CH713326B1 - Movement for a timepiece comprising an actuator controlled by a control device. - Google Patents

Abstract

The invention relates to a movement (1) for a timepiece, comprising: at least one energy source (3); a going train (5a, 5b) kinematically connecting said energy source (3) to a regulating member (7); a display member (11) arranged to be driven by said power source; an actuator (9) arranged to influence the transmission of rotation between said power source (3, 3a, 3b) and said display member (11); and a control device (13) arranged to control said actuator (9), said control device (13) comprising mobiles all having a diameter less than or equal to 2.5 mm.

Description

Technical area

The present invention relates to the field of watchmaking. It relates, more particularly, to a movement for a timepiece.

State of the art

[0002] Complicated watches, comprising several additional mechanisms such as date mechanisms, moon phase displays, chronographs, etc. typically require not only significant size, but also significant torque to operate them. To ensure an acceptable power reserve, the barrels must therefore be large. Therefore, the higher the number of complications, the larger the size of the piece, since current design techniques imply that each complication is built to conventional watch size.

[0003] Moreover, when the presence of complications involves a significant load on the energy source, the oscillations of the regulating member can be disturbed. Indeed, if no complication takes energy, the regulating member receives a high torque, this torque decreasing according to the energy demand of the complications when the latter are operating. Since the rate of the regulating member varies according to the torque it receives, the latter can be highly variable, which is detrimental to isochronism.

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

[0005] Document EP0108412 describes a time-setting device comprising several crenellated axes having a diameter of 0.8 mm. These axes are involved exclusively in setting the time of the movement, and therefore cannot contribute to overcoming these drawbacks, since this device is not involved in the transmission of torque between the barrel and the regulating organ of the movement.

Disclosure of Invention

More specifically, the invention relates to a movement for a timepiece, comprising at least one energy source, for example one or more barrels, a gear train kinematically connecting said energy source to a regulator such as an escapement associated with a balance-spring, and a display member arranged to be driven by said energy source as a function of the regulating member.

According to the invention, said movement further comprises an actuator arranged to influence, that is to say to control, block, release, trigger or to vary the speed of the rotation transmission between said source of energy and said display member, and a control device arranged to control said actuator, said control device comprising mobiles all having a diameter less than or equal to 2.5 mm. Furthermore, said control device is arranged to be driven by said regulating member or to be driven by said going train.

[0008] By these means, the control device consists of a set of mobiles which have extremely low inertia, and which consequently require a significantly reduced torque to drive them. Consequently, the operation of the control device requires the taking of less torque than usual from the source of energy and from the going train, which disturbs the regulating organ less and increases the power reserve of the movement. . Furthermore, the use of components of reduced size also allows the development of complications having a reduced number of components, and greater simplicity.

Said actuator can 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] In a variant, said actuator can be located in said going train, and/or can be integrated into said energy source, for example by being provided in or on the drum of a barrel.

[0011] Alternatively, said actuator may be located in an additional kinematic chain extending from said energy source, the control device being controlled by said regulating member. The torque used by the actuator can thus be independent of that distributed by the going train, which further reduces the influence on the operation of the regulating member.

[0012] Alternatively, the energy source may comprise a single motor member, or alternatively it may consist of a first motor member arranged to drive said going train, as well as a second motor member arranged to drive said additional drive train. This last possibility minimizes the impact of the control device and the actuator on the operation of the regulating organ, and also makes it possible to optimize the torque supplied to each part of the movement by choosing appropriate barrels.

[0013] In a variant where said control device is arranged to be driven by said going train, said control device and said actuator can be located in said going train, said regulating member comprising an oscillator having a diameter equal to or less than at 5mm. In this variant, the control device, which comprises a set of reduced-size mobiles, forms the interface between a driving source of conventional size and a reduced-size oscillator.

[0014] Alternatively, the movement may further comprise an additional display device arranged to be driven from said going train or by said regulating member. This additional display device can even be integrated into an escapement wheel or a tourbillon or carousel cage.

[0015] These variants can be combined according to all possibilities making technical sense.

Finally, the invention relates to a timepiece comprising a movement as defined above.

Brief description of the drawings

Other details of the invention will appear more clearly on reading the following description, given with reference to the appended drawings in which: FIGS. 1 and 3 to 7 are schematic representations of various variants of watch movements according to the invention; FIG. 2 is a schematic representation of a variant of a watch movement not forming the subject of the invention; FIGS. 8 and 10 to 14 are schematic representations of watch movement constructions corresponding respectively to those of FIGS. 1 and 3 to 7; and Figure 9 is a schematic representation of a construction of a watch movement corresponding to that of Figure 2.

