Device for coordinated actuation of two functions of a timepiece

Abstract

The device for coordinated actuation of two functions of a timepiece comprises one or more cams (7; 51, 53) arranged to be driven by the movement of the timepiece, and the respective profile or profiles of which each comprise(s) a discontinuity (9; 52, 54); and a first transmission member (11a, 11b; 49, 61) and a second transmission member (13a, 13b; 63) 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 the cams (51, 53) and to periodically drop into the discontinuity (9; 52) of the profile of the cam (7) or of the first (51) of the 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 the cams (51, 53) and to periodically drop, with the same period as the drops 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 the second (53) of the cams (51, 53), the drops of the cam follower (11a; 61) of the first transmission member being temporally offset with respect to those of the cam follower (13a; 64) of the second transmission member.

Description

[0001] Device for coordinated actuation of two functions of a timepiece

[0002] A first object of the present invention is a device for actuating two functions of a timepiece in a coordinated manner. For example, the two functions actuated by the device which is the subject 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, which comprises two functions and a device for actuating the two functions in a coordinated manner.

[0003] The present invention has in particular as its first object a device for coordinated actuation of two mechanisms of a timepiece, the two mechanisms each comprising a mobile, and the device comprising:

[0004] - a cam called a “snail” arranged to be driven by the movement of the timepiece and comprising an ascending profile ending in a step;

[0005] - 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 profile of the snail, and the toothed sectors being respectively kinematically connected to the two mobiles;

[0006] - return means arranged to return the cam followers of the first and second transmission members against the profile of the snail; the toothed sector of each of the transmission members being arranged to, during each revolution of the snail, pivot alternately in one direction and the other from an extreme angular position associated with the top of the profile of the snail to an opposite extreme angular position. PRIOR ART

[0007] Timepieces are already known which comprise a mechanism for providing time information and which is associated with another mechanism producing an animation. Patent document CH 55403, in particular, describes a cuckoo clock which comprises a mechanism with two bellows which is controlled by the clockwork and which is arranged to emit, at each passing of the hour, an alternation of two notes evoking the song of the cuckoo. This known clock further comprises an animation consisting of figures arranged on the front of the clock and which are activated by a mechanism which is also driven by the clockwork. According to this prior document, the animation and the song of the cuckoo are activated by the same mechanism so that the period during which the animation occurs exactly overlaps the period of emission of the cuckoo song.

[0008] 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 that the animation cannot be used to warn the viewer of an event concerning the time indication.

[0009] There is a need for timepieces in which the "coordination between time indication and animation" is not limited to ensuring that the time indication and animation occur at the same time, but consists just as much 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 unfolding.

[0010] BRIEF STATEMENT OF THE INVENTION

[0011] An object of the present invention is to overcome the disadvantages of the prior art which have just been explained. The present invention achieves this and other objects by providing a coordinated actuation device which is in accordance with the appended claim 1.

[0012] Thanks to the claimed characteristics, the device for coordinated actuation of two functions of a timepiece, object of the invention, makes it possible to ensure that the triggering of one of the two functions occurs at the desired moment in the progress of the operations of the other function.

[0013] BRIEF DESCRIPTION OF THE FIGURES

[0014] Other characteristics and advantages of the present invention will appear on reading the description which follows, given solely by way of non-limiting example, and made with reference to the appended drawings in which: Figures 1A and 1B are 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 times just before, during and just after the fall of the two cam followers in the recess of the profile of the snail; Figure 3A is a perspective view of a device for coordinated actuation of a retrograde display and an animation, according to a second embodiment of the invention;Figure 3B is a plan view of the coordinated actuation device according to the second embodiment of the invention; Figures 3C to 3F are schematic plan views of the coordinated actuation device according to the second embodiment of the invention at four successive times. DETAILED DESCRIPTION OF SEVERAL EMBODIMENTS;

