EP3619579A1

EP3619579A1 - Clock device having a positioning member

Info

Publication number: EP3619579A1
Application number: EP18723605.4A
Authority: EP
Inventors: Jean-Baptiste LE BRIS
Original assignee: Patek Philippe SA Geneve
Current assignee: Patek Philippe SA Geneve
Priority date: 2017-05-03
Filing date: 2018-04-26
Publication date: 2020-03-11
Anticipated expiration: 2038-04-26
Also published as: EP3619579B1; WO2018203187A1; EP3399373A1

Abstract

The invention relates to a clock 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 member (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 preset elastic member (14; 24; 44, 54; 64; 84; 94; 114; 124; 134; 144) connecting the engagement member (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 move into different consecutive rest positions, the engagement member (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) being arranged so that, in each of the rest positions, it is engaged between two consecutive teeth of the toothing (111; 311) of the toothed component (11; 31) and held between said two teeth by the elastic member (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) for holding said toothed component (11; 31) in the rest position in question, and so that, when a toothed component (11; 31) is moved by one step from a rest position to the next rest position, the engagement member (15; 25; 35; 45; 55; 65; 85 95; 115; 125; 135; 145) is lifted 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 said tooth and another consecutive tooth so that it holds the toothed component (11; 31) in said next rest position, the positioning member (10; 20; 30; 40 50, 60; 80; 90; 110; 120; 130; 140) being arranged so that, when said toothed component (11; 31) is moved by one step, the engagement member (15; 25; 45; 55; 65; 85; 95; 115; 125; 135; 145) moves in a predetermined range of positions relative to the support (12; 22; 32; 42; 52; 62; 82; 92; 112; 122, 39 132, 142), the stiffness of the elastic member (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) being nil or negative in at least one part of the predetermined range.

Description

Watchmaking device with positioning member

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

A jumper is an organ, usually a lever, terminated by two inclined planes which support between the tips of two consecutive teeth of a wheel, also called star, under the action of a spring, to maintain it in a certain angular position . When the wheel in question is activated, the teeth lift the jumper which then falls between two other teeth. A jumper allows the movement of the wheel in both directions.

A pawl is an organ, usually a lever, provided with a spout which enters the toothing 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 specific direction, the teeth lift the ratchet which then falls between two other teeth. In the other direction, the pawl prevents the wheel from turning by the shape of its nose and / or the teeth of the wheel.

Traditionally, jumpers and ratchets are built on the basis of leaf springs working in flexion. The moment of force exerted on the wheel is necessary to keep it in position. However, the moment of force required for the rotation of a pitch of the wheel must overcome the resistance exerted by the jumper or the pawl, which leads to a certain consumption of energy. To allow a good hold of the wheel, the moment of force required to initiate the rotation of the wheel should not be too low. But it is also essential that the maximum resistance exerted by the jumper or the ratchet when rotating a step of the wheel does not exceed a certain value so that the wheel is able to overcome it, otherwise the mechanism watchmaker could hang. In practice, the jumpers and ratchets currently used generate a peak energy consumption corresponding to maximum resistance. The aim of the invention is to propose a watchmaking device comprising a toothed component and a positioning member, said positioning member ensuring a good positional retention of the toothed component while at the same time reducing or even eliminating any peak in power consumption during operation. advancement of a pitch of said toothed component.

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 watch device.

Other features and advantages of the present invention will appear on reading the following detailed description given with reference to the accompanying drawings in which:

- Figure 1 is a top view of a clock device according to a first embodiment of the invention;

- Figure 2 is a top view of a positioning member of the clock device of Figure 1;

FIG. 3 is a schematic graphical representation of the moment of elastic return exerted in the positioning member of the clock device of FIG. 1;

FIG. 4 represents the coordinates of points defining a particular shape of an elastic blade of the positioning member of the clock device of FIG. 1;

FIGS. 5a and 5b are graphical representations of the elastic return moment exerted in a positioning member of the clock device of FIG. 1 comprising elastic blades having the shape as represented in FIG. 4;

FIG. 6 is a graphical representation of the moment of force measured on a toothed wheel of the clock device of FIG. 1 during its rotation of a step; Figure 7 is a top view of a watch device incorporating a jumper according to the prior art;

Figure 8 shows, in top view, a variant of the positioning member of the clock device of Figure 1;

Figure 9 shows, in top view, another variant of the positioning member of the clock device of Figure 1;

Figures 10a and 10b are views respectively from below and from above of another variant of the positioning member of the clock device of Figure 1;

Figure 1 1 is a top view of a clock device according to a second embodiment of the invention;

Figure 12 is a top view of a positioning member of the clock device of Figure 1 1;

Figure 13 is a graphical representation of the elastic restoring force exerted in the positioning member of the clock device of Figure 1 1;

FIG. 14 is a graphical representation of the moment of force measured on a toothed wheel of the watch device of FIG. 11 when it is rotating one step;

Figure 15 shows, in top view, a variant of the positioning member of the clock device of Figure 1 1;

FIG. 16 is a graphical representation of the moment of force measured on the toothed wheel of the clock device of FIG. 11, in which the positioning member corresponds to the variant illustrated in FIG. 15, during its rotation of a step;

Figure 17 shows, in top view, another variant of the positioning member of the clock device of Figure 1 1; FIG. 18 is a graphical representation of the moment of force measured on the toothed wheel of the device of FIG. 1 1 in which the positioning member corresponds to the variant illustrated in FIG. 17, during its rotation of a step;

- Figure 19a shows, in top view, another variant of the positioning member of the clock device of Figure 1 1;

- Figure 19b shows a portion of the positioning member shown in Figure 19a;

- Figures 20 to 24 respectively show, in top view, other variants of the positioning member of the clock device of Figure 1 1;

- Figure 25 shows, in perspective, another variant of the positioning member of the clock device of Figure 1 1;

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

The toothing 1 1 1 is typically a toothing with truncated teeth.

