CLOCK MOVEMENT FOR A CLOCK

Description

technical field

[0001] The present invention relates to the field of watchmaking. More particularly, it concerns a movement for a timepiece. State of the art

[0002] Complicated watches, incorporating multiple additional mechanisms such as date displays, moon phase indicators, chronographs, and so on, typically require not only a large size but also significant torque to operate. To ensure an adequate power reserve, the mainspring barrels must therefore be large. Consequently, the greater the number of complications, the larger the watch, since current design techniques dictate that each complication be built to a conventional watchmaking scale.

[0003] Furthermore, when complications place a significant load on the energy source, the oscillations of the regulating organ can be disrupted. Indeed, if no complications consume energy, the regulating organ receives a high torque, which decreases as the complications become more active and their energy demands increase. Since the regulating organ's behavior varies according to the torque it receives, this behavior can be highly variable, thus compromising isochronism.

[0004] The aim of the present invention is therefore to at least partially overcome at least one of the aforementioned drawbacks, and thus to offer a clock movement with increased power reserve and improved isochronism.

[0005] Document EP0108412 describes a time-setting device comprising several toothed shafts with a diameter of 0.8 mm. These shafts are involved exclusively in setting the time of the movement and therefore cannot help overcome these drawbacks, since this device is not involved in the transmission of torque between the mainspring barrel and the regulating organ of the movement. Furthermore, document EP 2 821 862 reveals a deadbeat seconds mechanism in which relatively small pinions are involved in driving the corresponding display. Disclosure of the invention

[0006] More specifically, the invention relates to a movement for a timepiece, comprising at least one energy source, for example one or more barrels, a finishing gear train kinematically linking said energy source to a regulating organ such as an escapement associated with a balance wheel and hairspring, and a display organ arranged to be driven by said energy source according to the regulating organ.

[0007] The movement further comprises an actuator arranged to influence, that is, to control, block, release, trigger, or vary the speed of the rotational transmission between the power source and the display unit, and a control device arranged to control the actuator. According to the invention, the control device comprises entities that are either a set of at least two elements fixed together and rotating about a common axis, or a single element rotating about its own axis, all of these entities having a diameter less than or equal to 2.5 mm, and / or, in the case of a lever, the maximum radius measured from its pivot point being less than or equal to 1.25 mm. Furthermore, the actuator is located within the finishing gear or is integrated into the power source.

[0008] By these means, the control mechanism consists of a set of moving parts with extremely low inertia, and therefore requires significantly less torque to drive them. Consequently, the operation of the control mechanism requires less torque than usual from the power source and the finishing gear train, which reduces stress on the regulating organ and increases the movement's power reserve. Furthermore, the use of smaller components also allows for the development of complications with fewer components and greater simplicity.

[0009] The said actuator may be, for example, a differential gear, a cam, a clutch, a lever, a rake, a rack, or a combination of several of these elements.

[0010] According to the invention, said actuator is located in said finishing gear, and / or is integrated into said energy source, such as for example by being provided in or on the drum of a barrel.

[0011] In one variant, said control device can be arranged to be controlled directly by said regulating organ.

[0012] In one variant, the actuator can be located in an additional kinematic chain extending from the energy source, with the control device being controlled by the regulating element. The torque used by the actuator can thus be independent of that distributed by the finishing gear, which further reduces the influence of the regulating element on its operation.

[0013] In one variant, the power source may consist of a single drive unit, or alternatively, it may consist of a first drive unit arranged to drive the finishing gear train, and a second drive unit arranged to drive the additional kinematic chain. This latter option minimizes the impact of the control device and actuator on the operation of the regulating organ, and also allows for optimization of the torque supplied to each part of the movement by selecting appropriate mainspring barrels.

[0014] In one variant, the said control device can be arranged to be controlled by a user, for example in the case where the control device drives a chronograph or similar.

[0015] In one variant, said control device can be arranged to be driven by said finishing gear.

[0016] In one variant, the control device and actuator are located within the finishing gear, the regulating member comprising an oscillator with a diameter of 5 mm or less. In this variant, the control device, which includes a set of reduced-sized moving parts, interfaces between a conventionally sized drive source and a reduced-sized oscillator.

