocking surfaces to block the rotation of the first escape wheel, a second blocking surface portion, arranged to come into contact with one of the plurality of the second blocking surfaces to block the rotation of the second escape wheel, impulse receiving means, arranged to receive a first impulse from the first escape wheel during a first alternation of an oscillation of the inertial element, and to receive a second impulse from the second escape wheel during a second alternation of said oscillation of the inertial element, impulse transmission means, arranged to transmit at least a part of the first or second impulse to the inertial element.

[0029] According to one embodiment, the first surface blocking portion is arranged so that a first force, exerted on the blocking mobile by the first escape mobile blocked by the first surface blocking portion, passes substantially in the vicinity of the fourth axis of rotation, in particular passes through the fourth axis of rotation.

[0030] According to one embodiment, the second blocking surface portion is arranged so that a second force, exerted on the blocking mobile by the second escape mobile blocked by the second blocking surface portion, passes substantially in the vicinity of the fourth axis of rotation, in particular passes through the fourth axis of rotation.

[0031] In one embodiment, the first escapement wheel and / or the second escapement wheel may be a single-plane, one-piece, monobloc component, or a component machined from a single piece of material. In one embodiment, the plurality of first locking surfaces and the first drive teeth may be arranged on the same plane. In one embodiment, the plurality of second locking surfaces and the second drive teeth may be arranged on the same plane.

[0032] In one embodiment, the first escapement wheel and / or the second escapement wheel may be a biplanar component, formed, for example, by two separate wheels, or, for example, by a multilevel component. In one embodiment, the plurality of first locking surfaces and the first drive teeth may be arranged on two different planes. In one embodiment, the plurality of second locking surfaces and the second drive teeth may be arranged on two different planes.

[0033] The escapement device according to the above implementation provides increased operational security, because the first or second blocking force passes through the fourth axis of rotation or substantially through the fourth axis of rotation: in the blocking position (or in the rest phase), the blocking mobile does not undergo any reversing torque, which makes it possible to obtain a stable blocking position.

[0034] It can be noted that the escapement device, as implemented above, transmits two impulses to the inertial element during a single oscillation (one round trip) of the inertial element, in order to maintain its oscillations. Indeed, the locking mechanism can: receive a first impulse from the first escape wheel and transmit it to the inertial element during a first alternation (for example, a forward movement constituting the first half of an oscillation) of the inertial element, and can receive a second impulse from the second escape wheel and transmit it to the inertial element during a second alternation (for example, a return movement constituting the second half of the oscillation considered) of the inertial element.

[0035] In one embodiment, the first force exerted on the locking armature by the first escapement armature, which is held in place by a first blocking surface portion, passes substantially near the fourth axis of rotation, and in particular through the fourth axis of rotation, so as to guarantee the absence of a reversing torque on the locking armature during a rest phase. In other words, the first force exerted on the locking armature by the first escapement armature, which is held in place by a first blocking surface portion, passes substantially near the fourth axis of rotation, and in particular through the fourth axis of rotation, so as to guarantee a stable rest position of the locking armature during a rest phase. During this rest phase, the locking armature is engaged only with the first escapement armature.

[0036] In one embodiment, the second force, exerted on the locking mechanism by the second escapement mechanism held in place by a second blocking surface portion, passes substantially near the fourth axis of rotation, and in particular through the fourth axis of rotation, so as to guarantee the absence of a reversing torque on the locking mechanism during a rest phase. In other words, the second force, exerted on the locking mechanism by the second escapement mechanism held in place by a second blocking surface portion, passes substantially near the fourth axis of rotation, and in particular through the fourth axis of rotation, so as to guarantee a stable rest position of the locking mechanism during a rest phase. During this rest phase, the locking mechanism is engaged only with the second escapement mechanism.

[0037] In one embodiment, the locking wheel is mounted via a free pivot joint. In another embodiment, the locking wheel is mounted via a free pivot joint on a bridge and / or on a plate of the timepiece. In another embodiment, the locking wheel is free of an elastic return device, and / or the escapement mechanism is free of an elastic return device coupled or engaged with the locking wheel to maintain or return it to a rest position (it being understood that the elastic element (a balance spring, conventionally speaking) of the oscillator coupled to the inertial element nevertheless causes, through the sustained movements of the inertial element, the release of the escape wheels and subsequently the movements of the locking wheel). In other words, the movements of the locking wheel are caused by the inertial element and / or the first escape wheel and / or the second escape wheel.In particular, during normal operation of the escape device, the movements of the blocking mechanism are caused exclusively by the inertial element and / or the first escape mechanism and / or the second escape mechanism.

[0038] In one embodiment, the escapement device is not a direct impulse escapement device. In other words, according to this embodiment, the first escapement wheel and / or the second escapement wheel do not cooperate directly with the inertial element (or an oscillator component typically formed by a balance wheel / spring couple).

[0039] In one embodiment, the inertial element comprises a balance wheel. In particular, the inertial element may comprise a balance wheel, a balance staff and a plate with a pin, coupled to a spiral spring.

[0040] According to one embodiment, the first blocking surface portion is arranged to block the rotation of the first escapement wheel, i.e. an escapement movement of the first escapement wheel, and / or the second blocking surface portion is arranged to block the rotation of the second escapement wheel, i.e. an escapement movement of the second escapement wheel.

[0041] According to one embodiment, the first surface portion of the blocking is arranged so that a first friction cone constructed around a point of application of the force exerted by the first escapement vehicle on the blocking vehicle includes, or encompasses, or passes through the fourth axis of rotation, and / or the second surface portion of the blocking is arranged so that a second friction cone constructed around a point of application of the force exerted by the second escapement vehicle on the blocking vehicle includes, or encompasses, or passes through the fourth axis of rotation.

[0042] According to one embodiment, the first blocking surface portion has a first normal direction passing through the fourth axis of rotation or passing substantially through the fourth axis of rotation, and the second blocking surface portion has a second normal direction passing through the fourth axis of rotation or passing substantially through the fourth axis of rotation.