The positioning member 10 shown in Figure 1 is a pawl. It keeps the wheel 1 1 in position and allows its rotation only in the counter-clockwise direction, as indicated by the arrow B.

The wheel 11 is typically a toothed wheel carrying, driving or forming a display member, such as a disk, a pointer or a display crown. Alternatively, it may also be for example a column wheel, a barrel or ratchet ratchet, a winding wheel, or any type of gear wheel traditionally positioned by a pawl. It is typically other than an escape wheel. As illustrated in Figure 1, the positioning member 10 comprises an engagement member 15, a support 12 and a resilient member 14 connecting the engagement member 15 to the support 12. The elastic member 14 typically comprises a plurality of blades distributed resiliently, preferably uniformly around the support 12. These resilient blades 14 connect the support 12 to the engagement member 15 which is itself engaged in the toothing 1 1 1 of the wheel 1 1 to position.

The positioning member 10 shown in FIGS. 1 and 2 further comprises a serge 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 on a fixed or movable frame 100, on which is also mounted the wheel 1 1, said frame 100 typically comprising the plate carrying the clock mechanism. The serge 13 and the engagement element 15 integral with it are guided in rotation relative to the support 12 by the elastic blades 14.

In the illustrated example, 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 January 1.

The set of elastic blades 14 exerts a return moment tending to pivot the serge 13 around the support 12 in the counterclockwise direction of FIGS. 1 and 2.

The rotation of the serge 13 in the counterclockwise direction is limited by a stop 16, fixed on the frame 100, against which a protrusion 17 of the serge 13 is supported, when the device 1 is in the rest position, that is to say when the engagement element 15 is engaged, centrally, in a recess 1 1a of the toothing January 1, between two consecutive teeth of the wheel January 1, as shown in Figure 1. FIG. 2 represents, for the understanding of the invention, the isolated positioning member 10, that is to say free of any interaction with the abutment 16 or with the wheel 1 1.

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

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

In general, when the engagement element 15 is in the angular position in which Θ = x °, it is said that the positioning member 10 is armed with x °.

As can be seen in the curve Μ (θ) of FIG. 3, this elastic return moment follows an evolution in three phases:

for an angle Θ between 0 and a first value θι, the elastic return moment increases rapidly with the angular position Θ; - Beyond this first value Θ1, the positioning member 1 0 is in a substantially stable phase. Indeed, between this first value Θ1 and a second value Θ2, the elastic return moment is substantially constant with respect to the angular position Θ.

By "substantially constant moment" is meant a moment not varying by more than 10%, preferably 5%, more preferably 3%, it being understood that this percentage may be further decreased. More precisely, Mmin and Mmax respectively are the values of the minimum and maximum moments exerted in the positioning member 1 0 isolated over a given range [Θ1, Θ2] of angular positions of the engagement element 1 5 with respect to the support. 1 2, the moment exerted in this isolated positioning member 1 0 is substantially constant since the inequation "(Mmax-Mmin) / ((Mmax + Mmin) / 2) <0, 1" is verified, more precisely, since the inequality "(Mmax-Mmin) / ((Mmax + Mmin) / 2) <y%", with y = 1 0, preferably y = 5, more preferably y = 3, is satisfied. In this substantially stable phase, the elastic return moment exerted by the set of spring blades 14 in the isolated positioning member 1 0, however, locally reaches a maximum for an angular position Q _a , then decreases in the range of angular positions between the values Q _a and 0b, where 0a and 0b are between Θ1 and Θ2;

- Beyond the value Θ2, the moment of elastic return increases again until reaching a limit value Mnmite, for an angular displacement Θ = θ3. This Mnmite value depends on the properties of the material in which the positioning member 1 0 is made and corresponds to the maximum stress that this member 1 0 can undergo.

The isolated positioning member 1 0 having a curve Μ (θ) of the type of that shown in Figure 3 differs from conventional elastic structures. Its properties are based on a sinuous shape of its elastic blades 1 4 which deform to generate a moment of elastic return substantially constant (the curve Μ (θ) has a plateau between Θ1 and Θ2) over a predetermined range of angular positions of its engagement element 15 with respect to its support 12. Obtaining such elastic blades requires a specific and parameterized design . 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., 21 1 - IEEE International Conference on robotics and Automation Shanghai International Conference Center May 9-13, China.

The topological optimization referred to in the above article uses parametric polynomial curves such as Bezier curves to determine the geometric shape of the elastic strips 14.

The Bézier curves are defined, together with a series of m = (n + 1) control points (Qo, Q1, ... Qn), 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 Bezier 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 stress "(Mmax-Mmin) / ((Mmax + Mmin) / 2) <0.05". The inequation "(Mmax-Mmin) / ((Mmax + Mmin) / 2) <0.05" corresponds to a constancy of the elastic return moment of 5% over an angular range.