[0017] In one variant, said actuator may be driven by said energy source or by said finishing gear, and said control device is controlled directly or indirectly by said regulating member.

[0018] In one variant, the movement may further include an additional display device arranged to be driven by said finishing gear or by said regulating organ. This additional display organ may even be integrated into an escape wheel or into a tourbillon or carousel cage.

[0019] In one variant, at least part of said finishing gear and / or at least one other kinematic linkage may exclusively be composed of entities being either a set of at least two elements joined together and rotating around a common axis, or a single element rotating around its own axis, said entities having a size less than or equal to 2.5mm.

[0020] These variants can be combined in any way that makes technical sense.

[0021] Finally, the invention relates to a timepiece comprising a movement as defined above. Brief description of the drawings

[0022] Further details of the invention will become clearer upon reading the following description, made with reference to the attached drawings in which: THE figures 1 to 7 are schematic representations of various variants of watch movements according to the invention; and the figures 8 to 14are schematic representations of watch movement constructions corresponding respectively to those of figures 1 to 7 . Embodiments of the invention

[0023] There figure 1This schematically illustrates a first variant of a watch movement 1 according to the invention. This movement 1 comprises a power source 3 including at least one driving element, such as one or more mainspring barrels, an electric motor, or the like, and a finishing gear train 5a, 5b which connects the power source 3 to a regulating element 7 constituting a time base. The regulating element, often also called a "regulator," typically includes an escapement and a balance-spring oscillator, but also, for example, a tuning fork regulator, a tourbillon, or any other known form of regulator. In this variant, an actuator 9 is incorporated into the finishing gear train 5a, 5b and drives a display element 11. The finishing gear train 5a, 5b may be of conventional size ("watch size"). Typically, watch-sized mobiles commonly used in finishing gears have a diameter of up to around 12mm.It is known that some wheels or pinions can have a very small diameter, down to around 0.90 mm, for example in the case of an escapement pinion, but these wheels or pinions are part of larger components, whose overall diameter (defined by the largest wheel composing the component) is significantly greater. By "large component," we mean either a set of at least two elements (wheel, pinion, cam, etc.) fixed together in rotation around a common axis, or a single rotating element (wheel, pinion, cam, etc.) around its own axis and which is not fixed in rotation to another element.

[0024] This actuator 9 is in turn controlled by a control device 13, which receives information from the regulating organ 7 via an arbitrary kinematic linkage 8. The control device 13 comprises moving parts (wheels, cams, etc.) all of which are "reduced size," that is, they have a diameter less than or equal to 2.5 mm, or even less than or equal to 2 mm, 1.5 mm, or even 1 mm, as well as any other components of a size suitable for interacting with such moving parts. The kinematic linkage 8 may consist of moving parts of clockwork size, or of reduced size (that is, all having a diameter less than or equal to 2.5 mm, or even less than or equal to 2 mm, 1.5 mm, or even 1 mm), and the kinematic linkage 10 between the control device 13 and the actuator 9 may also be of reduced size as defined above.

[0025] Thanks to the reduced size of the components constituting the control device 13 and possibly also the kinematic linkage 8, their force and torque requirements are significantly lower compared to watch-sized components. This minimizes the disturbance to the regulating organ 7, since the torque demand varies less than usual. Indeed, the inertia of the moving components of the control device 13 is negligible compared to those of conventional size, and the torque requirement can be reduced to nano-Newton x meters.

[0026] Furthermore, the control device occupies a significantly reduced space, which also allows for an increased number of complications controlled by the control device 13 (chronograph, date, other display, etc., see below) that can be integrated into a given volume, if necessary, without requiring substantial additional torque for their operation, and allowing for a simplification and / or reduction in the number of components for a given mechanism. In the variant of the figure 1 The control device 13 receives energy directly from the regulating organ, which is not normally possible without disrupting the latter. Therefore, a power take-off directly from the escapement wheel or even the balance wheel could be considered, given that the torque extracted is negligible compared to that of the conventional case.