[0043] According to one embodiment: A first straight line passing through the fourth axis of rotation and a point of contact between the first escapement and the first blocking surface during the first blocking phase, and a second straight line passing through the fourth axis of rotation and a point of contact between the second escapement and the second blocking surface during the second blocking phase, define an acute angle α between them. In other words, a triangle can be constructed with: its first vertex being the fourth axis of rotation, its second vertex the point of contact between the first escapement and the first blocking surface, and its third vertex the point of contact between the second escapement and the second blocking surface. According to the embodiment above, this triangle has an acute angle at its first vertex.Such a configuration ensures a reduced stroke for the locking mechanism between a first locking position (of the locking mechanism) in which the first escapement mechanism is blocked (by the locking mechanism) and a second locking position (of the locking mechanism) in which the second escapement mechanism is blocked (by the locking mechanism). This provides a compact assembly that is advantageously symmetrical with respect to a plane passing through the respective axes of rotation of the inertial element and the locking mechanism.

[0044] According to one embodiment, the means for receiving the pulse from the blocking device include: a first impulse input portion, arranged to receive the first impulse from the first escapement wheel during the first alternation of the balance wheel, a second impulse input portion, arranged to receive the second impulse from the second escapement wheel during the second alternation of the balance wheel.

[0045] According to one embodiment, the first pulse input portion is adjacent to the first blocking surface portion, and the second pulse input portion is adjacent to the second blocking surface portion.

[0046] According to one embodiment, the first pulse input portion is separated from the first surface blocking portion by a first resting nozzle, and the second pulse input portion is separated from the second surface blocking portion by a second resting nozzle.

[0047] According to one embodiment: a third straight line passing through the fourth axis of rotation and through a point of contact between the first escape wheel and the first portion of the impulse input during a first impulse phase, and a fourth straight line passing through the fourth axis of rotation and through a point of contact between the second escape wheel and the second portion of the impulse input during a second impulse phase, define between them an acute angle γ.

[0048] According to one embodiment, the angle γ is within a range of values ​​from 50° to 70°.

[0049] According to one embodiment, the angle γ is less than the angle α. In other words, the first and second pulse input portions are arranged between the first and second surface blocking portions.

[0050] In an alternative embodiment, the angle γ can be greater than the angle α. In other words, the first and second surface blocking portions are arranged between the first and second pulse input portions. Such an implementation can allow for the symmetrical distribution of displacements caused by any play in the escapement mechanisms about their respective axes of rotation. Description of the figures

[0051] Other features and advantages of the present invention will become more apparent upon reading the following detailed description of embodiment(s) of the invention given by way of non-limiting example(s) and illustrated by the accompanying drawings, in which: [ fig. 1 ] represents a regulator device for a movement of a timepiece, comprising on the one hand an escapement device including a locking wheel, a first escape wheel and a second escape wheel, and on the other hand an oscillator including an inertial element with a drive portion; fig. 2 ] represents in detail the blocking mechanism of the regulator device of the figure 1 ; fig. 3 ] represents in detail a range of the blocking mechanism of the figure 2 ; fig. 4 ] represents other aspects of the mobile blocking range of the figure 2 ; fig. 5 ] represents the regulator device of the figure 1 , during a rest phase of the escapement device, following a shock causing the locking mechanism to perform an angular rotation in a first direction S1; [ fig. 6 ] represents the regulator device of the figure 1 , during a rest phase of the escapement device, following a shock causing the locking mechanism to perform an angular rotation in a second direction S2; [ fig. 7 ] represents a fictitious regulator device in the same configuration as shown figure 6 , and including a fictitious blocking motive; [ fig. 8 ] represents the regulator device of the figure 6 , to demonstrate the movement of the locking mechanism, particularly at the locking mechanism's horns; [ fig. 9 ] represents the regulator device of the figure 1 , during a rebeat of the oscillator while the escapement device is in its rest phase; [ fig. 10 ] represents a detail of the regulator device of the figure 1 to show a total tilting angle of the locking mechanism occupying two successive rest positions; [ fig. 11 ] represents a very simplified range of a first embodiment of the locking mechanism and in particular of the range of the locking mechanism of the regulator device of the figure 1 ; fig. 12 ] represents a very simplified range of a second embodiment of the locking mechanism and in particular of the range of the locking mechanism of the regulator device of the figure 1 ; fig. 13 ] represents a variant of the regulator device of the figure 1 , including in particular a third embodiment of the locking mechanism of the regulator device figure 1 , during a rest phase of the escapement device; [ fig. 14 ] represents the regulator device of the figure 13 , during a pulse phase of the escapement device subsequent to the rest phase of the figure 13 ; fig. 15 ] represents the regulator device of the figure 13 , during a rest phase of the escapement device subsequent to the impulse phase of the figure 14 ; fig. 16 ] represents the regulator device of the figure 13 , during a pulse phase of the escapement device subsequent to the rest phase of the figure 15 ; fig. 17 ] represents in detail the blocking mechanism of the regulator device of the figure 13 ; fig. 18 ] represents in detail the blocking means and the pulse reception means of the blocking mobile of the regulator device of the figure 13 . Detailed description of implementation method(s)

[0052] There figure 1 represents a regulator device for a movement of a timepiece, comprising: an escapement device 10 comprising a blocking mobile 4, a first escapement mobile 1 and a second escapement mobile 2, an oscillator 20 comprising an inertial element (here a balance wheel 51) pivoting around a third axis of rotation A5 and having a drive portion (here a pin 511a) positioned on a plate 511 of the balance wheel 51, and an elastic return element (not shown) coupled to the balance wheel 51 (a spiral spring, or flexible elements, can typically be provided), two external stops, formed in this example by limiting pins 91 and 92, but stop pins could also be provided.

