DEVICE FOR THE COORDINATED OPERATION OF TWO FUNCTIONS OF A CLOCK

Description

[0001] A first object of the present invention is a device for actuating two functions of a timepiece in a coordinated manner. By way of example, the two functions actuated by the device of the invention may be, respectively, a time display function and an animation function. The two functions may be implemented by two different mechanisms or by the same mechanism. The second object of the present invention is a timepiece, particularly a watch, comprising two functions and a device for actuating the two functions in a coordinated manner.

[0002] The present invention relates in particular to a device for the coordinated actuation of two mechanisms of a timepiece, the two mechanisms each comprising a moving part, and the device comprising: a so-called "snail" cam arranged to be driven by the movement of the timepiece and having an upward profile ending in a step; a first and a second transmission member each comprising a pivoted toothed sector and a cam follower, the cam followers of the first and second transmission members both being arranged to cooperate with the snail profile, and the toothed sectors being respectively kinematically connected to the two moving parts; return means arranged to return the cam followers of the first and second transmission members against the snail profile; the toothed sector of each of the transmission members being arranged so that, during each revolution of the snail, it pivots alternately in one direction and in the other from an extreme angular position associated with the apex of the snail profile to an opposite extreme angular position. EARLIER ART

[0003] Clocks are already known that include a mechanism for providing time information, combined with another mechanism that produces an animation. Patent document CH 55403, in particular, describes a cuckoo clock that includes a two-bellows mechanism driven by the clock's gear train and arranged to emit, at each hour, an alternation of two notes evoking the cuckoo's call. This known clock also includes an animation consisting of figures arranged on the front of the clock, set in motion by a mechanism also driven by the clock's gear train. According to this earlier document, the animation and the cuckoo call are operated by the same mechanism, so that the period during which the animation occurs coincides exactly with the period during which the cuckoo's call is emitted.

[0004] It will be understood that according to this example, the cuckoo's song is likely to attract the viewer's attention to the animation, but the animation cannot be used to warn the viewer of an event concerning the time indication.

[0005] There is a need for clockwork mechanisms in which the "coordination between time indication and animation" is not limited to ensuring that the time indication and the animation occur at the same time, but consists equally in regulating successive sequences as simultaneous movements, a bit like a choreography in which the beauty of the spectacle depends on the extreme precision of its execution. BRIEF SUMMARY OF THE INVENTION

[0006] One object of the present invention is to overcome the drawbacks of the prior art just described. The present invention achieves this object, as well as others, by providing a coordinated actuation device that conforms to the attached claim 1.

[0007] Thanks to the claimed characteristics, the coordinated actuation device of two functions of a timepiece, the subject of the invention, makes it possible to ensure that the triggering of one of the two functions occurs at the desired moment in the course of the operations of the other function. BRIEF DESCRIPTION OF THE FIGURES

[0008] Other features and advantages of the present invention will become apparent from the following description, given solely by way of non-limiting example, and made with reference to the accompanying drawings in which: THE Figures 1A and 1Bare two perspective views, from different angles, of a coordinated actuation device according to a first embodiment of the invention; figures 2A, 2B , 2C and 2D are schematic plan views of the coordinated actuation device according to the first embodiment of the invention at four successive instants just before, during and just after the fall of the two cam followers into the step of the snail profile; the figure 3A is a perspective view of a coordinated actuation device for a retrograde display and animation, according to a second embodiment of the invention; the figure 3B is a plan view of the coordinated actuation device according to the second embodiment of the invention; the figures 3C to 3F are schematic plan views of the coordinated actuation device according to the second embodiment of the invention at four successive instants. DETAILED DESCRIPTION OF SEVERAL METHODS OF IMPLEMENTATION

[0009] THE Figures 1A and 1BAttached are two perspective views, from different angles, of a device for the coordinated actuation of two functions of a timepiece, more particularly of two mechanisms of the timepiece implementing these two functions, respectively. This device conforms to a first embodiment of the invention. The two mechanisms that the device is intended to actuate are not shown, with the exception of two moving parts (referenced 3 and 5), each belonging to one of the mechanisms. It can be seen that in the illustrated example, moving parts 3 and 5 are pinions. Depending on the type of mechanisms to be actuated, each of the pinions 3 and 5 can, for example, be used to directly actuate the mechanism, or to wind a mainspring which is itself dedicated to the actuating of this mechanism.To clarify, in this example, the two mechanisms that the device of the invention is designed to actuate in a coordinated manner can take the form, respectively, of an animation, for example, an automaton, and a retrograde time display. In this case, the animation could be driven by pinion 3, while the retrograde time display would be arranged to be driven by pinion 5. "Animation" is understood to mean a mechanism or function with a purely aesthetic and / or entertainment purpose (thus excluding any mechanism or function intended to display a measured quantity) involving the movement of one or more mechanical elements. When the animation imitates the movements of one or more living beings, it constitutes an automaton.