[0027] The control device 13 is arranged to control the actuator 9 in order to distribute torque arriving from the drive unit 3 to the display 11.

[0028] Several mechanisms are possible for constructing the actuator 9. For example, it could be a differential gear, on which the control device 13 acts to distribute torque to the display 11 by braking, locking, or releasing an input or output, for example, to create a differential-type clutch without interrupting the kinematic linkage. Alternatively, the actuator 9 could be a clutch, whose switching between the engaged and disengaged states is arranged to occur in response to a small control force. Actuators 9 could also be based on racks or pinions, one or more cams, or levers. Yet another alternative could be a gearbox, for example, composed of an epicyclic gear train, with the control device thus changing the display's speed.

[0029] For this purpose, the display 11 may be a date display (Western or otherwise), a display of the month, year, week, days of the week, moon phase, tides, biological, astronomical, or astrological cycles, an hour and / or minute and / or second display, a lightning bolt, or any other time-related display. The kinematic linkage 14 between the actuator 9 and the display element 11 may be of clockwork size or of reduced size as defined above. In the latter case, the display element may optionally be smaller than conventional and may be viewed through an optical device such as a magnifying glass.

[0030] Furthermore, and as illustrated by dotted lines, it is possible to provide one or more additional displays 11a in the movement 1, driven for example directly from the driving element 3, from a part of the finishing gear 5a, 5b, or otherwise.

[0031] Since the finishing gear train 5a, 5b consists of watch-sized components, and the power source provides conventionally sized torque, the display 11, as well as the additional displays 11a, can also be conventionally sized. With current technologies, if the entire movement were reduced in size, it would be difficult, if not impossible, to drive, for example, one or more conventionally sized hands, or a date disc. The movement according to the invention thus allows a conventionally sized display to be controlled by means of a reduced-sized control device.

[0032] There figure 8 schematically illustrates an architecture that corresponds to the functional diagram of the figure 1 This construction has been represented very schematically and is in no way to scale. Furthermore, some kinematic links have simply been represented by arrows, as those skilled in the art know how to implement them using conventional gears (for example), which also applies to the figures 9 to 14 .

[0033] In this architecture, the regulating organ 7 comprises a balance wheel and hairspring assembly 7a, which cooperates with an anchor 7b and an escape wheel 7c in a known manner. The actuator 9 is a differential gear comprising an input 9a and two outputs 9b and 9c. In the illustrated variant, this differential is of the spherical type, with a first sun wheel serving as the input and arranged to be driven by a mainspring barrel 3 acting as the power source. A second sun wheel serves as the first output 9b, which drives the regulating organ 7. The second output 9c is a planet carrier, which carries a plurality of bevel gears 101 that mesh with each of the sun wheels 9a and 9b in a known manner.

[0034] The control device 13 includes a constant-radius cam 13a, part of a moving part with a maximum diameter of 2.5 mm, driven directly or indirectly by the escapement pinion 7d, such that it is continuously driven when the movement 1 is in operation. This cam 13a is positioned within a first fork 13b of a double fork 13c, which is pivoted appropriately on a frame element. A second fork 13d engages with an external toothed section 9d in the differential's planet carrier 9c. This toothed section 9d may be conventional, edge-cut, double edge-cut, or any other suitable toothed section or arrangement with similar functionality.

[0035] When the cam 13a rotates, the double-fork 13c oscillates between two extreme positions arranged to release the planet carrier 9c in steps, typically one tooth per alternation of the double-fork. During each release of the planet carrier 9c, it is driven in rotation by one step by the torque supplied to the first input 9a by the barrel 3, without substantially affecting the torque supplied by the first output 9b to the regulating organ 7.

[0036] Since the display 11 is kinematically linked to the satellite carrier 9c, it is thus driven in steps each time the satellite carrier 9c is released. By these means, the control device 13 controls the distribution of torque to the display 11, by blocking and releasing it successively.

[0037] It should also be noted that a relatively small force is required to lock the satellite carrier 9d, and consequently the control device 13 can be small. Depending on the gear ratio between the escapement pinion 7d and the cam 13a, the display 11 can be advanced in steps over a desired period. For example, the manufacturer can plan to advance the display 11 at a rate of one step per second, per minute, per hour, per day, or at any other desired rate, substantially without affecting the torque supplied to the regulating element 7. Isochronism can thus be improved.

