Movement for a timepiece and timepiece comprising such a movement

Abstract

The present invention relates to a movement for a timepiece comprising a counting assembly (10) comprising a first energy source (14) and a gear train (16) kinematically linked to at least one time indicator; and a control assembly (11) comprising a control member (35). This timepiece movement is characterised in that it further comprises a blocking member (56) for said gear train (16); a mobile unit (33) supporting said control assembly (11); a guide assembly (12) for said mobile unit (33), comprising at least one rail (30, 32); a drive mechanism for said mobile unit (33) which is arranged to move this mobile unit along the guide assembly (12); and a release mechanism (13) for said blocking member (56). The invention also relates to a timepiece containing such a movement.

Description

TECHNICAL FIELD

[0001] The present invention relates to the field of mechanical watchmaking. It relates more particularly to a watch movement comprising a mobile regulating mechanism.

[0002] More specifically, this invention relates to a movement for a timepiece comprising a counting assembly comprising a first energy source and a gear train kinematically linked to at least one time indicator, this counting assembly forming part of a first kinematic chain; and a regulation assembly comprising a regulation member and forming part of a second kinematic chain distinct from said first kinematic chain.

[0003] The invention also relates to a timepiece comprising such a movement. PRIOR ART

[0004] There have long been clock movements with at least one tourbillon or carousel type regulating mechanism. These regulating mechanisms were developed with the aim of improving the isochronism of the timepiece movement by making the movement less sensitive to its position. More specifically, the regulating mechanism has the effect of moving the balance over time, so as to make it assume different positions. The average isochronism errors as a function of the balance position is in principle closer to zero than isochronism errors in a particular position of the movement.

[0005] Originally, tourbillon or carousel-type regulating mechanisms were developed for pocket watches, which are usually kept in vertical positions. Such regulating mechanisms are less relevant for wristwatches, whose position often changes depending on the wearer's movements.

[0006] To take into account the variable movements of the wearer of the watch and the changes in position and orientation of this watch, different watch movements have been developed, containing for example two or even three tourbillons moving along different axes, for example axes orthogonal to each other. In these embodiments, each tourbillon has a balance wheel, the position of the balance wheel axes being fixed during operation of the tourbillon.

[0007] There are also timepiece movements comprising a single balance wheel carried by a regulating mechanism moving this balance wheel along non-parallel axes. In known embodiments using this principle, the movement of the balance wheel axis is done along a cone. There is also a timepiece movement comprising a balance wheel carried by a regulating mechanism moving the balance wheel axis along a sphere.

[0008] In any case, the range of positions reached by the balance shaft is quite limited and corresponds to a geometric location. Therefore, this movement cannot be chosen freely.

[0009] There is no clockwork movement that allows the balance staff to be moved to a position and orientation freely chosen by the movement designer. As a result, the various regulating mechanisms have a relatively similar appearance.

[0010] It is therefore interesting to develop a timepiece movement in which the balance can move to any position, according to the choice of the movement designer, without these movements being restricted to geometric locations such as straight lines, cones or portions of spheres in particular.

[0011] Patent EP 3 543 797 describes a movement for a timepiece comprising a tourbillon-type regulating mechanism. This tourbillon is mobile according to a linear displacement so that the planes in which the tourbillon moves are always parallel to each other. This timepiece movement comprises two distinct kinematic chains. The first kinematic chain is conventional and is intended to allow the time to be displayed. The second kinematic chain is responsible for moving the regulating system in a direction perpendicular to the general plane of the timepiece movement.

[0012] The movement described in this patent does not allow the balance shaft to be freely chosen for its movement path. In fact, all the positions that this balance shaft can take are parallel to each other. Furthermore, the two kinematic chains described in the aforementioned patent are always separate and do not come together at any time to momentarily form a single kinematic chain. DESCRIPTION OF THE INVENTION

[0013] The present invention proposes to produce a clockwork movement in which a sprung balance is movable in a large number of different positions and orientations, these positions and orientations being chosen by the designer of the movement, without limitation due to the obligation to follow geometric rules.

[0014] The present invention relates to a movement for a timepiece as defined in the preamble and characterized in that this movement further comprises: a locking member for said gear train, this locking member being part of said first kinematic chain and being arranged to momentarily connect or separate said first kinematic chain and said second kinematic chain when said locking member is actuated; a moving assembly carrying said regulating assembly; a guide assembly for said moving assembly comprising at least one rail; a drive mechanism for said moving assembly arranged to move this moving assembly along the guide assembly; and a mechanism for releasing said locking member.