[0010] THE Figures 1A and 1BThey also show a cam of the type called a "snail" (reference 7). The snail 7 is arranged to be driven around an axis 8 by the movement of the timepiece (not shown) via the wheel 19 to which the snail 7 is attached. As can be seen, the profile of the snail 7 comprises a main spiral-shaped portion and a discontinuity 9 in the form of a step arranged to connect the apex of the spiral with its lowest point. The coordinated actuation device further includes a first transmission member formed by a cam follower 11a and a toothed sector 11b, and a second transmission member comprising a cam follower 13a and a toothed sector 13b. We can see that, in the example shown, the first and second transmission members are both pivoted on the same axis (referenced 21), and that their cam followers 11a and 13a are both arranged to cooperate with the profile of the snail 7.It can also be seen that the toothed sectors 11b, 13b of the two transmission elements mesh respectively with the pinions 3 and 5. The coordinated actuation device finally includes return means arranged to return the cam followers 11a and 13a against the profile of the snail 7. In the illustrated example, these return means include a first leaf spring (referenced 17).

[0011] The direction in which the movement (not shown) of the timepiece causes the snail 7 to rotate corresponds to the clockwise direction in the Figures 1A and 1BIt will therefore be understood that the spiral portion of the profile corresponds to its ascending portion. The cam followers 11a and 13a of the first and second transmission members are arranged to follow the profile of the snail 7 with a slight offset, the cam follower 13a being slightly behind the cam follower 11a. In this example, the offset between the two cam followers corresponds to a period of three minutes. As the cam 7 is driven by the movement at a rate of one revolution every twelve hours, the offset between the two cam followers corresponds to the time required for the cam to pivot by 1.5°. IlIt is worth noting that if cam 7 were driven at the higher speed of one revolution per hour, the cam would take only 15 seconds to pivot 1.5°. Generally, it is advantageous for the angle through which the cam pivots during the offset to be less than 30°, and preferably less than 5°. Generally, it is advantageous for the angle through which the cam pivots during the offset to be greater than 1.2°, and preferably greater than 1.3°, preferably greater than 1.4°.

[0012] Now also referring to figures 2A to 2D We can see that the toothed sector 11b of the first transmission member carries an eccentric 25a, while the cam follower 13a of the second transmission member has a shoulder serving as a bearing surface 25b. As shown in the figure 2BThe eccentric 25a and the bearing surface 25b can come together to block, in one direction, the pivoting of the toothed sector 11b relative to the cam follower 13a. The purpose of the locking means just described will be explained later.

[0013] As can be seen in the Figures 1A and 1BThe cam followers 11a and 13a are arranged to pivot around axis 21 in the same plane perpendicular to this axis. This arrangement has the advantage of making the coordinated actuation device more compact, particularly in terms of thickness. It can also be seen that cam follower 13a is slightly longer than cam follower 11a, and that its shape is adapted to allow it to fit over the latter. Finally, the end of cam follower 13a is curved so that both cam followers can bear against the profile of the snail 7 simultaneously, creating a gap between the surfaces 27a and 27b of the two cam followers.

[0014] In the illustrated example, the second transmission element forms a single-piece structure comprising two arms substantially perpendicular to each other. The two arms of the second transmission element are made up respectively of the cam follower 13a and the toothed sector 13b, these two elements being a single unit. In the illustrated example, this is not the case for the first transmission element. The figures 2A to 2D These figures show that the toothed sector 11b and the cam follower 11a are articulated relative to each other at the axis 21. It is understood that these two elements can thus pivot independently of each other around the axis 21. The cam follower 11a and the toothed sector 11b also share stop means (23a, 23b). Indeed, the cam follower 11a has a finger 23a, and the toothed sector 11b has a pin 23b. As shown in the Figures 2A And 2DThe pin 23b and the finger 23a can butt against each other to block the rotation of the toothed sector 11b relative to the cam follower 11a in one direction. The finger 23a and the pin 23b thus form the shared stopping means for the cam follower 11a and the toothed sector 11b. However, it will be understood that different stopping means could be used. According to alternative variations, these stopping means could be of any type suitable for limiting the angular sector within which the cam follower 11a and the toothed sector 11b can pivot relative to each other.