[0053] Specifically, the exhaust system 10 includes: the first escapement wheel 1, mounted pivotally about a first axis of rotation A1, arranged to engage with the clockwork mechanism via a pinion 13, and comprising a plurality of first locking surfaces 121a formed on first locking teeth 121 to cooperate with locking means for the locking wheel 4, and a first drive tooth 111; the second escapement wheel 2, mounted pivotally about a second axis of rotation A2, comprising a plurality of second locking surfaces 221a formed on second locking teeth 221 to cooperate with locking means for the locking wheel 4, and a second drive tooth 211 engaged with the first drive tooth 111 to transmit the driving force from the first escapement wheel 1 to the second escapement wheel 2; the locking wheel 4, mobile and rotatable about a fourth axis of rotation A4, and comprising: locking means,arranged to block, during a rest phase, the first escapement wheel 1 or the second escapement wheel 2, impulse receiving means, arranged to receive, during an impulse phase, an impulse from the first escapement wheel 1 or the second escapement wheel 2, a fork 400 having horns 410, 420. ,

[0054] There figure 2 represents in detail the blocking mechanism 4 of the regulator device of the figure 1 The blocking device 4 shown figure 2 includes, for its part: the blocking means, formed in this example by first and second surface blocking portions 43a, 43b, arranged to block, during a rest phase, the first escape wheel 1 or the second escape wheel 2 via respectively one of the first blocking surfaces 121a and one of the second blocking surfaces 221a, the impulse receiving means formed in this example by a first impulse input portion 41a, arranged to receive a first impulse from the first escape wheel 1 during a first alternation of the balance wheel 51, and by a second impulse input portion 41b, arranged to receive a second impulse from the second escape wheel 2 during a second alternation of the balance wheel 51; the fork 400 having two horns 410, 420 each comprising an inner wall 411, 421 having respectively: two first portions 411a, 421a called impulse portions,Arranged opposite each other and configured to transmit at least part of the received impulse to the balance wheel pin 511a during the impulse phase, two second portions 411b, 421b, called stop portions, arranged opposite each other and each projecting from one of the first portions 411a, 421a, and each configured to come into contact with a stop wall 511b of the balance wheel plate 511, if the movement of the timepiece receives a shock during the rest phase. It is understood that during the normal operation of the escapement device 10 (particularly in the absence of a shock), only the first two portions 411a, 421a contact or cooperate with the balance wheel pin 511a. During normal operation, the second portions 411b, 421b do not interact with either the pin 511a or the balance wheel 511.

[0055] In more detail, and as we can see figures 2 , 3 And 4Each horn 410, 420 comprises an inner wall 411, 421 equipped with: of a first portion 411a, 421a, called impulse portion, formed from the base of the fork, which is intended to cooperate with the pin 511a of the plate 511 of the balance wheel 51, of a second portion 411b, 421b, called stop portion, opening at the free end of each of the horns, the end of which B1, B2 forms a means, in particular a line or an edge or a surface, of stop intended to optionally cooperate with the wall 511b of the plate 511. The first and second portions can in particular be connected by a third portion 411c, 421c, called connecting portion, so that the second portion is in continuity with the first portion.

[0056] It can be noted that the first portion of the pulse 411a, 421a can be in the form of a single flat or curved surface, or be composed of several continuous or discontinuous surfaces. In one embodiment shown figure 4 , this first portion 411a, 421a of impulse is notably composed of a first flat surface 411a1, 421a1 and a second curved surface 411a2, 421a2 (in the shape of an arc of a circle) with a radius of curvature R1, this second surface being formed in continuity with the first surface.

[0057] The second portion 411b, 421b can be in the form of a single flat or curved surface, or be composed of several continuous or discontinuous surfaces. In one embodiment shown figures 2 à 4 , this second portion 411b, 421b is in the form of a single curved surface 411b, 421b (in the shape of a circular arc) having a radius of curvature R2 and a vertex S1, S2. This surface 411b, 421b is connected to a distal wall 412, 422 of the blocking mobile 4 at the end B1, B2, which is intended to come into contact with the periphery or the wall 511b of the plate 511 during the additional arc of the oscillator. This distal wall 412, 422 is situated between the inner wall 411, 421 and an outer wall 413, 423 of each of the horns 410 and 420. Each outer wall 413, 423 partially defines the contour of the locking mechanism 4 and extends respectively along a longitudinal direction D410, D420. Generally speaking, the longitudinal directions D410, D420 can be considered to define the longitudinal directions of each of the horns 410, 420.

[0058] The second portions 411b, 421b constitute protrusions projecting from the inner walls 411, 421 of each of the horns 410 and 420. In order to describe these protrusions, we can consider that the horn 410, 420 has a thickness E2 at the level of the second portion 411b, 421b, in particular at the endpoints B1, B2, measured perpendicular to the longitudinal direction D410, D420, and the thickness E2 is strictly greater than a thickness E1 measured at the level of the first impulse portion 411a, 421a, also measured perpendicular to the longitudinal direction D410, D420.

[0059] In a particular construction, this thickness E2 is maximum at the respective vertices S1, S2 of the second portions 411b, 421b. It is at the level of these vertices that contact is likely to occur between the second portions 411b, 421b and the tabletop pin 511a.

[0060] In a particular construction, the thickness E2, measured specifically at the vertices S1, S2, is approximately equal to 1.5E1. More generally, we can consider that E2>E1, or even E2>1.1E1, or even E3>1.2E1, or even E3>1.3E1.

[0061] On the figure 4 It can be noted that the radius of curvature R2 is smaller than the radius of curvature R1. In a particular construction, R1 is on the order of 5R2. More generally, we can consider that R2 <R1, voire 2.R2<R1, voire 4.R2<R1.