[0015] The present invention also relates to a timepiece comprising a movement as defined above.

[0016] In mechanical watches, different parts perform different functions, these functions being in principle the same in all movements. These functions are energy accumulation, counting and transmission, distribution, regulation, and finally time display. In known watches, the various components performing these functions are all continuously kinematically linked together so as to ensure the functioning of the timepiece's movement.

[0017] In the timepiece movement according to the present invention, the components performing these different functions are not always kinematically linked to each other, so that at certain times during the operating cycle of the movement, they form two separate and independent kinematic chains. This makes it possible in particular to move the components of one of the kinematic chains to any desired location, without having to be kinematically linked to the elements of the other kinematic chain for the entire duration of the movement. Despite this, the display of the time and the accuracy of this display can be guaranteed.

[0018] According to the invention, it is possible to choose the geometry of the movement of the balance staff in a completely free manner, without being limited by constraints of geometric locations such as straight lines, cones or spheres. In this way, the balance staff can take a large number of different positions and the correction of the isochronism of the timepiece no longer depends on the position of the latter.

[0019] The regulating mechanism can be integrated into a wristwatch in such a way that it is visible. Due to its particularly original operation, it gives the watch a remarkable aesthetic appearance, completely different from known regulating mechanisms. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The present invention and its advantages will be better understood with reference to the appended figures and to the detailed description of a particular embodiment, in which: there Figure 1is a general view of the clockwork movement according to the invention; Figure 2 represents a counting assembly of the clockwork movement of the invention; Figure 3 is a view of a set of regulation of the clockwork movement of the Figure 1 ; there Figure 4 illustrates a clockwork release mechanism according to the present invention; Figure 5 is a detailed view of a moving assembly forming part of the clockwork movement of the invention; Figure 6 is a bottom view of the moving assembly of the Figure 5 ; there Figure 7 is a detailed view of part of the moving equipment of the Figure 5 ; there figure 8 represents the regulatory set of the Figure 2 , in a first position, as well as the release mechanism of the Figure 4 ; there Figure 9 illustrates the regulatory set and the release mechanism of the figure 8 , in a second position; the Figure 10illustrates the release mechanism in a first position; the Figure 11 represents the release mechanism of the Figure 10 , in a second position; the Figure 12 represents the release mechanism of the Figure 10 , in a third position; and the Figure 13 illustrates a detail of the release mechanism of the Figure 10 , in a fourth position. METHOD OF CARRYING OUT THE INVENTION

[0021] With reference to the figures, the movement of the invention comprises a first set, here called counting set 10 illustrated in detail by the Figure 2 . This counting assembly ensures the functions of energy accumulation, counting and transmission. The movement of the invention comprises a second assembly, called regulation assembly 11 and represented in particular by the Figure 3 This regulation assembly ensures the distribution and regulation functions.

[0022] The movement of the timepiece according to the invention further comprises a guide assembly 12, shown in particular on the figures 1 to 4 , and a release mechanism 13 represented in particular by the Figure 4 , whose functions and structures are explained in detail below.

[0023] With particular reference to figures 1 And 2, the counting assembly 10 comprises a first energy source 14, which can advantageously be produced in the form of a conventional barrel 15, that is to say in particular containing a barrel spring. The counting assembly 10 also comprises a gear train 16 supplied with energy by the barrel spring. This gear train 16 can be formed of a center wheel 17 comprising a center wheel 18 and a center pinion 19, and of a middle wheel 20 comprising a middle wheel 21 and a middle pinion 22. The gear train 16 further comprises at least one minute indicator 23, formed for example by a hand carried by a cannon pinion 25.

[0024] The counting assembly 10 of the movement of the timepiece according to the invention comprises an energy transfer wheel set or transfer wheel set 26, formed of a connecting pinion 27, ensuring a kinematic connection with the gear train 16 of the counting assembly 10 and in particular with the middle wheel 21, as represented by the Figure 2 . The transfer wheel 26 further comprises a transfer wheel 28 provided with teeth whose function is explained below. The transfer wheel 26 further comprises a transfer pinion provided with return teeth 29. The connecting pinion 27, the return teeth 29 and the transfer wheel 28 are integral so that the rotation of one causes the rotation of the others.

