Timepiece drive device

Abstract

To provide a timepiece drive device for a system for displaying time-based or time-derived information, in particular for an instantaneous-jump calendar system.SOLUTION: A timepiece drive device 100 includes: an input mobile 10 which includes a first set of teeth 10a; a main wheel 11 which includes a second set of teeth 11a only over part of a periphery of the main wheel; a cam 12 which is connected to the main wheel, notably connected to the main wheel with minimum clearance, in particular fixed to the main wheel, and which has a cam profile 12a, 12b, 12c; a cam follower 21 which interacts with the profile; and an energy accumulator which elastically returns the cam follower against the profile of the cam.SELECTED DRAWING: Figure 4

Description

Technical Field

[0001] The present invention relates to a timepiece driving device. The present invention also relates to a timepiece calendar including the timepiece driving device. The present invention further relates to a timepiece movement including the timepiece driving device or the timepiece calendar. The present invention also relates to a timepiece including the timepiece movement, the timepiece driving device, or the timepiece calendar. The present invention also relates to a method of operating the timepiece movement, the timepiece, the timepiece driving device, or the timepiece calendar.

Background Art

[0002] The prior art discloses an instantaneous timepiece calendar system having a drive movable part provided with a cam that interacts with an energy storage device, such as a cam lever associated with a spring.

[0003] The cam driven by a drive gear enables the energy storage device to be filled during the filling stage and continuously returns energy during the instantaneous drive stage of the calendar. Thereafter, the cam is driven and rotates relative to the drive gear. The returned energy is used to drive the cam and a mechanism disposed downstream of the cam.

[0004] During the compensation stage after the instantaneous drive stage, the cam is immobilized until it is caught up by the drive gear and driven again by the drive gear to fill the energy storage device.

[0005] The compensation stage may last about 4 to 11 hours depending on the design of the calendar. During the compensation stage, the drive gear rotates without any load and consumes a very small amount of energy compared to the filling stage. This leads to fluctuations in the amplitude of the oscillator of the timepiece movement (assuming a mechanical timepiece movement) due to the difference in the load applied to the drive gear between the respective stages of compensation and filling.

[0006] Patent Document 1 discloses a drive movable part for driving a date disk. The drive movable part includes a first gear and a second gear that are coaxial and can be driven at different angular velocities by two essential pinions respectively. The angular velocity of the first gear is slightly lower than that of the second gear. The two gears are interconnected by a spring 14 which is intended to be wound up incrementally by an angular offset caused by the difference in speed between the gears. The tooth row of the first gear is cut off at the tip in a part. When the said part faces its drive pinion, the first gear can drive the date disk suddenly under the influence of the released spring. After driving, the spring is gradually rewound as soon as the tooth row of the first gear re-engages with the tooth row of its drive pinion. The solution proposed by the patent document does not make it possible to optimize the energy consumption of the movement driving such a date mechanism.

Prior Art Documents

Patent Documents

[0007]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0008] An object of the present invention is to provide a timepiece drive device that improves the device known from the prior art. In particular, the present invention provides a timepiece drive device that optimally distributes energy consumption over time, particularly over the rotation period of the drive gear.

Means for Solving the Problems

[0009] According to the present invention, the drive device is defined in claim 1.

[0010] Embodiments of the drive device are defined in claims 2 to 8.

[0011] According to the present invention, the timepiece calendar is defined in claim 9.

[0012] According to the present invention, the timepiece movement is defined in claim 10.

[0013] According to the present invention, the timepiece is defined in claim 11.

[0014] According to the present invention, the operating method is defined in claim 12.

[0015] Embodiments of the operating method are defined in claims 13 to 15.

[0016] The accompanying drawings illustrate, by way of example, two embodiments of a timepiece according to the present invention.

Brief Description of the Drawings

[0017]

Figure 1

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Figure 16

DETAILED DESCRIPTION OF THE INVENTION

[0018] The first embodiment of the timepiece 500 will be described in detail below with reference to FIGS. 1 to 8.

[0019] The timepiece 500 is, for example, a small timepiece, particularly a wristwatch. The timepiece 500 includes a timepiece movement 400 that is intended to be mounted within a timepiece casing or case to protect itself from the external environment.

[0020] The timepiece movement 400 is a mechanical movement, particularly an automatic movement, or a hybrid movement, or an electronic movement.

[0021] The timepiece movement 400 includes a timepiece calendar 300, particularly a system 300 that displays time-based or time-derived information, such as an instantaneous jump calendar.