[0062] Additionally, the first pulse segment 411a, 421a and the second segment 411b, 421b can be considered to form a salient angle δ, that is, strictly less than 180°, when viewed from inside the fork 400. In particular, a first tangent T1 to the first segment 411a, 421a and a second tangent T2 to the second segment 411b, 421b can be constructed, forming a salient angle δ when viewed from inside the fork. Specifically, the first tangent T1 can be tangent to the first segment at the point of intersection of the second tangent T2 with the first segment. More specifically, a plane of symmetry of the fork can be defined, and the second tangent T2 can be parallel or substantially parallel to the plane of symmetry of the fork.In particular, it is still possible to construct a first tangent T1 to the first portion 411a, 421a and a second half-line D2 passing through B1, B2, which form a salient angle δ when viewed from inside the fork.

[0063] In the representation illustrated by the figure 4 In which the second tangent T2 is substantially parallel to a plane of symmetry P4 of the fork, the angle δ formed by T1 and T2 is approximately 160°. This can vary from 70° to 179° depending on the respective positions of the tangents T1 and T2. More generally, it is possible to identify a first half-line D1 passing through at least one point of the first portion 411a, 421a and a second half-line D2 passing through at least one point of the second portion 411b, 421b, in particular B1 and B2 respectively, which form a salient angle δ when viewed from inside the fork.

[0064] In the configuration of the blocking mobile 4 shown figures 2 à 4 The following points can be noted: The blocking mobile 4 is symmetrical with respect to plane P4, the blocking mobile 4 is a planar component comprising only one level, the blocking mobile 4 is sting-free, the first and second pulse input portions 41a, 41b are arranged between the first and second surface blocking portions 43a, 43b, the second portions 411b, 421b are arranged at a distance or at a

[0065] radius R4 of the fourth rotation axis A4, and the first surface blocking portions 43a, 43b and / or the first and second pulse input portions 41a, 41b are arranged at a distance or radius R41 from the fourth rotation axis A4, and R4 > R41, preferably R4>1.4.R41, preferably R4>1.8.R41; an angle γ is less than an angle α; the angle γ being defined: between a line S3 connecting the first pulse input portion 41a to the fourth rotation axis A4 and a line S4 connecting the second pulse input portion 41b to the fourth rotation axis A4, the angle α being defined: between a line S1 connecting the first blocking surface portion 43a to the fourth rotation axis A4 and a line S2 connecting the second blocking surface portion 43b to the fourth rotation axis A4.

[0066] Returning to the figure 1 It can be noted that the escapement device 10 is of the double tangential impulse type. This escapement device 10 is shown in the figure 1 Its distinctive feature is that it offers operational safety made possible by the fact that, during the rest phase of the figure 1 The locking force F induced by the contact between the first escapement wheel 1 and the locking wheel 4 passes (or passes substantially through) the fourth axis of rotation A4 of the locking wheel 4, particularly due to the first and second concave locking surface portions, shaped to provide good locking security. Thus, during a given rest phase, the locking wheel 4 does not experience a reversing torque, which allows a stable locking position to be obtained.

[0067] In the event of a high-intensity shock, for example when the watch is dropped, the operational safety can be further improved by providing stops to limit the angular travel of the locking mechanism 4 when it is normally immobilized by one or the other of its first and second surface blocking portions.

[0068] There figure 5 represents the regulatory device of the figure 1 During a rest phase of the escapement device, following an impact causing the locking lug to rotate angularly in a first direction S1, external stops, such as limiting pins 91 and 92 or spacers, can be provided to limit the angular travel of the locking lug in the first direction S1. Thus, the travel of the locking lug 4 is limited in the direction of rotation S1, even in the event of an unexpected impact.

[0069] There figure 6 represents the regulatory device of the figure 1 , during a rest phase of the escapement device, following a shock causing the locking wheel to perform an angular rotation in a second direction S2. In this case, to further improve the safety of operation, it is possible to try to prevent a tooth of the first escape wheel 1 normally in contact with the first surface portion of the locking wheel 4 from coming into contact with the adjacent impulse input portion, which could thus induce an untimely displacement of the locking wheel 4 upstream of a release phase of the balance wheel 51.

[0070] To this end, it is proposed to form the second portions 411b and 421b, called stop portions, at the free ends of each of the horns 410, 420 of the locking mobile 4. These second portions 411b and 421b have the particularity of being constituted by the ends of protuberances projecting from the inner walls of each of the horns 410, 420 in order to move as far away as possible the fourth axis of rotation A4 of the locking mobile 4 from the contact area between the locking mobile 4 and the stop wall 511b of the balance wheel plate 511 (whose oscillations are maintained by the escapement). The angular play of the blocking mobile 4 is thus minimized, and it is not possible for a blocking tooth of an escapement mobile normally in contact with one of the first and second surface blocking portions 43a, 43b of the blocking mobile 4 to come into contact with one of the adjacent pulse input portions 41a, 41b.It can be noted that for the same angle of the locking mobile 4, a protuberance of the horn 410, 420 will make a greater displacement than another part of the locking mobile 4 due to its distance from the fourth axis of rotation A4 of the locking mobile 4.

[0071] There figure 7 represents a fictitious regulator device in the same configuration as the one shown figure 6 , and including a fictitious blocking motive. By way of comparison with the figure 6 , there figure 7 represents the escapement device 10 in the same configuration as that of the figure 6 but with a fictitious 4F locking mechanism whose horns have no protrusion at their free end, and with an inner wall shaped solely with respect to the impulse function. The locking tooth or blocking surface of an escapement mechanism is then likely to come into contact with a portion of the impulse input, as shown by the area surrounded by a dashed circle at the bottom of the figure.

[0072] There figure 8 represents the regulatory device of the figure 6 to show the play of the locking mechanism, particularly at the locking mechanism's horns. The second portions 411b and 421b, called stop portions, in cooperation with the plate pin 511a, also have the advantage of minimizing horn play, namely the angle Ω that the locking mechanism 4 is likely to traverse accidentally when the pin 511a is in the engagement or disengagement phase with the fork 400, at the very end or beginning of a rest phase, as shown in the figure 8 The possible contact between the second portions 411b and 421b, called stop portions, and the plate pin 511a ensures that a locking tooth or a locking surface of an escapement mobile normally in contact with one of the first and second surface locking portions 43a, 43b of the locking mobile 4 cannot come into contact with one of the adjacent impulse input portions 41a, 41b.

