EP3619579B1 - Clock device with positioning member - Google Patents

Description

The invention relates to a horological device including a positioning member such as a jumper or a pawl.

A jumper is an organ, generally a lever, terminated by two inclined planes which press between the points of two consecutive teeth of a wheel, also called a star, under the action of a spring, to maintain it in a certain angular position. . When the wheel in question is actuated, the teeth raise the jumper which then falls between two other teeth. A jumper allows the wheel to move in both directions.

A ratchet is a member, generally a lever, provided with a nose which penetrates into the teeth of a wheel under the action of a spring to maintain it in a certain angular position. When the wheel in question is actuated in a determined direction, the teeth raise the pawl which then falls between two other teeth. In the other direction, the pawl prevents the wheel from turning due to the shape of its nose and / or the toothing of the wheel.

Traditionally, jumpers and pawls are built on the basis of leaf springs working in flexion. DE 41 34 624 C1 discloses such a ratchet. Flexible blades are also used in the flexible exhaust mechanism of EP 645 189 A1 . The moment of force exerted on the wheel is necessary to hold it in position. However, the moment of force required for the rotation of one step of the wheel must overcome the resistance exerted by the jumper or by the pawl, which results in a certain consumption of energy. In order to maintain the wheel properly, the torque required to initiate the rotation of the wheel must not be too low. But it is also essential that the maximum resistance exerted by the jumper or by the pawl during the rotation of one step of the wheel does not exceed a certain value so that the wheel is able to overcome it, failing which the mechanism watchmaker could crash. In practice, jumpers and pawls currently used generate a peak in energy consumption corresponding to maximum resistance.

The object of the invention is to provide a timepiece device comprising a toothed component and a positioning member, said positioning member ensuring good maintenance in position of the toothed component while attenuating or even eliminating any peak in energy consumption during latching. advancement of said toothed component by one step.

For these purposes, the invention proposes a device according to claim 1. The invention also proposes a timepiece such as a wristwatch or a pocket watch comprising such a horological device.

• la figure 1 est une vue de dessus d'un dispositif horloger selon un premier mode de réalisation de l'invention ;
• la figure 2 est une vue de dessus d'un organe de positionnement du dispositif horloger de la figure 1 ;
• la figure 3 est une représentation graphique schématique du moment de rappel élastique exercé dans l'organe de positionnement du dispositif horloger de la figure 1 ;
• la figure 4 représente les coordonnées de points définissant une forme particulière d'une lame élastique de l'organe de positionnement du dispositif horloger de la figure 1 ;
• les figures 5a et 5b sont des représentations graphiques du moment de rappel élastique exercé dans un organe de positionnement du dispositif horloger de la figure 1 comprenant des lames élastiques ayant la forme telle que représentée à la figure 4 ;
• la figure 6 est une représentation graphique du moment de force mesuré sur une roue dentée du dispositif horloger de la figure 1 lors de sa rotation d'un pas ;
• la figure 7 est une vue de dessus d'un dispositif horloger intégrant un sautoir selon l'art antérieur ;
• la figure 8 représente, en vue de dessus, une variante de l'organe de positionnement du dispositif horloger de la figure 1 ;
• la figure 9 représente, en vue de dessus, une autre variante de l'organe de positionnement du dispositif horloger de la figure 1 ;
• les figures 10a et 10b sont des vues respectivement de dessous et de dessus d'une autre variante de l'organe de positionnement du dispositif horloger de la figure 1;
• la figure 11 est une vue de dessus d'un dispositif horloger selon un second mode de réalisation de l'invention ;
• la figure 12 est une vue de dessus d'un organe de positionnement du dispositif horloger de la figure 11 ;
• la figure 13 est une représentation graphique de la force de rappel élastique exercée dans l'organe de positionnement du dispositif horloger de la figure 11 ;
• la figure 14 est une représentation graphique du moment de force mesuré sur une roue dentée du dispositif horloger de la figure 11 lors de sa rotation d'un pas ;
• la figure 15 représente, en vue de dessus, une variante de l'organe de positionnement du dispositif horloger de la figure 11 ;
• la figure 16 est une représentation graphique du moment de force mesuré sur la roue dentée du dispositif horloger de la figure 11 dans lequel l'organe de positionnement correspond à la variante illustrée à la figure 15, lors de sa rotation d'un pas ;
• la figure 17 représente, en vue de dessus, une autre variante de l'organe de positionnement du dispositif horloger de la figure 11 ;
• la figure 18 est une représentation graphique du moment de force mesuré sur la roue dentée du dispositif de la figure 11 dans lequel l'organe de positionnement correspond à la variante illustrée à la figure 17, lors de sa rotation d'un pas ;
• la figure 19a représente, en vue de dessus, une autre variante de l'organe de positionnement du dispositif horloger de la figure 11 ;
• la figure 19b représente une partie de l'organe de positionnement représenté à la figure 19a ;
• les figures 20 à 24 représentent respectivement, en vue de dessus, d'autres variantes de l'organe de positionnement du dispositif horloger de la figure 11 ;
• la figure 25 représente, en perspective, une autre variante de l'organe de positionnement du dispositif horloger de la figure 11 ;

Other characteristics and advantages of the present invention will become apparent on reading the following detailed description given with reference to the appended drawings in which:

• the figure 1 is a top view of a timepiece device according to a first embodiment of the invention;
• the figure 2 is a top view of a positioning member of the watchmaking device of the figure 1 ;
• the figure 3 is a schematic graphic representation of the elastic return moment exerted in the positioning member of the watch device of the figure 1 ;
• the figure 4 represents the coordinates of points defining a particular shape of an elastic blade of the positioning member of the watch device of the figure 1 ;
• the figures 5a and 5b are graphic representations of the elastic return moment exerted in a positioning member of the watch device of the figure 1 comprising resilient blades having the shape as shown in figure 4 ;
• the figure 6 is a graphic representation of the moment of force measured on a toothed wheel of the watchmaking device of the figure 1 during its rotation by one step;
• the figure 7 is a top view of a watch device incorporating a jumper according to the prior art;
• the figure 8 shows, in top view, a variant of the positioning member of the watchmaking device of the figure 1 ;
• the figure 9 shows, in top view, another variant of the positioning member of the timepiece device of the figure 1 ;
• the figures 10a and 10b are views respectively from below and from above of another variant of the positioning member of the timepiece device of the figure 1 ;
• the figure 11 is a top view of a timepiece device according to a second embodiment of the invention;
• the figure 12 is a top view of a positioning member of the watchmaking device of the figure 11 ;
• the figure 13 is a graphic representation of the elastic return force exerted in the positioning member of the watch device of the figure 11 ;
• the figure 14 is a graphic representation of the moment of force measured on a toothed wheel of the watchmaking device of the figure 11 during its rotation by one step;
• the figure 15 shows, in top view, a variant of the positioning member of the watchmaking device of the figure 11 ;
• the figure 16 is a graphic representation of the moment of force measured on the toothed wheel of the watchmaking device of the figure 11 in which the positioning member corresponds to the variant illustrated in figure 15 , during its rotation by one step;
• the figure 17 shows, in top view, another variant of the positioning member of the timepiece device of the figure 11 ;
• the figure 18 is a graphical representation of the moment of force measured on the toothed wheel of the device of the figure 11 in which the positioning member corresponds to the variant illustrated in figure 17 , during its rotation by one step;
• the figure 19a shows, in top view, another variant of the positioning member of the timepiece device of the figure 11 ;
• the figure 19b represents a part of the positioning member shown in figure 19a ;
• the figures 20 to 24 respectively show, in top view, other variants of the positioning member of the watch device of the figure 11 ;
• the figure 25 shows, in perspective, another variant of the positioning member of the watchmaking device of the figure 11 ;

With reference to the figure 1 , a watch device 1 according to a first embodiment of the invention, intended to form part of a watch mechanism such as a movement or a mechanism additional to the movement, comprises a wheel 11 comprising a toothing 111, and a control member. positioning 10.

