Device for coordinating actuation of two functions of timepiece
By designing devices for coordinated actuation, including cam, transmission member and return device, the problem of difficulty in coordinated actuation between time indication and animation in existing clocks is solved, and the retrograde display of time is triggered at the desired moment of animation expansion is achieved, which improves the accuracy and aesthetics of the clock function.
Patent Information
- Application Number
- CN202380056380.8
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Priority Date
- 2022-08-24
- Filing Date
- 2023-07-05
- Publication Date
- 2025-03-04
AI Technical Summary
Existing clocks have difficulty achieving coordinated actuation between time indication and animation, especially in ensuring that time indication and animation occur simultaneously and adjusting continuous sequences and simultaneous motion.
By designing a device for coordinated actuation, the device including a cam, a transmission member and a return device, ensures that one of the two functions is triggered at a desired moment when the operation of the other function is deployed.
The retrograde display of time is triggered at the desired moment of animation expansion, ensuring coordinated activation between time indication and animation, and improving the accuracy and aesthetics of watch functions.
Smart Images
Figure CN119563145A_ABST
Abstract
Description
Technical Field
[0001] The first object of the present invention is a device for actuating two functions of a clock in a coordinated manner. By way of example, the two functions actuated by the device as the object of the present invention can be a time display function and an animation function. These two functions can be realized by two different mechanisms or the same mechanism. The second object of the present invention is a clock, in particular a watch, comprising two functions and a device for actuating these two functions in a coordinated manner.
[0002] In particular, a first object of the invention is a device for coordinated actuation of two clockwork mechanisms, each comprising a mobile, and comprising:
[0003] - a cam, called a "snail", arranged to be actuated by the movement of the timepiece and comprising an ascending profile terminating in a descending portion;
[0004] - a first transmission member and a second transmission member, each comprising a pivoting toothed sector and a cam follower, the cam followers of the first transmission member and the second transmission member being arranged to cooperate with the profile of the volute and the toothed sectors being kinematically connected to the two moving elements, respectively;
[0005] - return means arranged to return the cam followers of the first transmission member and of the second transmission member to the profile of the volute;
[0006] The tooth sectors of each transmission member are arranged in sequence and pivot alternately in one direction and the other during each rotation of the scroll from an extreme angular position associated with the tip of the scroll profile to an opposite extreme angular position. Background Art
[0007] Known clocks include a mechanism for providing time information, which is associated with another mechanism that produces an animation. Patent document CH55403 describes in particular a cuckoo clock, which includes a mechanism with two bellows, which is controlled by the clock's travel gear train and is arranged to alternately pronounce two notes at each passing hour to evoke the cuckoo's song. This known clock further includes an animation formed by graphics arranged on the front of the clock, and these graphics are moved by a mechanism that is also driven by the clock's travel gear train. According to this early document, the animation mechanism and the cuckoo's song are actuated by the same mechanism, so that the time when the animation is produced coincides with the time when the cuckoo's song is emitted.
[0008] From this example, it will be appreciated that the cuckoo song may catch the attention of a person viewing the animation, but the animation may not remind the viewer of an event related to the time indication.
[0009] What is needed is a timepiece in which the "coordination between time indications and animations" is not limited to ensuring that time indications and animations occur at the same time, but also includes regulating continuous sequences and simultaneous movements, somewhat similar to the beauty of a performance in dance choreography that depends on the ultimate precision of its unfolding. Summary of the invention
[0010] The object of the present invention is to overcome the drawbacks of the prior art just described. The present invention achieves this object and others by providing a device for coordinated actuation according to the appended claim 1 .
