Timepiece driving device

Abstract

A timepiece drive (100), in particular a system (300) for displaying time-based or time-derived information, in particular for an instantaneous jump calendar system, comprises: an input mover (10) comprising a first ring gear (10a); a main wheel (11) including a second ring gear (11a) on only a portion of its periphery, the second ring gear being in meshing engagement with the first ring gear; a cam (12) which is connected to the main wheel (11), in particular with minimal play, in particular fixed to the main wheel (11), and which has a cam profile (12a, 12b, 12c); a cam follower (21) interacting with the contours (12a, 12b, 12c); and an accumulator (22) that resiliently returns the cam follower against the contour (12a, 12b, 12c) of the cam (12).

Description

Technical Field

[0001] The present invention relates to a clock driving device. The present invention also relates to a clock calendar including such a clock driving device. The present invention also relates to a clock movement including such a clock driving device or such a clock calendar. The present invention also relates to a clock including such a clock movement or such a clock driving device or such a clock calendar. The present invention also relates to a method for operating such a clock movement or such a clock or such a clock driving device or such a clock calendar. Background Art

[0002] The prior art discloses an instantaneous clock calendar system having a driving moving member provided with a cam that interacts with an energy accumulation device (such as a cam lever associated with a spring).

[0003] Driven by a driving wheel, the cam enables the energy accumulation device to be armed during an arming phase and to return energy sequentially during an instantaneous driving phase of the calendar. Then the cam is driven and rotates relative to the driving wheel. The returned energy is used to drive the cam and the mechanism arranged downstream of the cam.

[0004] After the instantaneous driving phase, during a compensation phase, the cam is fixed until it is captured by the driving wheel and driven again by the driving wheel in order to arm the energy accumulation device.

[0005] Depending on the design of the calendar, the compensation phase can last approximately 4 to 11 hours. During this compensation phase, compared to the arming phase, the driving wheel rotates without load and consumes very little energy. Due to the difference in the loads applied to the driving wheel between the compensation phase and the arming phase, this results in an amplitude variation of the oscillator of the clock movement (assuming a mechanical clock movement).

[0006] Patent application CH256366A4 discloses a driving moving member for driving a date disk. The driving moving member includes a first wheel and a second wheel that are coaxial and can be driven by two integral pinions at different angular velocities respectively. The angular velocity of the first wheel is slightly less than that of the second wheel. The two wheels are interconnected by a spring 14 that is intended to be wound incrementally with an angular offset caused by the speed difference between the wheels. The toothed ring of the first wheel is truncated in part. When this part faces its driving pinion, the first wheel suddenly drives the date disk freely under the release of the spring. After driving, once the toothed ring of the first wheel re-engages with the toothed ring of its driving pinion, the spring is gradually rewound. The solution proposed here cannot optimize the energy consumption of the movement drive of such a date mechanism. Summary of the Invention

[0007] The object of the present invention is to provide a clock driving device which improves the device known from the prior art. In particular, the present invention provides a clock driving device for optimally dispersing the energy consumption over time, especially within the rotation period of the driving wheel.

[0008] According to the present invention, the driving device is defined by claim 1.

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

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

[0011] According to the present invention, the clock movement is defined by claim 10.

[0012] According to the present invention, the clock is defined by claim 11.

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

[0014] Embodiments of the operating method are defined by claims 13 to 15. Description of the Drawings

[0015] The drawings depict, by way of example, two embodiments of a clock according to the present invention.

[0016] Figure 1 is a view of a first embodiment of a clock according to the present invention, in which the driving device is shown from the dial side.

[0017] Figure 2 is a view of a first embodiment of a clock according to the present invention, in which the driving device is shown from the movement side.

[0018] Figure 3 is a set of views of an element forming part of a first embodiment of the driving device, including an exploded view and two perspective views.

[0019] Figures 4 to 8 is a view of the operating sequence of the driving device of the first embodiment.

[0020] Figure 9 is a set of views of a second embodiment of the driving device, including an exploded view and two perspective views.

[0021] Figures 10 to 16 is a view of the operating sequence of the driving device of the second embodiment. Detailed Description

[0022] The following refers to Figures 1 to 8 a detailed description of a first embodiment of the clock 500.

[0023] The timepiece 500 is, for example, a watch, in particular a wristwatch. The timepiece 500 includes a timepiece movement 400, which is intended to be installed in a timepiece housing or case in order to protect the timepiece movement 400 from the external environment.

[0024] The timepiece movement 400 is a mechanical movement, in particular an automatic movement or a hybrid movement or an electronic movement.

[0025] The timepiece movement 400 includes a system 300 for displaying information based on time or time-derived information, such as a timepiece calendar 300, in particular an instantaneous jump calendar.