The set of teeth 111 is typically a set of teeth comprising truncated teeth.

The positioning member 10 shown in figure 1 is a ratchet. It maintains the wheel 11 in position and allows its rotation only in the anti-clockwise direction, as indicated by arrow B.

The wheel 11 is typically a toothed wheel carrying, driving or forming a display member, such as a disc, a needle or a display crown. As a variant, it may also be, for example, a column wheel, a barrel or ring ratchet, a winding wheel, or any type of toothed wheel traditionally positioned by a pawl. It is typically other than an escape wheel.

As shown in figure 1 , the positioning member 10 comprises an engagement member 15, a support 12 and an elastic member 14 connecting the engagement member 15 to the support 12. The elastic member 14 typically comprises several elastic blades distributed, preferably uniformly , around the support 12. These elastic blades 14 connect the support 12 to the engagement element 15 which is itself engaged in the teeth 111 of the wheel 11 to be positioned.

The positioning member 10 shown in figures 1 and 2 further comprises a rim 13 in the form of a closed circle carrying the engagement element 15 and forming the connection between the latter and the elastic member 14.

Within the device 1, the support 12 is fixed to a fixed or mobile frame 100, on which the wheel 11 is also mounted, said frame 100 typically comprising the plate carrying the watch mechanism. The rim 13 as well as the engagement element 15 which is integral with it are guided in rotation with respect to the support 12 by the elastic blades 14.

In the example illustrated, the engagement element 15 takes the form of a radial projection defining two inclined planes forming an angle of 120 ° between them and preferably pointing towards the center of the wheel 11.

The set of elastic blades 14 exerts a return moment tending to cause the rim 13 to pivot around the support 12 in the anti-clockwise direction of the figures 1 and 2 .

The rotation of the rim 13 in the anti-clockwise direction is limited by a stop 16, fixed to the frame 100, against which a protuberance 17 of the rim 13 rests, when the device 1 is in the rest position, that is, that is to say when the engagement element 15 is engaged, in a centered manner, in a hollow 11a of the toothing 111, between two consecutive teeth of the wheel 11, as illustrated in figure 1 .

The figure 2 represents, for the understanding of the invention, the positioning member 10 isolated, that is to say free from any interaction with the stop 16 or with the wheel 11.

Due to the shape of its elastic blades 14, the positioning member 10 has a preferred direction of rotation of its rim 13, and therefore of its engagement element 15, relative to its support 12, this direction being defined as that which allows, from a state of rest of said isolated positioning member 10 in which all of its elastic blades 14 are at rest, the greatest relative angular displacement of the engagement element 15 with respect to the support 12. The arrow A shown on figures 1 and 2 illustrates this preferred direction of rotation of the engagement element 15 relative to the support 12; this direction corresponds to the clockwise direction in these figures.

Let θ be the angular position of the engagement element 15 of the isolated positioning member 10 relative to the support 12, θ being equal to zero when the isolated positioning member 10 is at rest, that is to say say when all of its elastic blades 14 are at rest, and increasing with the relative angular displacement of the engagement element 15 with respect to the support 12 in the preferred direction of rotation of the isolated positioning member 10; the figure 3 illustrates the evolution M (θ) of the elastic return moment exerted by the assembly of the elastic blades 14 in the isolated positioning member 10 as a function of the angular position θ of the engagement element 15 relative to the support 12 .

In general, when the engagement element 15 is in the angular position in which θ = x °, the positioning member 10 is said to be armed with x °.

• pour un angle θ compris entre 0 et une première valeur θ₁, le moment de rappel élastique augmente rapidement avec la position angulaire θ ;
• au-delà de cette première valeur θ₁, l'organe de positionnement 10 est dans une phase sensiblement stable. En effet, entre cette première valeur θ₁ et une seconde valeur θ₂, le moment de rappel élastique est sensiblement constant par rapport à la position angulaire θ.

As can be seen on the curve M (θ) of the figure 3 , this elastic restoring moment follows an evolution in three phases:

• for an angle θ between 0 and a first value θ ₁ , the elastic restoring moment increases rapidly with the angular position θ;
• beyond this first value θ ₁ , the positioning member 10 is in a substantially stable phase. Indeed, between this first value θ ₁ and a second value θ ₂ , the elastic restoring moment is substantially constant with respect to the angular position θ.

• au-delà de la valeur θ₂, le moment de rappel élastique augmente à nouveau jusqu'à atteindre une valeur limite M_limite, pour un déplacement angulaire θ=θ₃. Cette valeur M_limite dépend des propriétés du matériau dans lequel l'organe de positionnement 10 est réalisé et correspond à la contrainte maximale que peut subir cet organe 10.

The term “substantially constant” moment is understood to mean a moment not varying by more than 10%, preferably 5%, more preferably 3%, it being understood that this percentage can be reduced further. More precisely, let M _min and Mmax be respectively the values of the minimum and maximum moments exerted in the positioning member 10 isolated over a given range [θ ₁ , θ ₂ ] of angular positions of the engagement element 15 with respect to the support 12, the moment exerted in this isolated positioning member 10 is substantially constant as soon as the inequality "(M _max -M _min ) / ((M _max + M _min ) / 2) ≤ 0.1" is verified, more precisely, since the inequation "(Mmax-Mmin) / ((Mmax + Mmin) / 2) ≤ y%", with y = 10, preferably y = 5, more preferably y = 3, is verified . In this substantially stable phase, the elastic restoring moment exerted by all the elastic blades 14 in the isolated positioning member 10 however locally reaches a maximum for an angular position θ _a , then decreases in the range of angular positions. between the values θ _a and θ _b , where θ _a and θ _b are between θ ₁ and θ ₂ ;

• beyond the value θ _2, the time of elastic return again increases until it reaches a _limit threshold value M, for an angular displacement θ = θ _{3. This limit} value M depends on the properties of the material in which the positioning member 10 is made and corresponds to the maximum stress that this member 10 can undergo.

The isolated positioning member 10 exhibiting a curve M (θ) of the type shown in figure 3 differs from classical elastic structures. Its properties are based on a sinuous shape of its elastic blades 14 which deform so as to generate a substantially elastic restoring moment. constant (the curve M (θ) has a plateau between θ ₁ and θ ₂ ) over a predetermined range of angular positions of its engagement element 15 relative to its support 12. Obtaining such elastic blades requires a specific design and parameterized. They can for example be obtained by topological optimization by applying the teaching of the publication “Design of adjustable constant-force forceps for robot-assisted surgical manipulation”, Chao-Chieh Lan et al., 211 - IEEE International Conference on robotics and automation Shanghai International Conference Center May 9-13, China .

The topological optimization referred to in the aforementioned article uses parametric polynomial curves such as Bézier curves to determine the geometric shape of the elastic leaves 14.

Bézier curves are defined, jointly with a series of m = (n + 1) control points (Q ₀ , Q ₁ , ... Q _n ), by a set of points whose coordinates are given by sums of Bernstein polynomials weighted by the coordinates of said control points.

The geometric shape of each of the elastic blades 14 of the positioning member 10 is a Bézier curve whose control points have been optimized to take into account, in particular, the dimensions of the positioning member 10 to be designed as well as a constraint “(M _max -M _min ) / ((M _max + M _min ) / 2) ≤ 0.05”. The equation “(M _max -M _min ) / ((M _max + M _min ) / 2) ≤ 0.05” corresponds to a constancy of the elastic restoring moment of 5% over an angular range.