[0022] The system 300 that displays time-based or time-derived information - at least one display member 200, particularly a member that displays the day of the month, particularly a disk that displays the day of the month, and - a timepiece drive device 100, and includes At least one display member 200 and a drive device 100 are arranged such that the drive device 100 can drive at least one display member 200. The drive is of the instantaneous or instantaneous jump type.

[0023] A system 300 for displaying time-based or time-derived information enables, for example, at least one item of calendar information, such as information regarding the day of the week, day of the month, month, year, leap year, moon phase, to be displayed via at least one display member 200.

[0024] At least one item of calendar information may be indicated or borne by at least one display member 200, which may take the form of, for example, a hand or a disk.

[0025] The clock drive device 100 - an input movable part 10 including a first tooth row 10a, and - a main gear 11 including a second tooth row 11a only over a part around the main gear, the second tooth row being in meshing engagement with the first tooth row, and - a cam 12 connected to the main gear 11, especially connected to the main gear 11 with a minimum gap, especially fixed to the main gear 11, and having cam contours 12a, 12b, 12c, and - a cam follower 21 interacting with the contours 12a, 12b, 12c, and - an energy accumulator 22 that elastically returns the cam follower to the contours 12a, 12b, 12c of the cam 12, and includes.

[0026] "Connected with a minimum gap" means - a connection without a gap, such as a fixed connection, or - a connection having a very small assembly gap, or - a meshing connection showing a meshing gap, and is understood to mean.

[0027] The clock drive device 100, particularly the cam, the first tooth row, and the second tooth row, may be arranged such that the rotation of the main gear 11, which is independent of the input movable part 10, is possible within a time range and is caused by the action of the cam follower 21 on the cam 12. Therefore, the action of the cam follower 21 on the cam 12 can cause the main gear 11 to rotate independently of the input movable part 10.

[0028] In particular, as shown in FIG. 3, the instantaneous drive device 100 includes a main movable part including the main drive gear 11, - the drive element 13, and - the cam 12, also includes. The main gear 11, the cam 12, and the drive element 13 are fixed to each other. In particular, the main gear 11, the cam 12, and the drive element 13 are fixed to each other.

[0029] The main movable part is pivoted within the frame of the clock movement 400 or the frame of the calendar module around the axis A1. The drive element 13 is intended to directly and periodically drive the display member 200 by interacting, for example, by interfering with the teeth of the tooth row of the display member 200.

[0030] The instantaneous drive device 100 also includes an energy storage device 20 in which the cam 12 is intended to interact in order to periodically store and periodically return the energy required for the instantaneous drive of the display member 200.

[0031] The energy storage device 20 - includes a cam follower 21, such as a cam lever 21 pivoted within the frame, and - an energy accumulator 22, such as a spring or elastic return means 22 that enables the storage of the energy required for the instantaneous drive of the display member 200. In addition, the elastic return means 22 tends to return the lever 21 to the cam 12. Therefore, optionally, the lever 21 may be in constant contact with the cam 12.

[0032] The energy storage device 20 may be integrated.

[0033] As shown in FIG. 4, the main drive gear 11 is intended to be driven by a movable part 10 kinematically connected to the gear train of the clock movement 400. The movable part 10 may be part of an instantaneous drive system 100. More specifically, the main gear 11 includes a tooth row 11a that can interact with the tooth row 10a of the movable part 10. Optionally, the movable part 10 rotates at a constant speed during the operation of the clock movement 400.

[0034] A specific feature of the solution is that the tooth row 11a is interrupted or the tip is cut off over a part 11b of the main drive gear 11. In particular, the tooth row 11a is formed around the main gear 11. For this reason, the periphery has a flat part or a part without a tooth row. The flat part has a radius that is substantially equal to the radius of the pitch circle (as will be described below), for example. As a result, the shaping of the part 11b means that the main gear 11 is not driven by the movable part 10 over a predetermined angular range. In other words, the part 11b enables the main gear 11 to be separated from the movable part 10, in particular from the tooth row 10a, or to be separated from the meshing engagement with the movable part 10, in particular with the tooth row 10a.

[0035] For this reason, as shown in FIGS. 4, 5, and 6, the tooth row 11a is driven by the movable part 10 during the filling stage, thereby enabling the energy storage device 20 to be filled. Further, as shown in FIGS. 7 and 8, during the instantaneous drive stage, due to the disconnection between the main gear 11 and the movable part 10, the part 11b can instantaneously return the energy stored in the energy storage device 20 during the preceding filling stage. For this reason, the instantaneous drive stage corresponds to the stage in which the display member 200 is instantaneously driven by the drive element 13. During this stage, when the main gear 11 is disconnected from the movable part 10 or separated from the meshing engagement with the movable part 10, the main gear 11 rotates, and until the tooth row 11a is re-engaged with the tooth row 10a of the movable part 10a, the angular range of the part 11b moves instantaneously or substantially instantaneously. As a result, the angular range (around the axis A1) of the part 11b is equal to or substantially equal to the angular movement (around the axis A1) covered by the cam 12 during the instantaneous drive stage.