[0026] The system 300 for displaying information based on time or time-derived information includes:

[0027] - at least one display member 200, in particular a member for displaying the day of the month, in particular a disk for displaying the day of the month, and

[0028] - a timepiece drive 100,

[0029] The at least one display member 200 and the drive 100 are arranged such that the drive 100 is able to drive the at least one display member 200. The drive is of the instantaneous or instantaneous jump type.

[0030] The system 300 for displaying information based on time or time-derived information enables at least one item of calendar information, such as information about the day, the day of the month, the month, the year, the leap year, the lunar phase, to be displayed, for example via the at least one display member 200.

[0031] At least one item of calendar information can be indicated or carried by the at least one display member 200, which can, for example, take the form of a finger or a disk.

[0032] The timepiece drive 100 includes:

[0033] - an input moving member 10 including a first toothed ring 10a;

[0034] - a main wheel 11 including a second toothed ring 11a only on a part of its periphery, the second toothed ring meshing with the first toothed ring,

[0035] - a cam 12, which is connected to the main wheel 11, in particular with a minimal clearance to the main wheel 11, in particular fixed to the main wheel 11, and has cam profiles 12a, 12b, 12c,

[0036] - a cam follower 21 interacting with the profiles 12a, 12b, 12c, and

[0037] - An accumulator 22 that elastically returns the cam follower against the profiles 12a, 12b, 12c of the cam 12.

[0038] "Connected with a minimum clearance" is understood to mean:

[0039] - A connection without clearance, such as a fixation, or

[0040] - A connection with a very small assembly clearance, or

[0041] - A meshing connection presenting a meshing clearance.

[0042] The timepiece drive 100, in particular the cam, the first toothed ring and the second toothed ring, can be arranged such that during a time interval the main wheel 11 is allowed to rotate independently of the input moving member 10, and this rotation is caused by the action of the cam follower 21 on the cam 12. Thus, the action of the cam follower 21 on the cam 12 can cause the main wheel 11 to rotate independently of the input moving member 10.

[0043] In particular, as Figure 3 depicted, the instantaneous drive 100 includes a main moving member that includes the main drive wheel 11 and further includes:

[0044] - A drive element 13, and

[0045] - A cam 12.

[0046] The main wheel 11, the cam 12 and the drive element 13 are fixed to one another. In particular, the main wheel 11, the cam 12 and the drive element 13 are fixed to one another.

[0047] The main moving member pivots about an axis A1 within the frame of the timepiece movement 400 or within the frame of the calendar module. The drive element 13 is intended to directly and periodically drive the display member 200, for example by interacting with the teeth of the toothed ring of the display member 200 by blocking the teeth of the toothed ring of the display member 200.

[0048] The instantaneous drive 100 further includes an energy accumulation device 20, and the cam 12 is intended to interact with the energy accumulation device 20 in order to periodically accumulate and periodically return the energy required to instantaneously drive the display member 200.

[0049] The energy accumulation device 20 includes:

[0050] - A cam follower 21, such as a cam lever 21 pivoting within a frame, and

[0051] - An accumulator 22, such as a spring or an elastic return device 22, capable of accumulating the energy required to instantaneously drive the display member 200. In addition, the elastic return device 22 tends to return the lever 21 against the cam 12. Therefore, preferably, the lever 21 can be in continuous contact with the cam 12.

[0052] The energy accumulation device 20 can be integral.

[0053] As Figure 4 shown, the main drive wheel 11 is intended to be driven by a moving member 10 that is kinematically connected to the gear train of the timepiece movement 400. The moving member 10 can be part of the instantaneous drive system 100. More specifically, the main wheel 11 includes a gear ring 11a capable of interacting with the gear ring 10a of the moving member 10. Preferably, the moving member 10 rotates at a constant speed when the timepiece movement 400 is running.

[0054] A specific feature of this solution is that the gear ring 11a is interrupted or truncated on a portion 11b of the main drive wheel 11. It is noted that the gear ring 11a is produced around the perimeter of the main wheel 11. Thus, this perimeter has a smooth or toothless portion. The radius of this smooth portion is, for example, substantially equal to the pitch circle radius (as described below). As a result, the shaping of the portion 11b means that the main wheel 11 is not driven by the moving member 10 within a given angular range. In other words, the portion 11b enables the separation of the main wheel 11 from the moving member 10 (in particular the gear ring 10a) or the disengagement of the main wheel 11 from the meshing engagement with the moving member 10.