In general, the set of elastic blades 14 of the positioning member 10 of the device 1 is designed, in particular by its shape, to exert, in this member 10, a substantially constant elastic return moment (constancy of 5%) over a range of angular positions of the seam 13 and the engagement member 15 with respect to the support 12 by at least 10 °, preferably at least 15 °, more preferably at least 20 °. More specifically, the geometric shape of each of the elastic blades 14 of the positioning member 10 is defined by the set of points

where the B ¹ are the Bernstein polynomials given by the function fl. (t) = C ™ - ¹ ) ' _t i (_ tyn-ii _{with te [0 1 L}

^IJ i \ {r - \ - i) \ ^JLJ

and where the Qi are the control points Qo to Q _n . It corresponds to the graphical representation in an orthonormal coordinate system of the set of points defined by the pairs of coordinates (x; y) defined respectively by the functions x (t) and y (t), t G [0, 1], below :

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

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 decomposed into a succession of Bézier curves of order less than m, in which case the geometric shape of each of the elastic blades is a succession of Bezier curves.

Using this principle, the Applicant has designed a particular positioning member comprising four elastic blades evenly distributed around the support 12. The dimensions of this positioning member 10 are as follows:

Outside diameter of the serge: 12 mm Outside diameter of the support: 2 mm

Internal diameter of the serge: 10 mm

Height: 0, 12 mm

Thickness of the elastic blades: 24 pm

As part of this design, seven control points Qo, Qi, Q2, Cb, G, Q5, Û6 were used. The coordinates of these control points are shown in Table 1 below. Table 1: Coordinates of control points Qo to Qe.

With these seven control points it would have been possible to realize a Bezier curve of order seven. However, according to the principle indicated above, the Bézier curve has been decomposed into two segments, a first segment corresponding to a curve of Bezier of order 4 based on control points Qo to Q3 and a second segment corresponding to a Bezier curve of order 4 based on checkpoints Q3 to Û6.

By using the coordinates of the control points Q 0 to O 6 above in the above-mentioned functions x (t) and y (t), the applicant obtained the coordinates of the points defining the geometric shape of an elastic blade of the 10. A number of these pairs of coordinates are given in Table 2 below.

Table 2: Coordinates of points of passage of the optimized elastic blade.

The graph of FIG. 4 shows the geometry of the outer diameter of the support 12, the internal diameter of the serge 13 and one of the elastic strips 14 of the particular positioning member 10 that the Applicant has conceived, the geometry of said blade 14 being defined by a curve passing through the set of point coordinates defined in Table 2 above. This graph is made in an orthonormal frame. FIGS. 5a and 5b show 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 with respect to its support 12.

The simulation performed considers a positioning member 10 made of a cobalt, nickel and chromium-based alloy, more specifically 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, metal glass, plastic or CK101 (non-alloy structural steel) are also suitable. It is important to take into account the ratio between the elastic limit and the Young's modulus of the material to choose the material constituting the elastic blades 14.

It emerges from the analysis of the results presented in FIGS. 5a and 5b that a maximum and then decreasing local elastic return moment is obtained during a displacement of the engagement element 15 of the particular isolated positioning member 10 studied. relative to its support 12 an angular position Q _a = 17 ° at an angular position 0b = 28 °, ie over a range of 1 1.

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

On the range of angular positions [Q _a, Q b] on which the moment of force is decreasing, the stiffness of the single positioning member 10 is negative. The stiffness of the isolated positioning member 10 is zero at the point where the elastic return moment reaches a local maximum. In the present invention, is located within this range [Q _a, Q b] or at least partially within this range.

Within the device 1, the positioning member 10 is arranged so that, during the rotation of a pitch of the wheel 1 1 against the return action of the set of elastic blades 14, the element 'engagement 15 moves in a beach predetermined range of positions relative to the support 12, this range being included in the range of positions [θι, Θ2] associated with the positioning member 10 and comprising at least part of the range of positions [Q _a , Qb] in which the stiffness of the set of elastic blades 14 is zero or negative. Preferably said predetermined range is included in the range _[Qa, Qb] or constituted by the latter.

To obtain such an arrangement, the positioning member 10 is fixed by its support 12 to the frame 100 of the mechanism so that it is armed with Oarm degrees when the protuberance 17 bears against the abutment 16 and so this abutment 16 prevents the return of the engagement element 15 in the range of positions between θ = 0 and Q = Qam. Indeed, all of the resilient blades 14 exert an elastic return moment tending to pivot the serge 13 and the engagement element 15 that it carries around the support 12 in the direction of decreasing the angle Θ (counter-clockwise in Figure 1).

In addition, in the position in which the protuberance 17 of the positioning member 10 bears against the abutment 16, the engagement element 15 is positioned between two successive teeth of the toothing 1 1 1 of the wheel 1 1 to position now and the latter in position under the effect of the moment of return exerted by the set of elastic blades 14.

In addition, the angle Oarm, 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 toothing 1 1 1 of the wheel 1 1, are chosen so that, during the angular displacement of a pitch of the wheel 1 1, the engagement element 15 moves angularly relative to the support 12 in the range of positions [Θ1, Θ2] and at least partly in the range of positions [Qa, Qb]. Oarm is therefore between Θ1 and Θ2 and preferably about equal to Q _a .

