FR3066625A1 - MECHANICAL WATCHMAKING MOVEMENT WITH EXTENDED MARKET RESERVE - Google Patents

Abstract

The invention relates to a mechanical clockwork (1) comprising - a barrel spring (3) armed by a winder (2); - a first center wheel (4) meshing with the barrel spring (3); an inverter (12); According to the invention, the mechanical clockwork movement (1) comprises a mechanical assembly (II) intended to increase the power reserve of the mainspring (3). The mechanical assembly (II) being installed between the first center wheel (4) and the inverter (12), and comprises: - a second dividing wheel (5); a locking member (13) for rotating the second dividing wheel (5); - a mechanical turning member (6); - A third wheel (7) rotating about a threaded shaft (8) movable in translation in a first direction (L1) perpendicular to a plane of the third wheel (7); - a return means (9) bearing on the threaded shaft (8); a fourth inversion wheel (11) driven by the third wheel (7) and coupled to the inverter (12).

Description

POWER RESERVE MECHANICAL WATCHMAKING

EXTENDED

The invention relates to a mechanical watch movement with an extended power reserve.

The operation of a mechanical watch is exclusively ensured by mechanical components (forming the train and the time display system) cooperating with each other. The energy source necessary for these movements is provided by a spiral spring wound in a barrel, otherwise called barrel spring. This spring is compressed or armed by means of a winder and it releases energy to the cogs and other watch systems by relaxing.

The power reserve of a watch is the time necessary for the barrel spring to fully relax. The power reserve of a watch is one of the important criteria in the choice of purchase of a user, especially when it is a watch with manual winding. The more the power reserve, the less the need to wind the watch. An extended power reserve watch therefore improves user comfort. For this reason, watch manufacturers are seeking to increase the power reserve in order to meet this need.

One of the solutions for increasing the power reserve is to superimpose several barrel springs coaxially. However, such a stacked spring system is expensive and difficult to implement. In addition, the operation of this system is not reliable over time.

Thus, an objective of the invention is to provide a mechanical watch movement with an extended power reserve while remaining reliable and simple to implement.

To this end, the invention proposes a mechanical clockwork movement comprising a barrel spring armed with a winder;

a first center wheel meshing with the barrel spring;

an inverter.

According to the invention, the movement comprises a mechanical assembly intended to increase the power reserve of the barrel spring. The mechanical assembly is installed between the first center wheel and the reverser, and it includes:

a second dividing wheel meshing on the one hand with the first center wheel and on the other hand with a pinion of a mechanical turning member; said second dividing wheel comprising an axis of rotation parallel to a referential direction;

a member for blocking the rotation of the second dividing wheel; the mechanical turning member being connected to a third wheel; the third wheel rotating around a threaded shaft movable in translation in a first direction perpendicular to a plane of the third wheel between a start of race position in which the first direction is parallel to the referential direction and the threaded shaft is located the farthest from the blocking member;

an end position in which the first direction is parallel to the referential direction and the threaded shaft is in contact with the locking member;

a return means being supported on the threaded shaft between the start of travel position and the end of travel position of said threaded shaft; and a fourth reversing wheel driven by the third wheel and coupled to the reverser.

Thanks to the mechanical assembly, the power reserve of the barrel spring is significantly increased. Indeed, during each translational movement of the threaded shaft, the third wheel rotates around the shaft while the second dividing wheel is locked in rotation. At the end of travel of the threaded shaft, it is in contact with the locking member to deactivate it, that is to say to put the locking member in a state in which it no longer prevents the second wheel to spin. The second wheel, by turning, drives the pinion of the turning member in rotation. The third wheel and the threaded shaft are thus returned thanks to the turning member until the rotation of the second wheel is blocked again. The threaded shaft can then move again perpendicular to the plane of the third wheel and cause it to rotate. A new movement cycle begins again.

Thus, the third wheel can perform a number of turns greater than that of the second wheel for the same period of time. In other words, there is a reduction in the number of turns at the exit of the mechanical assembly. For example, for an X number of turns of the second dividing wheel, indirectly meshing with the barrel spring, the third wheel performs a multiplied number of X turns which will be transmitted to the cogs located after the reverser.

In other words, for the same amount of energy of the barrel spring, the movement according to the invention makes the clockwork of the watch work more compared to a conventional watch.

According to a characteristic of the invention, the third wheel performs a number p of revolutions per length of the threaded shaft; p belonging to a set of positive rational numbers and p being greater than or equal to 1. Thus, between each reversal, the third wheel performs a number p of turns. The greater this number p, the higher the reduction ratio as well as the power reserve.