[0055] Therefore, as Figure 4 、 Figure 5 and Figure 6 depicted, during the installation phase, the gear ring 11a is driven by the moving member 10, thereby enabling the installation of the energy accumulation device 20. In addition, as Figure 7 and Figure 8 depicted, during the instantaneous drive phase, due to the separation of the main wheel 11 and the moving member 10, the portion 11b can instantaneously return the energy accumulated in the energy accumulation device 20 during the previous installation phase. Therefore, the instantaneous drive phase corresponds to the phase in which the display member 200 is instantaneously driven by the driving element 13. During this phase, when the main wheel 11 is separated from the moving member 10 or disengaged from the meshing engagement with the moving member 10, the main wheel 11 rotates and instantaneously or almost instantaneously travels through the angular range of the portion 11b until the gear ring 11a re-engages with the gear ring 10a of the moving member 10a. Therefore, the angular range of the portion 11b (about the axis A1) is equal to or substantially equal to the angular travel (about the axis A1) covered by the cam 12 during the instantaneous drive phase.

[0056] When transitioning between the instantaneous jump phase and the winding phase, due to the meshing clearance between the ring gear 11a and 10a, the driving of the main wheel 11 can be started with a small delay or latency. In other words, during the winding phase, the effective winding of the energy accumulation device 20 can be started with a delay or lag caused by the meshing clearance and its compensation by the rotation of the moving member 10. This lag may be about a few minutes. Preferably, the profile of the ring gear is selected to limit or even eliminate the clearance as much as possible. Thus, preferably, the lag is less than 5 minutes, or even less than 3 minutes or less than 1 minute. A ring gear without clearance or any other clearance compensation device can be used to limit or eliminate the clearance of this meshing engagement. Therefore, the clock driving device 100, in particular the cam 12, the first ring gear 10a and the second ring gear 11a, are arranged such that, except for the driving phase where the cam 12 is driven by the accumulator 22 via the cam follower 21, the accumulator 22 is essentially permanently wound via the cam follower 21. For example:

[0057] - Ignoring the meshing clearance and considering a 1 / 25 e second jump, the winding duration corresponds to 99.99% of the rotation period of the main wheel 11,

[0058] - Considering a 1-minute lag due to the meshing clearance, the winding duration corresponds to 99.9% of the rotation period of the main wheel 11,

[0059] - Considering a 3-minute lag due to the meshing clearance, the winding duration corresponds to 99.8% of the rotation period of the main wheel 11, and

[0060] - Considering a 5-minute lag due to the meshing clearance, the winding duration corresponds to 99.7% of the rotation period of the main wheel 11.

[0061] More generally, from one phase to the next, the dimensions of the meshing transition between the ring gear 10a and the ring gear 11a are designed to be as continuous as possible without a sudden interruption or without significantly adversely affecting the energy consumption of the clock movement 400, and thus avoiding changes in the amplitude of the oscillator (assuming a mechanical clock movement). Of course, the geometries of the ring gears 10a and 11a are selected such that they can be disengaged from the meshing engagement and continuously meshed from one phase to the next. For this purpose, the profile of the ring gear 11a can be particularly corrected or adjusted at the start and / or end of the drive.

[0062] It is stipulated that the charging phase and the instantaneous drive phase follow each other indefinitely, such that the charging phase is effective essentially throughout the entire rotation period of the main wheel 11, except for the instantaneous drive phase and the potential hysteresis caused by the meshing clearance during the transition between the instantaneous jump phase and the charging phase. In other words, the instantaneous drive device 100 is arranged such that the energy accumulation device 20 can be charged essentially permanently and essentially throughout the entire rotation period of the main drive wheel 11, since the instantaneous drive phase and the clearance compensation phase are extremely short.

[0063] In the first embodiment, the instantaneous drive device 100 is arranged such that it can instantaneously drive a date calendar system 300 including a date disk 200 indexed by a positioning lever.

[0064] The drive element 13 can be a date finger 13 intended to interact with the toothed ring 201 of the date disk 200 during the instantaneous drive phase. The date finger 13 is fixed, in this case welded, to the core 16 in particular, and the core 16 itself is driven onto and / or riveted to the cam 12. The main drive wheel 11 is also driven onto and / or riveted to the core 16.

[0065] The core 16 pivots on the frame about the axis A1. Preferably, at least one indexing device 17 (such as a pin 17) is arranged within the main wheel so as to angularly index the main wheel 11 using the cam 12 and the date finger 13.

[0066] The profile of the cam 12 interacting with the energy accumulation device 20 continuously includes a charging portion 12a, a return portion 12b, and a stop portion 12c. The functions of these portions are described in more detail below.

[0067] The rotation period of the main drive wheel 11 is 24 hours, such that the calendar system 300 can be driven by at least one pitch per day. In other words, for each rotation period of the main wheel 11, the instantaneous drive device 100 will be exclusively and continuously in the charging phase or the instantaneous drive phase (apart from the possible compensation of the toothed ring clearance).