The choice of the angle Oarm defines the lower limit of the predetermined range of positions in which the engagement element 15 moves during the rotation. one step of the wheel 1 1. 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 toothing 1 1 1 of the toothed wheel 1 1, define to them, the upper bound of this range of positions.

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

i. fixing the support 12 of the positioning member 10 at rest on the frame 100; ii. pre-arming the positioning member 10 by rotation of the serge 13 in the preferred direction of rotation A of an angle Θ = Oarm _;

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 Oarm; and

iv. positioning the wheel 1 1 so that, when the protuberance 17 carried by the serge 13 bears against the abutment 16, the engagement element 15 is positioned between two successive teeth of the teeth 1 1 1 of the wheel

1 1, pointing, preferably towards the center of the wheel 1 1.

It is clear to the person 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 a pitch of the toothed wheel 11 may be obtained by a different sequence of steps.

FIG. 6 shows the results of measurements of the moment of force taken up on the wheel 1 1 of the device 1 as a function of its angular displacement, during a rotation of an angle a corresponding to a pitch of the wheel 1 1 in the direction of arrow B.

For these measurements, the same toothed wheel 1 1, 71 has been positioned either with the positioning member 10 of the device 1 according to the first embodiment of the invention (curve ci), or with a jumper 70 using a spring 74 with traditional positive stiffness (curve co) as represented in FIG. 7. As illustrated in FIG. 7, the device 7 comprising a jumper 70 of the studied prior art (curve c 0) comprises an engagement element 75 engaged in the toothing 71 1 of a toothed wheel 71. This jumper 70 allows the rotation of the toothed wheel 71 in both directions (clockwise and counterclockwise respectively corresponding to the arrows G and F of Figure 7), however only the rotation in the counterclockwise direction (arrow F) was studied here .

With reference to FIG. 6, the angle α = 0 ° corresponds to the position in which the engagement element 1 5 of the positioning member 1 0 represented in FIG. 1 or, as the case may be, the 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 1 1, 71. The angle increases with the rotation of the wheel 1 1 (curve ci) or 71 (curve co) respectively in the direction of the arrow B (Figure 1) or the arrow F (Figure 7). In this example, in the position where a = 0 °, the positioning member 1 0 is pre-armed with 0arm = 1 7 °, the rotation of a pitch of the wheel 1 1 corresponds to an angle a = 1 8 °, and the maximum armature of the positioning member 1 0 is 25 °.

With reference to FIG. 6, the moment necessary to initiate the rotation of the wheel 1 1 or "start moment" is approximately identical in the device 1 using the positioning member 1 0 and in the device 7 using the traditional jumper 70 . It is about 0, 084 N.mm. The wheel 1 1 is thus also held in position by the pawl consisting of the positioning member 1 0 according to the first embodiment of the invention as the traditional jumper 70.

A notable difference is that the use of the traditional jumper (device 7, curve co) generates a peak of operation of 0, 1 35 N.mm which increases the energy consumption and may block the mechanism if the wheel 1 1 n is not able to provide a moment of force sufficient to overcome this peak.

Because of the properties of the positioning member 10 in the predetermined position range used, in particular, because of the stiffness at least zero or negative part of the positioning member 10 in this range, the moment necessary to turn the wheel 1 1 by one step in the case of the device 1 (curve ci) has, meanwhile, no peak operation . On the contrary, it decreases constantly until reaching a value of 0.037 N.mm approximately corresponding to the time required to turn the wheel 1 1 when the engagement element 15 is opposite the truncated portion 1 1 b of the toothing 1 1 1.

The watch device 1 comprising a wheel 1 1 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 a pitch of the wheel. position relative to a traditional jumper 70 using a spring 74 with positive stiffness for holding in the equivalent position.

Such a watch device 1 also has the advantage of being less sensitive to linear shocks than jumpers or ratchets according to the prior art. This is due to the good balancing of its positioning member 10. This decrease in sensitivity to linear shocks can reduce the value of the start moment while maintaining good support in case of linear shocks and thus reduce overall consumption of energy during a rotation of a pitch of the toothed wheel 1 1.

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

Alternatively, the positioning member 10 may comprise only one elastic blade 14. The serge 13 may also be interrupted and take the form of a circular arc, as shown in Figure 8. The very structure of the positioning member 10 involves the centering of the support 12 relative to its serge 13. However, it may comprise a centering device for reinforcing the centering of the support 12. Such a device typically comprises a rigid element of junction 18, on the one hand, secured integrally to at least one zone of the serge 13 and on the other hand, positioned free in rotation about an axis 19, said axis 19 being integral with the support 12 and centered on this support 12 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 FIG. 8 also comprises such a centering device.

In variants, the watch device 1 according to the first embodiment of the invention may comprise a positioning member of a shape different from that illustrated in FIGS. 1 and 2, it may typically comprise elastic blades of a shape different from that illustrated in FIG. Figure 4. It can in particular take a form as shown in Figure 9.

The positioning member 20 shown in FIG. 9 comprises a support

22 and a serge 23 connected by elastic blades 24, the serge 23 carrying an engagement member 25 intended to be engaged in the toothing of a toothed component to be positioned and held in this toothing under the effect of the moment of restoring exerted by all the elastic blades 24.