[0073] In general, the second portions 411b and 421b, called stop portions, also have the advantage of widening the horns 410, 420 at their free end and thus preventing any reversal of the locking mechanism 4, the horns 410, 420 being always liable to come into contact with the wall of the balance wheel plate during the additional arc made by the balance wheel, or in other words when the balance wheel pin is not between the two horns. figure 9 represents the regulatory device of the figure 1 , during a rebeat of the oscillator while the escapement device is at rest. The general arrangement ensures rotation of the locking pod 4 in the first direction S1 until contact with a limiting pin 91.

[0074] Thus, the horns 410 and 420, with their protrusion, replace the dart known in prior art in its anti-overturning function. This is accentuated by the fact that the locking pod 4 of the escapement device 10 has a tilting angle β, on the order of 50°, much greater than that of a typical Swiss lever escapement, which is on the order of 15°. This allows the release of the balance wheel pin 511a from the fork 400 while also permitting the possible cooperation of the horns 410 and 420 with the stop wall 511b of the balance wheel plate 511 during the additional arc of the balance wheel 51 and, more generally, of the oscillator. The figure 10 represents a detail of the regulator's device figure 1 to show the total tilting angle β of the locking mobile 4 occupying two successive rest positions.

[0075] There figure 11 represents a very simplified 400A range of a first embodiment of the 400 range of the locking mobile 4 of the regulator device of the figure 1 . In this first extremely simplified variant, we can note a first half-line D1 which coincides with the first portion 411a, 421a and a second half-line D2 which passes through a single point of the second portion 411b, 421b which may correspond to the point B1, B2 or be distinct from it.

[0076] There figure 12 represents a very simplified 400B fork of a second embodiment of the 400 fork of the locking mobile 4 of the regulator device of the figure 1 . In this second extremely simplified embodiment variant, we can note a first half-line D1 which coincides with the first portion 411a, 421a and a second half-line D2 which coincides with the second portion 411b, 421b and which thus passes through a point corresponding to B1, B2.

[0077] Regardless of the variant considered and with reference to figures 2 , 3 , 4 , 11 , 12 , the inner walls 411 and 421, in particular the stop means B1, B2, are symmetrical with respect to a plane P4 passing through the fourth axis of rotation A4 of the locking mobile 4. More generally, the horns 410 and 420 are symmetrical with respect to this plane P4, that is to say that the walls 412 and 422, as well as the outer walls 413, 423 are also symmetrical with respect to this same plane.

[0078] Preferably, the 511a plate pin has a half-moon shape so that it can cooperate best with the second portions 411b, 421b, and thus minimize horn play, while allowing its insertion inside the fork and its cooperation with one or the other of the first portions 411a, 421a and thus allow the release of the balance wheel 51 and the transmission of the impulse to this same balance wheel during an alternation of the latter.

[0079] In normal operation of the escapement device 10, the first portions 411a, 421a are designed to cooperate exclusively with the pin 511a. In the event of a high-intensity shock, portions 411b, 421b are designed to cooperate with the plate wall 511b via the stop means B1, B2, or with the plate pin 511a via their respective apexes S1, S2. The outer walls 413, 423 are designed to cooperate exclusively with limiting pins 91, 92 (or, alternatively, stop pins), or with the pin 511a during a rebound of the oscillator.

[0080] Due to the specific nature of the double tangential impulse escapement device, and in particular the use of two escapement wheels, the locking wheel 4 has a significant tilting angle β, on the order of 50°. The displacement of the fork 400 is therefore very large compared to that of a Swiss lever fork, even though the size of this locking wheel 4 is particularly compact, on the order of those of the two escapement wheels and that of the balance wheel plate 511: the space dedicated to the escapement function in a watch can therefore be reduced.

[0081] In the exemplified construction in particular figure 10 , the radius R5 which separates the pin 511a from the third axis A5 of rotation of the balance corresponds or corresponds substantially to the radius R4 of the smallest circle C4 centered on the axis A4 within which the blocking mobile 4 can be inscribed.

[0082] In an alternative embodiment, it is possible to lengthen the body or the fork of the locking mobile 4 in order to maximize the displacement of the free ends of the horns 410, 420 while containing the tilting angle of the locking mobile 4.

[0083] There figure 13 represents a variant of the regulator device of the figure 1 , including in particular a third embodiment of the locking mechanism of the regulator device figure 1 , during a rest phase of the escapement device. In this third embodiment, a new geometry of the blocking mechanism is shown, which has the particularity of presenting first and second blocking surface portions 43a', 43b' arranged between two impulse input surfaces 41a', 41b', as can be seen in detail in figures 17 And 18 .

[0084] As will be detailed below, such a blocking mobile 4' makes it possible to ensure that the reaction forces of a given escape mobile with respect respectively to the blocking mobile 4' and the other escape mobile are arranged on either side of a plane passing through the respective axes of rotation of the given blocking mobile and escape mobile.

[0085] Advantageously, such an arrangement offers an operating method which allows for optimized control of assembly clearances, particularly with regard to the fact that the pivots of the two escapement mobiles will move symmetrically (during distinct operating phases) with respect to a plane passing through the respective axes of rotation of the blocking mobile and the oscillator.

[0086] This mastery of assembly techniques contributes to the definition of a robust escapement system.