[0015] THE figures 2A to 2DThese are four successive snapshots of the device's operation according to this first embodiment. In the example shown, the snail 7 is mounted coaxially on the cannon wheel (referenced 19) of the timepiece (the snail 7 is preferably made of the same material as the cannon wheel 19). It therefore completes exactly one revolution in twelve hours. Referring to the same figures, it will be noted that the first snapshot ( figure 2A ) shows the cam followers 11a and 13a arriving at the top of the spiral, just before the cam follower 11a falls into discontinuity 9, and the fourth and final snapshot ( figure 2D ) shows the cam followers 11a and 13a at the very bottom of the spiral, following the fall of the cam follower 13a into discontinuity 9.

[0016] The actuation device according to this first embodiment further includes a second leaf spring (referenced 15) which is arranged so that its distal end presses against the pin 23b of the toothed sector 11b. The toothed sector of the first transmission member is therefore constantly subjected to a restoring force which tends to rotate it around the axis 21 (the direction in which the restoring force causes the toothed sector 11b to rotate corresponds to the clockwise direction in the figures 2A to 2D The force exerted by the second leaf spring 15 on the toothed sector 11b also has the effect of returning the pin 23b towards the finger 23a. Finally, when the pin 23b is abutted against the finger 23a as illustrated in the Figures 2A And 2D , the force exerted by the second leaf spring 15 also has the effect of bringing the cam follower 11a back against the profile of the snail 7.

[0017] We have seen that the cam followers 11a, 13a travel along the spiral section of the snail profile from bottom to top. This ascending section is arranged to progressively lift the two cam followers, so as to rotate them around axis 21 (counterclockwise in the figures 2A to 2D ). When the cam follower 11a of the first transmission member pivots, its finger 23a pushes the pin 23b of the toothed sector 11b against the restoring force exerted by the second leaf spring 15. Thus, thanks to the presence of the stop means 23a, 23b, the toothed sector 11b pivots counterclockwise in conjunction with the cam follower 11a. Finally, the pivoting of the toothed sector 11b drives the pinion 3 clockwise (as shown in the figures 2A to 2D). Similarly, when the ascending part of the snail 7 lifts the cam follower 13a of the second transmission member, it gradually rotates it around the axis 21 in the counterclockwise direction, and it will be understood that when the second transmission member pivots in this way, the toothed sector 13b drives the pinion 5 in the clockwise direction.

[0018] It will be understood from the foregoing that the toothed sector 11b of the first transmission member and the toothed sector 13b of the second transmission member each reach an extreme angular position when the cam follower 11a or 13a of the same transmission member reaches the apex of the spiral portion of the snail 7. It will also be understood that, with each revolution of the snail 7, the two toothed sectors 11b and 13b pivot alternately in one direction and then the other from the extreme angular position associated with the apex of the profile of the snail 7 to an opposite extreme position. If we now refer to the snapshot of the figure 2AAs can be seen, the cam followers 11a and 13a are located at the very top of the spiral of the snail 7, with cam follower 11a even situated on the edge of the discontinuity 9. It is understood that at the instant shown, cam follower 11a has reached its maximum pivoting position in the counterclockwise direction. Furthermore, the interaction of the stop means 23a and 23b has resulted in cam follower 11a driving toothed sector 11b with it, so that the latter has also reached its extreme angular position in the counterclockwise direction. Finally, since pinion 3 is constantly meshing with toothed sector 11b, it has also reached the end of its travel (in the clockwise direction).

[0019] A snapshot of the figure 2BThe device is shown a few moments later. The cam follower 11a of the first transmission member has now fallen into the discontinuity 9, and it is the cam follower 13a of the second transmission member that is at the edge of the discontinuity 9. Having crossed the discontinuity 9, the cam follower 11a is no longer supported by the profile of the snail 7. Under these conditions, it is free to pivot. Its finger 23a is therefore no longer held in position, so that the stop means 23a, 23b are inoperative. Under these conditions, the second leaf spring 15 rotates the toothed sector 11b clockwise so as to drive the pinion 3 counterclockwise. It should be noted that in this example, the pinion 3 is arranged to drive an animation (not shown) that is part of the timepiece.

[0020] We saw earlier that the toothed sector 11b carries an eccentric 25a arranged to abut against a bearing surface 25b on the second transmission member, so as to prevent the toothed sector 11b from pivoting beyond a certain limit relative to the cam follower 13a. Under these conditions, when the toothed sector 11b of the first transmission member pivots clockwise, driven by the second leaf spring 15, the eccentric 25a abuts against the bearing surface 25b. As shown in the figure 2BThe eccentric's contact with the bearing surface interrupts the rotation of the toothed sector 11b. Furthermore, since pinion 3 meshes with the toothed sector, it also stops rotating the instant eccentric 25a abuts against the bearing surface 25b. Advantageously, the precise angular position at which pinion 3 stops when the stopping means 25a and 25b interrupt the rotation of the toothed sector 11b is chosen to coincide with a specific instant, for example, a high point, in the animation sequence. The synchronization between this specific instant in the animation sequence and the interruption of the rotation of the toothed sector 11b can be adjusted by slightly rotating the eccentric.