One way of obtaining such elastic blades 24 is in particular described 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 FIG. 11, a clock device 3 according to a second embodiment of the invention comprises a wheel 31 comprising a toothing 31 1, and a positioning member 30.

The positioning member 30 is here a jumper. It maintains in position the wheel 31 and allows its rotation in both directions, clockwise and anticlockwise, as indicated respectively by the arrows C and D in Figure 1 1. The wheel 31 is typically a toothed wheel carrying, driving or forming a display member such as a disk, a pointer or a display crown. Alternatively, it may also be for example a column wheel or any type of gear wheel traditionally positioned by a jumper. It is typically other than an escape wheel.

As illustrated in Figure 1 1, the positioning member 30 comprises a rigid element 33 movable 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 on a frame 300 on which is also mounted the wheel 31 and the rigid element 33 is movable relative to the support 32. The frame 300 can be fixed or movable and typically comprises the plate carrying the mechanism or movement watchmaker including the device 3.

The rigid element 33 is guided in translation by the elastic blades 34 and moves along a straight line (d) passing preferably through the center of the wheel 31. It comprises an engagement element 35 engaged in the toothing 31 1 of the wheel 31 to be positioned. In the illustrated example, 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 member 35 moves with the remainder of the rigid member 33 along the straight line (d) defined above.

In the example shown in Figure 1 1, the 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 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 represented by the arrow E in FIG.

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

The displacement 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.

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

With reference to FIG. 13, Δ is the position of the engagement element 35 of the positioning member 30 isolated along the straight line (d), Δ being equal to 0 when the engagement element 35 is as far as possible from the support 32 (in this position the flared preformed blades 34 are at rest) and increasing when the engagement element 35 approaches the support 32; FIG. 13 represents the evolution F (A) of the force exerted by the engagement element 35 towards the arrow E, this force being the resultant 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 hold the engagement member 35 in a given position. In general, when the engagement element 35 is in the position in which Δ = x mm, it is said that the positioning member 30 is armed with x mm.

As can be seen in the graph F (A) of FIG. 13, this force follows an evolution in several phases:

the starting point A = A _s i = 0, corresponds to a stable state of the positioning member 30. In fact, in this position, the force F (A _s i) is zero, that is, say that the engagement member 35 exerts no force;

for a position Δ between 0 and a first value Δι, the elastic return force increases linearly and rapidly with the position Δ;

when Δ reaches the first value Δι, the elastic return force reaches a maximum and then remains positive but starts to decrease linearly. Δ then reaches the position Δ2 in which the force is again zero. However, it is not strictly speaking a stable state but rather an unstable equilibrium;

- Beyond the position Δ2 the force becomes negative then continues to decrease linearly until the position Δ3 in which the force F (a) reaches a minimum. A negative force F (a) 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 Δ3 and at _S 2, the elastic return force remains negative but increases linearly and rapidly with the displacement Δ until it becomes zero for Δ = Δ ₅ 2. The point at _S 2 corresponds to a second Stable state of the positioning member 30. Indeed, in this position, the force F ( _S 2) is zero, that is to say that the engagement member 35 exerts no force.

The insulated positioning member 30 exhibiting an evolution of the force F (a) of the type shown in FIG. 13 differs from the conventional elastic structures. Its properties are based on the ability of its elastic blades 34 to work in buckling, which allows it to behave as a bistable. Obtaining elastic blades having these properties is within the reach of those skilled in the art.

The Applicant has devised a particular positioning member comprising a pair of parallel resilient blades 34. With reference to FIG. 12, the dimensions of this positioning member 30 are those indicated in table 1 below:

Table 1:

Figure 13 shows an analytical model representing the evolution of the force

F (A) of the particular positioning member 30 thus produced as a function of the position of its engagement member 35 along the straight line (d).

This model considers a monolithic 30 positioning member made of a cobalt based alloy, nickel and chromium, specifically Nivaflex ^® 45/18 but any suitable material may be used. For example materials such as silicon typically coated with silicon oxide, metallic glasses, mineral glasses, ceramic glasses, plastics or CK101 (non-alloy structural steel) are also suitable. However, it is conceivable to make a non-monolithic positioning device 30 several elements or parts, these elements may be made in identical materials or different from each other.

It is important to take into account the ratio 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 in FIG. 13 that a locally maximal and then a decreasing linear elastic return force is obtained during a displacement of the engagement element 35 of the particular isolated positioning member 30 studied from the position Δι "0.05 mm at position Δ2 = 0.4 mm.

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

In the range of positions [Δι, Δ2] on which the force is decreasing, the stiffness of the isolated positioning member 30 is negative. In the present invention it is placed in this range or at least partly in this range. Within the device 3, the positioning member 30 is thus 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 in a predetermined range of positions included in the range of positions [Δ1, Δ2] 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 gear 31 1 of the wheel 31 to position, now the latter in position under the effect of the restoring force exerted by the pair of resilient blades 34, the positioning member 30 being armed with a value to _am in this position .

The choice of the value to arm defines the lower bound of the predetermined range of positions in which the engagement member 35 moves during the rotation. one step of the wheel 31. The shape and the dimensions of the teeth of the toothing 31 1 and the angle between the inclined planes defining the engagement element 35 are chosen so that the maximum value Δ reached during the rotation of a pitch of the wheel 31 is less than or equal to Δ2.