According to another characteristic of the invention, the second dividing wheel comprises a number N of angularly regularly distributed holes on the periphery of said second wheel; N belonging to a set of positive integers. Furthermore, the member for blocking the rotation of the second dividing wheel comprises a spring carrying a pin designed to be engaged in one of the N holes of the second dividing wheel; said spring having a rest position in which the pin is engaged in one of the N holes and a deformed position in which the pin is disengaged from the N holes. Thus, when the pin is engaged in a hole in the second division wheel, the latter is locked in rotation. The force of the barrel spring transmitted to the first center wheel and to the second dividing wheel is stopped by the locking member. This is deactivated only after contact with the threaded shaft, which disengages the pin from the hole in the second division wheel allowing it to turn to the next hole.

Advantageously, the number N of holes in the second dividing wheel is greater than 2. For example, N may be four in number.

In this case, if the third wheel makes two turns between each turn, for a complete turn of the second division wheel, the third wheel makes eight full turns. Thus, we obtain a reduction ratio of eight.

According to a characteristic of the invention, the second dividing wheel comprises N parts, each of which is located between two adjacent holes. Each part has a number n of teeth corresponding to those located around a half-circumference of the pinion of the mechanical turning member. Thus, the third wheel, being connected to the arm and to the pinion of the turning member, is turned 180 ° when the second dividing wheel makes 1 / Nth of a turn.

According to another characteristic of the invention, the second dividing wheel comprises a guide groove connecting two adjacent holes. In this way, the spring pin is engaged in the guide groove going from one hole to another. The guide groove avoids the deviation of the pin out of the desired path.

According to a characteristic of the invention, at least one of the return means and the spring of the locking member is of the leaf spring type. Such a spring is light and compact, which is appreciated in a mechanical watch movement.

According to a characteristic of the invention, the threaded shaft comprises a helical groove extended at each of its two ends by a rectilinear groove parallel to an axis of the threaded shaft.

For example, the third wheel includes rolling elements engaged in the groove of the threaded shaft. Thus, the engagement of the rolling elements of the third wheel in the helical groove makes it possible to transform the translational movement of the threaded shaft into the rotational movement of the third wheel. In addition, when the rolling elements are engaged in the rectilinear groove, located at each end of the longitudinal groove, the threaded shaft moves rapidly in translation until contact with the blocking member to disengage the pin from a hole of the second wheel.

Optionally, the mechanical watch movement includes means for holding the shaft in an upright position relative to the third wheel.

According to a characteristic of the invention, the movement comprises a means for guiding the threaded shaft during the reversal thereof. By way of example, the means for guiding the threaded shaft may be a blade curved in the shape of an arc of a circle.

Optionally, the return means comprises a means for guiding the threaded shaft.

According to another characteristic of the invention, the third wheel comprises a spherical toothing. In this case, the third wheel comprises a multitude of balls distributed regularly at the periphery of said wheel. These balls can be made of ceramic, which facilitates the transmission of the rotational movement between the third wheel and the fourth reversing wheel.

The invention also relates to a mechanical watch comprising a clockwork movement produced according to one of the characteristics presented above.

Other innovative characteristics and advantages will emerge from the description below, provided for information and in no way limitative, with reference to the appended drawings, in which:

Figure 1 shows a perspective view of a mechanical clockwork movement according to the invention, partially closed by an upper box;

2 shows a perspective view of part of the clockwork movement of Figure 1, mounted on a lower base;

Figure 3 shows the same view as Figure 1 without the upper box;

Figure 4 shows a perspective view and a detail view referenced IV in Figure 3;

FIG. 5 represents a perspective view and a detailed view referenced V in FIG. 4;

Figure 6 shows a perspective view of the mechanical clockwork movement of Figure 1 from another angle;

Figure 7 shows a schematic view of a threaded shaft and a third spherical gear forming part of the mechanical clockwork movement of Figure 1;

FIG. 8 represents a perspective view and a bottom view of the mechanical clockwork movement of FIG. 1, in particular at the level of the third spherical gear;

FIGS. 9 to 12 schematically represent stages of operation of the mechanical clockwork movement of FIG. 1.