[0036] At the transition between each of the instantaneous jump stage and the filling stage, due to the meshing gap between the tooth rows 11a and 10a, it is possible to start driving the main gear 11 with a short waiting time or a short delay. In other words, during the filling stage, effective filling of the energy storage device 20 can be started by the delay or time difference caused by the meshing gap and its compensation by the rotation of the movable part 10. The time difference may be several minutes. Optionally, the profile of the tooth row may be selected to limit and even remove the maximum gap. For this reason, optionally, the time difference is less than 5 minutes, further less than 3 minutes, and further less than 1 minute. In order to limit or remove the meshing engagement gap, a tooth row without a gap or other gap compensation device can be used. As a result, the clock drive device 100, especially the cam 12, the first tooth row 10a, and the second tooth row 11a, are arranged to substantially continuously fill the energy storage 22 via the cam follower 21, except for the drive stage in which the cam 12 is driven by the energy accumulator 22 via the cam follower 21. For example, - Ignoring the meshing gap and considering a jump of 1 / 25 of a second, the filling duration corresponds to 99.99% of the rotation period of the main gear 11. - Considering the time difference of one minute due to the meshing gap, the filling duration corresponds to 99.9% of the rotation period of the main gear 11. - Considering the time difference of three minutes due to the meshing gap, the filling duration corresponds to 99.8% of the rotation period of the main gear 11. - Considering the time difference of five minutes due to the meshing gap, the filling duration corresponds to 99.7% of the rotation period of the main gear 11.

[0037] More generally, from one stage to the next, the meshing transition between the tooth rows 10a and 11a is dimensioned to be maximally continuous so as to prevent fluctuations in the amplitude of the oscillator (assuming a mechanical watch movement), without abrupt interruption or significantly adversely affecting the energy consumption of the clock movement 400. Of course, the dimensions of the tooth rows 10a and 11a are selected so as to be able to continuously remove from and arrange into meshing engagement from one stage to the next. For this reason, the profile of the tooth row 11a may be modified or adapted, especially at the start and / or end of the drive.

[0038] Except for the potential time difference caused by the meshing gap during the transition between the instantaneous drive stage, the instantaneous jump stage and the filling stage, the filling stage and the instantaneous drive stage are assumed to follow each other infinitely so that the filling stage is substantially carried out over the rotation period of the main gear 11. In other words, since the instantaneous drive and the gap compensation stage are very short, the instantaneous drive device 100 is provided so as to be able to substantially continuously fill the energy storage device 20 during substantially the entire rotation period of the main drive gear 11.

[0039] In the first embodiment, the instantaneous drive device 100 is provided to be able to instantaneously drive a date calendar system 300 including a date disk 200 indexed by a jumper.

[0040] The drive element 13 may be a date claw 13 intended to interact with the tooth row 201 of the date disk 200 during the instantaneous drive phase. The date claw 13 is in this case fixed, in particular welded, to the core 16, which is driven into and / or riveted to the cam 12. The main drive gear 11 is also driven into and / or riveted to the core 16.

[0041] The core 16 is pivoted on the frame about the axis A1. Optionally, at least one indexing means 17, such as a pin 17, is arranged in the main gear in order to angularly index the main gear 11 with respect to the cam 12 and the date claw 13.

[0042] The profile of the cam 12 interacting with the energy storage device 20 successively includes a filling part 12a, a return part 12b, and a stop part 12c. The functionality of these parts will be explained in detail below.

[0043] The rotation period of the main drive gear 11 is 24 hours in order to be able to drive the calendar system 300 at least one pitch per day. In other words, for each rotation period of the main gear 11, the instantaneous drive device 100 is exclusively and continuously in the filling phase or the instantaneous drive phase (except for any possible compensation of the tooth row clearance).

[0044] The angular range of the part 11b corresponds, in the instantaneous drive phase, to the angular movement instantaneously covered by the cam 12 with respect to the axis A1. In other words, the angular range corresponds to the angular movement covered by the cam 12 during the continuous interaction with the return part 12b and the stop part 12c by the cam lever 21. In addition, the angular range around the main gear 11 without a tooth row is equal to or substantially equal to the angular movement covered by the cam 12 when the cam 12 is driven by the energy accumulator 22 via the cam follower 21.