When present, the stop 36 prevents the displacement of the engagement element 35 in the range of positions in which Δ is greater than Δ2. This is a security to prevent the positioning member 30 from swinging to the stable state corresponding to the position _S 2 of the engagement member 35 in case of shock or manipulation affecting the device 3 .

i. positioning the wheel 31 on the frame 300 so that it is free to rotate about an axis fixed in the frame 300;

ii. positioning the positioning member 30 so that its engagement member 35 is centrally engaged between two consecutive teeth of the toothing 31 1 and exert a force on the positioning member 30 until the element engagement 35 is in a position Δ = Aarm, that is to say pre-armed with a value Aarm between Δ1 and Δ2; and

iii. fix the support 32 on the frame 300 in this position.

It is clear to the person 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 a pitch of the wheel 31 can be obtained by a different sequence of steps.

FIG. 14 presents the results of measurements of the moment of force noted on the wheel 31 of the device 3 as a function of its angular position β, for a rotation of the wheel 31 with an angle β corresponding to a pitch in the direction of the arrow D of FIG.

For these measurements, the same wheel 31, 71 has been positioned either with the positioning member 30 of the device 3 according to the second embodiment of the invention (curve C2), or with the jumper 70 using a spring 74 with stiffness traditional positive (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 toothing 71 1 of a wheel 71. This jumper 70 allows the rotation of the wheel 71 in both directions (clockwise and counterclockwise), however, only the rotation in the counterclockwise direction (arrow F) has been studied here.

With reference to FIG. 14, the angle β = 0 corresponds to the position in which the engagement element 35 of the positioning member 30 shown in FIG. 1 1 or, as the case may be, the element of engagement 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 C2) or 71 (curve co) respectively in the direction of the arrow D (Figure 1 1) or the arrow F (Figure 7). In this example, in the position in which β = 0 the positioning member 30 is pre-armed with Aarm = 0.1 mm, the rotation of a pitch of the gear wheel 31 corresponds to a rotation of an angle β = 18 ° and the maximum armature of the positioning member 30 is A = 0.4mm.

With reference to FIG. 14, the moment necessary to initiate the rotation of the wheel 31 or "start moment" is approximately identical in the case of the use of the positioning member 30 (0.083 N.mm) and in the the case of the use of the jumper 70 using a spring 74 with conventional positive stiffness (0.084 N.mm). The wheel 31 is thus 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 (curve co) generates a peak of 0, 135 N.mm which increases the energy consumption.

Due to the properties of the positioning member 30 in the predetermined position range used, in particular because of the negative stiffness of the positioning member 30 in this range, the time required to turn the wheel 31 of a not in the case of the positioning member 30 (C2 curve) has, meanwhile, no peak operation. On the contrary, it decreases constantly until reaching a value of almost zero, corresponding to the time required to turn the wheel 31 when the engagement element 35 is opposite the truncated portion 31b of the toothing 31 1.

Once the truncated portion 31b has been passed, for an angle β approximately equal to 14 °, the moment necessary to turn 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.

Figure 14 shows that both the jumper according to the second embodiment of the invention shown in Figure 1 1 that the jumper 70 according to the prior art allow the repositioning of the toothed wheel 31, 71 to be positioned.

The watch device 3 comprising a wheel 31 and a positioning member 30 according to the second embodiment of the invention makes it possible to reduce the maximum instantaneous energy consumption required during the rotation of a pitch of the wheel to be positioned by compared to a traditional jumper 70 using a spring 74 to positive stiffness for holding in the equivalent position.

In addition, over almost the entire extent of the rotation of a pitch of the wheel 31, the energy consumption is lower in the case of the use of the positioning member 30 than in the case of the use a jumper 70 according to art prior. The watch device 3 studied thus makes it possible to reduce the overall energy consumption during a rotation of a 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 ratchets according to the prior art. This is due to the low weight of the moving parts of its positioning member 30 that are the elastic blades 34 and the engagement element 35. This low sensitivity to linear shocks can reduce the value of the start moment while retaining good support in case of linear shocks and thus further reduce the overall energy consumption during a rotation of a pitch of the gear 31.

The low height of the blades 34 also reduces 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 is a jumper, the rotation of the wheel 31 is allowed in both directions, namely, in the direction of the arrow D but also in the direction of the arrow C (Figure 1 1) and the curve representing the moment of force noted on the wheel 31 to be positioned according to its angular displacement in the direction opposite to that studied would be identical to the curve C2.

In variants, the watch device 3 according to the second embodiment of the invention may comprise a positioning member of a shape different from that illustrated in FIGS. 11 and 12. It may in particular take a shape as shown in FIG. , Figure 17, Figure 19a, Figure 20, Figure 21, Figure 22, Figure 23, Figure 24 or Figure 25. FIGS. 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 represented in FIGS. 15 and 17 during the rotation of a pitch of this wheel 31, as for Figure 14. Each of these figures also represents the curve co of Figure 14 for comparison.

The positioning member 40 shown in Fig. 15 differs from the positioning member 30 shown in Fig. 12 in that its engagement member 45 is truncated. This reduces the recoil of the engagement member 45 during the rotation of a pitch of the wheel 31 to be positioned. The elements 42, 43, 44 of the variant shown in FIG. 15 respectively correspond to the elements 32, 33, 34 of the variant represented in FIG. 12.