[0011] By virtue of the claimed characteristics, the device for coordinated actuation of two functions of a timepiece, object of the invention, makes it possible to ensure that one of the two functions is triggered at the desired moment when the operation of the other function unfolds. BRIEF DESCRIPTION OF THE DRAWINGS
[0012] Other characteristics and advantages of the invention will become clear on reading the following description given purely by way of non-limiting example and with reference to the accompanying drawings, in which:
[0013] - Figure 1A and Figure 1B They are all three-dimensional views of the device for coordinated actuation at different angles according to the first embodiment of the present disclosure;
[0014] - Figure 2A , Figure 2B , Figure 2C and Figure 2D is a schematic plan view of the device for coordinated actuation according to the first embodiment of the present disclosure at four consecutive moments before, during and after two cam followers descend into the descending portion of the volute profile;
[0015] - Figure 3A is a perspective view of a device for coordinated actuation of retrograde display and animation according to a second embodiment of the present invention;
[0016] - Figure 3B is a plan view of a device for coordinated actuation according to a second embodiment of the present invention;
[0017] - FIG. 3C to FIG. 3F 1 is a schematic plan view of a device for coordinated actuation according to a second embodiment of the present invention at four consecutive moments. DETAILED DESCRIPTION
[0018] Figure 1A and Figure 1Bis a perspective view of a device for coordinated actuation of two functions of a timepiece, more specifically of two mechanisms of a timepiece that realize these two functions respectively, at different angles. The device corresponds to a first embodiment of the invention. The two mechanisms that the device is intended to actuate are not shown, except for two mobiles (reference numerals 3 and 5), each of which belongs to one of the mechanisms. It can be seen that in the illustrated example, mobiles 3 and 5 are pinions. Depending on the type of mechanism to be actuated, each of the pinions 3, 5 can be used, for example, to directly actuate the mechanism or to wind a spring that is itself dedicated to actuating the mechanism. For the sake of clarity, in this example, the two mechanisms that the device according to the invention is intended to actuate in a coordinated manner can take the form of an animation of the automaton type and a retrograde display of time, respectively. In this case, the animation can be driven by pinion 3, while the retrograde display of time is driven by pinion 5. "Animation" is understood to be a mechanism or function with a purely aesthetic and / or entertainment function involving the displacement of one or more mechanical elements (thus excluding any mechanism or function intended to display the value of a measured quantity). When an animation imitates the movement of one or more living beings, it constitutes an automaton.
[0019] Figure 1A and Figure 1B A cam of the so-called "snail" type is also shown (reference numeral 7). The snail 7 is arranged to be driven around an axis 8 by a movement of the timepiece (not shown) via a wheel 19 fixedly attached to the snail 7. As shown, the profile of the snail 7 comprises a main portion in the form of a spiral and a discontinuity 9 in the form of a descender arranged to connect the tip of the spiral to its lowest point. The means for coordinated actuation also comprise 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. It can be seen that, in the illustrated embodiment, both the first transmission member and the second transmission member pivot on the same axis (reference numeral 21), and that their cam followers 11a and 13a are 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 with the pinions 3 and 5, respectively. Finally, the means for coordinated actuation comprise return means arranged to return the cam followers 11a and 13a to the profile of the volute 7. In the example illustrated, these return means comprise a first leaf spring (reference numeral 17).
[0020] The movement (not shown) of the watch drives the volute 7 to rotate in a direction corresponding to Figure 1A and Figure 1BIn the clockwise direction of the profile. It will 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 volute 7 with a slight offset, the cam follower 13a slightly lagging behind relative to the cam follower 11a. In this example, the offset between the two cam followers corresponds to a duration of three minutes. Since the cam 7 is driven by the movement at a speed of one revolution every twelve hours, the offset between the two cam followers corresponds to the time required for the cam to pivot 1.5°. It is worth noting that if the cam 7 is driven at a higher speed of one revolution per hour, the cam only takes 15 seconds to pivot 1.5°. Generally speaking, it is advantageous that the angle at which the cam pivots during the offset duration is less than 30°, and the angle is preferably less than 5°. Generally speaking, it is advantageous that the angle at which the cam pivots during the offset duration is greater than 1.2°, and the angle is preferably greater than 1.3°, preferably greater than 1.4°.
[0021] Now also refer to FIG. 2A to FIG. 2D It can be seen that the toothed sector 11b of the first transmission member carries the eccentric 25a, while the cam follower 13a of the second transmission member has a shoulder that serves as a bearing surface 25b. Figure 2B As shown, the eccentric 25a and the bearing surface 25b can abut against each other, thereby blocking a pivoting of the toothed sector 11b relative to the cam follower 13a in one direction. The main purpose of the stop device just described will be explained below.
[0022] like Figure 1A and Figure 1B As shown, 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 device for coordinated actuation more compact, in particular in terms of thickness. It can also be seen that the cam follower 13a is longer than the cam follower 11a and that its shape is adapted to enable it to cover the latter. Finally, it can be seen that the ends of the cam follower 13a are bent so that the two cam followers can rest simultaneously at the profile of the volute 7, with some play between the surfaces 27a, 27b of the two cam followers.
[0023] In the example shown, the second transmission member forms an integral structure, comprising two arms substantially perpendicular to each other. The two arms of the second transmission member are respectively formed by a cam follower 13a and a toothed sector 13b, which are integral. In the example shown, this is not the case for the first transmission member. In fact, FIG. 2A to FIG. 2DThe toothed sector 11b and the cam follower 11a are shown articulated to one another at the axis 21. It will be understood that the two elements can pivot about the axis 21 independently of one another. The cam follower 11a and the toothed sector 11b also share abutment means (23a, 23b). In fact, it can be seen that the cam follower 11a carries the finger 23a and the toothed sector 11b carries the pin 23b. Figure 2A and Figure 2D As shown, the pin 23b and the finger 23a are able to abut against each other so as to prevent the pivoting of the toothed sector 11b relative to the cam follower 11a in one direction. Thus, the finger 23a and the pin 23b form abutment means common to the cam follower 11a and the toothed sector 11b. However, it will be understood that different abutment means can be used. According to alternative variants, these abutment means can be of any type suitable for limiting the angular segment in which the cam follower 11a and the toothed sector 11b can pivot relative to each other.