[0021] A snapshot of the figure 2Cshows the device a few moments later. The restoring force exerted by the first leaf spring 17 has now caused the cam follower 13a to fall into the discontinuity 9 following the cam follower 11a. As shown, the cam follower 13a has reached the bottom of the discontinuity 9, and it will be understood that at the instant shown, it has reached its extreme (opposite) angular position in the clockwise direction. As regards the other cam follower 11a, it will be understood that, as long as the pin 23b has not come to rest against the finger 23a, the cam follower 11a is not subjected to the restoring force generated by the spring 15. At this stage, the cam follower 11a is therefore free to rotate within a space between the bottom of the discontinuity 9 and the lateral edge 27a of the cam follower 13a.

[0022] As explained above, the cam follower 13a of the second transmission member is arranged so that it is returned against the profile of the snail 7 by the first leaf spring 17. Under these conditions, when the cam follower 13a falls into the discontinuity 9, the first leaf spring 17 rotates the second transmission member at an accelerated speed in a clockwise direction. The rotation of the second transmission member causes the stopping means 25a, 25b to separate, so that the toothed sector 11b again drives the pinion 3 counterclockwise, thus completing the animation. Furthermore, since the toothed sector 13b of the second transmission member meshes with the pinion 5, the latter is driven at an accelerated speed in a counterclockwise direction. It should be noted that in this example, the pinion 5 is arranged to trigger the retrograde display of the time.

[0023] Finally, referring to the figure 2DAs can be seen, pin 23b is now butted against finger 23a, while cam follower 11a is pressed against the profile of snail 7, the animation having been completed. It will be understood that the exemplary device just described allows for the coordinated activation of an animation and a retrograde time display in a timepiece. This device notably ensures that the retrograde time display is triggered at the desired moment in the animation sequence.

[0024] THE figures 3A to 3FThey demonstrate a coordinated actuation device for a retrograde display and an animation according to a second embodiment of the invention. The retrograde display comprises a retrograde hour hand 41 and a retrograde minute hand 43. In the illustrated example, the retrograde hands 41 and 43 are in the form of two figures, the hour figure carrying a parasol. The retrograde hands 41 and 43 are attached to two sector-toothed gears 42 and 44, whose axes are referenced 45 and 47, respectively. Furthermore, as will be seen in more detail below, the function of the figure-shaped hands 41 and 43 is not limited to displaying the time. The two hands 41 and 43 are also capable of performing coordinated movements, the combination of which constitutes an animation.This is why, in the description that follows, these hands are sometimes called animation organs rather than retrograde hands.

[0025] Always referring to figures 3A to 3F We can also see an hour wheel arranged to be driven around an axis 48 by the clockwork mechanism at a rate of one revolution every 12 hours, and a minute wheel arranged to be driven at a rate of one revolution every 120 minutes. The hour wheel comprises a wheel 19, as well as an hour cam 51 and an animation cam 53, both of which are coaxial with and fixed to the wheel 19, the cams 51 and 53 preferably being coplanar, as can be seen in the figure 3A in order to limit the thickness of the hour hand. The direction in which the hour hand is driven by the clockwork mechanism corresponds to the clockwise direction in the figures 3A to 3FAs is typical for a retrograde display, the hour cam 51 is a radial snail cam whose profile consists of a main spiral section and a discontinuity 52 in the form of a step that connects the apex of the spiral with its lowest point. The radial animation cam 53 is more unusual. It consists of a ring interrupted by an opening that passes through the ring wall, this opening forming a discontinuity 54 in the profile of the cam 53. The hour wheel 19, 51, 53 is preferably a single piece. The minute wheel, on the other hand, comprises a wheel 79, a pinion 80, and a minute cam 81 arranged coaxially and as a single unit. The pinion 80 meshes with the wheel 19 to drive it. In the illustrated example, the minute cam 81 has the shape of a double snail.The direction in which the minute hand is driven by the clockwork movement corresponds to the counterclockwise direction in the . figures 3A to 3F .