[0045] The angular range around the main gear including the second tooth row 11a is equal to or substantially equal to the angular movement covered by the cam 12 by dragging in the filling phase during which the cam lever 21 interacts with the filling part 12a.

[0046] The transmission ratio between the main gear 11 and the movable part 10 is selected such that the tooth row 10a drives all of the tooth row 11a over a duration or period that substantially corresponds to the rotation period of the main gear 11. In other words, the rotation period of the main gear 11 includes a drag rotation defined by the angular range of the tooth row 11a and an instantaneous rotation defined by the angular range of the part 11b. For this reason, the angular velocity of the main gear 11 is not constant over its rotation period.

[0047] The cam lever 21 interacts with the cam 12 via a bearing, more specifically a ruby stone or runner 23. The runner 23 makes it possible to reduce the frictional torque generated by the support force exerted on the cam 12 by the lever 21. For this reason, the runner 23 makes it possible to reduce the energy consumption of the timepiece movement 400 and the loss of the amplitude of the oscillator (assuming a mechanical timepiece movement).

[0048] For this reason, the drive device is - The cam 12 is driven by the action of the energy accumulator 22 via the cam follower 21 over a first angular range 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 range that complements the first angular range and corresponds to the cam profile portion 12a. is arranged as follows.

[0049] <Filling stage> As shown in succession in FIGS. 4 to 6, during the filling stage, the lever 21, and in particular the runner 23, disengages from the stop portion 12c and weights the filling portion 12a. The portion 12a is shaped to fill the energy storage device 20 and thus store the energy necessary to instantaneously drive at least one pitch of the display member 200. During the filling stage, the cam 12 is driven by the main drive gear 11 in the sense of the hands of a small timepiece through the influence of the interaction of the tooth row 10a of the movable part 10 with the tooth row 11a.

[0050] Optionally, the filling portion 12a is shaped (in the case of a mechanical watch movement) to minimize and make constant the consumption and the loss of the amplitude of the oscillator. In other words, the filling portion 12a makes it possible to obtain a constant and minimum filling torque in the main drive gear 11.

[0051] <Drive stage> As shown in FIG. 6, when the lever 21, and in particular the runner 23, reaches the apex of the cam 12 at the end of the filling portion 12a, at the very moment of its transition to the return portion 12b, the lever 21, and in particular the runner 23, instantaneously moves on the return portion 12b until it reaches the stop portion 12c. This transition substantially corresponds to the moment when the tooth row 10a is disengaged from the engagement with the tooth row 11a and faces the portion 11b. Thereafter, the main gear 11 is disconnected from the movable part 10. For this reason, the main gear 11 can freely and instantaneously move over the entire angular range of the portion 11b required for the drive stage, in the sense of the hands of a small watch.

[0052] Ideally, the disconnection and the transition from the apex of the cam should occur simultaneously. In practice, this is not possible. The disconnection cannot occur immediately before the transition from the apex, otherwise there is a risk that the movable part 10 can no longer drive the main gear 11. For this reason, the disconnection must occur immediately after the apex of the cam has passed, or immediately after the start of the jump. The moment when the apex of the cam has passed is such that, since only the last tooth of the tooth row 11a maintains the engagement with the tooth row 10a, when the drive ends, this tooth can freely disengage from the tooth row 10a immediately after the apex of the cam has passed.

[0053] As shown in FIG. 7, during the drive stage, the energy stored in the energy storage device 20 is returned in order to enable the rotation of the main movable part and, as a result, the instantaneous drive of the display member 200 by the date pawl 13. In other words, in the middle of the night, both the cam 12 and the date pawl 13 become the drive parts due to the return of the stored energy.

[0054] At the end of the driving phase, the date pawl 13 is stopped, interfering with the tooth row 201 of the date disk 200, thereby preventing an unintentional additional jump due to inertia and the considerable energy released during said phase. It is necessary to maintain the positioning at the location of the interference with the tooth row 201 of the date disk 200.

[0055] For this reason, as shown in FIG. 8, the lever 21, and in particular the runner 23, is located on the stop portion 12c, dimensioned to dissipate the residual kinematic energy after the display member 200 has been driven. The stop of the display member 200 is also instantaneous. In other words, the instantaneous drive phase includes the stop of the display member 200.

[0056] For this reason, the tooth row 10a of the pinion 10 is within the range of the tooth row 11a in such a way as to enable a new meshing connection when a new filling phase is started.

