Clock training device

Abstract

Clock drive device (100), in particular for a system (300) for displaying time information or information derived from the time, in particular for an instantaneous jump calendar system, comprising: - an input wheel set (10) comprising a first toothing (10a); - a main wheel (11) including a second toothing (11a) on only a part of the periphery of the main wheel, the second toothing cooperating by meshing with the first toothing, - a cam (12) linked to the main wheel (11), in particular linked with less play to the main wheel (11), in particular fixed on the main wheel (11), and having a cam profile (12a, 12b, 12c), - a cam follower (21) cooperating with the profile (12a, 12b, 12c), and - an energy accumulator (22) elastically biasing the cam follower against the cam profile (12a, 12b, 12c).

Description

[0001] The invention relates to a watch drive device. The invention also relates to a watch calendar comprising such a watch drive device. The invention further relates to a watch movement comprising such a watch drive device or such a watch calendar. The invention also relates to a timepiece comprising such a watch movement or such a watch drive device or such a watch calendar. The invention also relates to a method for operating such a watch movement or such a timepiece or such a watch drive device or such a watch calendar.

[0002] Known in the state of the art are instantaneous clock calendar systems which have a drive wheel equipped with a cam which cooperates with an energy accumulation device, such as a cam lever associated with a spring.

[0003] Driven by a drive wheel, the cam allows the energy storage device to be armed in a winding phase, and subsequently, to restore the energy during an instantaneous calendar drive phase. The cam is then driven and rotates relative to the drive wheel. The restored energy is used to drive the cam and a mechanism arranged downstream of the cam.

[0004] At the end of the instantaneous drive phase, in a catch-up phase, the cam is immobilized until it is caught and driven again by the drive wheel so as to arm the energy accumulation device.

[0005] The catch-up phase can last approximately 4 to 11 hours depending on the design of the calendar. During this catch-up phase, the drive wheel rotates idle and consumes very little energy compared to the winding phase. This results in variations in the amplitude of the watch movement oscillator (in the case of a mechanical watch movement) due to the difference in load on the drive wheel between the catch-up and winding phases respectively.

[0006] Patent application CH256366A4 discloses a wheel set for driving a date disc. The drive wheel set comprises a first wheel and a second coaxial wheel capable of being driven with different angular speeds, respectively by two integral pinions. The angular speed of the first wheel is slightly lower than that of the second wheel. The two wheels are connected to each other by a spring 14 intended to be wound as the angular offset generated by the difference in speed between said wheels increases. The teeth of the first wheel are truncated over a portion. When this portion is opposite its drive pinion, the first wheel is free to suddenly drive the date disc, under the effect of the spring being unwound. After driving, the spring is gradually rewound as soon as the teeth of the first wheel are again engaged with those of its drive pinion.The solution proposed here does not allow for optimizing the energy consumption of the movement driving such a date mechanism.

[0007] The aim of the invention is to provide a watch drive device making it possible to improve the devices known from the prior art. In particular, the invention proposes a watch drive device making it possible to distribute energy consumption as well as possible over time, in particular over a period of rotation of a drive wheel.

[0008] According to the invention, a training device is defined by claim 1.

[0009] Embodiments of the training device are defined by claims 2 to 8.

[0010] According to the invention, a clock calendar is defined by claim 9.

[0011] According to the invention, a watch movement is defined by claim 10.

[0012] According to the invention, a timepiece is defined by claim 11.

[0013] According to the invention, an operating method is defined by claim 12.

[0014] Modes of carrying out the method of operation are defined by claims 13 to 15.

[0015] The attached drawings represent, by way of example, two embodiments of a timepiece according to the invention. There Figure 1 is a view of a first embodiment of a timepiece according to the invention, a drive device being seen from the dial side. Figure 2 is a view of the first embodiment of the timepiece according to the invention, the drive device being seen from the movement side. Figure 3 is a set of views of elements taking part in the first embodiment of the training device comprising an exploded view and two perspective views. The figures 4 to 8are views of operating sequences of the drive device of the first embodiment. The Figure 9 is a set of views of the second embodiment of the training device comprising an exploded view and two perspective views. The figures 10 to 16 are views of operating sequences of the drive device of the second embodiment.

[0016] A first embodiment of a timepiece 400 is described below in detail with reference to figures 1 to 8 .

[0017] The timepiece 500 is for example a watch, in particular a wristwatch. The timepiece 500 comprises a watch movement 400 intended to be mounted in a timepiece case or box in order to protect it from the external environment.

[0018] The 400 watch movement is a mechanical movement, notably an automatic movement, or a hybrid movement or an electronic movement.