In general, all of the elastic blades 14 of the positioning member 10 of the device 1 is designed, in particular by virtue of its shape, to exert, in this member 10, a substantially constant elastic restoring moment (constancy of 5%) over a range of angular positions of the rim 13 and of the engagement element 15 which it carries relative to the support 12 of at least 10 °, preferably at least 15 °, more preferably at least 20 °.

où les $B_i^n$

sont les polynômes de Bernstein donnés par la fonction $$B_i\left(t\right)=\frac{\left(m-1\right)!}{i!\left(m-1-i\right)!}{t}^i{\left(1-t\right)}^{m-i-1}\mathrm{avec}\mathrm{t}\in \left[\mathrm{0,1}\right],$$

et où les Qi sont les points de contrôle Q₀ à Q_n. Elle correspond à la représentation graphique dans un repère orthonormé de l'ensemble des points définis par les couples de coordonnées (x ; y) définis respectivement par les fonctions x(t) et y(t), t ∈ [0, 1], ci-dessous : $$x\left(t\right)={\displaystyle {\sum }_{i=0}^{m-1}{Q}_{\mathit{ix}}{B}_i\left(t\right)}$$

$$y\left(t\right)={\displaystyle {\sum }_{i=0}^{m-1}{Q}_{\mathit{iy}}{B}_i\left(t\right)}$$

dans lesquelles Qix et Qiy sont respectivement les coordonnées x et y des points de contrôle Qi.More precisely, the geometric shape of each of the elastic blades 14 of the positioning member 10 is defined by the set of points $${\displaystyle {\sum }_{i=0}^{\mathrm{not}}{B}_i^{\mathrm{not}}\left(t\right).Q_i,\mathrm{with}\mathrm{t}\in \left[0.1\right]},$$

where the $B_i^{\mathrm{not}}$

are the Bernstein polynomials given by the function $$B_i\left(t\right)=\frac{\left(m-1\right)!}{i!\left(m-1-i\right)!}{t}^i{\left(1-t\right)}^{m-i-1}\mathrm{with}\mathrm{t}\in \left[0.1\right],$$

and where the Qi are the control points Q ₀ to Q _n . It corresponds to the graphic representation in an orthonormal frame of reference of all the points defined by the pairs of coordinates (x; y) defined respectively by the functions x (t) and y (t), t ∈ [0, 1], below : $$x\left(t\right)={\displaystyle {\sum }_{i=0}^{m-1}{Q}_{\mathit{ix}}{B}_i\left(t\right)}$$

$$y\left(t\right)={\displaystyle {\sum }_{i=0}^{m-1}{Q}_{\mathit{iy}}{B}_i\left(t\right)}$$

where Qix and Qiy are the x and y coordinates of the Qi control points, respectively.

The formulas given above give the coordinates of a Bézier curve of order m, that is to say a Bézier curve based on m control points. For practical reasons, such a Bézier curve can be broken down into a succession of Bézier curves of order less than m, in which case the geometric shape of each of the elastic sheets is a succession of Bézier curves.

Using this principle, the Applicant has designed a particular positioning member comprising four elastic blades distributed uniformly around the support 12. The dimensions of this positioning member 10 are as follows: Outside diameter of the rim: 12 mm Support outer diameter: 2 mm Inside diameter of the rim: 10 mm Height: 0.12 mm Thickness of elastic blades : 24 µm

For this design, seven control points Q ₀ , Q ₁ , Q ₂ , Q ₃ , Q ₄ , Q ₅ , Q ₆ were used. The coordinates of these control points are shown in Table 1 below. <b> Table 1 </b>: Coordinates of control points Q ₀ to Q ₆. Variables Coordinates x [mm] Coordinates y [mm] Q ₀ 0.756625 0.653875 Q ₁ 1.87325 1.619 Q ₂ 2.8125 -0.59125 Q ₃ 3.4375 0.4535 Q ₄ 3.75 1.032875 Q ₅ 4.375 0 Q ₆ 5 0

With these seven control points it would have been possible to produce a Bézier curve of order seven. However, according to the principle indicated above, the Bézier curve was broken down into two segments, a first segment corresponding to a curve of Bézier of order 4 based on control points Q ₀ to Q ₃ and a second segment corresponding to a Bézier curve of order 4 based on control points Q ₃ to Q ₆ .

By using the coordinates of the control points Q ₀ to Q ₆ above in the aforementioned functions x (t) and y (t), the applicant obtained the coordinates of the points defining the geometric shape of an elastic blade of the organ of positioning 10. A certain number of these pairs of coordinates are given in Table 2 below. <b> Table 2: </b> Coordinates of the passage points of the optimized elastic blade. X [mm] Y [mm] 0.756625 0.653875 1.0861324 0.8545816 1.404044 0.903348 1.7094066 0.8387564 2.001267 0.699389 2.2786719 0.5238281 2,540668 0.350656 2,7863021 0.2184549 3.014621 0.165807 3.2246714 0.2312946 3.4155 0.4535 3.4155 0.4535 3.5242745 0.5815901 3,648736 0.628816 3,7871415 0.6110484 3.937748 0.544158 4.0988125 0.4440156 4.268592 0.326492 4.4453435 0.2074579 4.627324 0.102784 4.8127905 0.0283411 5 0

The graph of the figure 4 shows the geometry of the external diameter of the support 12, of the internal diameter of the rim 13 and of one of the elastic blades 14 of the particular positioning member 10 that the applicant has designed, the geometry of said blade 14 being defined by a curve passing through all the coordinates of points defined in table 2 above. This graph is produced in an orthonormal coordinate system.

The figures 5a and 5b represent the results of a simulation of the evolution of the elastic return moment of the particular positioning member 10 thus produced as a function of the angular position θ of its engagement element 15 relative to its support 12.

The simulation carried out considers a positioning member 10 produced in an alloy based on cobalt, nickel and chromium, more precisely in Nivaflex® 45/18 (Young's modulus E = 220 GPa), but any suitable material can be used. For example materials such as silicon (E = 130 GPa), typically coated with silicon oxide, metallic glass, plastic or CK101 (unalloyed structural steel) are also suitable. It is important to take into account the relationship between the elastic limit and the Young's modulus of the material to choose the material constituting the elastic strips 14.

The analysis of the results presented to the figures 5a and 5b that a locally maximum then decreasing elastic restoring moment is obtained during a displacement of the engagement element 15 of the particular isolated positioning member 10 studied with respect to its support 12 by an angular position θ _a = 17 ° at an angular position θ _b = 28 °, ie over a range of 11 °.

The stiffness of the positioning member 10, more precisely of its set of elastic blades 14, is the derivative of the function M (θ) defined above.

Over the range of angular positions [θ _a , θ _b ] over which the moment of force is decreasing, the stiffness of the isolated positioning member 10 is negative. The stiffness of the isolated positioning member 10 is zero at the point at which the elastic restoring moment reaches a local maximum. In the present invention, one places oneself in this range [θ _a , θ _b ] or at least partly in this range.

Within the device 1, the positioning member 10 is therefore arranged so that, during the rotation of a pitch of the wheel 11 against the return action of the set of elastic blades 14, the element of engagement 15 moves within a range predetermined position with respect to the support 12, this range being included in the range of positions [θ ₁ , θ ₂ ] associated with the positioning member 10 and comprising at least part of the range of positions [θ _a , θ _b ] in which the stiffness of all the elastic blades 14 is zero or negative. Preferably, said predetermined range is included in the range [θ _a , θ _b ] or constituted by the latter.