In FIGS. 1 and 2, a mechanical clockwork movement 1, hereinafter called movement 1, is mounted in a circular trunk 15. The trunk 15 consists of a lower base 16 and an upper case 17. In the example illustrated, the lower base 16 is a disc comprising openings 161 opening out, one at the center and housings 162 for elements of the train. The upper housing 17 is composed of circular arcs 171, the assembly of which forms a ring of the same diameter as that of the lower base 16. Each circular arc 171 comprises housings (not visible in the figures) positioned opposite the housings 162 corresponding to the lower base 16 once it and the upper housing are assembled.

In the following description and claims, the terms “horizontal”, “vertical” are defined with respect to the orientation of the movement 1 once it is mounted in a watch frame as illustrated in the figure. 1. Specifically, the horizontal plane is a plane H passing through the lower base 16 or through the upper housing 17, as illustrated in FIG. 1. The horizontal belongs to this horizontal plane H. The vertical direction or the vertical is an axis Z perpendicular to the horizontal plane H. The terms "above", "below" or "lower", "upper" are defined with respect to the vertical direction Z. The vertical direction Z is also called the referential direction Z. Furthermore , the terms “before”, “after”, “upstream” or “downstream” refer to the direction of force distribution in the movement 1 starting from a barrel spring 3.

In Figures 2 and 3, the upper housing 17 is hidden to show the movement 1 according to the invention. This movement 1 is based on a first part I comprising a winder 2, a barrel spring 3, a first center wheel 4. The winder 2, thanks to a gear assembly (not illustrated in the figures), can reset the barrel spring 3. On the side of the barrel spring 3, it comprises a toothing 31 which meshes with a first pinion 41 of the first center wheel 4, hereinafter called in short the first wheel 4. The first pinion 41 is fitted in a rotation shaft 43 of the first wheel 4.

The first wheel 4 also comprises a first toothing 42 meshing with a second pinion 51 of a second part of the movement 1.

The second part of the movement is a mechanical assembly II intended to increase the power reserve of the barrel spring 3. It consists of a second division wheel 5, a mechanical turning member 6, a third wheel 7, a threaded shaft 8, a return means 9, a fourth reversing wheel 11, and a blocking member 13 for rotation of the second dividing wheel 5.

Figures 3 to 12 illustrate in more detail the parts of the second part II of the movement and the structural connection between them.

The second division wheel 5, hereinafter called the second wheel 5, is rotated by the first wheel 4 through the second pinion 51 meshing with the first teeth 42. The second division wheel rotates about an axis of rotation Xi which is parallel to the vertical direction Z.

In this example, the second wheel 5 comprises a set of four through holes 53 which are evenly distributed on a virtual circle C whose center is on the axis of rotation of the second wheel 5 and whose diameter is slightly less than that of the second wheel 5. In other words, the four holes 53 are distributed angularly regularly on the second wheel 5 and located close to the periphery thereof. Each hole 53 is designed to receive a pin 133 of a blocking member 13 which will be detailed later in the description. Optionally, a guide groove (not shown) in the form of a circular arc connects two adjacent holes.

The second wheel 5 further comprises a second toothing 52 standing vertically on its upper face 54. The second toothing 52 cooperates with a third pinion 61 of the mechanical turning member 6. In the following document, the third pinion 61 of the the mechanical turning member 6 will be called the pinion 61. The mechanical turning member 6 is hereinafter called the turning member 6.

The pinion 61 rotates around a rotation shaft 62 parallel to the horizontal. The rotation shaft 62 is held integral with the turning member 6 by means of jumpers 63. At an end opposite to that carrying the third pinion 61, the rotation shaft 62 is connected to a disc 64, which is secured with an arm 65. The disc 64 is mounted to rotate freely in an opening 661 made on a panel 66 arranged vertically. As illustrated in FIG. 6, said panel 66 is screwed onto the turning member 6.

First rolling elements 662, here balls, are installed between the disc 64 and the opening 661 of the panel in order to reduce the friction between these elements.

The arm 65 is connected to a support disc 67 which is parallel to the horizontal. The support disc 67 includes an orifice 671 passing through it at the center. A third wheel 7 is mounted coaxially and free to rotate relative to the support disc 67.

In the example illustrated, the third wheel 7 comprises a circular plate 72 with a hollow cylinder 73 in the center. The circular plate 72 and the hollow cylinder 73 are here made in one piece.

The circular plate 72 of the third wheel 7 comprises cylindrical housings 721 distributed regularly at the peripheral level of said plate 7. These cylindrical housings 721 are arranged in the plane of the circular plate 72. Each housing 721 receives a trunk 723 carrying a ball 722 , preferably ceramic. Thus, the third wheel 7 comprises a toothing 71 consisting of a set of balls, unlike a conventional wheel or pinion with teeth, hence its name "third wheel 7 with spherical toothing". In an exemplary embodiment, the diameter of the circular plate 72 is approximately 12.2 mm and that of each of these balls 722 is approximately 0.8 mm.