[0015] The attached Figures 1A and 1B are two perspective views, from different angles, of a device for coordinated actuation of two functions of a timepiece, more particularly of two mechanisms of the timepiece implementing these two functions, respectively. This device is in accordance with a first embodiment of the invention. The two mechanisms that the device is intended to actuate are not shown, except for two mobiles (referenced 3 and 5) which each belong to one of the mechanisms. It can be seen that in the illustrated example the mobiles 3 and 5 are pinions. Depending on the type of mechanisms to be actuated, each of the pinions 3, 5 can for example be used to directly actuate the mechanism, or to wind a mainspring which is itself dedicated to the actuation of this mechanism.To clarify the ideas, in the present example, the two mechanisms that the device of the invention is intended to actuate in a coordinated manner, can take the form respectively of an animation, for example of the automaton type, 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. By “animation” is meant a mechanism or a function for purely aesthetic and / or entertainment purposes (therefore excluding any mechanism or function intended to display a measured quantity) involving movements of one or more mechanical elements. When the animation imitates the movements of one or more living beings, it constitutes an automaton.

[0016] Figures 1A and 1B also show a cam of the type called a “snail” (referenced 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 secured. As can be seen, the profile of the snail 7 comprises a main part in the form of a spiral and a discontinuity 9 in the form of a step arranged so as to connect the top of the spiral with its lowest point. The coordinated actuation device also comprises a first transmission member formed by a cam follower 11a and a toothed sector 11b, as well as a second transmission member comprising a cam follower 13a and a toothed sector 13b.It can be seen 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 members mesh respectively with the pinions 3 and 5. The coordinated actuating device finally comprises return means arranged to return the cam followers 11a and 13a against the profile of the snail 7. In the example illustrated, these return means comprise a first leaf spring (referenced 17).

[0017] The direction in which the movement (not shown) of the timepiece drives the snail 7 in rotation corresponds to the clockwise direction in Figures 1A and 1B. It will therefore be understood that the spiral portion of the profile corresponds to the ascending portion of the latter. 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 the present example, the offset between the two cam followers corresponds to a duration of three minutes. As the cam 7 is driven by the movement at the rate of one revolution in twelve hours, the offset existing between the two cam followers corresponds to the time required for the cam to pivot by 1.5°. It is worth noting that if cam 7 were driven at the higher speed of one revolution per hour, the cam would only take 15 seconds to rotate 1.5°.Generally, it is advantageous for the angle by which the cam pivots during the duration of the offset to be less than 30°, and this angle is preferably less than 5°. Generally, it is advantageous for the angle by which the cam pivots during the duration of the offset to be greater than 1.2°, and this angle is preferably greater than 1.3°, preferably greater than 1.4°.

[0018] Referring now also to Figures 2A to 2D, it can be seen 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 Figure 2B, the eccentric 25a and the bearing surface 25b have the possibility of coming into abutment against each other so as to block, in one direction, the pivoting of the toothed sector 11b relative to the cam follower 13a. The reason for the stopping means which have just been described will be explained later.

[0019] As can be seen in Figures 1A and 1B, the cam followers 11a and 13a are arranged to pivot about the 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 thickness. It can also be seen that the cam follower 13a is slightly longer than the cam follower 11a, and that its shape is adapted to allow it to cover the latter. Finally, it can be seen that the end of the cam follower 13a is curved so as to allow the two cam followers to bear against the profile of the snail 7 at the same time, a clearance then being present between the surfaces 27a, 27b of the two cam followers.

[0020] In the illustrated example, the second transmission member forms a single-piece structure comprising two arms substantially perpendicular to each other. The two arms of the second transmission member are constituted respectively by the cam follower 13a and the toothed sector 13b, these two elements coming from a single piece. In the illustrated example, this is not the case with regard to the first transmission member. Figures 2A to 2D show in fact that the toothed sector 11b and the cam follower 11a are articulated relative to each other at the axis 21. It will be understood that these two elements thus have the possibility of pivoting around the axis 21 independently of each other. The cam follower 11a and the toothed sector 11b also share stop means (23a, 23b). It can be seen that the cam follower 11a carries a finger 23a, and that the toothed sector 11b carries a pin 23b.As shown in Figures 2A and 2D, the pin 23b and the finger 23a have the possibility of coming into abutment against each other so as to block in one direction the pivoting of the toothed sector 11b relative to the cam follower 11a. The finger 23a and the pin 23b thus form the stop means shared by the cam follower 11a and the toothed sector 11b. It will be understood, however, that different stop means could be used. According to alternative variants, these stop 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.