[0068] The angular range of the portion 11b corresponds to the angular stroke instantaneously covered by the cam 12 relative to the axis A1 during the instantaneous drive phase. In other words, it corresponds to the angular stroke covered by the cam 12 during the successive interactions of the cam lever 21 with the return portion 12b and the stop portion 12c. Additionally, the angular range of the periphery of the main wheel 11 without teeth is equal to or essentially equal to the angular stroke covered by the cam 12 when it is driven by the accumulator 22 via the cam follower 21.

[0069] When the cam lever 21 interacts with the charging portion 12a, the angular range of the periphery of the main wheel including the second toothed ring 11a is essentially equal to or equal to the angular stroke covered by the cam 12 in a dragging manner during the charging phase.

[0070] The transmission ratio between the main wheel 11 and the moving member 10 is selected such that the toothed ring 10a drives the entire toothed ring 11a in a duration or period substantially corresponding to the rotation period of the main wheel 11. In other words, the rotation period of the main wheel 11 includes a dragging rotation defined by the angular range of the toothed ring 11a and an instantaneous rotation defined by the angular range of the part 11b. Therefore, the angular velocity of the main wheel 11 is not constant throughout its rotation period.

[0071] The cam lever 21 interacts with the cam 12 via a bearing (more specifically, a stone or slider 23 made of ruby). The slider 23 can reduce the frictional torque caused by the supporting force exerted by the lever 21 on the cam 12. Therefore, this slider 23 enables the reduction of the energy consumption and amplitude loss of the oscillator of the watch movement 400 (assuming a mechanical watch movement).

[0072] Therefore, the drive device is arranged such that:

[0073] - The cam 12 is driven via the cam follower 21 by the action of the energy accumulator 22 in a first angular range corresponding to the cam profile parts 12b, 12c, and

[0074] - The cam 12 supplies energy to the energy accumulator 22 via the cam follower in a second angular range corresponding to the cam profile part 12a, which is complementary to the first angular range.

[0075] Equipment stage

[0076] During the arming phase, as successive Figures 4 to 6 shown, the lever 21, in particular the slider 23, exits from the stop part 12 and presses against the arming part 12a. This part 12a is shaped to arm the energy accumulation device 20 and thus accumulates the energy required to instantaneously drive the display member 200 by at least one pitch. During the arming phase, the cam 12 is driven by the main drive wheel 11 in the sense of the hands of the watch by the effect of the interaction between the toothed ring 10a of the moving member 10 and the toothed ring 11a.

[0077] Preferably, the arming part 12a is shaped such that the consumption and amplitude loss of the oscillator (in the case of a mechanical watch movement) are minimized and constant. In other words, the arming part 12a enables a constant and minimized arming torque to be obtained at the main drive wheel 11.

[0078] Drive stage

[0079] As Figure 6As shown, when the lever 21, in particular the slider 23, reaches the apex of the cam 12 at the end of the loading part 12a, at the moment when it just transitions to the return part 12b, the lever 21, in particular the slider 23, travels instantaneously on the return part 12b until it reaches the stop part 12c. This transition also substantially corresponds to the moment when the gear ring 10a disengages from the engagement with the gear ring 11a and faces the part 11b. Then, the main wheel 11 is separated from the moving part 10. Thus, the main wheel 11 can freely and instantaneously travel the entire angular range of the part 11b required for the driving phase in the sense of the hands of the watch.

[0080] Ideally, the separation and the transition from the apex of the cam should occur simultaneously. In practice, this is impossible. The separation cannot occur just before the transition from the apex, because otherwise there is a risk that the moving part 10 can no longer drive the main wheel 11. Therefore, the separation must occur just after the apex of the cam or at the start of the jump. Because at the moment of passing the apex of the cam, only the last tooth of the gear ring 11a remains engaged with the gear ring 10a, and at the end of the drive, this tooth can freely come out of the gear ring 10a just after passing the apex of the cam.

[0081] During the driving phase, as Figure 7 shown, the energy stored by the energy accumulation device 20 is returned to allow the rotation of the main moving part and thus allow the instantaneous drive of the date finger 13 on the display member 200. In other words, at midnight, both the cam 12 and the date finger 13 become drivers due to the return of the accumulated energy.

[0082] At the end of the driving phase, the date finger 13 must stop and remain positioned in a position interfering with the gear ring 201 of the date disc 200 in order to block the date disc 200 and thus avoid an unintentional additional jump due to its inertia and the considerable energy released during this phase.