[0019] The watch movement 400 comprises a system 300 for displaying time information or information derived from the time, such as a watch calendar 300, in particular an instantaneous jump calendar.

[0020] The system 300 for displaying time or time-derived information comprises: at least one display member 200, in particular a date display member, in particular a date display disc, and a watch drive device 100, the at least one display member 200 and the drive device 100 being arranged such that the drive device 100 is capable of driving the at least one display member 200. The drive is of the instantaneous or instantaneous jump type.

[0021] The system 300 for displaying time information or information derived from the time makes it possible, for example, to display, via the at least one display member 200, at least one calendar item of information such as day, date, month, year, leap year, or moon phase information.

[0022] The at least one item of calendar information may be indicated or carried by the at least one display member 200, which may for example take the form of a hand or a disc.

[0023] The watch drive device 100 comprises: an input wheel 10 comprising a first toothing 10a; a main wheel 11 including a second toothing 11a on only a part of the periphery of the main wheel, the second toothing cooperating by meshing with the first toothing, a cam 12 linked to the main wheel 11, in particular linked with less play to the main wheel 11, in particular fixed on the main wheel 11, and having a cam profile 12a, 12b, 12c, a cam follower 21 cooperating with the profile 12a, 12b, 12c, and an energy accumulator 22 elastically returning the cam follower against the profile 12a, 12b, 12c of cam 12.

[0024] By "less play connection" we mean: a connection without play, for example a fastener, or a connection with very little assembly play, or a gear connection having gear play.

[0025] The clockwork drive device 100, in particular the cam, the first toothing and the second toothing, can be arranged so that rotations of the main wheel 11 independently of the input wheel set 10 are permitted during time ranges and caused by the action of the cam follower 21 on the cam 12. Thus, an action of the cam follower 21 on the cam 12 can cause a rotation of the main wheel 11 independently of the input wheel set 10.

[0026] As represented in particular on the Figure 3 , the instantaneous drive device 100 comprises a main mobile comprising the main drive wheel 11, but also: a drive element 13, and the cam 12. The main wheel 11, the cam 12 and the drive element 13 are integral with each other. In particular, the main wheel 11, the cam 12 and the drive element 13 are fixed to each other.

[0027] The main wheel is pivoted within a frame of the watch movement 400 or a frame of a calendar module around an axis A1. The drive element 13 is intended to directly and periodically drive the display member 200, for example by cooperating by obstacle with teeth of a toothing of the display member 200.

[0028] The instantaneous drive device 100 also comprises an energy accumulation device 20 with which the cam 12 is intended to cooperate so as to periodically accumulate and periodically restore the energy necessary for instantaneous drive of the display member 200.

[0029] The energy storage device 20 comprises: a cam follower 21 such as a cam rocker 21 pivoted within the frame, and an energy accumulator 22 such as a spring or an elastic return means 22 which makes it possible to accumulate the energy necessary for the instantaneous driving of the display member 200. In addition, the elastic return means 22 tends to return the rocker 21 against the cam 12. Thus, preferably, the rocker 21 can be constantly in contact with the cam 12.

[0030] The energy storage device 20 may be a single-piece device.

[0031] As illustrated on the Figure 4, the main drive wheel 11 is intended to be driven by a mobile 10 kinematically linked to a gear train of the watch movement 400. The mobile 10 may be part of the instantaneous drive system 100. More particularly, the main wheel 11 comprises a toothing 11a capable of cooperating with a toothing 10a of the mobile 10. Preferably, the mobile 10 rotates at a constant speed during operation of the watch movement 400.

[0032] A particularity of the solution is that the toothing 11a is interrupted or truncated on a portion 11b of the main drive wheel 11. In particular, the toothing 11a is produced on the periphery of the main wheel 11. This periphery therefore has a smooth or toothless portion. This smooth portion has, for example, a radius substantially equal to the radius of the pitch circle (as explained below). Thus, the conformation of the portion 11b means that the main wheel 11 is not driven by the mobile 10 over a given angular extent. In other words, the portion 11b makes it possible to uncouple or disengage the main wheel 11 from the mobile 10, in particular from the toothing 10a.