[0087] There figure 13 represents a regulator device similar to that of the figures 1 à 10 for a movement of a timepiece, comprising: an escapement device 10' comprising a blocking mobile 4', a first escapement mobile 1' and a second escapement mobile 2', an oscillator 20' comprising an inertial element (here a balance wheel) with a drive portion (here a pin 511a') positioned on a plate 511' of the balance wheel 51, and an elastic return element (not shown) coupled to the balance wheel (typically a spiral spring, or flexible elements can be provided), two external stops, formed in this example by limiting pins 91' and 92', but stop pins could be provided.

[0088] THE figures 13 à 16 illustrate the regulator device including the 10' exhaust device, and the figures 17 And 18represent in detail the third particular variant of the blocking mobile 4'. It can be noted that the conformation of the fork 400' of the blocking mobile 4' is independent of the conformation of the first and second surface blocking portions 43a', 43b' and / or of the first and second pulse input portions 41a', 41b' of this same blocking mobile 4'.

[0089] There figure 18 details in particular the first and second concave surface blocking portions 43a', 43b' which are made up respectively of surfaces 43a1', 43a2' and 43b1', 43b2' forming a V with obtuse angle βa', βb' of the order of 165°.

[0090] This figure 18 in particular highlights an angle α' separating a first straight line S1' connecting the first surface portion of blocking 43a' to the axis of rotation A4' from a second straight line S2' connecting the second surface portion of blocking 43b' to the axis of rotation A4'.

[0091] In particular, the first line S1' passes through the junction point connecting surfaces 43a1' and 43a2', and the second line S2' passes through the junction point connecting surfaces 43b1' and 43b2'. In the construction variant shown, this angle α' is acute and is approximately 55°. More generally, the following range of values ​​can be predicted: 50° ≤ α' ≤ 70°.

[0092] This figure 18 also highlights an angle γ' separating a third line S3' connecting the first portion of pulse input 41a' to the rotation axis A4' from a fourth line S4' connecting the second portion of pulse input 41b' to the rotation axis A4'.

[0093] In particular, the third line S3' is tangent to the first pulse input portion 41a' and the fourth line S4' is tangent to the second pulse input portion 41b'. In the construction variant shown, this angle γ' is acute and is approximately 65°. More generally, the following range of values ​​can be predicted: 60° ≤ γ' ≤ 80°.

[0094] It can be noted that the 4' blocking mobile of the figure 18 differs from the blocking mobile 4 illustrated by the figure 2 because here, the first and second concave blocking surface portions 43a', 43b' are arranged between the first and second impulse input portions 41a', 41b'. Consequently, the angle α' is less than the angle γ' (whereas on the figure 2 , angle α is greater than angle γ).

[0095] With this specific 4' locking mobile conformation, the 10' escapement device according to the figures 13 à 16 Its distinctive feature is that it is actuated by a first escapement mechanism 1' (comprising in particular a pinion 13' driven in a first direction S1) arranged to the right of a plane P45' passing through the respective axes of rotation of the mechanism 4' and a balance wheel or oscillator 51', which distinguishes it from the escapement device 10 of the figure 1 equipped with a first escapement mechanism 1 (including in particular a pinion 13 driven in a first direction S1) arranged to the left of a plane P45 passing through the respective axes of rotation of the mechanism 4 and the balance wheel 51. The wheels 11' and 21' are identical to the wheels 11 and 21 of the figure 1 , with the difference that wheels 11' and 21' are mounted upside down on their respective axles A1', A2' compared to the arrangement of wheels 11 and 21 on their respective axles A1, A2.

[0096] There figure 13 Figure 10 illustrates the escapement mechanism with the second escapement wheel 2' bearing against a second blocking surface portion 43b' of the blocking wheel 4', inducing a reaction force F24' directed approximately towards the axis A4'. The meshing between the first and second escapement wheels 1', 2' also induces a reaction force F12'. The vectors representing these reaction forces are arranged on either side of a plane P24' passing through the respective axes of rotation of wheel 2' and wheel 4'. By assessing the forces applied to the second escapement wheel 2' during this rest phase, and noting that it is blocked or pressed against the second blocking surface portion 43b', we can deduce that the mounting clearances of the second escapement wheel 2' relative to the second axis of rotation A2' are taken up and allow or cause a displacement of the second escapement wheel 2' to the left of the figure 13 , approximately along the direction D21' (we can schematically summarize the movement along the direction D21' of the second escapement wheel 2' as a tilt or a rotation of the second escapement wheel 2' around the fulcrum of the second escapement wheel 2' on the blocking wheel 4').

[0097] There figure 14 Figure 10 illustrates the escapement mechanism as the second escapement element 2' imparts an impulse to the blocking element 4' by cooperating with the second impulse input portion 41b', inducing a reorientation of the reaction force F24' which no longer passes through the fourth axis of rotation A4'. The vectors representing the reaction forces F24' and F12' remain arranged on either side of the plane P24'. By analyzing the forces applied to the second escapement wheel 2' during this impulse phase, and noting on the one hand the impulse force F24' applied to the second portion of the impulse input 41b' and on the other hand the support force F12', we can deduce that the mounting clearances of the second escapement wheel 2' relative to the second axis of rotation A2' are taken up and allow or cause a displacement of the second escapement wheel 2' always to the left of the figure 14 , approximately along the D22' direction.

[0098] Thus, any play in the mounting of the second escapement wheel 2' relative to the second axis of rotation A2' is taken up and always allows or causes a displacement of the second escapement wheel 2' always to the left of the figure 13 Or 14 during the rest or impulse phase involving the second escapement mobile 2'.