[0021] Figures 2A to 2D are four successive snapshots of the operation of the device according to this first embodiment. In the example shown, the snail 7 is mounted in a coaxial position on the cannon wheel (referenced 19) of the timepiece (the snail 7 preferably comes from the same material as the cannon wheel 19). It therefore makes exactly one revolution in twelve hours. Still 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 the discontinuity 9, and that the fourth and last 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 the discontinuity 9.

[0022] The actuating device according to this first embodiment also comprises 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 permanently subjected to a restoring force which tends to make it pivot around the axis 21 (the direction in which the restoring force encourages the toothed sector 11b to pivot corresponding to the clockwise direction in FIGS. 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 in the direction of the finger 23a. Finally, when the pin 23b is in abutment against the finger 23a as illustrated in FIGS. 2A and 2D, the force exerted by the second leaf spring 15 still has the effect of returning the cam follower 11a against the profile of the snail 7.

[0023] It has been seen that the cam followers 11a, 13a travel along the spiral portion of the snail profile from bottom to top. This ascending portion is arranged to gradually lift the two cam followers, so as to pivot them around the axis 21 (counterclockwise in FIGS. 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 return 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 solidarity with the cam follower 11a. Finally, the pivoting of the toothed sector 11b drives the pinion 3 in the clockwise direction (as shown in 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 pivots 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.

[0024] It will be understood in particular from the above that the toothed sector 11 b of the first transmission member and the toothed sector 13 b of the second transmission member each reach an extreme angular position when the cam follower 11 a or 13 a of the same transmission member reaches the top of the spiral portion of the snail 7. It will also be understood that, at each revolution of the snail 7, the two toothed sectors 11 b, 13 b pivot alternately in one direction and the other from the extreme angular position associated with the top of the profile of the snail 7 to an opposite extreme position. Referring now to the snapshot in Figure 2A, it can be seen that the cam followers 11a and 13a are located at the very top of the spiral of the snail 7, with the cam follower 11a even being on the edge of the discontinuity 9. It will be understood that at the instant shown, the cam follower 11a has reached its maximum counterclockwise pivoting position.Furthermore, the cooperation of the stop means 23a and 23b has resulted in the cam follower 11a driving the toothed sector 11b with it, so that the latter has also reached its extreme angular position in the counterclockwise direction. Finally, since the pinion 3 is permanently meshing with the toothed sector 11b, it has also reached the end of its travel (in the clockwise direction).

[0025] The snapshot in Figure 2B shows the device 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 which 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 pivots the toothed sector 11b clockwise so as to drive the pinion 3 counterclockwise. It will be recalled that in the present example, the pinion 3 is arranged to drive an animation (not shown) that the timepiece includes.

[0026] We have seen above that the toothed sector 11 b carries an eccentric 25 a arranged to be able to come into abutment against a bearing surface 25 b that the second transmission member has, so as to block the pivoting of the toothed sector 11 b beyond a certain limit relative to the cam follower 13 a. Under these conditions, when the toothed sector 11 b of the first transmission member pivots in the clockwise direction driven by the second leaf spring 15, the eccentric 25 a comes into abutment against the bearing surface 25 b. As shown in Figure 2 B, the encounter of the eccentric with the bearing surface interrupts the pivoting of the toothed sector 11 b along the way. Furthermore, since the pinion 3 meshes with the toothed sector, it also stops rotating at the instant when the eccentric 25a comes into contact with the bearing surface 25b.Advantageously, the exact angular position at which the pinion 3 stops when the stopping means 25a, 25b interrupt the pivoting of the toothed sector 11b is chosen to coincide with a particular instant, for example a high point, in the course of the animation. The synchronization between the particular instant in the course of the animation and the interruption of the pivoting of the toothed sector 11b can be adjusted by slightly rotating the eccentric.