The hollow cylinder 73 of the third wheel 7 is fitted into the orifice 671 of the support disc 67. The hollow cylinder 73 and the support disc 67 include channels 732 and 672 located in radial correspondence so as to form a housing for a or several second rolling elements 75, here the balls.

A threaded shaft 8 passes through the hollow cylinder 73 of the third wheel 7. The threaded shaft 8 is movable in translation in a first direction Li perpendicular to a plane Pi of the third wheel 7. By definition, the plane of a wheel is a plane perpendicular to the axis of rotation of this wheel.

The threaded shaft 8 includes a helical groove 81 which is extended at its two ends by a rectilinear groove 82 parallel to an axis 83 of the shaft. The third wheel 7 comprises third rolling elements 731 which are engaged in the grooves of the shaft. In this example, the third rolling elements 731 are balls embedded in the hollow cylinder 73 of the third wheel 7. Of course, these balls can be installed elsewhere as long as they make it possible to transmit the vertical translation of the shaft 8 in rotation of the third wheel 7.

In FIG. 7, a retaining collar 10 is fixed to one end of the cylinder 73. The retaining collar 10 keeps the threaded shaft 8 in an upright position relative to the third wheel 7. The retaining collar 72 can be produced in ruby.

A fourth reversing wheel 11, hereinafter called the fourth wheel 11, is installed following the third wheel 7. This fourth wheel 11 has a toothing 111 of shape complementary to the balls 722 of the third wheel 7. The fourth wheel 11 is coupled with an inverter 12 which makes it possible to rotate the wheels located after it in a single direction, regardless of the direction of rotation of the part located upstream of the inverter. In the example illustrated, the fourth wheel 11 is followed by a gear train composed of a second wheel, then an escape wheel, then an anchor, and finally a balance wheel.

In FIGS. 9 to 12, a blocking member 13 for the rotation of the second wheel 5 is shown. The blocking member 13 comprises a spring 130 of the leaf spring type which is fixed at one end 131 and free at the end. 'other 132. In this example, the spring 130 is located at a level lower than that of the movement 1 relative to the vertical. The free end 132 of the spring 13 is positioned opposite the threaded shaft 8.

In addition, the spring 13 carries a pin 133 which is located opposite the virtual circle C of the second wheel 5. Thus, it can be engaged either in one of the holes 53 of the second wheel 5 or in the channel between two holes. When the pin 133 is engaged in a hole 53 of the second wheel 5, it prevents the rotation of the latter.

In a relaxed or at rest state, the spring 13 extends parallel to a plane P ₂ of the second wheel 5 while the pin 133 is engaged in a hole 53 of the second wheel 5, as illustrated in FIG. 9. In an elastically deformed state, the spring 13 flexes downwards and brings the pin 133 out of the hole 53, as illustrated in FIG. 10.

The operating principle of the mechanical clockwork movement according to the invention will be described below with the aid of the illustration of FIGS. 9 to 12.

Like any mechanical watch movement, movement 1 is wound up using the winder 2 which causes the barrel spring to compress 3. The rebound of the barrel spring 3 rotates the first wheel 4 by means of the first pinion 41.

The first wheel 4 in turn turns the second wheel 5. However, during a first step of operation of the movement as illustrated in FIG. 9, the second wheel 5 is prevented from turning by the engagement of the pin 133 in a first hole 531 of this second wheel 5.

At the start of the first step, the threaded shaft 8 is in a start-of-travel position in which the first direction Li of the threaded shaft 8 is parallel to the vertical direction Z. In other words, in this example, the axis 83 of the threaded shaft 8 is parallel to the vertical axis Z at the start of travel of said shaft 8. In this position, the threaded shaft 8 remains the farthest from the spring 130.

A return means 9 exerts a pressing force on the threaded shaft 8 from the start of the race. The threaded shaft 8 descends from the top to the bottom. The return means 9, in this example, is tensioned at the start of the movement of the threaded shaft 8. The more the threaded shaft 8 descends, the more relaxed the return means 9.

By way of example, the return means 9 can be a leaf spring in the shape of an arc of a circle. The return means 9 is fixed at one end and free at the other. The free end of the return means is supported on the threaded shaft 8 from the start of the race.