[0083] For this purpose, as Figure 8 shown, the lever 21, in particular the slider 23, is located on the stop part 12c, the dimensions of which are designed to dissipate the residual kinetic energy after the display member 200 is driven. The stop of the display member 200 is also instantaneous. In other words, the instantaneous driving phase includes the stop of the display member 200.

[0084] Thus, the gear ring 10a of the pinion 10 is again within the range of the gear ring 11a in order to allow a new meshing engagement and start a new loading phase.

[0085] Preferably, at least the first tooth of the gear ring 11a is optimized to limit the meshing clearance with the gear ring 10a and reduce the transition time between the instantaneous jump phase and the loading phase.

[0086] Additionally or alternatively, during this phase, at least the first teeth of the toothed ring 11a can be utilized to enable partial or complete dissipation of the residual kinetic energy. Thus, the teeth can have an optimized geometry to better support energy dissipation. Relative to the rest of the toothed ring 11a, the first teeth can significantly have a greater thickness and / or an asymmetric profile to better distribute the stress and thus limit the stress concentration on the teeth, thereby exhibiting better strength.

[0087] Time reset in the opposite direction

[0088] Advantageously, in order to avoid desynchronization between the main wheel 11 and the train of wheels of the timepiece movement 400, especially during the time reset in the opposite operating direction, the configuration of the part 11b and the toothed ring 10a is set to prevent the rotation of the latter, like a Maltese cross. Specifically, the part 11b has a cylindrical part that is concentric with the axis A1 and has a diameter close to the pitch circle diameter of the toothed ring 11a, so as to be able to interact with the adjacent sides of two teeth of the toothed ring 10a and prevent its rotation.

[0089] As an alternative or in addition, the rotation of the moving part 10 in the opposite operating direction and the driving of the display member 200 in the opposite direction can be prevented by a flywheel or a one-way coupling arranged between the moving part and the train of wheels of the timepiece movement 400. Of course, the one-way coupling must be shaped to maintain the synchronization of the triggering of the instantaneous driving phase with the train of wheels of the timepiece movement 400.

[0090] The following refers to Figures 9 to 16 Describe in detail the second embodiment of the timepiece 400.

[0091] This second embodiment advantageously includes the same devices or substantially the same devices as the first embodiment, except that it is particularly additionally provided with an auxiliary moving part that prevents the main wheel 11 from being desynchronized with respect to the train of wheels of the timepiece movement 400. This auxiliary moving part also enables the driving of the display member 200 during the time reset in the opposite operating direction.

[0092] The auxiliary moving part also pivots within the frame. The auxiliary moving part includes an auxiliary driving wheel 15 that is constantly driven by the train of wheels of the timepiece movement 400. The auxiliary driving wheel 15 can interact with an elastic device 14 fixed to or fastened to the main moving part.

[0093] More specifically, in this embodiment, the auxiliary moving part is coaxial with the main moving part. The auxiliary driving wheel 15 pivots around a core 16. The elastic device 14 is a helical spring 14, the inner end of which is driven onto or riveted to the core 16 fixed to the main wheel 11 and the cam 12. The outer end 14a of the spring 14 can interact with an angular stop 15b arranged on the auxiliary driving wheel 15.

[0094] The utilization of the interaction between the auxiliary driving wheel 15 and the spring 14 will be explained in detail below.

[0095] In this second embodiment, the moving member 10 includes an auxiliary gear ring 10b that is constantly engaged with the gear ring 15a of the auxiliary driving wheel 15, such that its rotational speed is constant and is fully synchronized with the gear train of the timepiece movement 400.

[0096] The transmission ratio between the pinion 10 and the auxiliary driving wheel 15 is selected such that the auxiliary driving wheel 15 has the same rotation period as the main driving wheel 11. It should be noted that the auxiliary driving wheel 15 performs a dragging rotation at a constant speed throughout its rotation period, which is contrary to the main driving wheel 11 that performs a dragging rotation within the angular range defined by the gear ring 11a and an instantaneous rotation within the angular range defined by the portion 11b. As a result, the duration or period during which the gear ring 10a engages with the gear ring 11a is the same as or substantially the same as the rotation period of the auxiliary driving wheel 15.

[0097] Therefore, during the mounting phase, the angular velocity of the auxiliary wheel 15 is higher than that of the main wheel 11. As will be explained in more detail below, relative to the auxiliary wheel 15, the main wheel 11 compensates for the angular offset that gradually accumulates during the mounting phase during the instantaneous driving phase.

[0098] The operating mode of the second embodiment is substantially the same as that of the first embodiment. Only the interaction between the spring 14 and the auxiliary driving wheel 15 adds new functions, which will be explained below.