[0099] There figure 15 Figure 10 illustrates the escapement mechanism with the first escape wheel 1' bearing against a first blocking surface portion 43a' of the locking wheel 4', inducing a reaction force F14' directed approximately towards the fourth axis of rotation A4'. The meshing between the first and second escape wheels 1', 2' also induces a reaction force F12' (very small) and / or at least contact until the mechanism comes to a stop at rest. The vectors representing these reaction forces are arranged on either side of a plane P14' passing through the respective axes of rotation of wheel 1' and wheel 4'. It should also be noted that the first escape wheel 1' is constantly subjected to the driving torque of the driving gear via the pinion 13'.By taking stock of the forces applied to the first escapement wheel 1' during this rest phase, and noting that it is blocked or pressed on the first surface portion of blocking 43a', we can deduce that the mounting clearances of the first escapement wheel 1' relative to the first axis of rotation A1' are taken up and allow or cause a displacement of the first escapement wheel 1' towards the right of the . figure 15 , approximately along the direction D11' (we can schematically summarize the movement along the direction D11' of the first escape wheel 1' as a tilt or a rotation of the first escape wheel 1' around the fulcrum of the first escape wheel 1' on the blocking wheel 4', due to the driving torque applied to the first escape wheel 1').

[0100] There figure 16 Figure 10 illustrates the escapement mechanism as the first escapement wheel 1' imparts an impulse to the locking wheel 4' by interacting with the first portion of the impulse input 41a'. This induces a reorientation of the reaction force F14', which no longer passes through the fourth axis of rotation A4'. The meshing between the first and second escapement wheels 1', 2' also induces a reaction force F12' (very weak) and / or at least some contact during this impulse phase. It should also be noted that the first escapement wheel 1' is constantly subjected to the driving torque of the drive gear via the pinion 13'. The vectors representing the reaction forces F14' and F12' remain arranged on either side of the plane P14'.By taking stock of the forces applied to the first escapement wheel 1' during this impulse phase, and noting on the one hand the impulse force F14' applied to the first portion of the impulse input 41a' and on the other hand the motor torque applied to the first escapement wheel 1', we can deduce that the mounting clearances of the first escapement wheel 1' relative to the first axis of rotation A1' are taken up and allow or cause a displacement of the first escapement wheel 1' always towards the right of the . figure 16 , approximately along the D12' direction.

[0101] Thus, any play in the mounting of the first escapement wheel 1' relative to the first axis of rotation A1' is taken up and always allows or causes a displacement of the first escapement wheel 1' always towards the right of the figure 15 Or 16 during the rest or impulse phase involving the first escapement mobile 1'.

[0102] Whether it is a rest phase ( Figures 13 And 15 ) or impulse ( Figures 14 And 16), the escape mobiles 1', 2' will move symmetrically (but in distinct phases) with respect to the plane P45'. In particular, the magnitude of the displacements D11' and D21' of the first and second escape mobiles 1', 2' is the same when the first and second escape mobiles 1', 2' are successively supported against the first and second surface blocking portions 43a', 43b', and the orientations of the displacements D11', D21' are symmetric with respect to the plane P45'. In particular, the magnitude of the displacements D12' and D22' of the first and second escape mobiles 1', 2' is the same when the first and second escape mobiles 1', 2' are successively in contact with the first and second pulse input portions 41a', 41b', and the orientations of the displacements D12', D22' are symmetrical with respect to the plane P45'.

[0103] This control of the movements of the first and second escapement wheels 1', 2' relative to their pivot bearing, and therefore of the assembly clearances, contributes to the definition of a robust escapement mechanism. It should be noted that this method of compensating for clearances is independent of the operational reliability provided by the second portions, known as stop portions, which are formed as protrusions or projections relative to the first portions 411a', 421a', known as impulse portions of the fork's horns 400'. Consequently, the locking wheel 4' may or may not include a fork 400' similar or identical to the fork 400 of the locking wheel 4 described previously in relation to the figures 2 à 4 .

[0104] Thus, the 4' locking mechanism makes it possible to define a particularly robust escapement device and, moreover, one that is shock-resistant. Industrial application

[0105] A locking mechanism according to the present invention, and its manufacture, are capable of industrial application.

[0106] It will be understood that various modifications and / or improvements obvious to a person skilled in the art can be made to the different embodiments of the invention described in this description without departing from the scope of the invention.

Claims

1. A locking mechanism (4; 4') of a timepiece movement, the timepiece movement comprising: - an escapement device (10; 10') including the locking mechanism (4; 4') and at least one escapement mechanism (1, 2; 1', 2'), - an oscillator (20; 20') including at least one inertial element having a drive portion such as a tooth or pin (511a; 511a'), and elastic return means coupled to the inertial element, the locking mechanism (4; 4') comprising: - locking means, arranged to lock, during a rest phase, said at least one escapement mechanism (1, 2; 1', 2') of the escapement device (10; 10'), - impulse receiving means, arranged to receive, during a phase of impulse, an impulse of said at least one escapement mobile (1, 2; 1', 2'), - a fork (400; 400') with two first portions (411a, 421a;411a', 421a'), said impulse portions, arranged opposite each other and arranged to transmit to the driving portion of the inertial element, during the impulse phase, at least a part of the impulse received from said at least one escapement moving part (1, 2; 1', 2'), ; characterized in that the fork (400; 400') includes two second portions (411b, 421b; 411b', 421b'), called stop portions, arranged opposite each other and each arranged in projection relative to one of the first portions (411a, 421a; 411a', 421a'), and each arranged to come into contact with the inertial element, if a shock is received by the movement of the clock part during the rest phase.

2. A locking device (4; 4') according to claim 1, the fork (400; 400') comprising two lugs (410, 420; 410', 420'), each elongated along a longitudinal lug direction (D410, D420; D410', D420'), wherein each lug (410, 420; 410', 420'), along a direction transverse to the respective longitudinal lug direction (D410, D420; D410', D420'), has: - a first width E1 at the level of the first portion (411a, 421a; 411a', 421a'), - a second width E2 at the level of the second portion (411b, 421b; 411b', 421b'), and wherein E2 > E1, preferably E2>1,1.E1, preferably E2>1,2.E1, preferably E2>1,3.E1.