[0038] Furthermore, this arrangement allows for a step-by-step display without requiring any spring to be wound, or a jumper to be overcome, as is typically the case in such conventional displays. The torque requirement is thus reduced, thereby increasing the power reserve of movement 1.

[0039] There figure 2illustrates a variant of a movement 1 according to the invention, which differs from that of the figure 1 in that the control device 13 is itself controlled by a user action, schematically represented by the dashed arrow 15. In this variant, the user can, for example, press a push button, a latch, or equivalent, or can rotate a ring or similar mechanism. The torque that drives the control device 13 is thus supplied by the user, and therefore there is no power take-off on the regulating element or the finishing gear for the operation of the control device 13.

[0040] In this context, the actuator 9 can be a conventional or differential clutch enabling the operation of a counter such as a chronograph or countdown timer, a tachometer, or similar device. Alternatively, the actuator 9 can be a gearbox, for example, composed of an epicyclic gear train, which allows the display element 11 to advance or retract (depending on the gear ratios) at one or more speeds higher than its normal operating speed, in order to perform a rapid correction of the display element 11, for example, when setting the time.

[0041] For this variant, the same comments regarding the size of the moving parts constituting the kinematic links 10 and 14 also apply here.

[0042] There figure 9 schematically illustrates an architecture that corresponds to the functional diagram of the figure 2This construction has been represented very schematically, and is in no way to scale.

[0043] In this variant, the actuator 9 is illustrated as an epicyclic gearbox 9f, which allows the display 11 to be driven at different speeds under the control of the control member 13, which includes one or more small moving parts (not illustrated) which are controlled by the pusher 13z. This gearbox 9f takes its force on an axis 9e which comprises the finishing gear 5a, 5b, and can take on a suitable shape.

[0044] Examples include epicyclic bicycle gearboxes, such as those described in US documents 2301852, US 3021728, DE 3440067, and others. Those skilled in the art know how to adapt these systems to a timepiece, particularly by modifying them for a relatively flat construction.

[0045] Another type of gearbox particularly suited to this role is a differential gear with a first input arranged to be driven by the barrel 3, a second input arranged to be locked or unlocked by the control member 13, and an output that drives the display 11. By locking or unlocking the second input, the rotational speed of the output is changed, according to the selected gear ratios. The second input is equipped with a disengageable linkage, such as a ratchet, friction, or similar device, which serves to kinematically connect it to the first input when the second input is not locked.

[0046] For example, if it is desired to be able to reverse the direction of rotation of display 11 following a user command, the differential can be arranged so that its planet carrier acts as said second input. When the planet carrier is not locked and therefore rotates with the first input, the gear ratio between the first input and the output is consequently 1:1.

[0047] By blocking the second input, the planetary gears act as reversers, and the gear ratio between the first input and the output consequently becomes 1 to -1, or another negative ratio depending on the number of teeth chosen and the differential's design (spherical, flat, etc.). This type of differential reverser is described, for example, in document WO2017071887 and is therefore part of the knowledge of those skilled in the art.

[0048] Such an inverter allows, for example, to provide a countdown timer on demand (if, for example, the kinematic chain between the actuator and the display 11 also includes a clutch in order to constitute a chronograph), or to make small corrections via a push button if the movement is ahead.

[0049] If, however, the first input is the satellite carrier and the second input is a solar wheel or a solar pinion, the rotational speed of the output can be varied while maintaining the same sign for the gear ratio. In other words, the output will always rotate in the same direction.

[0050] By choosing the construction of the differential gear (spherical, flat, ...) as well as the number of teeth, the gear ratios can be chosen at will by a person skilled in the art.

[0051] Furthermore, by providing two such differential gears in series, the manufacturer can be given more choice regarding speed ratios, and even several different speeds if one, the other or even both second inputs of the two differentials are blocked.