[0027] The snapshot in Figure 2C shows 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 bottomed out of the discontinuity 9, and it will be understood that at the instant shown it has reached its extreme (opposite) clockwise angular position. As regards the other cam follower 11a, it will be understood that, as long as the pin 23b has not come into abutment against the finger 23a, the cam follower 11a is not subjected to the return 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.

[0028] In accordance with what has just been explained, the cam follower 13a of the second transmission member is arranged so as to be 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 pivots the second transmission member at accelerated speed in the clockwise direction. The pivoting of the second transmission member causes the separation of the stop means 25a, 25b, so that the toothed sector 11b drives the pinion 3 again in the counterclockwise direction, the animation thus being able to be completed. In addition, since the toothed sector 13b of the second transmission member meshes with the pinion 5, the latter is driven at accelerated speed in the counterclockwise direction. It will be recalled that in the present example, the pinion 5 is arranged to trigger the retrograde display of the time.

[0029] Finally, referring to Figure 2D, it can be seen that the pin 23b is now in abutment against the finger 23a, while the cam follower 11a is pressed against the profile of the snail 7, the animation having been completed. It will be understood that the exemplary device which has just been described makes it possible to actuate in a coordinated manner an animation and a retrograde display of the time in a timepiece. This device makes it possible in particular to ensure that the triggering of the retrograde display of the time occurs at the desired moment in the course of the animation.

[0030] Figures 3A to 3F show a device for coordinated actuation of 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 example illustrated, the retrograde hands 41, 43 are in the form of two characters, the hour character carrying an umbrella. The retrograde hands 41, 43 are integral with two sector-toothed pinions 42, 44 whose axes are referenced respectively 45 and 47. Furthermore, as will be seen in more detail below, the function of the hands 41, 43, in the form of characters, is not limited to displaying the time. The two hands 41, 43 are also capable of performing coordinated movements, the composition of which constitutes an animation.This is why, in the following description, these needles are sometimes called animation organs rather than retrograde needles.

[0031] Still referring to Figures 3A to 3F, we can still see an hour wheel which is arranged to be driven around an axis 48 by the watch movement at the rate of one revolution in 12 hours and a minute wheel which is arranged to be driven at the rate of one revolution in 120 minutes. The hour wheel comprises a wheel 19, as well as an hour cam 51 and an animation cam 53 which are both coaxial with the wheel 19 and integral with the latter, the cams 51, 53 preferably being coplanar as visible in Figure 3A in order to limit the thickness of the hour wheel. The direction in which the hour wheel is driven by the watch movement corresponds to the clockwise direction in Figures 3A to 3F.It can be seen that, in a conventional manner for a retrograde display, the hour cam 51 is a radial cam of the snail type whose profile is formed by a main part in the form of a spiral and a discontinuity 52 in the form of a step which connects the top of the spiral with its lowest point. The radial animation cam 53 is more unusual. It consists in fact of a ring interrupted by an opening which passes through the wall of the ring, this opening forming a discontinuity 54 in the profile of the cam 53. The mobile of the hours 19, 51, 53 is preferably in one piece. The minute mobile, for its part, comprises a wheel 79, a pinion 80 and a minute cam 81 arranged coaxially and integrally. The pinion 80 meshes with the wheel 19 to drive it. In the example illustrated, the minute cam 81 has the shape of a double snail.The direction in which the minute wheel is driven by the clockwork corresponds to the counterclockwise direction in Figures 3A to 3F.

[0032] Conventionally for a retrograde display of the hours and minutes, the hands 41, 43 are controlled respectively by an hour rack 49 and a minute rack 82. Each of the two racks 49, 82 is pivoted about an axis (respectively 71 and 84) and its toothed sector meshes with the pinion 42, 44 which carries the corresponding retrograde hand 41, 43. The handle of the minute rack 82 ends with a cam follower finger 85 which is returned against the profile of the minute cam 81 by a leaf spring 83 or other spring means. It will be understood that the elements which have just been described allow the minute cam 81 to control the retrograde minute hand 43. As already mentioned, the minute cam 81 is driven at the speed of one revolution in two hours. However, this cam has rotational symmetry of order 2.The 82 minute rack and the 43 minute retrograde hand are therefore driven according to a cycle which repeats every sixty minutes.