In an exemplary embodiment, the circular plate 72 of the third wheel has a smaller diameter than the length of the trunks 723 carrying balls 722. This configuration makes it possible to arrange a space between two adjacent trunks 723 which is sufficiently wide, in which can be introduces the return means 9 during the inversion phase of the third wheel 7.

The translational movement of the threaded shaft 8 induces the rotation of the third wheel 7 around this shaft 8 in a first direction FI, thanks to the engagement of the third rolling elements 731 of the third wheel 7 in the helical groove 81 of the 'tree.

During the second stage of operation of movement 1, the third rolling elements 731 arrive in the rectilinear groove 82 of the threaded shaft 8 as illustrated in FIG. 10 A. This causes the threaded shaft to descend rapidly towards the spring 130.

At the end of this second step, the threaded shaft 8 reaches an end of travel position in which the first direction Li remains parallel to the direction Z and in which the threaded shaft 8 is in contact with the free end 132 of the spring 13 (see Figure 10). This contact causes the spring 13 to flex downwards and at the same time disengage the pin 133 from the first hole 531 of the second wheel 53. Note that the return means 9 is no longer supported on the threaded shaft 8 when that -this comes at the end of the race.

Consequently, as illustrated in FIG. 11, the second wheel 5 is free to rotate and driven by the first wheel 4 until the pin 133 engages in a second hole 532 consecutive to the first hole 531. During the rotation of the second wheel 5, the pin 133 is engaged in the guide groove. In parallel, the second wheel 5 rotates the pinion 61 of the turning member 6. Given the connection between the pinion 61 and the arm 65, the rotation of the pinion 61 makes the arm 65 pivot around an axis parallel to the horizontal. The pivoting of the arm 65 causes the third wheel 7 and the threaded shaft 8 to turn over. In the example illustrated, the rotation of the second wheel 5 is a quarter turn, that is to say the distance between two consecutive holes , corresponding to a half-turn of the pinion 61 and a 180 ° reversal of the third wheel 7.

A guide means 18 is arranged near the free end 132 of the spring 130 so as to guide the threaded shaft 8 during the inversion phase. The two ends of the shaft each include a U-shaped profile 84 and 85 cooperating with the guide means 18 during the inversion phase. In the example illustrated, the guide means 18 and the return means 9 are made in one piece.

The reversal of the third wheel 7 enables the return means 9 to be reset. The latter again exerts a pressing force on the threaded shaft 8 which returns to its position at the start of the stroke.

The pin 133 is again engaged in one of the holes of the second wheel, here the second hole 532 adjacent to the first hole 531. The second wheel 5 is again locked in rotation. In parallel, the threaded shaft 8, under the support of the return means 9, descends vertically towards the spring 130 and rotates the third wheel 7 in a second direction F2 opposite to the first direction F1 indicated in FIG. 9.

The movement repeats the same steps until the barrel spring 3 is fully relaxed.

It should be noted that rotation of the second wheel 5 and that of the third wheel 7 are independent. The energy of the barrel spring 3 is used as an inversion force of the third wheel 7.

According to an example of calculation, thanks to the movement according to the invention, the power reserve of the barrel spring 3 is significantly increased.

In one example, the barrel spring 3 is completely relaxed after 48 hours of operation and the second wheel 5 rotates in 12 hours. In other words, for four turns of the second wheel 5, the barrel spring 3 is completely relaxed.

On the side of the third wheel 7, the length of the threaded shaft 8 and the pitch of the helical groove 82 are dimensioned so as to allow the third wheel 7 to make two turns for each length of the threaded shaft 8. Each turn of the third wheel 7 corresponds to 12 hours. Thus, the rotation of the third wheel 7 between each reversal corresponds to a length of 24 hours. For example, the threaded shaft 8 can be 20 mm long and 1.90 mm in diameter while the helical groove 82 is inclined at an angle a of 130 ° relative to the horizontal.

The value of the angle a can be in the range between 130 ° and 160 °.

Here, the second wheel 5 has four holes. The rotation of the second wheel 5 by a quarter turn makes it possible to turn the third wheel 7 and the threaded shaft 8 by 180 °. The second wheel 5 is locked in rotation by the engagement of the pin 133 of the spring 13 in a hole 53 of the second wheel 5. During each blocking, the third wheel 7 makes two turns. Consequently, for a complete revolution of the second wheel 5, the third wheel 7 makes eight turns. However, it is known that each revolution of the third wheel 7 corresponds to 12 hours of operation. Thus, for a complete revolution of the second wheel 5, the third wheel 7 spins for a time of 12 h x 8, or 96 hours.