[0057] Optionally, at least the first tooth of the tooth row 11a is optimized to limit the meshing clearance with the tooth row 10a and reduce the transition time between each of the instantaneous jump phase and the filling phase.

[0058] Additionally or alternatively, at least the first tooth of the tooth row 11a may be utilized to enable partial or complete dissipation of said residual kinematic energy at this stage. Thus, said tooth has a shape optimized to better assist in the dissipation of energy. In relation to the rest of the tooth row 11a, the first tooth may have a greater thickness and / or an asymmetric profile, in particular to limit the concentration of stress across said tooth in order to better transmit the stress and thus exhibit a higher strength.

[0059] <Resetting of the time in the opposite direction> Advantageously, especially during the resetting of the time in the direction opposite to the operation, in order to prevent the desynchronization between the main gear 11 and the gear train of the timepiece movement 400, the engagement of the portion 11b with the tooth row 10a is provided to prevent the rotation of the tooth row 10a, like a Maltese cross. In particular, the portion 11b is capable of interacting with the adjacent side surfaces of two teeth of the tooth row 10a and has a cylindrical portion that is concentric with the axis A1 and has a diameter close to the pitch diameter of the tooth row 11a to prevent the tooth row 10a from rotating.

[0060] Additionally or alternatively, the rotation of the movable part 10 in the direction opposite to the 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 the movable part and the gear train of the timepiece movement 400. Of course, the one-way coupling must be shaped to maintain the synchronization of the induction of the instantaneous driving stage with the gear train of the timepiece movement 400.

[0061] A second embodiment of the timepiece 400 will be described in detail below with reference to FIGS. 9 to 16.

[0062] This second embodiment advantageously includes the same means as or substantially the means of the first embodiment, except that an additional auxiliary movable part is provided to prevent the asynchronization of the main gear 11 with respect to the gear train of the timepiece movement 400. The auxiliary movable part also makes it possible to drive the display member 200 during the resetting of the time in the direction opposite to the operation.

[0063] The auxiliary movable part is also pivoted within the frame. The auxiliary movable part includes an auxiliary drive gear 15 that is constantly driven by the gear train of the timepiece movement 400. The auxiliary drive gear 15 is capable of interacting with an elastic device 14 that is fixed to or adhered to the main movable part.

[0064] More specifically, in this embodiment, the auxiliary movable part is coaxial with the main movable part. The auxiliary drive gear 15 rotates around the core 16. The elastic device 14 is a spiral spring 14, and its inner end is driven into or riveted to the core 16 fixed to the main gear 11 and the cam 12. The outer end 14a of the spring 14 is capable of interacting with an angle stopper 15b disposed on the auxiliary drive gear 15.

[0065] The utilization of the interaction between the spring 14 of the auxiliary drive gear 15 will be described in detail below.

[0066] In the second embodiment, the movable part 10 includes an auxiliary tooth row 10b that always meshes with the tooth row 15a of the auxiliary drive gear 15 so that its rotation speed is constant and is completely synchronized with the gear train of the clock movement 400.

[0067] The transmission ratio between the pinion 10 and the auxiliary drive gear 15 is selected such that the auxiliary drive gear 15 has the same rotation period as the main drive gear 11. In contrast to the main drive gear 11, which performs a dragging rotation over the angular range defined by the tooth row 11a and an instantaneous rotation over the angular range defined by the portion 11b, it should be noted that the auxiliary drive gear 15 performs a dragging rotation at a constant speed over the entire rotation period thereof. As a result, the duration or period during which the tooth row 10a engages with the tooth row 11b is the same as or substantially the same as the rotation period of the auxiliary drive gear 15.

[0068] For this reason, during the filling stage, the angular velocity of the auxiliary gear 15 is higher than the speed of the main gear 11. As will be described in more detail below, with respect to the auxiliary gear 15, the main gear 11 cancels out the angular offset gradually accumulated during the charging stage during the instantaneous drive stage.

[0069] The operating mode of the second embodiment is substantially the same as that of the first embodiment. Only the interaction of the spring 14 with the auxiliary drive gear 15 adds a new function, as will be described below.

[0070] In a modified example, in the second embodiment, the main movable part and the auxiliary movable part of the drive device do not have to be coaxial and may be pivoted on two separate, preferably parallel axes. In this case, they are connected, for example, by meshing engagement.

[0071] In a further modified example, in the second embodiment, the elastic device 14 may include a lever or a click that interacts with the spring element.

[0072] <Filling stage> In the second embodiment, at the start of the filling stage, immediately after the end of the driving stage illustrated in FIG. 10, the free end 14a of the spring 14 substantially contacts the angle stopper 15b of the auxiliary drive gear 15.