[0024] FIG. 2A to FIG. 2D are four consecutive moments of operation of the device according to this first embodiment. In the example shown, the snail 7 is mounted in a coaxial position on the hour wheel (reference numeral 19) of the timepiece (the snail 7 is preferably made of the same material as the hour wheel 19). It therefore makes one revolution precisely in twelve hours. Still referring to the same figure, it will be noted that the first "snapshot" ( Figure 2A ) shows that the cam followers 11a and 13a reach the tip of the spiral just before the cam follower 11a descends into the discontinuity 9, and the fourth and final snapshot ( Figure 2D ) shows that the cam followers 11a and 13a are located at the bottom of the descending portion just after the cam follower 13a descends into the discontinuous portion 9.
[0025] The actuating device according to this first embodiment also comprises a second leaf spring (reference numeral 15), which is arranged with its distal end abutting against the pin 23b of the toothed sector 11b. The toothed sector of the first transmission member is thus permanently subjected to a return force which tends to cause it to pivot about the axis 21 (the direction in which the return force causes the toothed sector 11b to pivot corresponds to FIG. 2A to FIG. 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. Figure 2A and Figure 2D As shown, the force exerted by the second leaf spring 15 also has the effect of returning the cam follower 11 a to the profile of the volute 7 when the pin 23 b is in a position adjacent to the finger 23 a .
[0026] It can be seen that the cam followers 11a, 13a travel in an upward direction on a helical portion of the profile of the volute. This ascending portion is arranged to gradually ascend the two cam followers, thereby causing them to pivot about the axis 21 (along the spiral portion of the spiral). FIG. 2A to FIG. 2D When the cam follower 11a of the first transmission member pivots, its finger 23a repels the pin 23b of the toothed sector 11b against the return force exerted by the second leaf spring 15. Therefore, due to the presence of the abutment means 23a, 23b, the toothed sector 11b pivots together with the cam follower 11a in the counterclockwise direction. Finally, the pivoting of the toothed sector 11b drives the pinion 3 to rotate in the clockwise direction (as shown in FIG. Figures 2A to 2D In a similar manner, when the rising portion of the volute 7 causes the cam follower 13a of the second transmission member to rise, it causes the second transmission member to gradually pivot in the counterclockwise direction about the axis 21, and it will be appreciated that when the second transmission member pivots in this manner, the toothed sector 13b drives the pinion in the clockwise direction.
[0027] It will be understood, in particular, from the above statements that when the cam follower 11a or 13a of the same transmission member reaches the tip of the spiral portion of the volute 7, the toothed sectors 11b of the first transmission member and the toothed sectors 13b of the second transmission member each reach an extreme angular position. Furthermore, it will be understood that each time the volute 7 rotates, the two toothed sectors 11b, 13b pivot alternately from the extreme angular position associated with the tip of the volute 7 to the opposite extreme position, in one direction and in the other. Now referring to Figure 2A , it can be seen that the cam followers 11a and 13a are located exactly at the top of the spiral of the volute 7, with the cam follower 11a being located at the extreme edge of the discontinuity 9. It will be understood that, at the moment shown, the cam follower 11a has reached its maximum pivot position in the counterclockwise direction. In addition, the cooperation of the abutment means 23a and 23b causes the cam follower 11a to drive the toothed sector 11b to pivot together, so that the latter also reaches its extreme angular position in the counterclockwise direction. Finally, when the pinion 3 permanently meshes with the toothed sector 11b, it also reaches the end of its travel (in the clockwise direction).
[0028] Figure 2B The snapshot shows the device after a few minutes. The cam follower 11a of the first transmission member has now descended into the discontinuity 9, while the cam follower 13a of the second transmission member is located at the edge of the discontinuity 9. Having passed the discontinuity 9, the cam follower 11a is no longer supported by the profile of the volute 7. In this case, it is free to pivot. Therefore, its finger 23a is no longer fixed in place and the abutment means 23a, 23b are therefore inoperative. In this case, the second leaf spring 15 causes the toothed sector 11b to pivot in the clockwise direction in order to drive the pinion 3 in the counterclockwise direction. It will be remembered that in the present example, the pinion 3 is arranged to drive an animation (not shown) comprised by the timepiece.