[0099] In a variant, in this second embodiment, the main moving member and the auxiliary moving member of the driving device may not be coaxial, but pivot on two separate preferably parallel axes. Then they will be connected, for example, by meshing engagement.

[0100] In another variant, in this second embodiment, the elastic device 14 may include a lever or a pawl that interacts with the spring element.

[0101] Equipment stage

[0102] In the second embodiment, at the start of the mounting phase, immediately after Figure 10 the end of the driving phase shown, the free end 14a of the spring 14 is substantially in contact with the angular stop 15b of the auxiliary driving wheel 15.

[0103] Therefore, in the case where the angular velocity of the auxiliary wheel 15 is slightly higher than that of the main wheel 11, as Figure 11 shown, as the energy accumulating device is wound, the angular stop 15b gradually moves further and further away from the free end 14a.

[0104] At the end of the equipment phase, the angular spacing between the free end 14a and the angular stop 15b corresponds to or substantially corresponds to the angular range of the part 11b and, consequently, to the angular travel covered by the cam 12 during the instantaneous drive phase.

[0105] During the drive phase, the main moving members, in particular the main wheel 11, the cam 12 and the spring 14 instantaneously cover the angular travel required to drive the display member 200. As a reminder, said angular travel corresponds to the angular range of the part 11b and, consequently, to the maximum angular spacing between the free end 14a and the angular stop 15b. Thus, said angular spacing is instantaneously compensated for during the drive phase. After this phase, the free end 14a and the angular stop 15b return into contact or substantially into contact.

[0106] Additionally or alternatively, the elastic means 14 can be shaped so as to be able to partly or completely dissipate the residual kinetic energy after the drive of the display member 200 (i.e. at the end of the drive phase).

[0107] This second embodiment advantageously makes it possible to drive the display member 200 in the opposite operating direction without any risk of the main wheel 11 being out of step with the train of wheels of the timepiece movement 400. To this end, compared with the first embodiment, the part 11b does not interact with the moving member 10 in the manner of a Maltese cross, but is outside the latter's range. For example, the part 11b consists of a part of a cylinder, the radius of which is equal to or substantially equal to the root circle radius of the toothed ring 11a.

[0108] When the train of wheels of the timepiece movement is actuated in the opposite operating direction, the auxiliary toothed ring 10b drives the toothed ring 15a of the auxiliary wheel in a direction opposite to that of the hands of the watch, and the toothed ring 10a drives the toothed ring 11a of the main wheel until the part 11b faces the pinion 10, in other words until the lever 21 (in particular the sliding member 23) is on the stop part 12c. Thus, the toothed ring 10a rotates without load and is no longer able to drive the main wheel 11 in the opposite direction. Then, as Figure 14 shown, since the free end 14a of the spring 14 is in contact with the angular stop 15b, the main wheel 11 is driven by the auxiliary wheel 15 via the spring 14. Of course, the elastic means 14 are dimensioned to have sufficient angular stiffness to overcome the torque resulting from the interaction between the energy storage means 20 and the return part 12b and, consequently, to make it possible to drive the display member 200 in the opposite direction.

[0109] Once it has completely traveled through the return portion 12b in the opposite direction and at the moment it just transitions to the equipped portion 12a, the toothed ring 10a interacts with the toothed ring 11a of the main wheel 11 again. Therefore, due to the slight difference in angular velocity between the main wheel 11 and the auxiliary wheel 15, the spring 14 starts to be equipped. When the toothed ring 10a faces the portion 11b again, the maximum equipped level of the spring 14 is reached, as Figure 15 shown. The angular displacement or deformation of the free end 14a corresponding to its maximum equipment is equal to or substantially equal to the angular travel covered by the cam 12 during the instantaneous drive phase.

[0110] At this time, the main wheel 11 is separated from the moving member 10 and the energy accumulated in the spring 14 is thus returned, thereby instantaneously or substantially instantaneously driving the main wheel 11 and the display member 200 in the opposite direction. Therefore, the size of the elastic device 14 is also designed to accumulate sufficient energy to enable the lever 21, especially the sliding member 23, to return the return portion 12b in the opposite operating direction.

[0111] Continuing to actuate the gear train of the timepiece movement 400 in the opposite direction enables a new phase of equipping the elastic device 14 to be initiated by the interaction between the toothed ring 10a of the moving member 10 and the toothed ring 11a of the main wheel 11.

[0112] Therefore, for the second embodiment, resetting the time in the opposite direction enables a first dragging drive of the display member 200 to be achieved, and then a continuous instantaneous or substantially instantaneous drive in the opposite direction.

[0113] It should be noted that the energy required to equip the elastic device 14 is provided by the user when resetting the time in the opposite direction. In other words, this energy is not provided by the timepiece movement 400.