To obtain such an arrangement, the positioning member 10 is fixed by its support 12 on the frame 100 of the mechanism so that it is armed with θ _arm degrees when the protuberance 17 bears against the stop 16 and so that this stop 16 prevents the return of the engagement element 15 in the range of positions between θ = 0 and θ = θ _arm . Indeed, the set of elastic blades 14 exerts an elastic return moment tending to cause the rim 13 and the engagement element 15 that it carries around the support 12 to pivot in the direction of the reduction of the angle θ (counterclockwise on the figure 1 ).

In addition, in the position in which the protuberance 17 of the positioning member 10 bears against the stop 16, the engagement element 15 is positioned between two successive teeth of the teeth 111 of the wheel 11 to be positioned now. thus the latter in position under the effect of the return moment exerted by the set of elastic blades 14.

In addition, the angle θ _arm , the dimensions of the positioning member 10, in particular its diameter and the angle between the inclined planes of its engagement element 15, as well as the shape and dimensions of the teeth 111 of the wheel 11, are chosen so that, during the angular displacement of one step of the wheel 11, the engagement element 15 moves angularly with respect to the support 12 in the range of positions [θ ₁ , θ ₂ ] and at least partly in the range of positions [θ _a , θ _b ]. θ _arm is therefore between θ ₁ and θ ₂ and preferably approximately equal to θ _a .

The choice of the angle θ _arm defines the lower limit of the predetermined range of positions in which the engagement element 15 moves during the rotation of a pitch of the wheel 11. The dimensions of the positioning member 10, in particular its diameter and the angle between the inclined planes of its engagement element 15 as well as the shape and dimensions of the teeth 111 of the toothed wheel 11 define, for their part, the upper limit of this range of positions.

1. i. fixer le support 12 de l'organe de positionnement 10 au repos sur le bâti 100 ;
2. ii. pré-armer l'organe de positionnement 10 par rotation de la serge 13 dans le sens de rotation privilégié A d'un angle θ = θ_{arm ;}
3. iii. fixer la butée 16 sur le bâti 100 à proximité de la protubérance 17 de façon à empêcher le désarmage de l'organe de positionnement 10 en deçà de θ_arm ; et
4. iv. positionner la roue 11 de façon à ce que, lorsque la protubérance 17 portée par la serge 13 est en appui contre la butée 16, l'élément d'engagement 15 soit positionné entre deux dents successives de la denture 111 de la roue 11, en pointant, de préférence vers le centre de la roue 11.

The conditions listed above can be met, for example, by carrying out the following steps:

1. i. fixing the support 12 of the positioning member 10 at rest on the frame 100;
2. ii. pre-arm the positioning member 10 by rotating the rim 13 in the preferred direction of rotation A by an angle θ = θ _arm;
3. iii. fixing the stop 16 on the frame 100 near the protuberance 17 so as to prevent the disarming of the positioning member 10 below θ _arm ; and
4. iv. position the wheel 11 so that, when the protuberance 17 carried by the rim 13 bears against the stop 16, the engagement element 15 is positioned between two successive teeth of the teeth 111 of the wheel 11, in pointing, preferably towards the center of the wheel 11.

It is clear to those skilled in the art that the conditions necessary to limit the movements of the engagement element 15 to the predetermined range of values of interest during the rotation of one pitch of the toothed wheel 11 can be obtained. by a succession of different stages.

The figure 6 presents the results of measurements of the moment of force recorded on the wheel 11 of the device 1 as a function of its angular displacement, during a rotation of an angle α corresponding to a pitch of the wheel 11 in the direction of arrow B .

For these measurements, the same toothed wheel 11, 71 was positioned either with the positioning member 10 of the device 1 according to the first embodiment of the invention (curve c ₁ ), or with a jumper 70 using a spring 74 with traditional positive stiffness (co curve) as shown in figure 7 .

As shown in figure 7 , the device 7 comprising a jumper 70 of the prior art studied (curve co) comprises an engagement element 75 engaged in the teeth 711 of a toothed wheel 71. This jumper 70 allows the rotation of the toothed wheel 71 in the two directions (clockwise and anti-clockwise corresponding respectively to arrows G and F of the figure 7 ), however only counterclockwise rotation (arrow F) has been studied here.

With reference to the figure 6 , the angle a = 0 ° corresponds to the position in which the engagement element 15 of the positioning member 10 shown in figure 1 or, as the case may be, the engagement element 75 of the jumper 70 using a pre-armed spring 74 shown in figure 7 , is engaged centrally between two teeth of the wheel 11, 71. The angle α increases with the rotation of the wheel 11 (curve c ₁ ) or 71 (curve co) respectively in the direction of arrow B ( figure 1 ) or the arrow F ( figure 7 ). In this example, in the position in which a = 0 °, the positioning device 10 is pre-armed with θ _arm = 17 °, the rotation of one step of the wheel 11 corresponds to an angle a = 18 °, and the maximum winding of the positioning member 10 is 25 °.

With reference to the figure 6 , the moment necessary to initiate the rotation of the wheel 11 or "starting moment" is approximately identical in the device 1 using the positioning member 10 and in the device 7 using the traditional jumper 70. It is approximately 0.084 N.mm. The wheel 11 is therefore held in position by the pawl consisting of the positioning member 10 according to the first embodiment of the invention as well as by the traditional jumper 70.

A notable difference is that the use of the traditional jumper (device 7; curve co) generates an operating peak of 0.135 N.mm which increases the energy consumption and risks blocking the mechanism if the wheel 11 is not in operation. able to provide sufficient moment of force to overcome this peak.

Due to the properties of the positioning member 10 in the predetermined range of positions used, in particular, due to the stiffness at least in zero or negative part of the positioning member 10 in this range, the moment necessary to rotate the wheel 11 by one step in the case of the device 1 (curve c ₁ ) does not include any operating peak . On the contrary, it constantly decreases until it reaches a value of approximately 0.037 N.mm corresponding to the moment necessary to rotate the wheel 11 when the engagement element 15 is opposite the truncated portion 11b of the toothing 111.

The horological device 1 comprising a wheel 11 and a positioning member 10 according to the first embodiment of the invention therefore allows a reduction in the maximum instantaneous energy consumption required during the rotation of one step of the wheel to be positioned. compared to a traditional jumper 70 using a spring 74 with positive stiffness allowing an equivalent position to be maintained.

Such a horological device 1 also has the advantage of being less sensitive to linear shocks than jumpers or pawls according to the prior art. This is due to the good balancing of its positioning member 10. This reduction in sensitivity to linear shocks can make it possible to lower the value of the starting moment while maintaining good support in the event of linear shocks and thus to reduce overall consumption. energy during a one-pitch rotation of the toothed wheel 11.

The positioning member 10 of the device 1 according to the first embodiment of the invention is typically monolithic. It can for example be manufactured by machining, in particular in the case where it is made of metal or of an alloy such as Nivaflex®, by DRIE etching in the case of silicon for example, or also by molding, cutting, machining, especially in the case where it is made of plastic or metallic glass.

As a variant, the positioning member 10 may only comprise a single elastic blade 14. The rim 13 may also be interrupted and take the form of an arc of a circle, as illustrated in FIG. figure 8 .

The very structure of the positioning member 10 involves the centering of the support 12 relative to its rim 13. However, it may include a centering device aimed at reinforcing the centering of the support 12. Such a device typically comprises a rigid element of junction 18, on the one hand, fixed integrally to at least one zone of the rim 13 and on the other hand, positioned freely in rotation about an axis 19, said axis 19 being integral with the support 12 and centered on this support 12 . The figures 10a and 10b are views respectively from below and from above of a positioning member 10 equipped with such a centering device. The positioning member 10 illustrated in figure 8 also includes such a centering device.

In variants, the horological device 1 according to the first embodiment of the invention may comprise a positioning member of a different shape from that illustrated in figures 1 and 2 , it can typically include elastic strips of a different shape from that illustrated in figure 4 . It can in particular take a form such as shown in figure 9 .