[0033] Figures 3A to 3F also show a first transmission member arranged to allow the hour cam 51 to control the retrograde hour hand 41. In the example shown, the first transmission member consists of the hour rack 49 which is pivotally mounted on the axis 71, as well as 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 rack 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 from 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 making it possible to return the lever 61 against the hour cam 51.A portion of the pin 73 projecting from 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 while being clamped by the elastic arm 76 against the rigid arm 75.

[0034] Figures 3A to 3F 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 lever 63 which is provided with a cam follower finger 64 arranged to cooperate with the profile of the animation cam 53. The animation lever 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. We can also see an eccentric 89 which is mounted on the frame of the coordinated actuation device - typically the frame of the watch movement - and which is arranged so as to be able to cooperate with a heel 87 which the animation lever 63 has.As shown in Figure 3E, the heel 87 has the possibility of coming into contact with the eccentric 89 so as to block the pivoting of the animation rocker 63 in the clockwise direction.

[0035] The animation lever 63 carries a second pin 91 arranged to cooperate with a flank of the hour rack 49 to drive the hour rack 49 in the counterclockwise direction when the animation lever 63 pivots in the clockwise direction, that is to say when the cam follower finger 64 falls into the discontinuity 54 of the profile of the animation cam 53.

[0036] 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.

[0037] The hour cam 51, the animation cam 53, the cam follower lever 61 and the cam follower finger 64 are arranged so that the falls of the cam follower lever 61, which occur periodically with the same period as the falls of the cam follower finger 64, are time-shifted relative to the falls of the cam follower finger 64. In a typical example, the time shift between the two cam followers 61, 64 corresponds to a duration of three minutes. Since the hour wheel 19, 51, 53 is driven by the watch movement at the rate of one revolution in twelve hours, the time shift between the two cam followers 61, 64 corresponds to the time required for the hour wheel 19, 51, 53 to pivot by 1.5°. Generally speaking, it is advantageous for the angle by which the mobile of hours 19, 51, 53 pivots during the duration of the shift to be less than 30°, and this angle is preferably less than 5°.Generally, it is advantageous for the angle by which the mobile of hours 19, 51, 53 pivots during the duration of the shift to be greater than 1.2°, and this angle is preferably greater than 1.3°, preferably greater than 1.4°.

[0038] The device according to this second embodiment operates in the following manner. At the start of the operating cycle (Figures 3A, 3B and 3C), just 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, 43 have angular positions spaced apart from each other forming a V, these positions being called zero positions. Rotation of the hour and minute cams 51, 81 causes the cam follower lever 61 to gradually lift (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 graduation, until (a little less than 12 hours after the start of the cycle) the cam follower lever 61 arrives at the top of the hour cam 51 (figure 3D) corresponding to a substantially vertical position of the hour hand 41.

[0039] The lifting of the cam follower finger 85 and the minute rack 82 to which it belongs by the minute cam 81 causes the minute hand 43 to pivot counterclockwise along a sectorial minute scale via the pinion 44. Every sixty minutes, the cam follower finger 85 drops along one of the two recesses of the minute cam 81, which causes the minute hand 43 to return to its zero position. The minute hand 43 thus moves alternately counterclockwise (gradually) and clockwise (abruptly) while the hour hand 41 gradually advances clockwise.During all this time, the animation lever 63 is held by the pin 69 of the cam follower lever 61 (when the lever 61 is resting against the bottom of the hour cam 51; figures 3A to 3C) or by the animation cam 53 (the rest of the time; figure 3D) in an angular position where it acts neither on the hour rack 49 nor on the minute rack 82.