[0114] The present invention also relates to a method for operating a timepiece drive device 100 as described above. As described above, the operating method includes equipping the accumulator 22 substantially permanently via the cam follower 21, in addition to the drive phase in which the cam 12 is driven by the accumulator 22 via the cam follower 21.

[0115] Advantageously, the duration of the equipment corresponds to at least 90% of the time of the rotation period of the main wheel 11 of the timepiece drive device 100, or even corresponds to at least 99% of the time of the rotation period of the main wheel 11 of the timepiece drive device 100, or even at least 99.5%, or even substantially 100%.

[0116] Preferably, the method includes at least one iteration of the following steps, especially multiple iterations of the following steps:

[0117] - Engaging the first toothed ring 10a and the second toothed ring 11a to drive the cam 12 to equip the accumulator 22, and then

[0118] - Disengage the first gear ring 10a and the second gear ring 11a from the meshing engagement, and drive the cam 12 via the cam follower 21 by means of the accumulator 22.

[0119] The proposed solution advantageously enables the energy consumption of the timepiece movement 400 to be equalized during the assembly phase, which substantially corresponds to the rotation period of the main wheel 11 except for the instantaneous drive phase and the potential hysteresis caused by the meshing clearance during the transition between the instantaneous jump phase and the assembly phase. Thus, compared with the solutions known from the prior art, the energy consumed and thus the amplitude loss of the balance wheel can be constant or substantially constant.

[0120] In addition, considering that the energy required to instantaneously drive the display member 200 can be accumulated over a longer rotation duration or period than in the known solutions, the instantaneous consumption of the same total amount of accumulated energy can also be reduced. By increasing the assembly duration from 13 hours to 24 hours, for example, the assembly power can be reduced by 46%. By increasing the assembly duration from 20 hours to 24 hours, for example, the assembly power can be reduced by 17%.

[0121] Advantageously, the instantaneous drive device 100 also enables the display member 200 to be directly driven, with only the drive element 13 being implemented. This is because this solution does not require a lever arranged at the interface between the said members.

[0122] Of course, these solutions are not limited to simple date calendar systems, but are also particularly suitable for calendar systems that require, for example, more energy, such as annual date or perpetual date calendars. More generally, these solutions can be applied to any instantaneous jump display system for displaying time-based or time-derived information.

[0123] In the described embodiment, it is provided that for each rotation period of the main drive wheel 11, the calendar system 300 is driven by at least one pitch. However, regardless of the embodiment or variant, the instantaneous drive device can be adapted to drive the display system within each multiple or each submultiple of the rotation period of the main drive wheel 11. Of course, the geometries of the cam 12 and the main wheel 11 must then be specified.

[0124] Regardless of the embodiment or variant, the cam 12 can be replaced by a simple geometric element (such as a pin) that interacts with a profile similar to a cam profile formed on the cam follower 21 of the energy accumulation device 20.

[0125] Regardless of the embodiment or variant, the toothing of the moving part 10 and the toothing of the main wheel 11 can be produced at a plurality of separate levels, in particular a first level and a second level. This makes it possible to distribute the drive by appropriately truncating certain teeth of the first level and / or the second level in order to optimize the successive operations of engaging these teeth in meshing and disengaging them from meshing between the equipment phase and the drive phase. This configuration can be particularly advantageous if the moving part 10 includes a large number of teeth and / or if the difference in pitch circle diameter between the moving part 10 and the main wheel 11 is too small. This configuration can also make it possible to optimize the toothing profile, thus limiting or even eliminating to the greatest extent possible the meshing clearance when transitioning between the instantaneous jump phase and the equipment phase. Additionally or alternatively, this shaping of the teeth of the moving part 10 and the teeth of the main wheel 11 at two or more levels can also be particularly advantageous for implementing, for example, a Maltese cross type at the first level and a function of engaging in meshing at the second level.

[0126] Regardless of the embodiment or variant, preferably, the drive device (in particular the profile of the cam 12) is arranged such that the mechanical power supplied to the accumulator 22 is constant or substantially constant throughout the entire period or substantially throughout the entire period during which the cam 12 is not driven by the accumulator 22 via the cam follower 21.

[0127] Preferably, "instantaneous" refers to an action with a duration of one or more small fractions of approximately one second, which is typically about one hundredth or about one twenty-fifth or about one tenth of one second.

[0128] In contrast, "dragging" refers to a slow and even continuous action, such as displacement, for example, lasting for at least several seconds.