The positioning member 20 shown in figure 9 comprises a support 22 and a rim 23 connected by elastic blades 24, the rim 23 carrying an engagement element 25 intended to be engaged in the teeth of a toothed component to be positioned and held in this teeth under the effect of the moment return exerted by all the elastic blades 24.

A means of obtaining such elastic blades 24 is described in particular in the article “Functional joint mechanisms with constant torque outputs”, Mechanism and machine theory 62 (2013) 166-181, Chia-Wen Hou et al.

With reference to the figure 11 , a horological device 3 according to a second embodiment of the invention comprises a wheel 31 comprising a toothing 311, and a positioning member 30.

The positioning member 30 is here a jumper. It maintains the wheel 31 in position and allows it to rotate in both directions, clockwise and anti-clockwise, as indicated respectively by arrows C and D on the left. figure 11 .

The wheel 31 is typically a toothed wheel carrying, driving or forming a display member such as a disk, a needle or a display crown. As a variant, it may also be, for example, a column wheel or any type of toothed wheel traditionally positioned by a jumper. It is typically other than an escape wheel.

As shown in figure 11 , the positioning member 30 comprises a rigid mobile element 33 and an elastic member 34 connecting the latter to a rigid support 32. The elastic member 34 typically comprises a pair of parallel elastic blades working in buckling. Each of these blades 34 is interrupted in its central part by the rigid element 33 and has its two ends joined to said rigid support 32.

The support 32 is fixed to a frame 300 on which the wheel 31 is also mounted and the rigid element 33 is movable relative to this support 32. The frame 300 can be fixed or movable and typically comprises the plate carrying the mechanism or movement. watchmaker of which the device is part 3.

The rigid element 33 is guided in translation by the elastic blades 34 and moves along a straight line (d) preferably passing through the center of the wheel 31. It comprises an engagement element 35 engaged in the teeth 311. of the wheel 31 to be positioned. In the example illustrated, the engagement element 35 takes the form of a projection defining two inclined planes forming an angle of 120 ° between them and preferably pointing towards the center of the wheel 31.

The engagement element 35 moves with the rest of the rigid element 33 along the line (d) defined above.

In the example shown in figure 11 , the straight line (d) passes through the center of the wheel 31 and the assembly comprising the elastic blades 34 and the rigid element 33 is symmetrical with respect to this straight line (d).

Within the device 3, the pair of blades 34 is pre-armed and exerts a force tending to push the engagement element 35 against the wheel 31, as shown by the arrow E at the bottom. figure 11 .

The elastic blades 34 are here preformed flamed, that is to say they are machined with a flamed shape. They could however be preformed straight and work in buckling under the effect of compression of their ends. To do this, the support 32 could be split in its central part to define two parts movable with respect to one another allowing adjustment of the compression. Each of them could also be preformed in the form of two V-shaped half-lines, and only buckle under the effect of its pre-winding.

The movement of the engagement element 35 in the direction opposite to the arrow E can be limited by a stop 36 forming part of the support 32.

The figure 12 represents, for the understanding of the invention, the isolated positioning member 30. The positioning member 30 is therefore considered here without the stop 36 and outside the device 3, that is to say free from any interaction with the toothed wheel 31.

With reference to the figure 13 , let Δ be the position of the engagement element 35 of the isolated positioning member 30 along the straight line (d), Δ being equal to 0 when the engagement element 35 is moved as far away as possible from the support 32 (in this position the flamed preformed blades 34 are at rest) and increasing when the engagement element 35 approaches the support 32; the figure 13 represents the evolution F (Δ) of the force exerted by the engagement element 35 in the direction of the arrow E, this force being the result of the forces exerted by the pair of elastic blades 34.

This force was measured, for each position Δ, by measuring the opposite force required to maintain the engagement element 35 in a given position.

In general, when the engagement element 35 is in the position in which Δ = x mm, the positioning member 30 is said to be armed with x mm.

• le point de départ Δ=Δ_s1=0, correspond à un état stable de l'organe de positionnement 30. En effet, dans cette position, la force F(Δ_s1) est nulle, c'est-à-dire que l'élément d'engagement 35 n'exerce aucune force ;
• pour une position Δ comprise entre 0 et une première valeur Δ₁, la force de rappel élastique augmente linéairement et rapidement avec la position Δ ;
• lorsque Δ atteint la première valeur Δ₁, la force de rappel élastique atteint un maximum puis reste positive mais se met à décroître linéairement. Δ atteint alors la position Δ₂ dans laquelle la force est à nouveau nulle. Cependant, il ne s'agit pas à proprement parler d'un état stable mais plutôt d'un équilibre instable ;
• au-delà de la position Δ₂ la force devient négative puis continue à décroître linéairement jusqu'à atteindre la position Δ₃ dans laquelle la force F(Δ) atteint un minimum. Une force F(Δ) négative correspond à une force de sens opposé à la flèche E, l'élément d'engagement 35 est « tiré » vers le support 32 ;
• pour une position Δ comprise entre Δ₃ et Δ_s2, la force de rappel élastique reste négative mais augmente linéairement et rapidement avec le déplacement Δ jusqu'à devenir nulle pour Δ=Δ_s2. Le point Δ_s2 correspond à un second état stable de l'organe de positionnement 30. En effet, dans cette position, la force F(Δ_s2) est nulle, c'est-à-dire que l'élément d'engagement 35 n'exerce aucune force.

As can be seen on the graph F (Δ) of the figure 13 , this force follows an evolution in several phases:

• the starting point Δ = Δ _s1 = 0, corresponds to a stable state of the positioning member 30. In fact, in this position, the force F (Δ _s1 ) is zero, that is to say that l engagement element 35 exerts no force;
• for a position Δ between 0 and a first value Δ ₁ , the elastic return force increases linearly and rapidly with the position Δ;
• when Δ reaches the first value Δ ₁ , the elastic restoring force reaches a maximum then remains positive but begins to decrease linearly. Δ then reaches the position Δ ₂ in which the force is again zero. However, it is not strictly speaking a stable state but rather an unstable equilibrium;
• Beyond the position Δ _2, the force becomes negative then continues to decrease linearly until it reaches the position Δ ₃ in which the force F (Δ) reaches a minimum. A negative force F (Δ) corresponds to a force in the opposite direction to the arrow E, the engagement element 35 is “pulled” towards the support 32;
• for a position Δ between Δ ₃ and Δ _s2 , the elastic return force remains negative but increases linearly and rapidly with the displacement Δ until it becomes zero for Δ = Δ _s2 . The point Δ _s2 corresponds to a second stable state of the positioning member 30. In fact, in this position, the force F (Δ _s2 ) is zero, that is to say that the engagement element 35 does not exert any force.

The isolated positioning member 30 exhibiting an evolution of the force F (Δ) of the type shown in figure 13 differs from classical elastic structures. Its properties are based on the capacity of its elastic blades 34 to work in buckling, which allows it to behave like a bistable.

Obtaining elastic blades exhibiting these properties is within the abilities of those skilled in the art.

The Applicant has designed a particular positioning member 30 comprising a pair of elastic blades 34 parallel. With reference to the figure 12 , the dimensions of this positioning member 30 are those indicated in Table 1 below: Table 1: Dimensions Unit Value Arrow (f) of blades 34 at rest [mm] 0.3 Blade length (L) 34 [mm] 12.5 Slat thickness (e) 34 [mm] 0.12 Height of slats 34 [µm] 35 Angle of the inclined planes defining the engagement element 35 [°] 120 ° Jump back of the jumper during the rotation of one step of the wheel 31 [mm] 0.3

The figure 13 shows an analytical model representing the evolution of the force F (Δ) of the particular positioning member 30 thus produced as a function of the position of its engagement element 35 along the line (d).