[0040] Shortly before noon or midnight (Figure 3D), 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 tops 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 3E), which triggers the animation (automaton).Concretely, the pin 91 of the animation lever 63 comes into contact with the hour rack 49 and pivots it counterclockwise. Simultaneously, an activation finger 66 of the animation lever 63 comes into contact with an arm 86 of the minute rack 82 to pivot the minute rack 82 clockwise. These movements, which stop when the heel 87 of the animation lever 63 abuts against the eccentric 89, cause the hour and minute hands 41, 43 to move even closer to each other, outside the sectorial graduations of the hours and minutes, so as to give the impression that the two characters are kissing each other.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 abutment against 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 in FIG. 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 culmination of the animation, i.e. at the moment of the kiss. Then (FIG. 3F), after a time corresponding to the duration of the offset between the two cam followers 61, 64 (typically three minutes, as already indicated), 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 lever 63 and free it from any interaction with the hour rack 49 and the minute rack 82. By its cooperation with the elastic arm 76, the pin 73 of the cam follower lever 61 drives the hour rack 49 in a clockwise direction. Simultaneously, the cam follower finger 85 falls into one of the recesses of the minute cam 81, which corresponds to a pivoting of the minute rack 82 in a counterclockwise direction. The hour and minute hands 41, 43 thus abruptly return to their zero position from the highest point of the animation. The 12-hour cycle is completed.

[0041] It will be understood that the exemplary device which has just been described makes it possible to activate in a coordinated manner an animation and a retrograde display of the time in a timepiece. This device makes it possible in particular to ensure that the triggering of the retrograde display of the time occurs at the desired moment in the course of the animation.

[0042] 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 consisting of producing a chime slightly before the start of the race and a second function consisting of producing a new chime at the time of the start.

[0043] It will further be understood that various modifications and / or improvements obvious to a person skilled in the art may be made to the embodiments which are the subject of the present description without departing from the scope of the present invention defined by the appended claims. In particular, the device of the invention may be arranged to coordinate a greater number of functions or mechanisms and may comprise for this purpose a greater number of cams and a greater number of transmission members.Furthermore, although the coaxial arrangement of the cams 51, 53 in the second embodiment is preferred for reasons of precision, size and simplicity 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 shift between the falls of the cam follower lever 61 and those of the cam follower finger 64.

Claims

CLAIMS 1. Device for coordinated actuation of two functions of a timepiece, the device comprising: - one or more cams (7; 51, 53) arranged to be driven by the movement of the timepiece and the respective profile(s) of which 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 drop periodically in 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 drop periodically, with the same period as the falls of the cam follower (11a; 61) of the first transmission member, in 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 temporally offset relative to those of the cam follower (13a; 64) of the second transmission member.; 2. Coordinated actuating device according to claim 1, characterized in that the offset between the cam followers (11a, 13a; 61, 64) is equal to the time required for the cam (7) or cams (51, 53) to rotate through a predetermined angle when 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°. Coordinated actuating device according to claim 1 or 2, characterized in that said one or more cams consist of a snail (7), the cam followers (11a, 13a) of the first and 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 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 ahead of the cam follower (13a) of the second transmission member.Coordinated actuating device according to claim 3, characterized 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 an ascending profile ending in a step forming said discontinuity (9), and in that the first and second transmission members each further comprise a toothed sector (11b, 13b) arranged to, during each revolution of the snail (7), pivot alternately in one direction and the other from an extreme angular position associated with the top of the profile of the snail to an opposite extreme angular position.Coordinated actuating device according to claim 4, characterized in that the first and second transmission members share stopping means (25a, 25b) arranged to stop the toothed sector (11 b) of the first transmission member in an intermediate angular position. predetermined when the toothed sector (11 b) of the first transmission member pivots towards 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. Coordinated actuating device according to claim 5, characterized 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 (11 b) then being free to pivot from the intermediate angular position to the opposite extreme angular position.

7. Coordinated actuation device according to one of claims 3 to 6, characterized in that the first and second transmission members are pivoted around the same axis (21).