[0033] So, as shown on the figures 4 , 5 And 6 , the toothing 11a is driven by the mobile 10 during an arming phase, thus allowing the arming of the energy accumulation device 20. Furthermore, as shown in the figures 7And 8 , in an instantaneous drive phase, the portion 11b allows the instantaneous restitution of the energy accumulated within the energy accumulation device 20 during the previous winding phase due to the uncoupling of the main wheel 11 and the mobile 10. The instantaneous drive phase therefore corresponds to the phase in which the display member 200 is driven instantaneously by the drive element 13. During this phase, when the main wheel 11 is uncoupled or disengaged from the mobile 10, the main wheel 11 rotates and travels instantly or almost instantly the angular extent of the portion 11b until the toothing 11a is again engaged with the toothing 10a of the mobile 10. The angular extent of the portion 11b (around the axis A1) is consequently equal or substantially equal to the angular travel (around the axis A1) traveled by the cam 12 during the instant training phase.

[0034] At the time of the transition between the instantaneous jump phase and the winding phase, the drive of the main wheel 11 can be initiated with a small latency or delay due to the gear play between the teeth 11a and 10a. In other words, during the winding phase, the effective winding of the energy storage device 20 can be initiated with a delay or delay resulting from the gear play and its compensation by rotation of the mobile 10. This delay can be of the order of a few minutes. Preferably, the profiles of the teeth are chosen so as to limit or even eliminate the play as much as possible. Thus, preferably, the delay is less than 5 minutes, or even less than 3 minutes or even less than 1 minute. A backlash-free tooth or any other backlash compensation device could be used to limit or eliminate the play of this gear.Consequently, the clockwork drive device 100, in particular the cam 12, the first toothing 10a and the second toothing 11a, is arranged so as to arm the energy accumulator 22 via the cam follower 21 in a substantially permanent manner, with the exception of drive phases during which the cam 12 is driven by the energy accumulator 22 via the cam follower 21. For example: . neglecting the gear backlashes and considering a jump of 1 / 25 e< of a second, the duration of the winding corresponds to 99.99% of the rotation period of the main wheel 11, considering a delay of 1 minute due to the gear backlashes, the duration of the winding corresponds to 99.9% of the rotation period of the main wheel 11, considering a delay of 3 minutes due to the gear backlashes, the duration of the winding corresponds to 99.8% of the rotation period of the main wheel 11, and considering a delay of 5 minutes due to the gear backlashes, the duration of the winding corresponds to 99.7% of the rotation period of the main wheel 11.

[0035] More generally, from one phase to the next, the meshing transitions between the teeth 10a and the teeth 11a are dimensioned so as to be as continuous as possible, without abrupt interruption or without significant disturbance with regard to the energy consumption of the watch movement 400, and thus avoid variations in the amplitude of the oscillator (in the hypothesis of a mechanical watch movement). Of course, the geometries of the teeth 10a and 11a are chosen so as to allow their successive disengagement and meshing, from one phase to the next. To do this, the profile of the teeth 11a can in particular be corrected or adapted at the start and / or end of the drive.

[0036] It is intended that the winding phase and the instantaneous drive phase follow one another indefinitely so that the winding phase is effective for substantially the entire rotation period of the main wheel 11, with the exception of the instantaneous drive phase and the potential delay caused by the gear backlashes during the transition between the instantaneous jump phase and the winding phase. In other words, the instantaneous drive device 100 is provided so as to allow the winding of the energy storage device 20 in a substantially permanent manner, over substantially the entire rotation period of the main drive wheel 11, knowing that the instantaneous drive and backlash compensation phases are extremely brief.

[0037] In a first embodiment, the instantaneous drive device 100 is provided to allow instantaneous drive of a date calendar system 300 comprising a date disc 200 indexed by a jumper.

[0038] The drive element 13 may be a date finger 13 intended to cooperate with a toothing 201 of the date disc 200 during the instantaneous drive phase. The date finger 13 is here fixed, in particular welded, to a core 16 itself driven and / or riveted onto the cam 12. The main drive wheel 11 is also driven and / or riveted onto the core 16.

[0039] The core 16 is pivoted on the frame around the axis A1. Preferably, at least one indexing means 17 such as a pin 17 is arranged within the main wheel set so as to angularly index the main wheel 11 with the cam 12 and the date finger 13.

[0040] The profile of the cam 12 which cooperates with the energy accumulation device 20 successively comprises an arming portion 12a, a restitution portion 12b and a stop portion 12c. The functionalities of these portions are described in more detail below.

[0041] The rotation period of the main drive wheel 11 is 24 hours, so as to allow the calendar system 300 to be driven by at least one step per day. In other words, for each rotation period of the main wheel 11, the instantaneous drive device 100 will be exclusively and successively in the winding phase or in the instantaneous drive phase (excluding any adjustments to the tooth sets).