[0026] In a conventional retrograde display of hours and minutes, the hands 41 and 43 are controlled respectively by an hour rack 49 and a minute rack 82. Each of the two racks 49 and 82 is pivoted around an axis (71 and 84 respectively), and its toothed sector meshes with the pinion 42 and 44, which carries the corresponding retrograde hand 41 and 43. The handle of the minute rack 82 terminates in a cam follower 85, which is held against the profile of the minute cam 81 by a leaf spring 83 or other spring mechanism. It will be understood that the elements just described allow the minute cam 81 to control the retrograde minute hand 43. As already mentioned, the minute cam 81 is driven at a rate of one revolution every two hours. However, this cam exhibits a rotational symmetry of order 2.The minute rake at 82 minutes and the retrograde minute hand at 43 minutes are therefore driven according to a cycle which repeats every sixty minutes.

[0027] THE figures 3A to 3Fshow a first transmission element arranged to allow the hour cam 51 to control the retrograde hour hand 41. In the example shown, the first transmission element consists of the hour rack 49 which is pivotally mounted on the axis 71, and a cam follower lever 61 which is pivotally mounted on an axis 65 and which is arranged to cooperate with the profile of the hour cam 51 under the action of a return leaf spring 62 or other spring means. The hour rake 49 and the cam follower lever 61 are coupled to each other by means of a pin 73 which is rigidly fixed to the lever 61 and which passes through the lever 61 parallel to its axis 65. A portion of the pin 73 projecting on one of the surfaces of the lever 61 serves as a support for the free end of the leaf spring 62 and thus receives from the latter the force enabling the lever 61 to return against the hour cam 51.A portion of the pin 73 projecting on the opposite surface of the lever 61 is interposed between a rigid arm 75 of the handle of the hour rake 49 and an elastic arm 76 of the same handle, the pin 73 being able to slide slightly in the longitudinal groove formed by the arms 75, 76 by being clamped by the elastic arm 76 against the rigid arm 75.

[0028] THE figures 3A to 3FThey also show a second transmission member arranged to allow the animation cam 53 to control the two animation members or retrograde hands 41, 43. The second transmission member comprises an animation rocker 63 which is provided with a cam follower finger 64 arranged to cooperate with the profile of the animation cam 53. The animation rocker 63 is pivoted on an axis 67, and a leaf spring 55 or other spring means is also provided to return the cam follower finger 64 against the profile of the animation cam 53. An eccentric 89 can also be seen, which is mounted on the frame of the coordinated actuation device – typically the frame of the watch movement – ​​and which is arranged to cooperate with a heel 87 on the animation rocker 63. As shown in the figure 3E , the heel 87 has the possibility of coming against the eccentric 89 so as to block the pivoting of the animation rocker 63 in the clockwise direction.

[0029] The animation rocker 63 carries a second pin 91 arranged to cooperate with a flank of the hour rake 49 to drive the hour rake 49 counterclockwise when the animation rocker 63 pivots clockwise, i.e. when the cam follower finger 64 falls into the discontinuity 54 of the profile of the animation cam 53.

[0030] It can also be seen that the cam follower lever 61 carries a third pin 69 arranged to cooperate with a shoulder 68 of the animation rocker 63. When the cam follower lever 61 crosses the top of the profile of the hour cam 51 and falls into its discontinuity 52, the pivoting of the lever 61 in the clockwise direction causes the pin 69 to pivot the animation rocker 63 in the counterclockwise direction.

[0031] The hour cam 51, the animation cam 53, the cam follower lever 61, and the cam follower finger 64 are arranged so that the drops of the cam follower lever 61, which occur periodically with the same period as the drops of the cam follower finger 64, are offset in time relative to the drops of the cam follower finger 64. In a typical example, the offset between the two cam followers 61 and 64 corresponds to a duration of three minutes. As the hour hand 19, 51, and 53 is driven by the clockwork mechanism at a rate of one revolution every twelve hours, the offset between the two cam followers 61 and 64 corresponds to the time required for the hour hand 19, 51, and 53 to rotate by 1.5°. In general, it is advantageous that the angle at which the hour 19, 51, 53 mobile pivots during the duration of the shift be less than 30°, and this angle is preferably less than 5°.In general, it is advantageous that the angle at which the hour 19, 51, 53 mobile pivots during the duration of the offset be greater than 1.2°, and this angle is preferably greater than 1.3°, preferably greater than 1.4°.