[0052] These types of gearboxes are suitable for clockwise display corrections controlled by a push button. For example, in the case of an 11-digit display showing minutes and hours, if the gear ratio is 1:1 when the second input(s) is / are free and 1:1440 when it / they are blocked, the display will complete a full 24-hour cycle in one minute. Of course, these gear ratios can be chosen at will, particularly in the case of a small gearbox (i.e., one with moving parts having a diameter of 2.5 mm or less).

[0053] There figure 3illustrates yet another variant of a movement 1 according to the invention. This variant differs from that of the figure 1The actuator is not located within the finishing gear 5, but has its own kinematic linkage consisting of an additional gear 17 extending from the drive unit 3. The drive unit can thus divide its torque between the finishing gear 5 and the additional gear 17 via a differential gear (not shown). This differential can be arranged according to the design requirements to distribute the torque symmetrically between the two gears 5 and 17, or asymmetrically, depending on the gear ratios used. In this way, the torque supplied to each gear can be optimized for the operation of either the regulating element or the display. For example, a display requiring high torque and a regulating element requiring little energy, or vice versa, can be driven from a single barrel.

[0054] Alternatively, in a less complex drive unit construction 3, one of the gears 5, 17 can be driven from the drum of a barrel, the other from its shaft. This variant has fewer components compared to the differential solution described above. In order to manage the torque ratio distributed to the two gears 5, 17, the diameters of the moving parts that serve as power take-offs on the drum and on the barrel shaft can be chosen accordingly.

[0055] For this variant, the same comments regarding the size of the moving parts constituting the kinematic links 8, 10, and 14 also apply here. Typically, the kinematic link 14 between the actuator 9 and the display element 11 would be of watch-like size.

[0056] There Figure 10 schematically illustrates an architecture that corresponds to the functional diagram of the figure 3This construction has been represented very schematically, and is in no way to scale.

[0057] In this variant, the torque from the barrel 3 is divided by means of a differential gear 3c in a known manner. The torque arriving at the input 3d of the differential 3c from the barrel 3 exits in two directions through each of the two outputs 3e (which leads to the regulating element 7) and 3f (which drives the display 11). The shape of this differential is not significant and does not need to be described in further detail. Furthermore, the aspects that are identical to the variant of the figure 8 do not bear any reference signs and will not be described again.

[0058] The control device 13 is driven by the exhaust pinion 7d and is similar to that illustrated on the figure 8Therefore, it does not need to be described a second time. However, the actuator 9 has a toothed wheel 9g which interacts with the second fork 13d so as to be locked and released in steps at each alternation of the double-fork 13c.

[0059] This toothed wheel 9g is driven by the second output 3f of the differential, and is locked and unlocked in stages with each alternation of the double fork 13c. The control device 13c thus controls the torque distribution between the barrel 3 and the display 11. The advantages of this variant are the same as those of the figure 9 .

[0060] The variant of the figure 4 differs from that of the figure 3in that the drive unit 3 comprises two separate energy sources 3a, 3b, such as a pair of barrels. In this variant, the torque used by the display 11 has no influence on the finishing gear 5, and cannot in any way disturb the regulating element 7. Furthermore, the size of the two energy sources 3a, 3b can be chosen according to their respective roles. The same comments regarding the kinematic links 8, 10, and 14 also apply here.

[0061] There figure 11 illustrates a construction that corresponds to the diagram of the figure 4 , and will be described exclusively by its differences from that of the Figure 10 Again, this construction has been represented very schematically, and is in no way to scale.

[0062] In this variant, the power source 3 comprises a first barrel 3a that drives the regulating organ, and a second barrel 3b that drives the display 11. A distinctive feature of the construction illustrated here is that a toothed section on the barrel meshes directly with the escapement pinion 7d of the regulating organ, making the finishing train 5 as compact as possible and minimizing the number of components. This is made possible by the fact that the display 11 is not driven by the finishing train 5, but is only controlled by it. Indeed, the control device 13 receives information only from the regulating organ 7 (more specifically from the escapement pinion 7).The display drive is therefore located entirely outside the finishing gear under the control of the control device 13, which regulates the rotation speed of the display under the effect of the torque supplied by the second barrel 3b and thus regulates the gear ratios for the display 11.