[0042] The angular extent of the portion 11b corresponds to the angular travel that the cam 12 travels instantaneously relative to the axis A1, in the instantaneous drive phase. In other words, it corresponds to the angular travel that the cam 12 travels during the successive cooperation of the cam rocker 21 with the restitution portion 12b and with the stop portion 12c. In addition, the angular extent of the periphery of the main wheel 11 without teeth is equal or substantially equal to the angular travel that the cam 12 travels when it is driven by the energy accumulator 22 via the cam follower 21. The angular extent of the periphery of the main wheel comprising the second toothing 11a is substantially equal or equal to the angular travel that the cam 12 travels in a trailing manner in the winding phase, when the cam rocker 21 cooperates with the winding portion 12a.

[0043] The transmission ratio between the main wheel 11 and the mobile 10 is chosen so that the toothing 10a drives the entire toothing 11a over a duration or period corresponding substantially to the rotation period of the main wheel 11. In other words, the rotation period of the main wheel 11 comprises a trailing rotation defined by the angular extent of the toothing 11a and an instantaneous rotation defined by the angular extent of the portion 11b. Consequently, the angular speed of the main wheel 11 is not constant over its entire rotation period.

[0044] The cam lever 21 cooperates with the cam 12 via a bearing, more particularly a ruby ​​stone or roller 23. The roller 23 makes it possible to reduce the friction torque induced by the bearing force of the lever 21 against the cam 12. Consequently, this roller 23 makes it possible to reduce the energy consumption and the amplitude losses of the oscillator of the watch movement 400 (in the case of a mechanical watch movement).

[0045] The drive device is therefore arranged so that: the cam 12 is driven by an action of the energy accumulator 22 via the cam follower 21 over a first angular extent, corresponding to the cam profile portions 12b, 12c, and the cam 12 supplies energy to the energy accumulator 22 via the cam follower over a second angular extent, corresponding to the cam profile portion 12a, which is complementary to the first angular extent. Arming phase

[0046] During the arming phase, as illustrated by the succession of figures 4 to 6 , the rocker 21, in particular the roller 23, leaves the stop portion 12c and rests on the winding portion 12a. This portion 12a is shaped so as to wind the energy accumulation device 20 and thus to accumulate the energy necessary for the instantaneous driving of the display member 200 by at least one step. During the winding phase, the cam 12 is driven by the main drive wheel 11 in a clockwise direction by means of the cooperation of the teeth 10a of the mobile 10 with the teeth 11a.

[0047] Preferably, the winding portion 12a is shaped so as to generate a minimized and constant consumption and loss of amplitude of the oscillator (in the case of a mechanical watch movement). In other words, the winding portion 12a makes it possible to obtain a minimized and constant winding torque at the main drive wheel 11. Training phase

[0048] As shown in the Figure 6, when the lever 21, in particular the roller 23, reaches the top of the cam 12, at the end of the winding portion 12a, at the exact moment of the transition with the restitution portion 12b, the lever 21, in particular the roller 23, instantly travels the restitution portion 12b until reaching the stop portion 12c. This transition also corresponds substantially to the moment when the toothing 10a disengages from the toothing 11a and is opposite the portion 11b. The main wheel 11 is then uncoupled from the mobile 10. From then on, the main wheel 11 can freely and instantly travel, in a clockwise direction, the entire angular extent of the portion 11b necessary for the drive phase.

[0049] Ideally, uncoupling and cam apex passage should occur simultaneously. In practice, this is not possible. Uncoupling cannot occur just before the apex passage, otherwise there is a risk that the wheel set 10 can no longer drive the main wheel 11. Uncoupling must therefore occur just after crossing the cam apex or the start of the jump. Because at the time of crossing the cam apex, only the last tooth of the toothing 11a is still engaged with the toothing 10a and at the end of the drive, this tooth can freely exit the toothing 10a just after crossing the cam apex.

[0050] During the training phase, as illustrated in the Figure 7, the energy stored by the energy accumulation device 20 is restored to allow the rotation of the main wheel and consequently, the instantaneous driving of the display member 200 by the date finger 13. In other words, at midnight, the cam 12 and the date finger 13 become motors thanks to the restitution of the accumulated energy.

[0051] At the end of the drive phase, it is necessary for the date finger 13 to be stopped and remain positioned in an interference position with the toothing 201 of the date disc 200 in order to obstruct it and thus avoid an additional untimely jump due to its inertia and the considerable energy which is released during this phase.

[0052] To do this, as illustrated in the figure 8, the rocker 21, in particular the roller 23, is located on the stop portion 12c which is dimensioned so as to dissipate the residual kinetic energy after the driving of the display member 200. The stopping of the display member 200 is also instantaneous. In other words, the instantaneous driving phase includes the stopping of the display member 200.