[0025] The counting assembly 10, from the barrel 15 to the transfer wheel 26, forms a first kinematic chain of the movement of the invention.

[0026] The guide assembly 12 of the clockwork movement according to the invention comprises two rails. One of the rails, called the drive rail 30, is provided with a rack 31 and the other rail, called the guide rail 32, is smooth. In a preferred embodiment, these two rails can have any shape, but must always be in a determined geometric relationship, detailed below. These rails are fixed and linked to a plate of the movement.

[0027] The regulation assembly 11 includes in particular a mobile assembly 33, illustrated in particular by the figures 3 , 5 And 6. This mobile assembly 33 carries a second energy source 34 and a regulating member 35. In the illustrated embodiment, this second energy source 34 comprises a spiral spring 36 secured to a toothed crown 37 and a paddle wheel 38. The paddle wheel 38 is held armed and in position by a pawl 39. The toothed crown 37 meshes with a pinion of an intermediate mobile 41. A toothed wheel 42 of this intermediate mobile 41 in turn meshes with a pinion of a drive wheel 44 of the mobile assembly 33. This drive wheel 44 meshes with the rack 31 of the drive rail 30 so as to ensure the movement of the mobile assembly 33 along the rails during the rotation of the drive wheel 44. This is illustrated in particular by the Figure 7 The rails being fixed relative to a plate of the movement, the rotation of the drive wheel 44 causes the moving assembly 33 to move along the rails.

[0028] As can be seen on the Figure 6 in particular, the drive wheel 44 is linked to an escape wheel 45 via a mechanism called "remontoir d'égalité 46". This escape wheel 45 cooperates with a balance spring 47 via an anchor 48. The anchor 48 and the balance spring 47 act as a regulating member 35 in particular on the movement of the moving assembly 33, so that this moving assembly moves in steps whose frequency is regulated in particular by the oscillation frequency of the balance spring 47. In addition to regulating the movement of the moving assembly 33, the anchor 48 and the balance spring 47 provide the distribution and regulating functions as in a conventional mechanical clockwork movement.

[0029] As indicated above, the guide assembly 12 comprises a drive rail 30 provided with a rack 31 and a guide rail 32 along which the moving assembly 33 moves. To ensure constant contact between the drive wheel 44 and the drive rail 30 and to ensure predictable positioning of the moving assembly 33, this moving assembly comprises a first carriage 49 provided with at least one double roller 50 intended to bear against the part of the drive rail 30 opposite the rack 31. This moving assembly 33 further comprises a second carriage 51 also comprising at least one double roller 52 and arranged to bear against the guide rail 32. In a preferred embodiment, one of the carriages comprises a double roller and is mounted on a bridge 53 of the moving assembly so as to be able to pivot, while the other carriage comprises two double rollers 50.The geometric relationship between the two rails of the guide assembly 12 is such that the total clearance of the carriages 49, 51 relative to the rails remains substantially constant regardless of the position of the moving assembly and regardless of the curvature of the rails. In this way, the moving assembly 33 remains constantly guided between the drive rail 30 and the guide rail 32, by means of the carriages.

[0030] The second energy source 34, the sprung balance 47, the drive wheel 44 and the elements kinematically linked thereto form a second kinematic chain, distinct from the first kinematic chain. These two kinematic chains can cooperate at certain times and be independent of each other at other times, as explained in detail below.

[0031] The release mechanism 13 is carried partly by the moving assembly 33 and partly by a plate of the movement. The part of the release mechanism carried by the moving assembly 33 is called the moving part 54 of the release mechanism. The part of the release mechanism carried by the plate is called the pivoting part 55 of the release mechanism.

[0032] This release mechanism 13 comprises a locking member 56 of the gear train arranged to prevent uncontrolled rotation of the gear train 16 of the counting assembly 10. This locking member 56 can act on any wheel set of this counting assembly, depending on the design of the movement. The locking member 56 comprises a release arm 57 pivoting around an axis 58 linked to a plate (not shown). This locking member 56 is provided with a lift 59, a return finger 60 and a safety stop 61.