[0073] Therefore, assuming that the angular velocity of the auxiliary gear 15 is slightly higher than the angular velocity of the main gear 11, as shown in FIG. 11, the angle stopper 15b gradually moves away from the free end 14a as the energy storage device is wound up.

[0074] At the end of the filling stage, the angular interval between the free end 14a and the angle stopper 15b corresponds to the angular range of the portion 11b and to or substantially corresponds to the angular movement covered by the cam 12 during the instantaneous driving stage.

[0075] During the driving stage, the main movable part, in particular the main gear 11, the cam 12, and the spring 14 instantaneously cover the angular movement necessary to drive the display member 200. As a note, the angular movement corresponds to the angular range of the portion 11b and as a result corresponds to the maximum angular interval between the free end 14a and the angle stopper 15b. Therefore, during the driving stage, the angular interval is instantaneously compensated. After the stage, the free end 14a and the angle stopper 15b return to contact or substantial contact.

[0076] Additionally or alternatively, the elastic device 14 may be shaped to be able to partially or completely dissipate the excess kinematic energy after driving the display member 200, i.e., at the end of the driving stage.

[0077] Advantageously, the second embodiment enables the driving member 200 to be driven in the opposite direction of operation without the risk that the main gear 11 is desynchronized from the train of wheels of the time movement 400. Thus, in contrast to the first embodiment, the part 11b does not interact with the movable part 10 in the form of a Maltese cross and is outside the scope of the movable part 10. For example, the part 11b may consist of a cylindrical part having a radius equal to or substantially equal to the radius of the pitch circle of the tooth row 11a.

[0078] When the train of wheels of the time movement is actuated in the opposite direction of operation, the auxiliary tooth row 10b drives the tooth row 15a of the auxiliary gear in the opposite direction of the hands of the small clock, and the tooth row 10a drives the tooth row 11a of the main gear until the part 11b faces the pinion 10, in other words until the lever 21, in particular the runner 23, is on the stop part 12c. Thus, the tooth row 10a rotates without load and can no longer drive the main gear 11 in the opposite direction. As shown in FIG. 14, the main gear 11 is then driven by the auxiliary gear 15 via the spring 14 due to the contact with the angle stop 15b of the free end 14a. Of course, the elastic device 14 is dimensioned to have sufficient angular stiffness to overcome the torque resulting from the interaction with the return part 12b of the energy storage device 20 and to enable the driving member 200 to be driven in the opposite direction.

[0079] At the moment when the return part 12b has completely moved in the opposite direction and transitions to the filling part 12a, the tooth row 10a interacts again with the tooth row 11a of the main gear 11. Thus, the spring 14 starts to wind up as a result of the slight difference in angular velocity between the main gear 11 and the auxiliary gear 15. As shown in FIG. 15, the maximum winding level of the spring 14 is reached when the tooth row 10a faces the part 11b again. The angular displacement or deformation of the free end 14a corresponding to the maximum winding is equal to or substantially equal to the angular movement covered by the cam 12 during the instantaneous drive phase.

[0080] At that moment, the main gear 11 is separated from the movable part 10. As a result, the energy stored in the spring 14 is returned so as to drive the main gear 11 and the display member 200 instantaneously or substantially instantaneously in opposite directions. For this reason, the elastic device 14 is also dimensioned such that the lever 21, in particular the runner 23, can accumulate sufficient energy to climb the return part 12b in the opposite direction of operation.

[0081] Continuing the operation of the train of wheels of the timepiece movement 400 in the opposite direction makes it possible to initiate a new stage of filling of the elastic device 14 due to the interaction of the tooth row 10a of the movable part 10 with the tooth row 11a of the main gear 11.

[0082] According to the second embodiment, resetting the time in the opposite direction first enables the dragging drive of the display member 200 and then, subsequently, an instantaneous or substantially instantaneous drive in the opposite direction.

[0083] It should be noted that the energy required to fill the elastic device 14 is provided by the user when the user resets the time in the opposite direction. In other words, the said energy is not provided by the timepiece movement 400.

[0084] The present invention also relates to a method of operating the timepiece drive device 100 described above. As described above, the method of operation includes substantially continuously filling the energy accumulator 22 via the cam follower 21, except for the drive stage in which the cam 12 is driven by the energy accumulator 22 via the cam follower 21.

[0085] Advantageously, the duration of filling may be at least 90%, further at least 99%, further at least 99.5%, and further substantially 100% of the time of the rotation period of the main gear 11 of the timepiece drive device 100.