This model considers a monolithic positioning member made of an alloy based on cobalt, nickel and chromium, more precisely in Nivaflex® 45/18, but any suitable material can be used. For example materials such as silicon typically coated with silicon oxide, metallic glasses, mineral glasses, ceramic glasses, plastics or CK101 (unalloyed structural steel) are also suitable. It is however conceivable to produce a non-monolithic positioning member 30 by assembling several elements or parts, these elements can moreover be made of identical materials or different from each other.

It is important to take into account the relationship between the elastic limit and the Young's modulus of the material to choose the material constituting the elastic strips 34.

It emerges from the analytical model presented to the figure 13 that a locally maximum then linearly decreasing elastic restoring force is obtained during a displacement of the engagement element 35 of the particular isolated positioning member 30 studied from the position Δ ₁ ≈0.05 mm to the position Δ ₂ = 0.4 mm.

The stiffness of the positioning member 30 is the derivative of the function F (Δ) defined above.

Over the range of positions [Δ ₁ , Δ ₂ ] over which the force is decreasing, the stiffness of the isolated positioning member 30 is negative. In the present invention, we are in this range or at least in part in this range. Within the device 3, the positioning member 30 is therefore arranged to force, during the rotation of a pitch of the wheel 31 against the return action of the pair of elastic blades 34, the engagement element 35 to remain within a predetermined range of positions included in the range of positions [Δ ₁ , Δ ₂ ] associated with the positioning member 30.

To obtain such an arrangement, the positioning member 30 is fixed by its support 32 on the frame 300 of the mechanism so that the tip of the engagement element 35 is engaged centrally between two consecutive teeth of the toothing 311 of the wheel 31 to be positioned, maintaining the latter in position under the effect of the return force exerted by the pair of elastic blades 34, the positioning member 30 being armed with a value Δ _arm in this position.

The choice of the value Δ _arm defines the lower bound of the predetermined range of positions in which the engagement element 35 moves during the rotation. a pitch of the wheel 31. The shape and dimensions of the teeth of the toothing 311 and the angle between the inclined planes defining the engagement element 35 are chosen so that the maximum value Δ reached during the rotation d 'a pitch of the wheel 31 is less than or equal to Δ ₂ .

When present, the stopper 36 prevents movement of the engagement element 35 in the range of positions in which Δ is greater than Δ ₂ . This is a safety aiming to prevent the positioning member 30 from tilting towards the stable state corresponding to the position Δ _s2 of the engagement element 35 in the event of impact or manipulation affecting the device 3.

1. i. positionner la roue 31 sur le bâti 300 de sorte qu'elle soit libre en rotation autour d'un axe fixé dans le bâti 300 ;
2. ii. positionner l'organe de positionnement 30 de sorte que son élément d'engagement 35 soit engagé de manière centrée entre deux dents consécutives de la denture 311 et exercer une force sur l'organe de positionnement 30 jusqu'à ce que l'élément d'engagement 35 soit dans une position Δ = Δ_arm, c'est-à-dire pré-armé d'une valeur Δ_arm comprise entre Δ₁ et Δ₂ ; et
3. iii. fixer le support 32 sur le bâti 300 dans cette position.

The conditions listed above can be met, for example, by carrying out the following steps:

1. i. positioning the wheel 31 on the frame 300 so that it is free to rotate about an axis fixed in the frame 300;
2. ii. position the positioning member 30 so that its engagement member 35 is engaged centrally between two consecutive teeth of the toothing 311 and exert a force on the positioning member 30 until the engagement member engagement 35 either in a position Δ = Δ _arm , that is to say pre-armed with a value Δ _arm between Δ ₁ and Δ ₂ ; and
3. iii. fix the support 32 on the frame 300 in this position.

It is clear to those skilled in the art that the conditions necessary to limit the movements of the engagement element 35 to the predetermined range of values of interest during the rotation of one pitch of the wheel 31 can be obtained by a succession of different stages.

The figure 14 presents the results of measurements of the moment of force recorded on the wheel 31 of the device 3 as a function of its angular position β, for a rotation of the wheel 31 by an angle β corresponding to a step in the direction of arrow D of the figure 11 .

For these measurements, the same wheel 31, 71 was positioned either with the positioning member 30 of the device 3 according to the second embodiment of the invention (curve c ₂ ), or with the jumper 70 using a spring 74 to traditional positive stiffness (co curve) as shown in figure 7 .

As indicated above, the device 7 comprising a jumper 70 of the prior art studied (curve co) comprises an engagement element 75 engaged in the teeth 711 of a wheel 71. This jumper 70 allows the rotation of the wheel 71 in both directions (clockwise and anti-clockwise), however only anti-clockwise rotation (arrow F) has been studied here.

With reference to the figure 14 , the angle β = 0 corresponds to the position in which the engagement element 35 of the positioning member 30 shown in figure 11 or, as the case may be, the engagement element 75 of the jumper 70 using a spring 74 shown in figure 7 , is engaged centrally between two teeth of the wheel 31, 71. The angle β increases with the rotation of the wheel 31 (curve c ₂ ) or 71 (curve co) respectively in the direction of arrow D ( figure 11 ) or the arrow F ( figure 7 ). In this example, in the position in which β = 0, the positioning member 30 is pre-armed with Δ _arm = 0.1 mm, the rotation of one pitch of the toothed wheel 31 corresponds to a rotation of an angle β = 18 ° and the maximum winding of the positioning member 30 is Δ = 0.4mm.

With reference to the figure 14 , the moment necessary to initiate the rotation of the wheel 31 or "starting moment" is approximately the same in the case of the use of the positioning member 30 (0.083 N.mm) and in the case of the use of the jumper 70 using a spring 74 with traditional positive stiffness (0.084 N.mm). The wheel 31 is therefore held in position by the jumper using the positioning member 30 according to the second embodiment of the invention as well as by the jumper 70 of the prior art.

A notable difference is that the use of the traditional jumper (co curve) generates an operating peak of 0.135 N.mm which increases the energy consumption.

Due to the properties of the positioning member 30 in the predetermined range of positions used, in particular due to the negative stiffness of the positioning member 30 in this range, the moment required to rotate the wheel 31 of a not in the case of the positioning member 30 (curve c ₂ ) does not, for its part, include any operating peak. On the contrary, it constantly decreases until it reaches an almost zero value, corresponding to the moment necessary to rotate the wheel 31 when the engagement element 35 is opposite the truncated portion 31b of the toothing 311.

Once the truncated portion 31b has passed, for an angle β approximately equal to 14 °, the moment required to rotate the wheel 31 is negative, that is to say that the engagement element 35 exerts a force on the wheel 31 and thus participates in its repositioning.

The figure 14 therefore shows that both the jumper according to the second embodiment of the invention shown in figure 11 that the jumper 70 according to the prior art allow the repositioning of the toothed wheel 31, 71 to be positioned.

The horological device 3 comprising a wheel 31 and a positioning member 30 according to the second embodiment of the invention allows a reduction in the maximum instantaneous consumption of energy required during the rotation of one step of the wheel to be positioned by compared to a traditional jumper 70 using a spring 74 with positive stiffness allowing an equivalent position to be maintained.

Furthermore, over almost the entire extent of the rotation of one pitch of the wheel 31, the energy consumption is less in the case of the use of the positioning member 30 than in the case of the use. a saltire 70 according to art prior. The watch device 3 studied therefore makes it possible to reduce the overall consumption of energy during a rotation of one pitch of the toothed wheel 31.