[0033] The movable part 54 of the release mechanism is illustrated in particular by the figures 5 And 6 This mobile part 54 comprises a release arm 62 secured to a bridge 43 of the mobile assembly 33. This release arm 62 comprises a lift 63 whose function is described in detail below.

[0034] The pivoting portion 55 of the release mechanism is illustrated in particular by the figures 8 to 13This pivoting part 55 comprises a whip 64 mounted on the plate of the movement so as to be able to pivot freely around a whip axis 65. This whip 64 comprises a ramp 66 having a shape and a position such that it can cooperate with the lifting 63 of the release arm 62 when the moving assembly 33 passes close to this ramp 66. The whip 64 also comprises a groove 67 in which the release arm 57 of the locking member 56 can move. This whip 64 further comprises a safety shoulder 68 arranged to cooperate with the safety stop 61 of the locking member 56, and a return spring 69 intended to return the whip 64 to a rest position.

[0035] To prevent the locking member 56 from releasing the transfer wheel 26 inadvertently during an impact for example, the rotation around its rotation axis 58 of the locking member 56 is limited by the safety stop 61, which can come to bear against the safety shoulder 68 of the whip 64. The lifting 59 of the locking member 56 remains in the path of a first tooth 70 of the transfer wheel 26.

[0036] When the movement of the timepiece is in operation, the counting assembly 10 is first held stationary by the blocking member 56 of the release mechanism 13.

[0037] In a position, called the locking position and corresponding to a rest position of the release arm 57 of the locking member 56, the lift 59 of this locking member is in contact with the first tooth 70 of the transfer wheel 28 and prevents the transfer mobile 26 from rotating around its axis of rotation. The elements forming the first kinematic chain are at a standstill. This position is illustrated by the Figures 12 and 13 .

[0038] Energy is stored in the spiral spring 36 of the second energy source 34 of the regulating assembly 11. This energy has the effect of actuating the sprung balance 47 and the anchor 48, in a conventional manner.

[0039] The energy is also transmitted to the drive wheel 44 of the moving assembly 33. Thus, at each alternation of the movement, the anchor 48 releases the cog of the moving assembly and allows the drive wheel 44 to pivot, which has the effect of moving the moving assembly 33 along the drive rail 30 by means of the rack 31. Due to the respective position of the drive rail 30 and the guide rail 32 and due to the position of the carriages 49, 51, the moving assembly 33 is guided along the path defined by the rails. The movement of the moving assembly 33 is carried out at a known, constant and predefined speed which depends in particular on the oscillation frequency of the sprung balance 47.

[0040] During most of the path of the moving assembly 33, the moving part 54 of the release mechanism does not cooperate with the pivoting part 55 of this release mechanism. The whip 64 is at rest, held in this position by the return spring 69.

[0041] During the movement of the mobile assembly 33, when the latter arrives in a predefined position of its path, illustrated by the Figure 9 , the release arm 62 of the movable part 54 of the release mechanism comes into contact with the ramp 66 of the whip 64. The contact of the lift 63 of the release arm 62 with this ramp 66 has the effect of pivoting the whip 64 around its axis of rotation 65. The release arm 57 of the locking member 56 slides in the groove 67 of the whip 64, under the effect of the rotation of the whip around the whip axis 65. The pivoting part 55 of the release mechanism is armed to its maximum.

[0042] During the continuation of the movement of the mobile crew 33, illustrated by the Figure 10 , the lift 63 of the release arm 62 escapes from the ramp 66 of the whip 64. Under the effect of the return spring 69, the whip 64 falls back by pivoting around the whip axis 65 and stores energy during its fall, in such a way that it exceeds its rest position. The release arm 57 of the locking member 56 comes into contact with the edge of the groove 67. The locking member 56 then pivots around its rotation axis 58. This causes the movement of this locking member 56 into a so-called unlocked position, in which the release arm 57 is moved so that its lift 59 is no longer in abutment against the first tooth 70 of the transfer wheel 28 by creating a recoil angle for this transfer wheel. The return finger 60 is placed between two teeth of the return toothing 29.

[0043] The transfer wheel 26 can then rotate around its axis under the effect of the force transmitted from the barrel 15, via the gear train 16 and the transfer pinion 29. This position is illustrated by the Figure 11 .