[0053] From then on, the teeth 10a of the pinion 10 are again within reach of the teeth 11a so as to allow a new meshing and so as to initiate a new winding phase.

[0054] Preferably, at least a first tooth of the toothing 11a is optimized so as to limit the gear play with the toothing 10a, and reduce the transition time between respectively the instantaneous jump phase and the arming phase.

[0055] In a complementary or alternative manner, at least a first tooth of the toothing 11a can in this phase be used to allow the partial or total dissipation of said residual kinetic energy. Said tooth can consequently have an optimized geometry allowing better support of the dissipation of energy. Relative to the rest of the toothing 11a, the first tooth can in particular have a greater thickness and / or an asymmetrical profile allowing better distribution of the stresses, and therefore limit the stress concentrations on said tooth so as to present better resistance. Setting the time in reverse

[0056] Advantageously, in order to avoid desynchronization between the main wheel 11 and the gear train of the watch movement 400, in particular when setting the time in the opposite direction of operation, the conformation of the portion 11b with the toothing 10a is provided so as to prevent the rotation of the latter, like a Maltese cross. Concretely, the portion 11b has a portion of cylinder concentric to the axis A1 with a diameter close to the primitive diameter of the toothing 11a so as to be capable of cooperating with the adjacent flanks of two teeth of the toothing 10a and prevent its rotation.

[0057] Alternatively or additionally, the rotation of the mobile 10 in the opposite direction of operation and the driving of the display member 200 in the opposite direction can be prevented by a freewheel or a one-way coupling arranged between said mobile and the gear train of the watch movement 400. Of course, the one-way coupling must be shaped so as to maintain the synchronization of the triggering of the instantaneous drive phases with the gear train of the watch movement 400.

[0058] A second embodiment of a timepiece 400 is described below in detail with reference to figures 9 to 16 .

[0059] This second embodiment advantageously comprises the same means or substantially the same means as those of the first embodiment except that it is in particular additionally provided with an auxiliary mobile preventing the desynchronization of the main wheel 11 relative to the gear train of the clockwork movement 400. The auxiliary mobile also allows the display member 200 to be driven when setting the time in the opposite direction of operation.

[0060] The auxiliary wheel is also pivoted within the frame. The auxiliary wheel comprises an auxiliary drive wheel 15 constantly driven by the gear train of the watch movement 400. The auxiliary drive wheel 15 is capable of cooperating with an elastic device 14 fixed to the main wheel or integral with the main wheel.

[0061] More particularly, in this embodiment, the auxiliary mobile is coaxial with the main mobile. The auxiliary drive wheel 15 pivots around the core 16. The elastic device 14 is a spiral-shaped spring 14 whose inner end is driven or riveted onto the core 16 secured to the main wheel 11 and the cam 12. The outer end 14a of the spring 14 is capable of cooperating with an angular stop 15b arranged on the auxiliary drive wheel 15.

[0062] The use of the cooperation of the auxiliary drive wheel 15 with the spring 14 is explained in detail below.

[0063] In this second embodiment, the mobile 10 comprises an auxiliary toothing 10b constantly meshing with a toothing 15a of the auxiliary drive wheel 15 so that its rotation speed is constant and entirely synchronized with the gear train of the watch movement 400.

[0064] The transmission ratio between the pinion 10 and the auxiliary drive wheel 15 is chosen so that the latter has the same rotation period as the main drive wheel 11. It should be noted that the auxiliary drive wheel 15 performs a trailing rotation, at constant speed, over its entire rotation period, unlike the main drive wheel 11 which performs a trailing rotation of an angular extent defined by the toothing 11a, and an instantaneous rotation of an angular extent defined by the portion 11b. As a result, the duration or period in which the toothing 10a is engaged with the toothing 11a is identical or substantially identical to the rotation period of the auxiliary drive wheel 15.

[0065] Therefore, in the arming phase, the angular speed of the auxiliary wheel 15 is higher than that of the main wheel 11. As explained in more detail below, relative to the auxiliary wheel 15, the main wheel 11 catches up with its angular offset, accumulated gradually during the arming phase, during the instantaneous drive phase.

[0066] The operation of the second embodiment is substantially the same as that of the first embodiment. Only the cooperation of the spring 14 with the auxiliary drive wheel 15 provides new functionalities explained below.

[0067] Alternatively, in this second embodiment, the main mobile and the auxiliary mobile of the drive device could not be coaxial, but pivoted on two separate axes, preferably parallel. They would then be connected for example by a gear.