3. A locking mechanism (4; 4') according to claim 1 or 2, wherein each of the second portion (411b, 421b; 411b', 421b') comprises at least: - a distal stop end, formed at a free end of the fork (400; 400'), in particular at a free end of the horn (410, 420; 410', 420') of the fork (400; 400'), - a radial surface, oriented essentially in a direction normal to a pivoting direction of the locking mechanism (4; 4'), wherein: - the distal stop end is arranged to abut the inertial element if a shock is applied to the movement of the timepiece during a traverse of an additional upward or downward angle performed by the inertial element, preferably during a traverse of an additional upward or downward angle performed by the element inertial during which the training portion is not in the engagement or disengagement phase with the fork (400;400'), and / or - the radial surface is arranged to come into contact with the drive portion of the inertial element if a shock is applied to the movement of the timepiece during a path of an additional upward or downward angle made by the inertial element, preferably during a path of an additional upward or downward angle made by the inertial element during which the drive portion is in the phase of engaging or disengaging with the fork (400; 400').; 4. Locking mobile (4; 4') according to any one of claims 1 to 3, wherein each first portion (411a, 421a; 411a', 421a') is connected to a second portion (411b, 421b; 411b', 421b') by a third portion (411c, 421c; 411c', 421c') called connecting portion, preferably with a slope reversal and / or a hollow arranged at the level of the third portion.

5. Locking mobile (4; 4') according to any one of claims 1 to 4, wherein a first tangent to a first portion (411a, 421a; 411a', 421a') forms with a second tangent to the second portion (411b, 421b; 411b', 421b') arranged projecting from said first portion (411a, 421a; 411a', 421a') an angle δ less than 180° when said first portion (411a, 421a; 411a', 421a') and said second portion (411b, 421b; 411b', 421b') projecting are seen from inside the fork (400; 400').

6. Locking mobile (4; 4') according to any one of claims 1 to 5, wherein each first portion (411a, 421a; 411a', 421a') comprises, preferably moving away from an axis of rotation (A4; A4') of the locking mobile (4; 4'), at least one flat surface and at least one curved surface.

7. Locking mobile (4; 4') according to any one of claims 1 to 6, wherein each second portion (411b, 421b; 411b', 421b') comprises at least one curved surface.

8. Locking mobile (4; 4') according to any one of claims 1 to 7, wherein: - the locking means and / or the impulse receiving means are arranged at a radial distance R41 from an axis of rotation of the locking mobile (4; 4'), - the second portions (411b, 421b; 411b', 421b'), called stop portions, are arranged at a radial distance R4 from the axis of rotation of the locking mobile (4; 4'), wherein R4>R41, preferably R4>1.4.R41, preferably R4>1.8.R41.

9. Blocking mechanism (4; 4') according to any one of claims 1 to 8, characterized - in that it is planar or formed by a planar component, and / or - in that It is stingless, and / or - in that It came from a single piece or was formed by an assembly of at least two components.

10. Regulator device for a movement of a timepiece, comprising: - an escapement device (10; 10') including a locking pin (4; 4') according to any one of claims 1 to 9 and at least one escapement pin (1, 2; 1', 2') arranged to be engaged with a gear of the timepiece movement, such as a driving gear, to receive a driving force, - an oscillator (20; 20') including an inertial element having a driving portion such as a tooth or a pin (511a; 511a'), and elastic return means coupled to the inertial element, - two external stops, formed for example by limiting pins (91, 92; 91', 92') or by stops, in which, during the rest phase, the fork (400; 400') of the locking mobile (4; 4') is arranged to come into contact with one of the two external stops and with the drive portion in the case of a re-beat or oscillator re-beat (20; 20').

11. Regulator device for a movement of a timepiece, comprising: - an escapement device (10; 10') including a locking mobile (4; 4') according to any one of claims 1 to 9 and at least one escapement mobile (1, 2; 1', 2') arranged to be engaged with a gear of the timepiece movement, such as a driving gear, to receive a motive force, - an oscillator (20; 20') including an inertial element having a driving portion such as a tooth or a pin (511a; 511a'), and elastic return means coupled to the inertial element, in which the locking mobile (4; 4') is pivotally mounted and exhibits between two successive rest positions a rocking motion of an amplitude greater than 30°, preferably greater than 40°, preferably greater than 45°.

12. Regulator device according to any one of claims 10 to 11, wherein the escapement device (10; 10') comprises: - a first escapement wheel (1; 1'), mounted pivotally about a first axis of rotation (A1; A1'), arranged to be engaged with the gear train of the clock movement, and comprising a plurality of first locking surfaces for cooperating with the locking means of the locking wheel (4; 4') and a first drive toothing, - a second escapement wheel (2; 2'), mounted pivotally about a second axis of rotation (A2; A2'), comprising a plurality of second locking surfaces for cooperating with the locking means of the locking wheel (4; 4') and a second drive toothing engaged with the first drive toothing to transmit the motive force from the first escapement wheel (1; 1') to the second escapement wheel (2; 2').

13. Regulator device according to any one of claims 10 to 12, wherein: - the drive portion is arranged at a radial distance R5 from the axis of rotation of the inertial element, - the second portions (411b, 421b; 411b', 421b'), referred to as stop portions, are arranged at a radial distance R4 from the axis of rotation of the locking sprocket (4; 4'), wherein 0.8R5 <R4<1,2.R5 et de préférence 0,9.R5<R4<1,1.R5.

14. Regulator device according to any one of claims 10 to 13, wherein: - the drive portion has a crescent shape, and / or - the inertial element comprises a cylindrical lateral surface forming a stop wall arranged to come into contact with one of the two second portions (411b, 421b; 411b', 421b'), referred to as stop portions, if a shock is received by the movement of the timepiece during the rest phase, wherein: - the drive portion is arranged at a radial distance R5 from the axis of rotation of the inertial element, in which, - the stop wall is arranged at a radial distance R6 from the axis of rotation of the inertial element, in which preferably R5>R6, preferably R5>1.2.R6, preferably R5>1.3.R6.

15. Timepiece, comprising a regulator device according to any one of claims 10 to 14.

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