The positioning member 50 shown in Figure 17 differs from the positioning member 30 shown in Figure 12 in that it further has blades 59 working in bending. This improves 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 FIG. 17 respectively correspond to the elements 32, 33, 34, 35 of the variant represented in FIG. 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 respectively correspond to the elements 32, 33, 35 of the variant shown in Figure 12. The rigid element 93 may optionally be guided along the line (d) previously defined through a guiding 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 1 10 shown in FIG. 22 differs from the positioning member 90 represented in FIG. 21 in that its rigid element 1 13 and therefore its engagement element 1 15 interrupt the elastic blade 1 14 outside. its central portion, in this case approximately 3/8 of the length of said blade 1 14. The eccentricity of the rigid element 1 13 on the elastic blade 1 14 decreases the intensity of the force generated by the elastic member comprising this blade 1 14, however the elastic member maintains a negative stiffness over a predetermined range of positions of the engagement member 1 15 relative to the support 1 12.

The positioning member 120 shown in FIG. 23 is a variant of the intermediate positioning member between that represented in FIG. 12 and that represented in FIG. 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 respectively correspond to the elements 32, 33, 35 of the variant represented in FIG. 12.

The positioning member 130 shown in FIG. 24 differs from the positioning member 90 represented in FIG. 21 in that its elastic blade 134 comprises on either side of its rigid element 133, more precisely at the level of each junctions of its elastic blade 134 with the support 132, a hinge 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 retains a negative stiffness over a predetermined range of positions of the engagement member 135 relative to the 132. The elements 132, 133, 135 of the variant represented in FIG. respectively to the elements 92, 93, 95 of the variant shown in Figure 21. As a variant, such a positioning member 130 may comprise only one articulation 136, at a single junction of its elastic blade 134 with its support 132.

The positioning member 140 illustrated in FIG. 25 differs from the positioning member 90 represented in FIG. 21 in that it is not monolithic but obtained by assembling two pieces, each of these pieces defining a part 142a, 142b of the support 142, a half-blade 144a, 144b and a portion 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 modify 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 member 63 and in particular its engagement member 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 straight line (d) and a second plane forming an angle of 85 ° with the straight line (d). ), as shown in Figure 19b. The slope difference of the inclined planes makes it possible to have a low starting moment with the slope of 85 ° and thus a low energy consumption to initiate the rotation of the wheel 31. In addition, it limits the tangential effort on the jumper. The 60 ° slope allows a good repositioning of the wheel. The elements 62 and 64 of the variant represented in FIG. 19a respectively correspond to elements 92 and 94 of the variant represented in FIG.

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

As can be seen in FIGS. 14, 16 and 18, the various 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 position the wheel 31 to be positioned effectively with a reduction of the overall energy consumption during the rotation of a pitch of said wheel 31. These different variants have the same advantages as those associated with the variant presented in FIG. They allow in particular to eliminate the peak energy consumption occurring during the rotation of a pitch of the wheel 31 to be positioned with a conventional jumper using a spring with positive stiffness for holding in the equivalent position.

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, 1 10, 120, 130, 140 of the device 3 according to the second embodiment of the described invention can be combined.

It is furthermore very feasible to produce a watch device according to the invention comprising an elastic member of a structure different from those presented. Indeed, any elastic member having a negative or zero stiffness over at least one position range may be suitable. Whatever the embodiment of the invention, any device according to the invention considered at rest is associated with a force moment value for initiating 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 truncated toothed gear used in the various variants of the invention presented is preferred because it makes it possible to limit the recoil of the engagement member of the positioning member when it is rotating a step. However, it can easily be replaced by a conventional toothed wheel such as a star or an asymmetric toothed wheel. In all cases, the two inclined planes of the engagement element advantageously have two respective bearing points with the toothing of the wheel when the latter is in the rest position (a = 0 ° or β = 0 °).

The person skilled in the art may furthermore replace the toothed wheel to be positioned in 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 a display , with internal teeth.

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

The watch device according to any one of the presented variants has the advantage of eliminating the peak of energy consumption observed in the jumpers and ratchets conventionally used. It also makes it possible to reduce or even cancel the friction within the positioning member, especially 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 ratchets or jumpers which results in an increase in reliability. The device according to the invention is insensitive to linear shocks and advantageously allows a reduction in the overall energy consumption during the rotation of a pitch of its wheel.

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

Claims

Watchmaking 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); positioning (10; 20; 30; 40; 50; 60; 80; 90; 110; 120; 130; 140) comprising an engagement member (15; 25; 35; 45; 55; 65; 85; 125; 135; 145), a support (12; 22; 32; 42; 52; 62; 82; 92; 112; 122; 132; 142) and a resilient member (14; 24; 34; 44; 54; 64; 84; 94; 114; 124; 134; 144) pre-armored connecting the engagement member (15; 25; 35; 45; 55; 65; 85; 95; 115; support (12; 22; 32; 42; 52; 62; 82; 92; 112; 122; 132; 142), the toothed component (11; 31) being able to assume different consecutive rest positions; 15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) being arranged so that, in each of said rest positions, it is engaged between two consecutive teeth d the teeth (111; 311) of the toothed component (11; 31) and held between these two teeth by the resilient member (14; 24; 34; 44; 54; 64; 84; 94,114; 124; 134; 144) so that it maintains said toothed component (11; 31) in the rest position in question, and so that, when the tooth component (11; 31) is moved one step from a rest position to the next rest position the engagement member (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) is lifted 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 maintains the toothed component (11; ) in said next rest position, characterized in that the positioning member (10; 20; 30; 40; 50; 60; 80; 90; 110; 120; 130; 140) is arranged so that, during said displacement of a pitch of the toothed component (1 1; 31), the engagement member (15; 25; 35; 45; 55; 65; 85; 95; 115; 125; 135; 145) moves within a predetermined range of positions relative to the support (12; 22, 32, 42;

52; 62; 82; 92; 1 12; 122; 132; 142), the stiffness of the resilient member (14; 24; 34; 44; 54; 64; 84; 94; 1,14; 124; 134; 144) being zero or negative in at least a portion of the predetermined range.