[0029] It has been shown above that the toothed sector 11b has an eccentric 25a which is arranged to abut against a bearing surface 25b on the second transmission member, thereby preventing the toothed sector 11b from pivoting relative to the cam follower 13a beyond a certain limit. In this case, when the toothed sector 11b of the first transmission member pivots in the clockwise direction under the drive of the second leaf spring 15, the eccentric 25a abuts against the bearing surface 25b. Figure 2B As shown, the contact of the eccentric with the bearing surface interrupts the pivoting of the toothed sector 11b. Moreover, when the pinion 3 is meshing with the toothed sector, it also stops rotating when the eccentric 25a abuts the bearing surface 25b. In an advantageous manner, when the stop means 25a, 25b interrupt the pivoting of the toothed sector 11b, the precise angular position at which the pinion 3 stops is selected to coincide with a specific moment in the animation development, for example at the apex. The synchronization between the specific moment of the animation development and the interruption of the pivoting of the toothed sector 11b can be adjusted by slightly turning the eccentric.
[0030] Figure 2C The snapshot shows the device after a few minutes. The return force exerted by the first leaf spring 17 has now caused the cam follower 13a to descend into the discontinuity 9 behind the cam follower 11a. As shown, the cam follower 13a has come into contact with the bottom of the discontinuity 9 and it will be understood that, at the moment shown, it has reached its (opposite) extreme angular position in the clockwise direction. As for the other cam follower 11a, it will be understood that the cam follower 11a is not subject to the return force generated by the spring 15 as long as the pin 23b has not yet abutted against the finger 23a. At this stage, the cam follower 11a is therefore free to rotate in the space between the bottom of the discontinuity 9 and the side edge 27a of the cam follower 13a.
[0031] According to the above description, the cam follower 13a of the second transmission member is arranged to return to the profile of the volute 7 by means of the first leaf spring 17. In this case, when the cam follower 13a descends into the discontinuity 9, the first leaf spring 17 causes the second transmission member to pivot in the clockwise direction at an accelerated speed. The pivoting of the second transmission member causes the stop means 25a, 25b to disengage, so that the toothed sector 11b drives the pinion 3 in the counterclockwise direction again, thus making it possible to end the animation. In addition, when the toothed sector 13b of the second transmission member meshes with the pinion 5, the pinion is driven in the counterclockwise direction at an accelerated speed. It will be remembered that in the present example, the pinion 5 is arranged to trigger a retrograde display of the time.
[0032] Finally, refer to Figure 2D, it can be seen that the pin 23b is now in a position adjacent to the finger 23a, while the cam follower 11a rests on the profile of the snail 7, and the animation is complete. It will be understood that the exemplary device just described makes it possible to actuate the animation and the retrograde display of time in a timepiece in a coordinated manner. This device makes it possible in particular to ensure that the retrograde display of time is triggered at the desired moment of the animation's unfolding.
[0033] FIG. 3A to FIG. 3F A device for coordinated actuation of retrograde display and animation according to a second embodiment of the present invention is shown. The retrograde display includes a retrograde hour hand 41 and a retrograde minute hand 43. In the illustrated example, the retrograde pointers 41, 43 are in the form of two figures, and the hour hand figure holds an umbrella. The retrograde pointers 41, 43 are fixedly attached to two pinions with toothed fans 42, 44, and the main shafts of the toothed fans are referenced as 45 and 47. On the other hand, as will be seen in more detail below, the functions of the pointers 41, 43 in the form of figures are not limited to displaying the time. The two pointers 41, 43 are also capable of coordinated movement, the combination of which constitutes an animation. This is why these pointers are sometimes referred to as animation components rather than retrograde pointers in the following description.
[0034] Still refer to FIG. 3A to FIG. 3F , and the hour hand mobile and the minute hand mobile can also be seen, the hour hand mobile is arranged to be driven by the watch movement at a speed of one rotation every 12 hours around the main shaft 48, and the minute hand mobile is arranged to be driven at a speed of one rotation every 120 minutes. The hour hand mobile comprises a wheel 19 and an hour hand cam 51 and an animation cam 53, both of which are coaxial with the wheel 19 and fixedly attached to the wheel 19, and the cams 51, 53 are preferably as shown in FIG. Figure 3A The direction in which the hour hand moving member is driven by the watch movement corresponds to FIG. 3A to FIG. 3F clockwise direction in the figure. It can be seen that, in the conventional manner shown in retrograde, the hour cam 51 is a radial snail cam, the profile of which is formed by a main part in the form of a spiral and by a discontinuity 52 in the form of a descending part connecting the tip of the spiral with the lowest point. The radial animation cam 53 is more unusual. In fact, it consists of a ring interrupted by an opening through the wall of the ring, which forms a discontinuity 54 in the profile of the cam 53. The hour mobile 19, 51, 53 is preferably integral. The minute mobile comprises a wheel 79, a pinion 80 and a minute cam 81, which are arranged coaxially and in a fixedly attached manner. The pinion 80 meshes with the wheel 19 to drive the wheel 19. In the example shown, the minute cam 81 is in the form of a double snail. The direction in which the minute mobile is driven by the watch movement corresponds to FIG. 3A to FIG. 3F In the counterclockwise direction.