8. Coordinated actuating device according to claim 7, characterized in that the cam followers (11a, 13a) of the first and second transmission members are arranged to pivot around the axis (21) in the same plane.

9. Coordinated actuation device according to one of claims 3 to 8, characterized in that: - the toothed sector (11 b) and the cam follower (11 a) of the first transmission member are articulated on the axis (21 ) so as to also allow them to pivot relative to each other around the axis (21 ), while the toothed sector (13 b) and the cam follower (13 a) of the second transmission member are integral with each other; and - the cam follower (11a) and the toothed sector (11b) of the first transmission member share stop means (23a, 23b) limiting the angular sector within which they can pivot relative to each other, and allowing the cam follower (11a) to drive the toothed sector (11b) with it when it pivots while being lifted by the ascending profile of the snail (7).

10. Coordinated actuating device according to one of claims 3 to 9, characterized 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 (11 b) of the first transmission member, and the bearing surface forming part of the other of the second transmission member and the toothed sector (11 b) of the first transmission member.

11. Coordinated actuating device according to claim 10, characterized in that the bearing surface (25b) and the eccentric (25a) are arranged so as to be able to abut against each other so as to block, in one direction, the pivoting of the toothed sector (11b) of the first transmission member relative to the cam follower (13a) of the second transmission member.

12. Coordinated actuating device according to one of claims 3 to 11, characterized in that the stopping means comprise an eccentric (25a) carried by the toothed sector (11b) of the first transmission member, and a bearing surface (25b) presented by the second transmission member, the eccentric (25a) and the bearing surface (25b) being arranged so as to be able to come into abutment against each other so as to block, in one direction, the pivoting of the toothed sector (11 b) of the first transmission member relative to the cam follower (13a) of the second transmission member. Coordinated actuation device according to claim 1 or 2, characterized in that said one or more 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). Coordinated actuation device according to claim 13, characterized in that the first and second cams (51, 53) are coaxial and integral. Coordinated actuation device according to claim 14, characterized in that the first and second cams (51, 53) form or are part of a single-piece assembly. Coordinated actuation device according to one of claims 13 to 15, characterized in that the first cam (51) is a snail. Coordinated actuation device according to one of claims 13 to 16, characterized in that the second cam (53) has a circular profile interrupted by the discontinuity (54). Coordinated actuation device according to one of claims 13 to 17, characterized in that the second transmission member (63) is a rocker. Coordinated actuation device according to one of claims 13 to 15. 18, characterized in that the first transmission member comprises a rake (49) coupled to the cam follower (61) of the first transmission member. Coordinated actuation device according to claim 19, characterized in that the second transmission member (63) is arranged to move the rake (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). Coordinated actuation device according to one of claims 13 to 19, characterized in that the second transmission member (63) is arranged to act on 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).Coordinated actuation device according to claim 20 or 21, characterized in that the cam follower (61) of the first transmission member is arranged to, during its fall in the discontinuity (52) of the profile of the first cam (51), 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). Coordinated actuation device according to one of claims 20 to 22, characterized 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). Coordinated actuating device according to claim 23, characterized in that the third transmission member (82) is a rake. Coordinated actuating device according to claim 23 or 24, characterized in that the third transmission member (82) is arranged to actuate a first retrograde display, preferably a retrograde display of the minutes. Coordinated actuating device according to one of claims 13 to 25, characterized in that the first transmission member (49, 61) is arranged to actuate a second retrograde display, preferably a retrograde display of the hours.Coordinated actuation device according to claim 26, characterized in that the second transmission member (63) is arranged to actuate an animation using an indicator needle (41) of the second retrograde display. Coordinated actuation device according to claims 25 and 26, characterized in that the second transmission member (63) is arranged to actuate an animation using an indicator needle (41, 43) of each of the first and second retrograde displays. Coordinated actuation device according to one of the preceding claims, characterized in that one of the two functions is a function for displaying a physical quantity and in that the other of the two functions is an animation function, preferably an automaton function. Timepiece comprising two functions and a device according to one of the preceding claims for actuating the two functions in a coordinated manner.

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