[0086] Optionally, the method - To drive the cam 12 for filling the energy accumulator 22, the first tooth row 10a and the second tooth row 11a are brought into meshing engagement, and then, - The first tooth row 10a and the second tooth row 11a are disengaged from the meshing engagement, and the cam 12 is driven by the energy accumulator 22 via the cam follower 21, including at least one repetition of the steps, and in particular at least a plurality of repetitions of the steps.

[0087] The proposed solution advantageously makes it possible to keep the energy consumption of the clock movement 400 during the filling phase substantially corresponding to the rotation period of the main gear 11, except for the potential time difference caused by the meshing clearance during the transition between the instantaneous drive phase, the instantaneous jump phase and the filling phase. For this reason, the consumed energy and the resulting loss of the amplitude of the filling can be constant or substantially constant, contrary to the solutions known from the prior art.

[0088] In addition, assuming that the energy required to instantaneously drive the display member 200 can be stored over a longer duration or rotation period than that of the known solutions, it is also possible to reduce the instantaneous consumption for the same total amount of stored energy. By increasing the filling duration from 13 hours to 24 hours, for example, it is possible to reduce the filling force by 46%. By increasing the filling duration from 20 hours to 24 hours, for example, it is possible to reduce the filling force by 17%.

[0089] Advantageously, the instantaneous drive device 100 also makes it possible to directly drive the display member 200, which exclusively implements the drive element 13. This is because the solution does not require a lever arranged on the contact surface between the members.

[0090] Of course, the solution is not limited to a simple date calendar system, and is particularly suitable for more energy-consuming calendar systems, such as annual or perpetual date calendars. More generally, the solution is applicable to any instantaneous jump display system that displays time-based or time-derived information.

[0091] In the described embodiment, the calendar system 300 is assumed to be driven at least one pitch per rotation period of the main drive gear 11. However, regardless of the embodiment or variation, the instantaneous drive device may be adapted to drive the display system at multiples or divisors of the rotation period of the main drive gear 11. Of course, as a result, the shapes of the cam 12 and the main gear 11 must be specified.

[0092] Regardless of the embodiment or variation, the cam 12 may be replaced by a simple shape such as a pin that interacts with a contour formed on the cam follower 21 of the energy storage device 20 that is similar to the cam contour.

[0093] Regardless of the embodiment or variation, the tooth rows of the movable part 10 and the main gear 11 may be formed at a plurality of separate heights, especially over the first and second heights. This makes it possible to distribute the drive by appropriately cutting off the tips of specific teeth at the first height and / or the second height in order to optimize the continuous operation of bringing these teeth into meshing engagement and disengaging them from the meshing engagement during the filling and driving stages. This configuration is particularly advantageous when the movable part 10 includes a large number of teeth and / or when the difference between the pitch circle diameters between the movable part 10 and the main gear 11 is too small. This configuration also makes it possible to optimize the tooth row contour in order to limit or eliminate the meshing clearance during the transition between each of the instantaneous jump stage and the filling stage to the maximum possible extent. Additionally or alternatively, the shape of two or more heights of the teeth of the movable part 10 and the main gear 11 is also particularly advantageous, for example, for implementing the function of meshing engagement at the second height in the form of a Maltese cross at the first height.

[0094] Regardless of the embodiments and modifications, optionally, the drive device, in particular the contour of the cam 12, is arranged such that the mechanical force supplied to the energy accumulator 22 is constant or substantially constant during or substantially during the period when the cam 12 is not driven by the energy accumulator 22 via the cam follower 21.

[0095] Optionally, "instantaneous" means an operation having a duration of 1 or more fractions of a second, typically about 1 / 100 of a second, or about 1 / 25 of a second, or about 1 / 10 of a second.

[0096] Conversely, "drag" means a slow operation such as displacement, for example lasting at least several seconds.

Explanation of reference numerals

[0097] 10 Movable part 10a First tooth row 11 Main gear 11a Second tooth row 12 Cam 12a, b, c Cam contour 21 Cam follower 22 Energy accumulator 100 Clock drive device 200 Display member 300 Clock calendar 400 Clock movement

Claims

1. A clock drive (100) for a system (300), particularly an instantaneous jump calendar system, that displays time-based or time-derived information, comprising: An input movable part (10) including a first tooth row (10a); A main gear (11) including a second tooth row (11a) covering only a part around the main gear, wherein the second tooth row meshes and engages with the first tooth row; A cam (12) connected to the main gear (11), particularly connected to the main gear (11) with a minimum gap, and especially fixed to the main gear (11), having cam contours (12a, 12b, 12c); A cam follower (21) interacting with the contours (12a, 12b, 12c); An energy accumulator (22) elastically returning the cam follower to the contours (12a, 12b, 12c) of the cam (12); Including; The clock drive (100).