[0035] In the conventional manner of displaying the hour and minute hands in retrograde, the hands 41, 43 are controlled by an hour rack 49 and a minute rack 82, respectively. Each of the two racks 49, 82 pivots about a main axis (71 and 84, respectively) and its toothed sector meshes with a pinion 42, 44 carrying the corresponding retrograde hand 41, 43. The neck of the minute rack 82 ends in a cam follower finger 85, which is returned to the profile of the minute cam 81 by a leaf spring 83 or other spring means. It will be understood that the elements just described enable the minute cam 81 to control the retrograde minute hand 43. As previously mentioned, the minute cam 81 is driven at a speed of one revolution every two hours. However, this cam has a 2nd order rotational symmetry. Therefore, the minute rack 82 and the retrograde minute hand 43 are driven in a cycle that repeats every sixty minutes.
[0036] FIG. 3A to FIG. 3F The first transmission member is shown again, which is arranged so that the hour cam 51 can control the retrograde hour hand 41. In the example shown, the first transmission member is formed by the hour rack 49, which is pivotally mounted on the main shaft 71, and the cam follower 61, which is pivotally mounted on the main shaft 65 and is arranged to cooperate with the profile of the hour cam 51 under the action of the return leaf spring 62 or other spring means. The hour rack 49 and the cam follower 61 are mutually connected by a pin 73, which is rigidly fixed to the rod 61 and passes through the rod 61 parallel to its main shaft 65. The part of the pin 73 protruding relative to one surface of the rod 61 serves as a support point for the free end of the leaf spring 62 and therefore receives a force from the leaf spring so that the rod 61 can return to the hour cam 51. The part of the pin 73 that protrudes relative to the opposite surface of the rod 61 is interposed between the rigid arm 75 of the neck of the hour hand rack 49 and the elastic arm 76 of the same neck. The pin 73 can easily slide in the longitudinal groove formed by the arms 75 and 76 and is clamped on the rigid arm 75 by the elastic arm 76.
[0037] FIG. 3A to FIG. 3F The second transmission member is shown again, which is arranged so that the animation cam 53 can 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, which is arranged to cooperate with the profile of the animation cam 53. The animation rocker 63 pivots on the main shaft 67, and a leaf spring 55 or other spring means is again provided in order to return the cam follower finger 64 to the profile of the animation cam 53. The eccentric 89 can be seen again, which is mounted on the frame of the device 14 for coordinated actuation - typically the frame of a watch movement - and is arranged to be able to cooperate with a lug 87 on the animation rocker 63. As shown in FIG. Figure 3E As shown, the lug 87 can abut the eccentric 89, thereby preventing the animation rocker 63 from pivoting in the clockwise direction.
[0038] The animation rocker 63 carries a second pin 91 which is arranged to cooperate with the side of the hour hand rack 49 so as to drive the hour hand rack 49 in the counterclockwise direction when the animation rocker 63 pivots in the clockwise direction, that is, when the cam follower finger 64 descends into the descending portion 54 of the profile of the animation cam 53.
[0039] It can also be seen that the cam follower 61 carries a third pin 69 arranged to cooperate with a shoulder 68 of the animation rocker 63. When the cam follower 61 passes over the tip of the profile of the hour cam 51 and descends into the discontinuity 52 thereof, the pivoting of the rod 61 in the clockwise direction causes the pin 69 to cause the animation rocker 63 to pivot in the counterclockwise direction.
[0040] The hour cam 51, the animation cam 53, the cam follower 61 and the cam follower finger 64 are arranged so that the descent of the cam follower 61 is offset in time relative to the descent of the cam follower finger 64, and the descent period of the cam follower 61 is the same as the descent period of the cam follower finger 64. In a typical example, the offset between the two cam followers 61, 64 corresponds to a duration of three minutes. Since the hour hand moving member 19, 51, 53 is driven by the clock movement at a speed of one revolution every twelve hours, the offset between the two cam followers 61, 64 corresponds to the time required for the hour hand moving member 19, 51, 53 to pivot 1.5°. Generally speaking, it is advantageous that the angle at which the hour hand moving member 19, 51, 53 pivots within the offset duration is less than 30°, and the angle is preferably less than 5°. Generally speaking, it is advantageous if the angle through which the hour mobile 19 , 51 , 53 pivots during the excursion duration is greater than 1.2°, and this angle is preferably greater than 1.3°, preferably greater than 1.4°.