[0063] As in the variant of the Figure 10 , the escapement pinion 7d drives the control device 13, the toothed wheel being driven by the second barrel 3b, and driving the display device 11.

[0064] This variant allows the torque supplied by each of the barrels to be adapted according to its role, since the first barrel 3a can be adapted for driving the regulating organ 7, while the second barrel 3b can be more powerful in order to drive the display device 11. The control device 13 again having moving parts with a diameter of 2.5mm at most, it consumes very little energy and therefore hardly disturbs the regulating organ 7. However, it can control higher torques from the second barrel 3b.

[0065] There figure 5 illustrates a variant based on that of the figure 3However, this version differs from the latter in that the control device 13 receives information from the finishing gear 5 upstream of the regulating member 7. This variant allows the control device 13 to receive more torque, which in turn can supply more torque and / or force to the actuator 9 to activate / deactivate it. Consequently, the control device 13 can operate with an actuator 9 that requires more force to trigger its operation. The same comments regarding the kinematic links 8, 10, and 14 also apply here.

[0066] There figure 12 illustrates a construction that corresponds to the diagram of the figure 5 , and will be described exclusively by its differences from that of the figure 11 This construction has been represented very schematically, and is not to scale.

[0067] In this variant, only one drum 3 is present, and it has a first power take-off 3m on its drum, as well as a second power take-off on its shaft 3n. The first power take-off 3m drives the regulating element 7 again, and the second drives the actuator 9 via the additional kinematic chain 17. Otherwise, this variant operates similarly to that of the figure 11 However, it is also noted that the control device 13 can alternatively be driven by the barrel drum 3m, or by any possible moving part in a kinematic chain linking the drum 3m to the escape pinion 7d.

[0068] There figure 6illustrates yet another variant of a movement 1 according to the invention. In this variant, the actuator 9 is located directly in the finishing gear 5a, 5b, 5c, and the control device 13 is also located in the same finishing gear 5a, 5b, 5c, upstream of the regulating member 7 and downstream of the actuator 9. In so doing, the control device 13 drives the actuator 9 by transmitting timing information to it from the regulating member 7.

[0069] In this variant, the actuator can be, for example, a cam arranged in the finishing gear train 5a, 5b, or alternatively in a branch thereof, to advance the display element 11 in increments, and the regulating element 7 can itself be of reduced size. In this case, the regulating element 7 can include a balance wheel with a diameter equal to or less than 5 mm, depending on the material chosen for its manufacture, and the control device 13 acts as an interface between the parts of the finishing gear train 5a, 5b which have a conventional horological size and the reduced-size regulating element 7.

[0070] Of course, other possibilities are conceivable.

[0071] In this variant, the part of the finishing gear 5b which is located between the actuator 9 and the control device 13 can be composed of clock-sized or reduced-size mobiles, and the part 5c which links the control device 13 to the regulating organ is of course reduced in size in order to cooperate with the reduced-size regulating organ 7.

[0072] There figure 13 illustrates a construction that corresponds to the diagram of the figure 6 This construction has been represented very schematically, and is in no way to scale.

[0073] In this variant, the overall construction of the movement 1 is conventional, the barrel 3 being kinematically linked to the regulating organ 7 via a finishing gear 5.

[0074] A constant-radius cam 9j is mounted on one of the moving parts of the finishing gear, which is part of the actuator 9 and the control device 13. This cam interacts with a toothed wheel 103 via a hook 105 carried by a flexible arm 107. The flexible arm 107 is attached to a rigid arm 109 extending from a fork 111 that cooperates with the cam 9j. When the cam 9j rotates, the rigid arm 109 oscillates about its pivot axis 113, advancing the toothed wheel 103 clockwise (in the figure) by one tooth increment. The wheel 103 is positioned by a jumper 115 in a known manner. The shape of the hook 105 and the flexibility of the arm 107 allow the hook 105 to skip teeth as it moves to the left. Since the wolf's toothed wheel 103 is kinematically linked to the display 11, the latter is also driven in turn.

[0075] There figure 7illustrates yet another variant of a movement 1 according to the invention.