[0044] During this rotation, the energy supplied by the barrel 15 to the transfer wheel 26 is transmitted to the paddle wheel 38 of the second energy source 34. For this, a third tooth 72 of the transfer wheel 28 comes into contact with a blade 73 of the paddle wheel 38 of the second energy source. The rotation of the transfer wheel 26 has the effect of pivoting the paddle wheel 38 and charging the spiral spring 36 of the second energy source 34.

[0045] In principle, the transfer wheel 28 performs a rotation corresponding to one tooth. During this rotation, a second tooth 71 of the return toothing 29 pushes the return finger 60 of the locking member 56. This locking member pivots around its axis 58 to return to the rest position. Simultaneously, the release arm 57 of the locking member bears on the edge of the groove 67 and returns the whip 64 to the rest position.

[0046] At the end of this rotation corresponding to a tooth of the transfer wheel 26, the locking member 56 returns to a locking position in which a fourth tooth 75 of the transfer wheel 28 again presses against the lift 59 of the locking member 56 and the second tooth 71 of the return toothing 29 has pushed the return finger 60 so that the lift 59 is on the path of the fourth tooth 75 of the transfer wheel 28. The fourth tooth 75 presses on the lift 59 and rotates the locking member 56, around the axis 58, so that it comes to bear against a stop 76 of the locking member. The return to the rest position by the release arm 57, in the absence of constraint from the release mechanism 13, prevents the transfer wheel 26 from pivoting further. This position is illustrated by the Figure 12 .

[0047] The third tooth 72 of the transfer wheel 28 has pushed the blade 73 sufficiently, so that one of the blades 74 is wedged on the pawl 39.

[0048] When the transfer wheel 26 rotates, energy contained in the first energy source 14 is released and transmitted to the second energy source 34 via the gear train 16, the energy transfer wheel 26 and the paddle wheel 38. At this time, the first kinematic chain containing the barrel 15 and the transfer wheel 26 and the second kinematic chain containing the second energy source 34 and the escapement are kinematically linked to each other.

[0049] The energy transferred from the first energy source 14 to the second energy source 34 is sufficient for the moving assembly 33 to perform a sufficient movement to bring it to the next location in which energy will again be transferred from the first energy source to the second energy source.

[0050] The release of the blocking member 56 also involves the release of the gear train 16 and the movement of the minute indicator 23 by a duration corresponding to the movement time of the moving assembly 33.

[0051] The recharging of the second energy source 34 can be done in one alternation of the escapement. In this case, the moving assembly 33 remains stationary during recharging. This recharging can also be carried out during more than one alternation of the escapement. In this case, the moving assembly 33 moves during recharging.

[0052] When the transfer of energy between the first energy source and the second energy source is complete and when the blocking member 56 has returned to the position preventing rotation of the transfer mobile 26, the two kinematic chains are again separated and no longer interact.

[0053] The moving assembly 33 continues its journey along the rails while the counting assembly 10 remains stationary until the next release of the blocking member 56.

[0054] The assembly comprising the whip 64, the blocking member 56 and the transfer mobile 26 can be considered as a “recharging station” in the sense that energy is recharged in the second energy source 34 when the mobile assembly 33 arrives opposite the whip.

[0055] For example, it is possible to dimension the parts so that the moving assembly 33 completes one revolution of the rails in one minute and that only one recharging station is provided. In this case, at the moment when the blocking member 56 is released, the time indicator, for example the minute indicator 23, will be displaced by an angle corresponding to a duration of one minute.

[0056] Unlike known clockwork movements, in the movement described here, the counting assembly 10 and the regulating assembly 11 do not always cooperate with each other. Indeed, the regulating assembly 11 is autonomous and independent of the counting assembly 10 throughout the path it takes, except when it cooperates with the whip 64. This independence makes it possible to move the regulating assembly 11 along almost any path defined by the rails.

[0057] At some location along the path of the moving assembly 33, the counting assembly 10 and the regulating assembly 11 form a single kinematic chain, as in a conventional movement, before separating again.

[0058] The invention has been described according to a specific embodiment. However, many variants are conceivable. In the illustrated embodiment, a single "recharging station" is provided. However, it is possible to place several stations along the route taken by the moving assembly, such as for example three equidistant stations or at irregular intervals. In this case, the minute indicator is moved by a position corresponding to 20 seconds or the appropriate duration, each time the counting assembly and the distribution assembly form the same kinematic chain.