[0041] The device according to this second embodiment functions in the following manner. At the beginning of an operating cycle ( Figure 3A , Figure 3B and Figure 3C ), just after noon or midnight, the cam follower 61 and the cam follower finger 85 abut 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 shape, these positions are called zero positions. The rotation of the hour and minute cams 51, 81 causes the cam follower 61 to gradually rise (in the counterclockwise direction) and the cam follower finger 85 to gradually rise (in the clockwise direction). The cam follower 61 drives the hour rack 49 via its pin 73, and the hour rack 49 itself drives the hour hand 41 to rotate clockwise along the arc-shaped hour scale via the pinion 42 until (slightly less than 12 hours after the start of the cycle) the cam follower 61 reaches the tip of the hour cam 51 ( Figure 3D), which corresponds to the approximately vertical position of the hour hand 41.
[0042] The rise of the cam follower finger 85 and the minute hand rack 82 to which the minute hand cam 81 belongs causes the minute hand 43 to pivot in the counterclockwise direction along the arc-shaped minute scale via the pinion 44. Every sixty minutes, the cam follower finger 85 descends along one of the two descending portions of the minute hand cam 81, which causes the minute hand 43 to return to its zero position. Thus, the minute hand 43 moves alternately in the counterclockwise direction (gradually) and the clockwise direction (suddenly), while the hour hand 41 gradually advances in the clockwise direction. During this period, the animation rocker 63 is fixed by the pin 69 of the cam follower lever 61 (when the lever 61 abuts against the bottom of the hour hand cam 51; FIG. 3A to FIG. 3C ) or fixed by the animation cam 53 (other times; Figure 3D ), which is in an angular position that acts neither on the hour hand rack 49 nor on the minute hand rack 82.
[0043] Shortly before noon or midnight ( Figure 3D ), for example one to three minutes before noon or midnight, the cam follower 61 is almost at the tip of the hour cam 51, the cam follower finger 85 is almost at one of the two tips of the minute cam 81, and the hour and minute hands 41, 43 are close to each other, in a substantially vertical position, almost at the maximum of the arc scale. In this configuration, the pin 69 carried by the cam follower 61 is not in the pivoting path of the animation rocker 63 and its shoulder 68. The cam follower finger 64 of the animation rocker 63, which had previously slid on the animation cam 53, drops into the discontinuity 54 ( Figure 3E ), thereby triggering the animation (automaton). Specifically, the pin 91 of the animation rocker 63 contacts the hour hand rack 49 and pivots it in the counterclockwise direction. At the same time, the starting finger 66 of the animation rocker 63 contacts the arm 86 of the minute hand rack 82 to pivot the minute hand rack 82 in the clockwise direction. These displacements stop when the lug 87 of the animation rocker 63 abuts the eccentric wheel 89, driving the hour and minute hands 41, 43 to move further toward each other away from the arc-shaped hour and minute scales, giving the impression that the two characters are kissing each other. The displacement of the hour hand rack 49 by the pin 91 has no effect on the position of the cam follower 61, which continues to abut against the hour hand cam 51 under the action of its return spring 62, and the elastic arm 76 in contact with the pin 73 is deformed to allow the displacement, as Figure 3E It will be appreciated that the eccentric wheel 89 serves as a means for adjusting the relative angular positions of the minute and hour hands 41, 43 at the apex of the animation, ie the moment of the kiss.
[0044] Then( Figure 3F), after a time corresponding to the duration of the offset between the two cam followers 61 , 64 (typically three minutes, as previously mentioned), the cam follower 61 descends into the discontinuity 52 of the profile of the hour cam 51. During this descent, the pin 69 of the cam follower 61 acts on the shoulder 68 to raise the animation rocker 63 and remove any interaction between it and the hour rack 49 and the minute rack 82. By cooperating with the elastic arm 76, the pin 73 of the cam follower 61 drives the hour rack 49 in the clockwise direction. At the same time, the cam follower finger 85 descends into one of the descending portions of the minute cam 81, which corresponds to the pivoting of the minute rack 82 in the counterclockwise direction. The hour and minute hands 41 , 43 thus return abruptly from the apex of the animation to their zero position. The 12-hour cycle is terminated.
[0045] It will be appreciated that the exemplary device just described enables the animation and the retrograde display of time in a coordinated manner to be actuated in a timepiece. The device in particular enables the retrograde display of time to be triggered at the desired moment of the animation's unfolding.
[0046] The invention is not limited to a retrograde time display in combination with an animation. For example, it can be applied to a regatta watch, which includes a first function including generating a time signal just before the start of a race and a second function including generating a new time signal when the race starts.