[0032] The device according to this second embodiment operates as follows. At the beginning of the operating cycle ( figures 3A, 3B And 3CJust after noon or midnight, the cam follower lever 61 and the cam follower finger 85 are resting against the bottom of the hour cam 51 and the minute cam 81 respectively, and the hour and minute hands 41 and 43 are positioned at angles separated from each other, forming a V; these positions are called zero positions. The rotation of the hour and minute cams 51 and 81 gradually raises the cam follower lever 61 (counterclockwise) and the cam follower finger 85 (clockwise). By its pin 73, the cam follower lever 61 drives the hour rack 49, which itself drives, via the pinion 42, the hour hand 41 clockwise along a sectorial hour scale, until (a little less than 12 hours after the start of the cycle) the cam follower lever 61 reaches the top of the hour cam 51 ( 3D figure) corresponding to a substantially vertical position of the hour hand 41.

[0033] The lifting of the cam follower finger 85 and the minute rack 82 to which it belongs by the minute cam 81 pivots the minute hand 43 counterclockwise along a sectorial minute scale via the pinion 44. Every sixty minutes, the cam follower finger 85 falls along one of the two notches of the minute cam 81, which returns the minute hand 43 to its zero position. The minute hand 43 thus moves alternately counterclockwise (gradually) and clockwise (abruptly) while the hour hand 41 advances gradually clockwise. During all this time, the animation rocker 63 is held by the pin 69 of the cam follower lever 61 (when the lever 61 is against the bottom of the hour cam 51; figures 3A to 3C) or by animation cam 53 (the rest of the time; 3D figure ) in an angular position where it does not act on either the hour rake 49 or the minute rake 82.

[0034] Shortly before noon or midnight ( 3D figure), for example, one to three minutes before noon or midnight, the cam follower lever 61 is almost at the top of the hour cam 51, the cam follower finger 85 is almost at one of the two peaks of the minute cam 81, and the hour and minute hands 41, 43 are close to each other, in substantially vertical positions, almost at the maximum of the sector graduations. In this configuration, the pin 69 carried by the cam follower lever 61 is not in the pivot path of the animation rocker 63 and its shoulder 68. The cam follower finger 64 of the animation rocker 63, which until then slid on the animation cam 53, falls into the discontinuity 54 under the action of its return spring 55 ( figure 3EThis triggers the animation (automaton). Specifically, the pin 91 of the animation rocker 63 makes contact with the hour rake 49 and rotates it counterclockwise. Simultaneously, an activation finger 66 of the animation rocker 63 makes contact with an arm 86 of the minute rake 82 to rotate the minute rake 82 clockwise. These movements, which stop when the heel 87 of the animation rocker 63 abuts against the eccentric 89, cause the hour and minute hands 41 and 43 to move even closer together, outside the sector markings of the hours and minutes, so as to give the impression that the two figures are kissing.The movement of the hour rake 49 by the pin 91 has no effect on the position of the cam follower lever 61, which remains in contact with the hour cam 51 under the action of its return spring 62, the elastic arm 76 in contact with the pin 73 deforming to allow said movement as can be seen on the . figure 3E . It will be understood that the eccentric 89 serves as a means of adjusting the relative angular position occupied by the hour and minute hands 41, 43 at the culminating point of the animation, that is to say at the moment of the kiss.

[0035] Afterwards ( figure 3FAfter a time corresponding to the duration of the offset between the two cam followers 61 and 64 (typically three minutes, as already mentioned), the cam follower lever 61 falls into the discontinuity 52 of the profile of the hour cam 51. During this fall, the pin 69 of the cam follower lever 61 acts on the shoulder 68 to raise the animation rocker 63 and free it from any interaction with the hour rack 49 and the minute rack 82. Through its cooperation with the elastic arm 76, the pin 73 of the cam follower lever 61 drives the hour rack 49 clockwise. Simultaneously, the cam follower finger 85 falls into one of the notches of the minute cam 81, which corresponds to a pivoting of the minute rack 82 counterclockwise. The hour and minute hands, 41 and 43, abruptly return to their zero position from the animation's peak. The 12-hour cycle is complete.

[0036] It will be understood that the exemplary device just described allows for the coordinated activation of an animation and a retrograde time display in a clockwork mechanism. This device notably ensures that the retrograde time display is triggered at the desired moment within the animation sequence.

[0037] The present invention is not limited to a retrograde time display coordinated with an animation. It could, for example, be applied to a regatta watch comprising a first function of producing a chime slightly before the start of the race and a second function of producing another chime at the time of the start.