[0076] In this variant, the regulating member 7 is in direct kinematic connection with the driving member 3 via the finishing gear 5, and an additional display member 12 is provided downstream of the regulating member 7.

[0077] This time, the control device 13 takes information downstream of the regulating organ 7, or alternatively directly from the latter, and the actuator takes force from a moving part of the finishing gear 5 or alternatively directly from the energy source.

[0078] In doing so, the actuator 9 can drive the display 11 under the control of the control device 13, and the regulating member 7 can drive an additional display member 12.

[0079] In this variant, the kinematic linkage 8 between the regulating organ 7 and the control device 13, as well as that between the latter and the actuator, will be of reduced size, and that joining the finishing gear 5 to the actuator 9 can be of watchmaking size or reduced.

[0080] Furthermore, the additional display element 12 could be located directly on the regulating element 7, for example by being integrated into an escape wheel, a tourbillon or carousel cage, or similar.

[0081] There figure 14 illustrates a construction that corresponds to the diagram of the figure 7 This construction has been represented very schematically, and is in no way to scale.

[0082] The construction comprises a single barrel 3, whose torque is divided by a differential gear 3c in a known manner. The torque arrives at a first sun wheel 3g and exits at a first output 3h (a second sun wheel) to drive the regulating organ 7, and at a second output 3i (a planet carrier) to drive the actuator 9. Of course, other arrangements are possible, such as those of the Figures 10 And 12 among other things.

[0083] The actuator 9 shown here is a wheel carrying a single finger 9h, which is held by a retaining beak 13i which has a lever 13g.

[0084] The control device 13 consists of this lever 13g, which also provides the kinematic link 10 between the regulating member 7 and the actuator 9.

[0085] The lever 13g is actuated by a pin 8a carried by the rim of the balance wheel 7a, or by another element such as a plate that is rotationally fixed to the balance wheel 7a. It is therefore clear that the pin 8a constitutes the kinematic link 8 between the regulating organ 7 and the control device 13. It is also possible to actuate the lever 13g by the escapement pinion 7d or by an element driven by it.

[0086] Lever 13g pivots around a point at 1 o'clock, chosen here at one end of lever 13g to simplify the diagram. However, pivoting at an intermediate point, combined with a more realistic mechanism geometry, is preferable.

[0087] In the sense of the invention, the "diameter" of the lever is twice its maximum radius measured from its pivot point 13h, and is at most 2.5 mm.

[0088] The shapes of lever 13g and pin 8a are chosen so that, when balance wheel 7a oscillates, pin 8a strikes lever 13h and causes it to pivot. If the lever acts in the same plane as the balance wheel, this can be done without particular difficulty. If, however, the lever acts in a different plane, as implied by the figure 14 Beveled surfaces, cam surfaces or similar can be provided to ensure that the 13g lever is actuated in a suitable manner.

[0089] When the lever is lifted, the beak 13i releases the finger 9h, and the actuator wheel 9 can rotate once. A spring return element 13j ensures that the lever 13g is brought back against the surface of the wheel 9 when it is not under the control of the pin 8a and can block the passage of the finger 9h. In doing so, with each oscillation of the balance wheel 7a, the actuator 9 completes one revolution, and drives the display 11 by one step.

[0090] If pin 8a is retractable in one direction of rotation of the balance wheel 7a but not in the other, lever 13g will be actuated once per oscillation of the balance wheel 7a. Furthermore, it is possible to provide several fingers (or a toothed section) on actuator 9 to select the desired gear ratio between the barrel and the display 11.

[0091] It is also noted that the additional display 12 is illustrated as being driven by the escapement pinion 7d included in the regulating organ 7. However, it is also possible that the lever carries or actuates a hook which advances an additional actuator, for example of the type illustrated on the figure 13 , in order to trigger an additional display.

[0092] In each variant, it is possible for the actuator 9 and the control device 13 to be integrated into a single unit performing both functions, as is the case in the variant of the figure 13 Furthermore, the actuator 9 and / or the control device 13 can act as a kinematic link, as is notably the case with the figure 14 , and it is also possible that the actuator 9 is integrated into a drum of a barrel constituting the driving element 3.