Claims

1. A timepiece drive device (100), in particular a system (300) for displaying time-based or time-derived information, in particular an instantaneous jump calendar system, the timepiece drive device (100) comprising: An input moving member (10) including a first ring gear (10a); a main wheel (11) including, on only a portion of its periphery, a second toothed ring (11a), said second toothed ring being in meshing engagement with said first toothed ring, a cam (12) connected to the main wheel (11), in particular connected to the main wheel (11) with minimal play, in particular fixed to the main wheel (11), and having a cam profile (12a, 12b, 12c), a cam follower (21) interacting with said profiles (12a, 12b, 12c), and An accumulator (22) elastically returns the cam follower against the profile (12a, 12b, 12c) of the cam (12).

2. The timepiece drive device (100) according to claim 1, wherein: The angular range of the periphery of the main wheel including the second toothed ring (11a) is equal to or substantially equal to the angular travel covered by the cam (12) when it is not driven by the energy accumulator (22) via the cam follower (21), and / or the angular range of the periphery of the main wheel (11) without teeth is equal to or substantially equal to the angular travel covered by the cam (12) when it is driven by the energy accumulator (22) via the cam follower (21), and / or The clock drive device (100), in particular the cam, the first gear ring and the second gear ring are arranged so that the action of the cam follower (21) on the cam (12) causes the main wheel (11) to rotate independently of the input moving member (10).

3. The timepiece drive device (100) according to claim 1 or 2, wherein: The timepiece drive device (100), in particular the cam (12), the first toothed ring (10a) and the second toothed ring (11a), are arranged so that the energy accumulator (22) is substantially permanently equipped via the cam follower (21), except for the driving phase in which the cam (12) is driven by the energy accumulator (22) via the cam follower (21).

4. A timepiece drive device (100) according to any one of the preceding claims, wherein: The drive device is arranged so that: The cam (12) is driven within a first angle range via the cam follower (21) by the action of the accumulator (22), and The cam (12) supplies energy to the energy storage device (22) via the cam follower in a second angular range complementary to the first angular range.

5. A timepiece drive device (100) according to any one of the preceding claims, wherein: The drive device, in particular the profile of the cam (12), is arranged so that the mechanical power supplied to the accumulator (22) is constant or substantially constant throughout the entire time period during which the cam (12) is not driven by the accumulator (22) via the cam follower (21).

6. A timepiece drive device (100) according to any one of the preceding claims, wherein: The cam follower (21) comprises a lever (21).

7. A timepiece drive device (100) according to any one of the preceding claims, wherein: The energy storage device (22) comprises a spring (22), in particular a spring blade.

8. A timepiece drive device (100) according to any one of the preceding claims, wherein: The cam (12) is movably connected to a drive element (13) for driving a display element (200) for displaying time-based information, in particular the cam (12) is fixed to a drive element (13) for driving a display element (200) for displaying time-based information, for example a finger (13) which interacts with a toothed ring (201) of the display element (200) for displaying time-based information.

9. A timepiece calendar (300), in particular a simple date calendar or an annual calendar or a perpetual calendar, comprising a timepiece drive device (100) according to any of the preceding claims, the calendar comprising a display element (200) for displaying time-based information, such as a disc with numbers, the display element (200) comprising a toothed ring (201).

10. A watch movement (400), comprising: A timepiece drive device (100) according to any one of claims 1 to 8, and / or A timepiece calendar (300) according to claim 9.

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

12. A method for operating a timepiece drive device (100), the timepiece drive device (100) comprising: Cam (12), a cam follower (21), and The cam follower (21) is pressed against the accumulator (22) returning the cam (12), The method comprises substantially permanently arming the accumulator (22) via the cam follower (21), except for a drive phase in which the cam (12) is driven by the accumulator (22) via the cam follower (21).

13. The operating method according to claim 12, wherein: The duration of the arming corresponds to at least 90% of the time of a rotation cycle of the main wheel (11) of the timepiece drive (100), or even to at least 99% of the time of a rotation cycle of the main wheel (11) of the timepiece drive (100), or even to at least 99.5% of the time of a rotation cycle of the main wheel (11) of the timepiece drive (100), or even to substantially 100%.

14. An operating method according to claim 12 or 13, in particular a method for operating a timepiece (500) according to claim 11 or a timepiece movement (400) according to claim 10 or a timepiece calendar (300) according to claim 9 or a timepiece drive device (100) according to any one of claims 1 to 8, said method comprising at least one iteration of the following steps: The first gear ring (10a) and the second gear ring (11a) are meshed and engaged to drive the cam (12) to equip the accumulator (22), and then The first gear ring (10a) and the second gear ring (11a) are disengaged and the cam (12) is driven by the accumulator (22) via the cam follower (21).

15. The operating method according to any one of claims 12 to 14, wherein: The driving of the cam (12) is instantaneous.

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