[0038] It will also be understood that various modifications and / or improvements, obvious to a person skilled in the art, can be made to the embodiments described herein without departing from the scope of the present invention as defined by the appended claims. In particular, the device of the invention can be arranged to coordinate a greater number of functions or mechanisms and may, for this purpose, include a greater number of cams and a greater number of transmission elements.Furthermore, although the coaxial arrangement of the cams 51, 53 in the second embodiment is preferred for reasons of precision, size and ease of assembly, these cams could be part of two different mobiles, for example two mobiles connected by meshing, provided that they rotate at the same angular speed and that their relative angular position (adjustable for example by an eccentric) is chosen to obtain the desired time offset between the drops of the cam follower lever 61 and those of the cam follower finger 64.

Claims

1. Device for coordinated actuation of two functions of a timepiece, the device comprising: - one or a plurality of cams (7; 51, 53) arranged to be driven by the movement of the timepiece and of which the respective profile or profiles each comprise a discontinuity (9; 52, 54): - a first (11a, 11b; 49, 61) and a second (13a, 13b; 63) transmission member each comprising a cam follower (11a, 13a; 61, 64), the cam follower (11a; 61) of the first transmission member being arranged to cooperate with the profile of the cam (7) or of a first (51) of said cams (51, 53) and to fall periodically into the discontinuity (9; 52) of the profile of the cam (7) or of said first (51) of said cams (51, 53), the cam follower (13a; 64) of the second transmission member being arranged to cooperate with the profile of the cam (7) or of a second (53) of said cams (51, 53) and to fall periodically, with the same period as the falls of the cam follower (11a; 61) of the first transmission member, into the discontinuity (9; 54) of the profile of the cam (7) or of said second (53) of said cams (51, 53), the falls of the cam follower (11a; 61) of the first transmission member being offset in time with respect to those of the cam follower (13a; 64) of the second transmission member.

2. Device for coordinated actuation as claimed in claim 1, characterised in that the offset between the cam followers (11a, 13a; 61, 64) is equal to the time necessary for the cam (7) or for the cams (51, 53) to turn by a predetermined angle when they are driven by the movement, the predetermined angle preferably being less than 30°, preferably less than 5°, and preferably being greater than 1.2°, preferably greater than 1.3°, preferably greater than 1.4°.

3. Device for coordinated actuation as claimed in claim 1 or 2, characterised in that said one or said plurality of cams consists of a snail (7), the cam followers (11a, 13a) of the first and of the second transmission members both being arranged to cooperate with the profile of the snail (7), and in that the cam followers (11a, 13a) of the first and of the second transmission members are arranged to follow the profile of the snail (7) with an offset, the cam follower (11a) of the first transmission member being in advance with respect to the cam follower (13a) of the second transmission member.

4. Device for coordinated actuation as claimed in claim 3, characterised in that it comprises return means (15, 17) arranged to return the cam followers (11a, 13a) of the first and second transmission members against the profile of the snail (7), said snail (7) comprising a rising profile terminating by a drop forming said discontinuity (9), and in that the first and second transmission members each further comprise a toothed sector (11b, 13b) arranged in order, during each revolution of the snail (7), to pivot alternately in one direction and the other from an extreme angular position associated with the tip of the profile of the snail to an opposite extreme angular position.

5. Device for coordinated actuation as claimed in claim 4, characterised in that the first and the second transmission members share stopping means (25a, 25b) arranged to stop the toothed sector (11b) of the first transmission member in a predetermined intermediate angular position when the toothed sector (11b) of the first transmission member pivots in the direction of the opposite extreme angular position following the fall of the cam follower (11a) of the first transmission member into the discontinuity (9) of the profile of the snail (7).

6. Device for coordinated actuation as claimed in claim 5, characterised in that the stopping means (25a, 25b) are rendered inoperative by the fall of the cam follower (13a) of the second transmission member into the discontinuity (9), the toothed sector (11b) then being free to pivot from the intermediate angular position to the opposite extreme angular position.

7. Device for coordinated actuation as claimed in any one of claims 3 to 6, characterised in that the first and the second transmission members are pivoted about the same axis (21).

8. Device for coordinated actuation as claimed in claim 7, characterised in that the cam followers (11a, 13a) of the first and of the second transmission member are arranged to pivot about the axis (21) in the same plane.

9. Device for coordinated actuation as claimed in any one of claims 3 to 8, characterised in that: - the toothed sector (11b) and the cam follower (11a) of the first transmission member are articulated on the axis (21) so as also to enable them to pivot with respect to each other about the axis (21), while the toothed sector (13b) and the cam follower (13a) of the second transmission member are fixedly connected to each other; and - the cam follower (11a) and the toothed sector (11b) of the first transmission member share abutment means (23a, 23b) limiting the angular sector in which they can pivot with respect to each other, and enabling the cam follower (11a) to drive the toothed sector (11b) with it when it pivots, being raised by the rising profile of the snail (7).