[0093] Small-sized mobiles, i.e. those forming part of the control device 13, as well as certain kinematic chains as mentioned above, can be manufactured for example by micromachining processes capable of defining elements with voxels on the order of a few hundred nanometers, and thus of creating shapes with a precision on the order of the micrometer.

[0094] Examples include LIGA processes, masking and etching processes using a material slab, photostructuring of glass or quartz with a femtosecond laser, and high-resolution additive manufacturing in metal, epoxy, or ceramics. "Additive manufacturing" is the general term for all manufacturing processes that involve adding material, particularly 3D printing, including 3D photolithography, laser sintering, and others. A more detailed discussion of this topic can be found in Swiss patent application CH360 / 16.

[0095] Although the invention has been described above in connection with specific embodiments, additional variants are also conceivable without departing from the scope of the invention as defined by the claims. Il It should be noted, in particular, that aspects of the various variants can be combined in any way that makes technical sense.

Claims

1. Movement (1) for a timepiece, comprising: - at least one energy source (3, 3a, 3b); - a finishing gear train (5, 5a, 5b, 5c) kinematically connecting said energy source (3, 3a, 3b) to a regulating member (7); - a display member (11) arranged to be driven by said energy source; - an actuator (9) arranged to influence the transmission of rotation between said energy source (3, 3a, 3b) and said display member (11); and - a control device (13) arranged to control said actuator (9), characterized in that said control device (13) comprises entities selected from: - a set of at least two elements rotating together about a common axis; - a single element rotatable about its own axis, wherein said entities all have a diameter less than or equal to 2.5 mm and / or, in the case of a lever, the maximum radius measured from its pivot point is less than or equal to 1.25 mm, and in that said actuator (9) is located in said finishing gear train (5, 5a, 5b) or is integrated into said power source (3, 3a, 3b).

2. Movement (1) according to claim 1, wherein said actuator (9) comprises at least one of: a differential gear, a cam, a clutch, a lever, a rake, a rack.

3. Movement (1) according to one of the preceding claims, wherein said control device (13) is arranged to be controlled by said regulating member (7).

4. Movement (1) according to one of the preceding claims, wherein said actuator (9) is located in an additional kinematic chain (17) extending from said power source (3, 3a, 3b), the control device (13) being controlled by said regulating member (7).

5. Movement (1) according to claim 4, wherein said energy source (3) comprises a single drive member (3).

6. Movement (1) according to claim 4, wherein said power source (3, 3a, 3b) comprises a first drive member (3a) arranged to drive said finishing gear train (5), as well as a second drive member (3b) arranged to drive said additional kinematic chain (17).

7. Movement (1) according to one of claims 1 to 3, wherein said control device (13) is arranged to be controlled by a user.

8. Movement (1) according to one of claims 1 to 3, wherein said control device (13) is arranged to be driven by said finishing gear train (5, 5a, 5b).

9. Movement (1) according to claim 8, wherein said control device (13) and said actuator (9) are located in said finishing gear train (5a, 5b, 5c), said regulating member (7) comprising an oscillator having a diameter equal to or less than 5 mm.

10. Movement (1) according to claims 4 and 8.

11. Movement (1) according to one of claims 1 to 3, wherein said actuator (9) is driven by said power source (3, 3a, 3b) or by said finishing gear train (5, 5a, 5b), and said control device (13) is controlled directly or indirectly by said regulating member (7).

12. Movement (1) according to one of the preceding claims, further comprising an additional display device (11a, 12) arranged to be driven from said finishing gear train (5, 5a, 5b) or by said regulating member (7).

13. Movement (1) according to one of the preceding claims, in which at least part of said finishing gear train (5, 5a, 5b) and / or at least one other kinematic link (8, 10, 14, 17) comprised by said movement (1) comprises exclusively entities selected from: - an assembly of at least two elements rotating together about a common axis; - a single element rotating about its own axis, said entities having a diameter of less than 2.5 mm and / or, in the case of a lever, the maximum radius measured from its pivot point being less than or equal to 1.25 mm.

14. Timepiece comprising a movement (1) according to one of the preceding claims.