Such a watch device 3 also has the advantage of being less sensitive to linear shocks than jumpers or pawls according to the prior art. This is due to the low weight of the movable parts of its positioning member 30, which are the elastic blades 34 and the engagement element 35. This low sensitivity to linear shocks can make it possible to lower the value of the starting moment while maintaining good support in the event of linear shocks and thus further reduce the overall energy consumption during a rotation of one pitch of the toothed wheel 31.

The low height of the blades 34 also makes it possible to reduce the height of the device 3. It is thus possible to reduce the height of the timepieces comprising such devices.

The positioning member 30 of the device 3 according to the second embodiment of the invention is typically monolithic. It can typically be manufactured by the same methods as those described for the positioning member 10 of the device 1 according to the first embodiment of the invention.

It should be noted that the positioning member 30 being a jumper, the rotation of the wheel 31 is authorized in both directions, namely, in the direction of arrow D but also in the direction of arrow C ( figure 11 ) and the curve representing the moment of force recorded on the wheel 31 to be positioned as a function of its angular displacement in the direction opposite to that studied would be identical to the curve c ₂ .

In variants, the horological device 3 according to the second embodiment of the invention may comprise a positioning member of a different shape from that illustrated in figures 11 and 12 . It can in particular take a form such as shown in figure 15 , to the figure 17 , to the figure 19a , to the figure 20 , to the figure 21 , to the figure 22 , to the figure 23 , to the figure 24 or at the figure 25 .

The figures 16 and 18 represent, respectively by the curves c ₃ and c ₄ the moment of force necessary to rotate a toothed wheel such as the wheel 31 positioned with a positioning member respectively as shown in figures 15 and 17 during the rotation of one step of this wheel 31, as for the figure 14 . Each of these figures also represents the curve co of the figure 14 for comparison.

The positioning member 40 shown in figure 15 differs from the positioning member 30 shown in figure 12 in that its engagement element 45 is truncated. This makes it possible to reduce the recoil of the engagement element 45 during the rotation of one pitch of the wheel 31 to be positioned. Elements 42, 43, 44 of the variant shown in figure 15 correspond respectively to elements 32, 33, 34 of the variant shown in figure 12 .

The positioning member 50 shown in figure 17 differs from the positioning member 30 shown in figure 12 in that it also has blades 59 working in flexion. This makes it possible to improve the repositioning of the wheel 31 by the positioning member 30 at the end of a step. The elements 52, 53, 54, 55 of the variant shown in figure 17 correspond respectively to elements 32, 33, 34, 35 of the variant shown in figure 12 .

The positioning member 90 shown in figure 21 differs from the positioning member 30 shown in figure 12 in that it has a single elastic blade 94 working in buckling to replace the pair of elastic blades 34. The elements 92, 93, 95 of the variant shown in figure 21 correspond respectively to elements 32, 33, 35 of the variant shown in figure 12 . The rigid element 93 can optionally be guided along the straight line (d) defined above by means of a guide system including for example a finger and a groove. In the absence of such a guide system, the elastic blade 94 of the positioning member 90 does not behave like a bistable but however, has a negative stiffness over a predetermined range of positions of the engagement member 95.

The positioning member 110 shown in figure 22 differs from the positioning member 90 shown in figure 21 in that its rigid element 113 and therefore its engagement element 115 interrupt the elastic blade 114 outside its central part, in this case approximately at 3/8 of the length of said blade 114. The eccentricity of the rigid element 113 on the elastic blade 114 decreases the intensity of the force generated by the elastic member comprising this blade 114, however the elastic member maintains a negative stiffness over a predetermined range of positions of the engagement element 115 by compared to support 112.

The positioning member 120 shown in figure 23 is a variant of the intermediate positioning member between that shown in figure 12 and the one shown in figure 21 . The positioning member 120 according to this variant comprises an elastic member comprising on one side of its rigid element 123 a half-blade 124a and on the other side of its rigid element 123 a pair of half-blades 124b. The elements 122, 123, 125 of the variant shown in FIG. 120 correspond respectively to elements 32, 33, 35 of the variant shown in figure 12 .

The positioning member 130 shown in figure 24 differs from the positioning member 90 shown in figure 21 in that its elastic blade 134 comprises on either side of its rigid element 133, more precisely at the level of each of the junctions of its elastic blade 134 with the support 132, an articulation 136, typically elastic, increasing the flexibility of the blade 134 at said junctions. This has the consequence of reducing the intensity of the force generated by the elastic member comprising this blade 134, however, the elastic member maintains a negative stiffness over a predetermined range of positions of the engagement member 135 with respect to the support 132. The elements 132, 133, 135 of the variant shown in figure 24 correspond respectively to elements 92, 93, 95 of the variant shown in figure 21 . As a variant, such a positioning member 130 may comprise only a single articulation 136, at the level of only one of the junctions of its elastic blade 134 with its support 132.

The positioning member 140 illustrated on figure 25 differs from the positioning member 90 shown in figure 21 in that it is not monolithic but obtained by assembling two parts, each of these parts defining a part 142a, 142b of the support 142, a half-blade 144a, 144b and a part 143a, 143b of the rigid element 143 comprising the engagement element 145. This variant makes it possible to increase the height of the rigid element 143 without modifying the height of the elastic member 144.

The positioning member 60 shown in figure 19a differs from the positioning member 90 shown in figure 21 in that its rigid element 63 and in particular its engagement element 65 are not symmetrical. The engagement element 65 defines two inclined planes forming an angle of 145 ° between them, a first plane forming an angle of 60 ° with the line (d) and a second plane forming an angle of 85 ° with the line (d ), as shown in figure 19b . The difference in slope of the inclined planes makes it possible to have a low starting moment with the slope of 85 ° and therefore a low consumption of energy to initiate the rotation of the wheel 31. In addition, this makes it possible to limit the force. tangential on the saltire. The 60 ° slope allows a good repositioning of the wheel. Elements 62 and 64 of the variant shown in figure 19a correspond respectively to elements 92 and 94 of the variant shown in figure 21 .

The positioning member 80 shown in figure 20 differs from the positioning member 30 shown in figure 12 in that it comprises a pair of elastic half-blades 84 replacing the pair of elastic blades 34. The elements 82 and 83 of the variant shown in figure 20 correspond respectively to elements 32 and 33 of the variant shown in figure 12 . However, the rigid element 83 comprises a protuberance 87 bearing against a stop 86. The fact that these elements bear against each other makes it possible to guide the engagement element 85 along the straight line (d ) preferably passing through the center of the wheel 31. It is also possible to envisage an elastic system for guiding in translation which makes it possible to avoid friction between the protuberance 87 of the rigid element 83 and the stop 36.

As can be seen on the figures 14 , 16 and 18 , the different variants of the positioning member that can be used in the device 3 according to the second embodiment of the invention make it possible to effectively position the wheel 31 to be positioned with a reduction in the overall energy consumption during the rotation of a pitch of said wheel 31. These different variants also have the same advantages as those associated with the variant presented in figure 11 . They make it possible in particular to eliminate the peak in energy consumption occurring during the rotation of a pitch of the wheel 31 to be positioned with a traditional jumper using a spring with positive stiffness allowing an equivalent position to be maintained.

It is clear to those skilled in the art that the present invention is in no way limited to the embodiments presented above and illustrated in the figures. In particular, it is clear that the characteristics of the different variants of the positioning member 30, 40, 50, 60, 80, 90, 110, 120, 130, 140 of the device 3 according to the second embodiment of the invention described can be combined.

It is also very well conceivable to produce a horological device according to the invention comprising an elastic member of structure different from those presented. Indeed, any elastic member having negative or zero stiffness over at least one range of positions may be suitable.

Whatever the embodiment of the invention, any device according to the invention considered at rest is associated with a moment of force value making it possible to initiate the rotation of the toothed wheel to be positioned.