[0068] Alternatively, in this second embodiment, the elastic device 14 could comprise a rocker or a ratchet cooperating with a spring element. Arming phase

[0069] In the second embodiment, at the beginning of the arming phase, immediately after the end of the training phase illustrated in Figure 10 , the free end 14a of the spring 14 is substantially in contact with the angular stop 15b of the auxiliary drive wheel 15.

[0070] Therefore, given that the angular speed of the auxiliary wheel 15 is slightly higher than that of the main wheel 11, the angular stop 15b is progressively further and further away from the free end 14a, as the energy accumulation device is armed as illustrated in the Figure 11 .

[0071] At the end of the arming phase, the angular difference between the free end 14a and the angular stop 15b corresponds or corresponds substantially to the angular extent of the portion 11b and therefore to the angular travel that the cam 12 travels during the instantaneous drive phase.

[0072] During the drive phase, the main wheel, in particular the main wheel 11, the cam 12 and the spring 14, instantly travel the angular travel necessary to drive the display member 200. As a reminder, said angular travel corresponds to the angular extent of the portion 11b and consequently to the maximum angular difference between the free end 14a and the angular stop 15b. Said angular difference is therefore instantly taken up during the drive phase. The free end 14a and the angular stop 15b are again in contact or substantially in contact at the end of this phase.

[0073] In a complementary or alternative manner, the elastic device 14 can be shaped so as to allow partial or total dissipation of the residual kinetic energy after the display member 200 has been driven, i.e. at the end of the drive phase.

[0074] This second embodiment advantageously allows the display member 200 to be driven in the opposite direction of operation, without the risk of the main wheel 11 becoming desynchronized from the gear train of the watch movement 400. To do this, unlike the first embodiment, the portion 11b does not cooperate with the mobile 10 in the manner of a Maltese cross, but it is out of reach of the latter. For example, the portion 11b is constituted by a portion of cylinder having a radius equal or substantially equal to the radius of the foot circle of the toothing 11a.

[0075] When the gear train of the watch movement is operated in the reverse direction of operation, the auxiliary toothing 10b drives the toothing 15a of the auxiliary wheel in the counterclockwise direction, and the toothing 10a drives the toothing 11a of the main wheel until the portion 11b is opposite the pinion 10, in other words, until the lever 21, in particular the roller 23, is on the stop portion 12c. From then on, the toothing 10a rotates in the void and no longer allows the main wheel 11 to be driven in the reverse direction. As illustrated in the Figure 14, the main wheel 11 is then driven by the auxiliary wheel 15 via the spring 14 thanks to its free end 14a in contact with the angular stop 15b. Of course, the elastic device 14 is dimensioned so as to have sufficient angular rigidity to overcome the torque generated by the cooperation of the energy accumulation device 20 with the restitution portion 12b, and thus allow the display member 200 to be driven in the opposite direction.

[0076] Once the restitution portion 12b has been completely traversed in the opposite direction, at the exact moment of the transition with the winding portion 12a, the toothing 10a cooperates again with the toothing 11a of the main wheel 11. From then on, the spring 14 begins to wind as a result of the slight difference in angular speed between the main wheel 11 and the auxiliary wheel 15. The maximum winding level of the spring 14 is reached when the toothing 10a is again opposite the portion 11b, as illustrated in the figure. Figure 15 The deformation or angular displacement of the free end 14a corresponding to its maximum reinforcement is equal or substantially equal to the angular travel that the cam 12 travels during the instantaneous drive phase.

[0077] At this instant, the main wheel 11 is uncoupled from the mobile 10 and the energy stored in the spring 14 is, consequently, restored so as to drive the main wheel 11 and the display member 200 instantly or substantially instantly in the opposite direction. The elastic device 14 is therefore also dimensioned so as to accumulate sufficient energy so that the lever 21, in particular the roller 23, can raise the restitution portion 12b in the opposite direction of operation.

[0078] By continuing to operate the gear train of the watch movement 400 in the opposite direction, a new winding phase of the elastic device 14 can then be initiated thanks to the cooperation of the teeth 10a of the mobile 10 with the teeth 11a of the main wheel 11.

[0079] With the second embodiment, setting the time in the reverse direction thus allows a first dragging drive of the display member 200 then, successively, instantaneous or substantially instantaneous drives in the reverse direction.

[0080] It should be noted that the energy required to wind the elastic device 14 is provided by the user when setting the time in the opposite direction. In other words, this energy is not provided by the watch movement 400.