[0047] It will also be understood that various modifications and / or improvements apparent to those skilled in the art may be made to the embodiments described in this specification without departing from the scope of the invention as defined by the appended claims. In particular, the device of the present invention may be arranged to coordinate more functions or mechanisms and may include more cams and more transmission members for this purpose. In addition, although in the second embodiment the cams 51, 53 are preferably arranged coaxially for reasons of precision, space and ease of assembly, these cams may be part of two different moving parts, such as two moving parts connected by gears, as long as they rotate at the same angular velocity and their relative angular position (e.g., adjustable by an eccentric) is selected so that the desired time offset is obtained between the descent of the cam follower rod 61 and the descent of the cam follower finger 64.
Claims
1. A device for coordinating the activation of two functions of a timepiece, the device comprising: - one or more cams (7; 51, 53), arranged to be driven by a movement of said timepiece, and the corresponding one or more profiles of said one or more cams (7; 51, 53) each comprising a discontinuity (9; 52, 54): - a first transmission member (11a, 11b; 49, 61) and a second transmission member (13a, 13b; 63), each transmission member comprising a cam follower (11a, 13a; 61, 64), the cam follower (11a; 61) is arranged to cooperate with the profile of the cam (7) or the profile of the first cam (51) of the cams (51, 53) and periodically descends into the profile of the cam (7) or the discontinuous portion (9; 52) of the profile of the first cam (51) of the cams (51, 53), and the cam follower (13a; 64) of the second transmission member is arranged to cooperate with the profile of the cam (7) or the profile of the second cam (53) of the cams (51, 53) and periodically descends into the profile of the cam (7) or the discontinuous portion (9; 52) of the profile of the first cam (51) of the cams (51, 53). The cam follower (13a; 64) of the second transmission member descends into the profile of the cam (7) or the discontinuous portion (9; 54) of the profile of the second cam (53) of the cams (51, 53), the descending period of the cam follower (13a; 64) of the second transmission member is the same as the descending period of the cam follower (11a; 61) of the first transmission member, and the descending of the cam follower (11a; 61) of the first transmission member is offset in time relative to the descending of the cam follower (13a; 64) of the second transmission member.
2. The device for coordinated actuation 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 the cam (51, 53) to rotate a predetermined angle when driven by the movement, the predetermined angle being preferably less than 30°, preferably less than 5°, and preferably greater than 1.2°, preferably greater than 1.3°, preferably greater than 1.4°.
3. The device for coordinated actuation according to claim 1 or 2, characterized in that: The one or more cams consist of a volute (7), the cam followers (11a, 13a) of the first transmission member and the second transmission member are arranged to cooperate with the profile of the volute (7), and the cam followers (11a, 13a) of the first transmission member and the second transmission member are arranged to follow the profile of the volute (7) in an offset manner, with the cam follower (11a) of the first transmission member leading relative to the cam follower (13a) of the second transmission member.
4. The device for coordinated actuation according to claim 3, characterized in that: The device comprises return means (15, 17) arranged to return the cam followers (11a, 13a) of the first and second transmission members to the profile of the volute (7), the volute (7) comprising an ascending profile terminating in a descending portion forming the discontinuity (9), and the first and second transmission members each further comprising a toothed sector (11b, 13b) arranged in sequence and pivoting alternately in one direction and the other direction from an extreme angular position associated with the tip of the profile of the volute to an opposite extreme angular position during each rotation of the volute (7).
5. The device for coordinated actuation according to claim 4, characterized in that: The first transmission member and the second transmission member share a stop device (25a, 25b), and the stop device (25a, 25b) is arranged to stop the tooth sector (11b) of the first transmission member at a predetermined intermediate angular position when the tooth sector (11b) of the first transmission member pivots in the direction of the opposite extreme angular position after the cam follower (11a) of the first transmission member descends into the discontinuity (9) of the profile of the volute (7).
6. The device for coordinated actuation according to claim 5, characterized in that: By the cam follower (13a) of the second transmission member descending into the discontinuity (9), the stop means (25a, 25b) are deactivated and the toothed sector (11b) is then free to pivot from the intermediate angular position to the opposite extreme angular position.
7. The device for coordinated actuation according to any one of claims 3 to 6, characterized in that: The first transmission member and the second transmission member pivot about the same axis (21).
8. The device for coordinated actuation according to claim 7, characterized in that: The cam followers (11a, 13a) of the first transmission member and the second transmission member are arranged to pivot about the axis (21) in the same plane.