Advantageously, whatever the embodiment of the invention, during normal operation of the device, the toothed component is permanently in contact with the positioning member. This gives the device good indexing, positioning and repositioning properties.

The toothed wheel with truncated teeth used in the various variants of the invention presented is preferred because it makes it possible to limit the recoil of the engagement element of the positioning member when it rotates by one step. However, it can easily be replaced by a conventional toothed wheel such as a star or by an asymmetric toothed wheel. In all cases, the two inclined planes of the engagement element advantageously have two respective support points with the toothing of the wheel when the latter is in the rest position (α = 0 ° or β = 0 °).

Those skilled in the art can also replace the toothed wheel to be positioned of one or the other of the two embodiments described by any other toothed component such as a rack or such as a crown, for example display. , internally toothed.

The angle between the two inclined planes defined by the engagement element of the positioning member is typically between 120 ° and 170 ° but may be different.

The watch device according to any one of the variants presented has the advantage of eliminating the peak in energy consumption observed in the jumpers and pawls traditionally used. It also makes it possible to reduce or even cancel the friction within the positioning member, in particular when it is monolithic, which leads to a reduction in its wear. In addition, such a device makes it possible to reduce the number of components in a mechanism. watchmaker using pawls or jumpers which results in an increase in reliability. The device according to the invention is not very sensitive to linear shocks and advantageously allows a reduction in the overall consumption of energy during the rotation of one pitch of its wheel.

The invention also relates to a timepiece such as a wristwatch or a pocket watch comprising such a horological device.

Claims (22)

1. Timepiece device (1; 3) comprising a toothed component (11; 31) and a positioning member (10; 20; 30; 40; 50; 60; 80; 90; 110; 120; 130; 140), said positioning member (10; 20; 30; 40; 50; 60; 80; 90; 110; 120; 130; 140) comprising an engagement element (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145), a support (12; 22; 32; 42; 52; 62; 82; 92; 112; 122; 132; 142) and a pre-wound elastic member (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) connecting the engagement element (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) to the support (12; 22; 32; 42; 52; 62; 82; 92; 112; 122; 132; 142), the toothed component (11; 31) being able to adopt different consecutive resting positions, the engagement element (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) being arranged such that in each of said resting positions it is engaged between two consecutive teeth of the toothing (111; 311) of the toothed component (11; 31) and held between these two teeth by the elastic member (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) so that it is holds said toothed component (11; 31) in said resting position, and such that, upon displacement by one pitch of the toothed component (11; 31) from one resting position to the following resting position, the engagement element (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) is raised by one of said two teeth against the action of the elastic member (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) and is then positioned between this tooth and another consecutive tooth so that it holds the toothed component (11; 31) in said following resting position,
   the positioning member (10; 20; 30; 40; 50; 60; 80; 90; 110; 120; 130; 140) being arranged such that, upon said displacement by one pitch of the toothed component (11; 31), the engagement element (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) moves within a predetermined range of positions with respect to the support (12; 22; 32; 42; 52; 62; 82; 92; 112; 122; 132; 142), characterised in that the stiffness of the elastic member (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) is null or negative in at least a part of the predetermined range.
2. Timepiece device (1; 3) as claimed in claim 1, characterised in that the stiffness of the elastic member (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) is null or negative in substantially the whole predetermined range.
3. Timepiece device (1; 3) as claimed in claim 1 or 2, characterised in that the stiffness of the elastic member (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) is negative in substantially the whole predetermined range.
4. Timepiece device (1; 3) as claimed in any one of claims 1 to 3, characterised in that said elastic member comprises at least one elastic strip (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) connecting the engagement element (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) to the support (12; 22; 32; 42; 52; 62; 82; 92; 112; 122; 132; 142).
5. Timepiece device (1; 3) as claimed in any one of claims 1 to 4, characterised in that the engagement element (15; 25) is guided in rotation with respect to the support (12; 22) by the elastic member (14; 24).
6. Timepiece device (1) as claimed in claim 5, characterised in that the elastic member (14; 24) is designed to exert a substantially constant elastic return moment through a range of angular positions of the engagement element (15; 25) with respect to the support (12; 22) of at least 10°, preferably at least 15°, preferably at least 20°, said predetermined range being at least partly within this range.
7. Timepiece device (1) as claimed in claim 5 or 6, characterised in that the positioning member (10; 20) further comprises a felloe (13; 23) connected to the support (12; 22) by the elastic member (14; 24) and bearing the engagement element (15; 25).
8. Timepiece device (1) as claimed in claim 7, characterised in that the felloe (13; 23) is in the shape of an arc of a circle.
9. Timepiece device (1) as claimed in claim 7 or 8, characterised in that it comprises at least one device (18) for centring the support (12; 22) with respect to the felloe (13; 23).
10. Timepiece device (1) as claimed in any one of claims 7 to 9, characterised in that it further comprises a stop (16), typically fixed to a frame (100) on which the support (12; 22) is fixed, the felloe (13;23) being arranged to cooperate with said stop (16) to pre-wind the elastic member (14; 24).
11. Timepiece device (1) as claimed in any one of claims 5 to 10 when claim 5 depends on claim 4, characterised in that the elastic strip or each of the elastic strips (14; 24) is of a sinuous shape.
12. Timepiece device (1) as claimed in any one of claims 5 to 11 when claim 5 depends on claim 4, characterised in that the geometric shape of the elastic strip or of each elastic strip (14; 24) is a Bezier curve or a succession of Bezier curves.
13. Timepiece device (3) as claimed in claim 4, characterised in that the positioning member (30; 40; 50; 60; 80; 90; 110; 120; 130; 140) comprises a mobile rigid element (33; 43; 53; 63; 83; 93; 113; 123; 133; 143) defining the engagement element (35; 45; 55; 65; 85; 95; 115; 125; 135; 145) and in that said at least one elastic strip (34; 44; 54; 64; 84; 94; 114; 124; 134; 144) connects the rigid element (33; 43; 53; 63; 83; 93; 113; 123; 133; 143) to the support (32; 42; 52; 62; 82; 92; 112; 122; 132; 142) and is arranged to work by buckling.
14. Timepiece device (3) as claimed in claim 13, characterised in that said at least one elastic strip comprises at least one elastic strip (34; 44; 54; 64; 84; 94; 114; 124; 134) which is pre-formed in a buckled shape or pre-formed in a V shape.
15. Timepiece device (3) as claimed in claim 13 or 14, characterised in that the positioning member (50) further comprises at least one strip (59) arranged to work by flexing in order to improve the repositioning of the toothed component (31) by said positioning member (50).
16. Timepiece device (3) as claimed in any one of claims 13 to 15, characterised in that said rigid element (33; 43; 53; 63; 83; 93) is mobile along a straight line (d).
17. Timepiece device (3) as claimed in claim 16, characterised in that the assembly comprising the elastic strip(s) (34; 44; 54; 94) and the rigid element (33; 43; 53; 93) is symmetrical with respect to said straight line (d).
18. Timepiece device (1; 3) as claimed in any one of the preceding claims, characterised in that the engagement element (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) comprises two inclined planes forming between them an angle of preferably between 120° and 170° and pointing in the direction of the toothing (111; 311).
19. Timepiece device (1; 3) as claimed in any one of the preceding claims, characterised in that said toothing (111; 311) comprises truncated teeth.
20. Timepiece device (1; 3) as claimed in any one of the preceding claims, characterised in that said toothed component is a wheel (11; 31).
21. Timepiece device (1; 3) as claimed in any one of the preceding claims, characterised in that said positioning member (10; 20; 30; 40; 50; 60; 80; 90; 110; 120; 130) is of a single piece.
22. Timepiece comprising a timepiece device (1; 3) as claimed in any one of the preceding claims.

Images