However, according to the context given above, one revolution of the second wheel 5 corresponds to a quarter of the life of the barrel spring.

Consequently, for 48 hours of operation of the barrel spring, the third wheel operates the gear train for 96 h x 4, or 384 hours.

In the end, thanks to the movement according to the invention, one obtains sixteen days of operation of the watch with a barrel of 48 hours of life time. We can also say that the power reserve is increased by 8 times.

This factor can be further increased by modifying different movement parameters such as the number of holes in the second wheel, number of turns made by the third wheel for each length of the threaded shaft, etc.

For example, in another configuration of movement 1, the number of 5 holes of the second wheel is increased to six while the rest of the movement is identical to the previous configuration. In this case, 576 hours of operation of movement 1 are obtained, or twelve times more power reserve.

Claims (12)

1. Mechanical clockwork movement (1) comprising a barrel spring (3) armed by a winder (2); a first center wheel (4) meshing with the barrel spring (3); an inverter (12); characterized in that said movement (1) comprises a mechanical assembly (II) intended to increase the power reserve of the barrel spring (3), the mechanical assembly (II) being installed between the first center wheel (4) and the reverser (12), and comprising: a second dividing wheel (5) meshing on the one hand with the first center wheel (4) and on the other hand with a pinion (61) of a mechanical turning member (6); said second dividing wheel (5) comprising an axis of rotation (Χ-ι) parallel to a referential direction (Z); a blocking member (13) for rotation of the second dividing wheel (5); the mechanical turning member (6) being connected to a third wheel (7); the third wheel (7) rotating around a threaded shaft (8) movable in translation in a first direction (L1) perpendicular to a plane of the third wheel (7) between a start of race position in which the first direction ( L1) is parallel to the referential direction (Z) and the threaded shaft (8) is located furthest from the locking member (13); an end position in which the first direction (L1) is parallel to the referential direction (Z) and the threaded shaft (8) is in contact with the locking member (13); a return means (9) being supported on the threaded shaft (8) between the start of travel position and the end position of said threaded shaft (8); and a fourth reversing wheel (11) driven by the third wheel (7) and coupled to the reverser (12). 2. Mechanical clockwork movement (1) according to claim 1 characterized in that the third wheel (7) performs a number p of revolutions per length of the threaded shaft (8); p belonging to a set of positive rational numbers and p being greater than or equal to 1. 3. Mechanical clockwork movement (1) according to claim 1 or according to claim 2 characterized in that the second dividing wheel (5) comprises a number N of holes (53) angularly regularly distributed at the periphery of said second wheel (5); N belonging to a set of positive integers; and the blocking member (13) of the rotation of the second dividing wheel (5) comprises a spring (130) carrying a pin (133) designed to be engaged in one of the N holes (53) of the second dividing wheel division (5); said spring having a rest position in which the pin (133) is engaged in one of the N holes (53) and a deformed position in which the pin (133) is disengaged from the N holes (53). 4. Mechanical clockwork movement (1) according to claim 3 characterized in that the number N of holes (53) of the second division wheel (5) is greater than 2. 5. Mechanical clockwork movement (1) according to one of claims 3 or 4 characterized in that the second dividing wheel (5) comprises N parts, each of which is located between two adjacent holes (53, 531, 532), each part comprising a number n of teeth corresponding to those located around a semi-circumference of the pinion (61) of the mechanical turning member (6). 6. Mechanical clockwork movement (1) one of claims 3 to 5 characterized in that the second dividing wheel (5) comprises a guide groove connecting two adjacent holes. 7. Mechanical clockwork movement (1) according to one of claims 3 to 6 characterized in that at least one of the return means (9) and the spring (130) is of the leaf spring type. 8. Mechanical clockwork movement (1) according to one of the claims 5 previous characterized in that the threaded shaft (8) comprises a helical groove (81) extended at each of its two ends by a rectilinear groove (82) parallel to an axis (83) of the threaded shaft (8 ). 9. Mechanical clockwork movement (1) according to one of the preceding claims characterized in that it comprises a guide means (18) of the shaft 10 threaded (8) during the inversion of said threaded shaft (8). 10. Mechanical clockwork movement (1) according to claim 9 characterized in that the return means (9) comprises a guide means (18) of the threaded shaft (8). 11. Mechanical clockwork movement (1) according to one of the claims 15 above characterized in that the third wheel (7) comprises a spherical toothing (71). 12. Mechanical watch characterized in that it comprises a clockwork movement (1) according to one of claims 1 to 11.