9. The device for coordinated actuation according to any one of claims 3 to 8, characterized in that - the toothed sector (11b) and the cam follower (11a) of the first transmission member are hinged on the axis (21), so that the toothed sector (11b) and the cam follower (11a) can also pivot relative to each other around the axis (21), while the toothed sector (13b) and the cam follower (13a) of the second transmission member are fixedly attached to each other; and - The cam follower (11a) and the toothed sector (11b) of the first transmission member share abutment means (23a, 23b), which limit the angular section in which the cam follower (11a) and the toothed sector (11b) can pivot relative to each other and enable the cam follower (11a) to drive the toothed sector (11b) to pivot together when the cam follower (11a) pivots due to the rising profile of the volute (7).
10. The device for coordinated actuation according to any one of claims 3 to 9, characterized in that: The stop device comprises an eccentric (25a) carried by one of the tooth sectors (11b) of the second transmission member and the first transmission member, and a bearing surface (25b), the eccentric being carried by one of the tooth sectors (11b) of the second transmission member and the first transmission member, and the bearing surface forming part of the other of the tooth sectors (11b) of the second transmission member and the first transmission member.
11. The device for coordinated actuation according to claim 10, characterized in that The bearing surface (25b) and the eccentric wheel (25a) are arranged to be able to abut against each other, thereby preventing the toothed sector (11b) of the first transmission member from pivoting relative to the cam follower (13a) of the second transmission member in one direction.
12. The device for coordinated actuation according to any one of claims 3 to 11, characterized in that The stopping device comprises an eccentric wheel (25a) and a bearing surface (25b), wherein the eccentric wheel (25a) carries the tooth sector (11b) of the first transmission member, and the bearing surface (25b) is located on the second transmission member, and the eccentric wheel (25a) and the bearing surface (25b) are arranged to be able to abut against each other, thereby preventing the tooth sector (11b) of the first transmission member from pivoting relative to the cam follower (13a) of the second transmission member in one direction.
13. The device for coordinated actuation according to claim 1 or 2, characterized in that: The one or more cams include the first cam (51) and the second cam (53), wherein the first cam (51) is arranged to cooperate with the cam follower (61) of the first transmission member (49, 61), and the second cam (53) is arranged to cooperate with the cam follower (64) of the second transmission member (63).
14. The device for coordinated actuation according to claim 13, characterized in that The first cam and the second cam (51, 53) are coaxial and fixedly attached.
15. The device for coordinated actuation according to claim 14, characterized in that The first cam and the second cam (51, 53) form an integral component or form part of an integral component.
16. The device for coordinated actuation according to any one of claims 13 to 15, characterized in that: The first cam (51) is a volute.
17. The device for coordinated actuation according to any one of claims 13 to 16, characterized in that: The second cam (53) has a circular profile interrupted by the discontinuity (54).
18. The device for coordinated actuation according to any one of claims 13 to 17, characterized in that: The second transmission component (63) is a rocker.
19. The device for coordinated actuation according to any one of claims 13 to 18, characterized in that The first transmission member includes a rack (49) coupled to a cam follower (61) of the first transmission member.
20. The device for coordinated actuation according to claim 19, characterized in that The second transmission member (63) is arranged to move the rack (49) when a cam follower (64) of the second transmission member (63) descends into a discontinuity (54) in the profile of the second cam (53).
21. The device for coordinated actuation according to any 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 a cam follower (64) of the second transmission member (63) descends into a discontinuity (54) of the profile of the second cam (53).
22. The device for coordinated actuation according to claim 20 or 21, characterized in that: The cam followers (61) of the first transmission member are arranged in sequence, and when the cam followers (61) descend into the discontinuous portion (52) of the profile of the first cam (51), the cam followers (64) of the second transmission member (63) rise to the outside of the discontinuous portion (54) of the profile of the second cam (53).
23. The device for coordinated actuation according to any one of claims 20 to 22, characterized in that: The device comprises a third cam (81) and a third transmission member (82), the 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) descends into a discontinuity (54) of the profile of the second cam (53).
24. The device for coordinated actuation according to claim 23, characterized in that The third transmission component (82) is a rack.
25. The device for coordinated actuation 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 minute hand display.
26. The device for coordinated actuation according to any 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 hour display.
27. The device for coordinated actuation according to claim 26, characterized in that The second transmission member (63) is arranged to actuate an animation using the hand (41) of the second retrograde display.
28. Device for coordinated actuation according to claims 25 and 26, characterized in that The second transmission member (63) is arranged to actuate an animation using the hands (41, 43) of each of the first and second retrograde displays.
29. Device for coordinated actuation according to any one of the preceding claims, characterized in that One of the two functions is a function for displaying a physical quantity, and the other of the two functions is an animation function, preferably an automaton function.
30. A timepiece comprising two functions and a device for actuating said two functions in a coordinated manner as claimed in any one of the preceding claims.