2. The angular range of the contour of the main gear including the second tooth row (11a) is equal to or substantially equal to the angular movement covered by the cam (12) when the cam is not driven by the energy accumulator (22) via the cam follower (21), and / or the angular range of the contour of the main gear (11) without a tooth row is equal to or substantially equal to the angular movement covered by the cam (12) when the cam is driven by the energy accumulator (22) via the cam follower (21), and / or For the clock drive (100), particularly the cam, the first tooth row, and the second tooth row, the action of the cam (12) on the cam follower (21) is arranged to rotate the main gear (11) independently of the input movable part (10). The clock drive (100) according to Claim 1.

3. For the clock drive (100), particularly the cam (12), the first tooth row (10a), and the second tooth row (11a), except for the driving stage when the cam (12) is driven by the energy accumulator (22) via the cam follower (21), they are arranged to substantially permanently fill the energy accumulator (22) via the cam follower (21). The clock drive (100) according to Claim 1 or 2.

4. The drive device is The cam (12) is driven by the action of the energy accumulator (22) via the cam follower (21) over a first angular range. The cam (12) supplies energy to the energy accumulator (22) via the cam follower over a second angular range that complements the first angular range. It is arranged as follows. The timepiece drive device (100) according to any one of claims 1 to 3.

5. The contour of the drive device, in particular the cam (12), is arranged such that the mechanical force supplied to the energy accumulator (22) is constant or substantially constant during or substantially during the period when the cam (12) is not driven by the energy accumulator (22) via the cam follower (21). The timepiece drive device (100) according to any one of claims 1 to 4.

6. The cam follower (21) includes a lever (21). The timepiece drive device (100) according to any one of claims 1 to 5.

7. The energy accumulator (22) includes a spring (22), in particular a leaf spring. The timepiece drive device (100) according to any one of claims 1 to 6.

8. The cam (12) is kinematically connected to a drive element (13) that drives a display element (200) for displaying time-based information, such as a claw (13), which interacts with a tooth row (201) of the display element (200) for displaying time-based information, and is fixed, in particular, to the drive element (13) that drives the display element (200) for displaying time-based information. The timepiece drive device (100) according to any one of claims 1 to 7.

9. A timepiece calendar (300), in particular a simple date calendar or an annual calendar or a perpetual calendar, including the timepiece drive device (100) according to any one of claims 1 to 8, wherein the calendar includes a display element (200) for displaying time-based information, such as a disk having numbers and including a tooth row (201). Timepiece calendar (300).

10. The timepiece drive device (100) according to any one of claims 1 to 8, and / or The timepiece calendar (300) according to claim 9 Including Timepiece movement (400).

11. The timepiece movement (400) according to claim 10, and / or The timepiece calendar (300) according to claim 9, and / or The timepiece drive device (100) according to any one of claims 1 to 8, Including A timepiece (500), in particular a wristwatch.

12. A method of operating a timepiece drive (100), said timepiece drive (100) comprising: a cam (12); a cam follower (21); an energy accumulator (22) for returning said cam follower (21) to said cam (12); and said method includes substantially continuously filling the energy accumulator (22) via the cam follower (21), except during a driving phase in which the cam (12) is driven by the energy accumulator (22) via the cam follower (21). Operating method.

13. The duration of said filling corresponds to at least 90% of the time of the rotation period of said main gear (11) of said timepiece drive (100), further at least 99% of the time of the rotation period of said main gear (11) of said timepiece drive (100), further at least 99.5%, further substantially 100% of the time of the rotation period of said main gear (11) of said timepiece drive (100). The operating method according to claim 12.

14. To drive said cam (12) for filling said energy accumulator (22), a first tooth row (10a) and a second tooth row (11a) are brought into meshing engagement, and then the first tooth row (10a) and the second tooth row (11a) are disengaged from the meshing engagement, and the cam (12) is driven by the energy accumulator (22) via the cam follower (21). including at least one repetition of the steps. The operating method according to claim 12 or 13, in particular the method of operating the timepiece (500) according to claim 11 or the timepiece movement (400) according to claim 10 or the timepiece calendar (300) according to claim 9 or the timepiece drive (100) according to any one of claims 1 to 8.

15. The driving of said cam (12) is an instantaneous drive. The operating method according to any one of claims 12 to 14.

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