10. Device for coordinated actuation as claimed in any one of claims 3 to 9, characterised in that the stopping means comprise an eccentric (25a) and a bearing surface (25b), the eccentric being carried by one of the second transmission member and the toothed sector (11b) of the first transmission member, and the bearing surface forming part of the other of the second transmission member and the toothed sector (11b) of the first transmission member.

11. Device for coordinated actuation as claimed in claim 10, characterised in that the bearing surface (25b) and the eccentric (25a) are arranged to be able to come into abutment against each other so as to block, in one direction, the pivoting of the toothed sector (11b) of the first transmission member with respect to the cam follower (13a) of the second transmission member.

12. Device for coordinated actuation as claimed in any one of claims 3 to 11, characterised in that the stopping means comprise an eccentric (25a) which carries the toothed sector (11b) of the first transmission member, and a bearing surface (25b) on the second transmission member, the eccentric (25a) and the bearing surface (25b) being arranged to be able to come into abutment against each other so as to block, in one direction, the pivoting of the toothed sector (11b) of the first transmission member with respect to the cam follower (13a) of the second transmission member.

13. Device for coordinated actuation as claimed in claim 1 or 2, characterised in that said one or said plurality of cams comprise said first cam (51) arranged to cooperate with the cam follower (61) of the first transmission member (49, 61) and said second cam (53) arranged to cooperate with the cam follower (64) of the second transmission member (63).

14. Device for coordinated actuation as claimed in claim 13, characterised in that the first and second cams (51, 53) are coaxial and fixedly connected.

15. Device for coordinated actuation as claimed in claim 14, characterised in that the first and second cams (51, 53) form, or form part of, a monobloc assembly.

16. Device for coordinated actuation as claimed in any one of claims 13 to 15, characterised in that the first cam (51) is a snail.

17. Device for coordinated actuation as claimed in any one of claims 13 to 16, characterised in that the second cam (53) has a circular profile interrupted by the discontinuity (54).

18. Device for coordinated actuation as claimed in any one of claims 13 to 17, characterised in that the second transmission member (63) is a rocker.

19. Device for coordinated actuation as claimed in any one of claims 13 to 18, characterised in that the first transmission member comprises a rack (49) coupled to the cam follower (61) of the first transmission member.

20. Device for coordinated actuation as claimed in claim 19, characterised in that the second transmission member (63) is arranged to move the rack (49) when the cam follower (64) of the second transmission member (63) falls into the discontinuity (54) of the profile of the second cam (53).

21. Device for coordinated actuation as claimed in any one of claims 13 to 19, characterised in that the second transmission member (63) is arranged to act upon the first transmission member (49, 61) when the cam follower (64) of the second transmission member (63) falls into the discontinuity (54) of the profile of the second cam (53).

22. Device for coordinated actuation as claimed in claim 20 or 21, characterised in that the cam follower (61) of the first transmission member is arranged in order, as it falls into the discontinuity (52) of the profile of the first cam (51), to cause the cam follower (64) of the second transmission member (63) to rise out of the discontinuity (54) of the profile of the second cam (53).

23. Device for coordinated actuation as claimed in any one of claims 20 to 22, characterised in that it comprises a third cam (81) and a third transmission member (82) comprising a cam follower (85) arranged to cooperate with the profile of the third cam (81), the second transmission member (63) being arranged to act on the third transmission member (82) when the cam follower (64) of the second transmission member (63) falls into the discontinuity (54) of the profile of the second cam (53).

24. Device for coordinated actuation as claimed in claim 23, characterised in that the third transmission member (82) is a rack.

25. Device for coordinated actuation as claimed in claim 23 or 24, characterised in that the third transmission member (82) is arranged to actuate a first retrograde display, preferably a retrograde minute display.

26. Device for coordinated actuation as claimed in any one of claims 13 to 25, characterised in that the first transmission member (49, 61) is arranged to actuate a second retrograde display, preferably a retrograde hour display.

27. Device for coordinated actuation as claimed in claim 26, characterised in that the second transmission member (63) is arranged to actuate an animation using an indicating hand (41) of the second retrograde display.

28. Device for coordinated actuation as claimed in claims 25 and 26, characterised in that the second transmission member (63) is arranged to actuate an animation using an indicating hand (41, 43) of each of the first and second retrograde displays.

29. Device for coordinated actuation as claimed in any one of the preceding claims, characterised in that one of the two functions is a function of displaying a physical magnitude and in that the other of the two functions is an animation function, preferably an automaton function.

30. Timepiece comprising two functions and a device as claimed in any one of the preceding claims to actuate the two functions in a coordinated manner.