[0081] The invention also relates to a method of operating a watch drive device 100 as described previously. As seen previously, the operating method comprises winding the energy accumulator 22 via the cam follower 21 in a substantially permanent manner, with the exception of drive phases during which the cam 12 is driven by the energy accumulator 22 via the cam follower 21.

[0082] Advantageously, the duration of the winding corresponds to at least 90% of the time of the rotation period of the main wheel 11 of the watch drive device 100, or even at least 99%, or even at least 99.5%, or even substantially 100%, of the time of the rotation period of the main wheel 11 of the watch drive device 100.

[0083] Preferably, the method comprises at least one iteration of the following steps, in particular several iterations of the following steps: meshing of the first toothing 10a and the second toothing 11a, so as to drive the cam 12 allowing the energy accumulator 22 to be armed, then disengaging of the first toothing 10a and the second toothing 11a, and driving of the cam 12 by the energy accumulator 22 via the cam follower 21.

[0084] The proposed solution advantageously makes it possible to smooth the energy consumption of the watch movement 400 during the winding phase, which corresponds substantially to the rotation period of the main drive wheel 11 with the exception of the instantaneous drive phase and the potential delay caused by the gear play during the transition between the instantaneous jump phase and the winding phase. Consequently, the energy consumed and therefore the amplitude losses of the balance can be constant or substantially constant, unlike the known solutions of the state of the art.

[0085] Furthermore, since the energy required for instantaneous driving of the display member 200 can be accumulated over a longer duration or rotation period than those of known solutions, it is also possible to reduce the instantaneous consumption for the same amount of total accumulated energy. By increasing the arming duration from 13 hours to 24 hours, it is for example possible to reduce the arming power by 46%. By increasing the arming duration from 20 hours to 24 hours, it is for example possible to reduce the arming power by 17%.

[0086] Advantageously, the instantaneous drive device 100 also allows direct drive of the display member 200, with the exclusive use of a drive element 13. Indeed, the solution does not require a rocker arranged at the interface of said members.

[0087] Of course, the solutions are not limited to a simple calendar system, but are also particularly suitable for calendar systems requiring, for example, more energy, such as an annual calendar or a perpetual calendar. More generally, the solutions can be applied to any display system with instantaneous jumps of time information or information derived from the time.

[0088] In the described embodiments, it is intended that the calendar system 300 is driven at least one step for each rotation period of the main drive wheel 11. However, regardless of the embodiment or variant, the instantaneous drive device could be adapted to drive the display system for each multiple or each sub-multiple of the rotation period of the main drive wheel 11. Of course, the geometries of the cam 12 and the main wheel 11 must be provided accordingly.

[0089] Regardless of the embodiment or variant, the cam 12 could be replaced by a simple geometry, such as a pin, cooperating with a profile, similar to a cam profile, provided on the cam follower 21 of the energy storage device 20.

[0090] Regardless of the embodiment or variant, the teeth of the mobile 10 and the main wheel 11 could be produced on several distinct levels, in particular first and second levels. This makes it possible to distribute the drive by judiciously truncating certain teeth of the first level and / or the second level so as to optimize the successive meshing and dismeshment of these teeth between the winding and driving phases. This configuration can be particularly advantageous in the case where the mobile 10 would comprise a lot of teeth and / or in the case where the difference in primitive diameter between the mobile 10 and the main wheel 11 would be too small. This configuration can also make it possible to optimize the tooth profiles so as to limit, or even eliminate as much as possible, the gear play during the transition between respectively the instantaneous jump phase and the winding phase.In a complementary or alternative manner, this conformation on two or more levels of the teeth of the mobile 10 and the main wheel 11 could also be particularly advantageous for, for example, achieving a Maltese cross type function on a first level and a meshing on a second level.

[0091] Regardless of the embodiment or variant, preferably, the drive device, in particular the profile of the cam 12, is arranged so that the mechanical power supplied to the energy accumulator 22 is constant or substantially constant throughout the duration or substantially throughout the duration during which the cam 12 is not driven by the energy accumulator 22 via the cam follower 21.

[0092] Preferably, by "instantaneous" we mean an action having a duration of the order of one or more fractions of a second, typically about one hundredth of a second or about one twenty-fifth of a second or even about one tenth of a second.

[0093] In contrast, by "dragging" we describe an action, such as a movement, which is slow and regular, lasting for example at least several seconds.