Watchmaking device (1; 3) according to Claim 1, characterized in that the stiffness of the elastic member (14; 24; 34; 44; 54; 64; 84; 94; 114; 134; 134; 144) is zero or negative in substantially the entire predetermined range.

Watch device (1; 3) according to claim 1 or 2, characterized in that the stiffness of the elastic member (14; 24; 34; 44; 54; 64; 84;

94; 1 14; 124; 134; 144) is negative in substantially the entire predetermined range.

Watchmaking device (1; 3) according to one of claims 1 to 3, characterized in that said elastic member comprises at least one elastic blade (14; 24; 34; 44; 54; 64; 84; 94; 124; 134; 144) connecting the engagement member (15; 25; 35; 45; 55; 65; 85;

95; 1 15; 125; 135; 145) to the support (12; 22; 32; 42; 52; 62; 82; 92; 12; 122; 132; 142).

5. Watch device (1; 3) according to one of claims 1 to 4, characterized in that the engagement element (15; 25) is guided by rotation relative to the support (12; 22) by the elastic member (14; 24).

Watch device (1) according to claim 5, characterized in that the elastic member (14; 24) is designed to exert a substantially constant elastic return moment over a range of angular positions of the engagement member (15; 25) relative to the support (12; 22) by at least 10 °, preferably at least 15 °, preferably at least 20 °, said predetermined range being at least partly in this range.

Watch device (1) according to claim 5 or 6, characterized in that the positioning member (10; 20) further comprises a serge (13; 23) connected to the support (12; 22) by the elastic member ( 14; 24) and carrying the engagement member (15; 25).

Watch device (1) according to claim 7, characterized in that the serge (13; 23) is in the shape of an arc of a circle.

Watch device (1) according to claim 7 or 8, characterized in that it comprises at least one device (18) for centering the support (12; 22) with respect to the serge (13; 23).

Watch device (1) according to one of claims 7 to 9, characterized in that it further comprises a stop (16), typically fixed on a frame (100) on which is fixed the support (12; 22), the serge (13; 23) being arranged to cooperate with said stop (16) to pre-arm the elastic member (14; 24). Watch device (1) according to one of claims 5 to 10, when claim 5 depends on claim 4, characterized in that the or each of the resilient blades (14; 24) is sinuous.

Watchmaking device (1) according to one of claims 5 to 1 1, when claim 5 depends on claim 4, characterized in that the geometric shape of the or each elastic blade (14; 24) is a Bezier curve or a succession of Bezier curves.

Watchmaking device (3) according to claim 4, characterized in that the positioning member (30; 40; 50; 60; 80; 90; 110; 120; 130; 140) comprises a rigid element (33; 43; 53; 63; 83; 93; 1 13; 123; 133; 143) movable defining the engagement member (35; 45; 55; 65; 85; 95; 115; 125; 135; 145); said at least one resilient blade (34; 44; 54; 64; 84; 94; 1,14; 124; 134; 144) connects the rigid member (33; 43; 53; 63; 83; 93; 123; 133; 143) to the support (32; 42; 52; 62; 82; 92; 12; 122; 132; 142) and is arranged to work in buckling mode.

Watchmaking device (3) according to claim 13, characterized in that said at least one resilient blade comprises at least one preformed resilient flamed blade (34; 44; 54; 64; 84; 94; 114; 124; 134) or preformed in V.

Watchmaking device (3) according to claim 13 or 14, characterized in that the positioning member (50) further comprises at least one blade (59) arranged to work in flexion to improve the repositioning of the toothed component (31) by said positioning member (50).

16. Watchmaking device (3) according to one of claims 13 to 15, characterized in that said rigid element (33; 43; 53; 63; 83; 93) is movable along a straight line (d).

17. Watch device (3) according to claim 16, characterized in that the assembly comprising the elastic blade (s) (34; 44; 54; 94) and the rigid element (33; 43; 53; 93) is symmetrical with respect to said straight line (d).

Watch device (1; 3) according to one of the preceding claims, characterized 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 towards the toothing (1 1 1, 31 1).

19. Clock device (1; 3) according to one of the preceding claims, characterized in that said toothing (1 1 1; 31 1) comprises truncated teeth.

20. Watch device (1; 3) according to one of the preceding claims, characterized in that said toothed component is a wheel (1 1; 31). 21. Watchmaking device (1; 3) according to one of the preceding claims, characterized in that said positioning member (10; 20; 30; 40; 50; 60; 80; 90; 110; 120; 130) is monolithic.

22. Timepiece comprising a watch device (1; 3) according to one of the preceding claims.