[0059] In the described embodiment, the second energy source is powered by the first energy source. It is conceivable to use a second independent energy source which could be mechanical or even electrical.

[0060] The guides are represented by roller carriages. These carriages could, however, take other forms.

[0061] It is also possible to provide a constraint mechanism ensuring that the teeth of the drive wheel always remain in contact on a flank located on the same side of the rack, so as to take up the play between the teeth.

[0062] In principle, each rail forms a closed circuit so that the moving part always moves in the same direction. However, it is possible to provide a mechanism allowing the moving part to move in two opposite directions. In such a case, the rails can form an open circuit.

[0063] In the example described, the function of transferring energy by means of the transfer wheel and the function of moving the time indicator are linked and are performed when the moving assembly is in a determined position. These two functions could, however, be performed independently. Thus, the energy transfer could, for example, be performed twice for each revolution of the moving assembly, while the movement of the time indicator could be performed only once per revolution or, on the contrary, three times per revolution.

Claims

1. Movement for timepiece comprising: • a counting assembly (10) comprising a first power source (14) and a geartrain (16) kinematically linked to at least one time indicator, this counting assembly being part of a first kinematic chain; and • a regulation assembly (11) comprising a regulation member (35) and being part of a second kinematic chain distinct from said first kinematic chain; • a mobile equipment (33) carrying said regulation assembly (11); • a guiding assembly (12) of said mobile equipment (33) comprising at least one rail (30, 32); • a driving mechanism of said mobile equipment (33) arranged to move this mobile equipment along the guiding assembly (12); this movement for timepiece being characterized in that it further comprises: • a locking member (56) of said geartrain (16), this locking member (56) being part of said first kinematic chain and being arranged to momentarily connect or separate said first kinematic chain and said second kinematic chain when said locking member is actuated; and • a release mechanism (13) of said locking member (56).

2. Movement for timepiece according to claim 1, characterized in that the guiding assembly (12) comprises at least one driving rail (30) provided with a rack (31).

3. Movement for timepiece according to claim 1 or 2, characterized in that the guiding assembly (12) comprises at least one guiding rail (32).

4. Movement for timepiece according to claim 3, characterized in that the mobile equipment (33) comprises at least one carriage (49, 51) holding this mobile equipment (33) between said driving rail (30) and said guiding rail (32).

5. Movement for timepiece according to claim 2, characterized in that the driving mechanism of the mobile equipment (33) comprises a driving wheel (44) engaging with the rack (31) of the driving rail (30), this driving wheel (44) being kinematically linked to the regulation member (35).

6. Movement for timepiece according to claim 1, characterized in that the release mechanism (13) comprises a mobile part (54) carried by said mobile equipment (33) and a pivoting part (55) carried by a plate of the timepiece movement.

7. Movement for timepiece according to claim 1, characterized in that the counting assembly (10) comprises at least one transfer mobile body (26) kinematically linked to said first power source (14) and in that the locking member (56) acts on said transfer mobile body (26).

8. Movement for timepiece according to claim 6, characterized in that the pivoting part (55) of the release mechanism comprises a whip (64) pivoting about a whip axis (65) integral with a plate, and a release arm (57).

9. Movement for timepiece according to claims 6 to 8, characterized in that the locking member (56) of the release mechanism comprises a lift (59) acting on said transfer mobile body (26) and actuated by said release arm (57).

10. Movement for timepiece according to claim 8, characterized in that said whip (64) comprises a ramp (66) arranged to pivot the whip (64) about the whip axis (65) when the mobile part (54) of the release mechanism acts on the ramp (66).

11. Movement for timepiece according to claim 10, characterized in that the mobile part (54) of the release mechanism comprises a release arm (62) arranged to actuate the ramp (66) of the pivoting part (55) of the release mechanism when the mobile equipment (33) moves along the guiding assembly (12).

12. Movement for timepiece according to claim 1, characterized in that the regulation assembly (11) comprises a second power source (34).

13. Movement for timepiece according to claim 12, characterized in that the second power source (34) comprises a spiral spring (36) kinematically linked to a paddle wheel (38).

14. Movement for timepiece according to claim 12, characterized in that it comprises at least two power transfer mobile bodies (26) arranged to transfer energy from said first power source (14) to said second power source (34).

15. Timepiece comprising a movement according to any one of claims 1 to 14.

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