Claims

1. Clock drive device (100), in particular for a system (300) for displaying time information or information derived from the time, in particular for an instantaneous jump calendar system, comprising: - an input wheel set (10) comprising a first toothing (10a); - a main wheel (11) including a second toothing (11a) on only a part of the periphery of the main wheel, the second toothing cooperating by meshing with the first toothing, - a cam (12) linked to the main wheel (11), in particular linked with less play to the main wheel (11), in particular fixed on the main wheel (11), and having a cam profile (12a, 12b, 12c), - a cam follower (21) cooperating with the profile (12a, 12b, 12c), and - an energy accumulator (22) elastically biasing the cam follower against the cam profile (12a, 12b, 12c).

2. A watch drive device (100) according to claim 1, characterized in thatthe angular extent of the periphery of the main wheel comprising the second toothing (11a) is equal or substantially equal to the angular travel that the cam (12) travels when it is not driven by the energy accumulator (22) via the cam follower (21) and / or the angular extent of the periphery of the main wheel (11) without toothing is equal or substantially equal to the angular travel that the cam (12) travels when it is driven by the energy accumulator (22) via the cam follower (21), and / or in that the clockwork drive device (100), in particular the cam, the first toothing and the second toothing, is arranged so that an action of the cam follower (21) on the cam (12) causes a rotation of the main wheel (11) independently of the input wheel (10).

3. Watch drive device (100) according to claim 1 or 2, characterized in thatthe clockwork drive device (100), in particular the cam (12), the first toothing (10a) and the second toothing (11a), is arranged so as to arm the energy accumulator (22) via the cam follower (21) in a substantially permanent manner, with the exception of drive phases during which the cam (12) is driven by the energy accumulator (22) via the cam follower (21).

4. Watch drive device (100) according to one of the preceding claims, characterized in that the drive device is arranged so that: - the cam (12) is driven by an action of the energy accumulator (22) via the cam follower (21) over a first angular extent, and - the cam (12) supplies energy to the energy accumulator (22) via the cam follower over a second angular extent which is complementary to the first angular extent.

5. Watch drive device (100) according to one of the preceding claims, characterized in thatthe drive device, in particular the profile of the cam (12), is arranged such that the mechanical power supplied to the energy accumulator (22) is constant or substantially constant throughout the duration or substantially throughout the duration during which the cam (12) is not driven by the energy accumulator (22) via the cam follower (21).

6. Watch drive device (100) according to one of the preceding claims, characterized in that the cam follower (21) comprises a rocker (21).

7. Watch drive device (100) according to one of the preceding claims, characterized in that the energy accumulator (22) comprises a spring (22), in particular a leaf spring.

8. Watch drive device (100) according to one of the preceding claims, characterized in thatthe cam (12) is kinematically linked to a drive element (13) of a time information display element (200), in particular fixed to a drive element (13) of a time information display element (200), such as a finger (13), cooperating with a toothing (201) of a time information display element (200).

9. Clock calendar (300), in particular a simple date calendar or an annual date calendar or a perpetual date calendar, comprising a clock drive device (100) according to one of the preceding claims, the calendar comprising an element for displaying time information (200), such as a disc bearing numbers, including teeth (201).

10. Watch movement (400) comprising: - a watch drive device (100) according to one of claims 1 to 8, and / or - a watch calendar (300) according to the preceding claim.

11. Timepiece (500), in particular wristwatch, comprising: - a watch movement (400) according to claim 10, and / or - a watch calendar (300) according to claim 9, and / or - a watch drive device (100) according to one of claims 1 to 8.

12. A method of operating a watch drive device (100), the watch drive device (100) comprising: - a cam (12), - a cam follower (21), and - an energy accumulator (22) biasing the cam follower (21) against the cam (12), the method comprising winding the energy accumulator (22) via the cam follower (21) substantially permanently, with the exception of drive phases in which the cam (12) is driven by the energy accumulator (22) via the cam follower (21).

13. Operating method according to the preceding claim, characterized in thatthe duration of the winding corresponds to at least 90% of the time of the rotation period of the main wheel (11) of the watch drive device (100), or even at least 99%, or even at least 99.5%, or even substantially 100%, of the time of the rotation period of the main wheel (11) of the watch drive device (100).

14. Operating method according to claim 12 or 13, in particular a method of operating a timepiece (500) according to claim 11 or a watch movement (400) according to claim 10 or a watch calendar (300) according to claim 9 or a watch drive device (100) according to one of claims 1 to 8, the method comprising at least one iteration of the following steps: - meshing of a first toothing (10a) and a second toothing (1 1a) so as to drive the cam (12) making it possible to arm the energy accumulator (22), then - disengaging of the first toothing (10a) and the second toothing (1 1a) and driving of the cam (12) by the energy accumulator (22) via the cam follower (21).

15. Operating method according to one of claims 12 to 14, characterized in that the cam drive (12) is an instantaneous drive.

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