Embodiments of the Invention

Figure 1 schematically illustrates a first variant of a watch movement 1 according to the invention. This movement 1 comprises an energy source 3 comprising at least one driving member, such as one or more barrels, an electric motor or the like, and a going train 5a, 5b which links the driving source 3 to a regulating member 7 constituting a time base. The regulating organ, often also called “regulator”, typically comprises an escapement and a balance-spring oscillator, but also, for example, a tuning fork regulator, a tourbillon, or any other form of known regulator. In this variant, an actuator 9 is incorporated in the going train 5a, 5b, and drives a display member 11. The going train 5a, 5b can be of conventional size (“watch size”). Typically, watch-size mobiles commonly used in going trains have a diameter ranging up to around 12 mm. It is known that certain 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 mobiles, whose diameter overall (defined by the largest wheel making up the mobile) is significantly higher. By “mobile“, we mean either a set of at least two elements (wheel, pinion, cam, etc.) integral in rotation around a common axis, or a single rotating element (wheel, pinion, cam, etc.). ) around its own axis and which is not integral in rotation with another element.

This actuator 9 is controlled in turn by a control device 13, which takes information from the regulating member 7 via any kinematic link 8. The control device 13 comprises mobiles (wheels, cams etc.) all having a "reduced size", that is to say that they have a diameter less than or equal to 2.5 mm, or even less than or equal to 2mm, 1.5mm or even 1mm, as well as any other components having a size adapted to interact with such mobiles. The kinematic link 8 can be made up of mobiles of watchmaking size, or of reduced size (that is to say 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 at 1 mm), and the kinematic link 10 between the control device 13 and the actuator 9 can also be reduced in size as defined above.

[0020] Thanks to this reduced size of the elements constituting the control device 13 and possibly also the kinematic link 8, their need for force and torque is greatly reduced compared to components of watchmaking size, which minimizes the disturbance of the regulating member 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 down to nano-Newton×meters.

[0021] Furthermore, the control device occupies a greatly reduced space, which also makes it possible to increase the number of complications controlled by the control device 13 (chronograph, date, other display, etc., see below). below) that can be integrated into a given volume, if necessary, and this without the need to provide a substantial additional torque for their operation, and allowing a simplification and/or a reduction in the number of elements for a given mechanism. In the variant of FIG. 1, the control device 13 receives energy directly from the regulating member, which is not normally possible without disturbing the latter. As such, it is even possible to provide a power take-off directly on the escapement wheel set or even on the balance wheel, given that the torque taken off is insignificant in comparison with that of the conventional case.

[0022] The control device 13 is arranged to control the actuator 9 in order to distribute the torque arriving from the motor member 3 to the display 11.

Several mechanisms are possible to constitute the actuator 9. For example, the latter can be a differential gear, on which the control device 13 acts to distribute torque to the display 11, by braking, blocking or releasing an input or an output, for example, to produce a differential-type clutch, without interrupting the kinematic connection. Alternatively, the actuator 9 can be constituted by a clutch, the switching between the engaged state and the disengaged state of which is arranged to take place in response to a small control force. One can also imagine actuators 9 based on racks or racks, one or more cams, or levers. Still alternatively, the actuator 9 can be a gearbox, for example composed of an epicyclic gear train, the control device thus effecting a change of speed of the display.

[0024] For this purpose, the display 11 can be a calendar display device (Western or other), months, years, week, days of the week, moon phase display, tides, biological, astronomical or astrological cycles, a display of hours and/or minutes and/or seconds, a thunderbolt, or any other time-related display. The kinematic link 14 between the actuator 9 and the display member 11 can be of horological size or of reduced size as defined above. In the latter case, the display member may optionally be smaller than conventionally, and may be viewed through an optical device such as a magnifying glass.

[0025] Furthermore, and as illustrated by dotted lines, it is possible to provide one or more additional displays 11a in movement 1, driven for example directly from motor member 3, of part of the gear train finishing 5a, 5b, or otherwise.

[0026] Since the going train 5a, 5b is made up of components of watchmaking size, and the energy source provides a torque of conventional magnitude, the display 11, as well as the additional displays 11a, can also be of size conventional. With current technologies, if the entire movement were small, it would be difficult, if not impossible, to drive, for example, one or more hands, or a date disc, of conventional size. The movement according to the invention thus makes it possible to control a display of conventional size via a control device of reduced size.

Figure 8 schematically illustrates an architecture which corresponds to the block diagram of Figure 1. This construction has been shown very schematically, and is not to scale in any way. Moreover, certain kinematic links have simply been represented by arrows, the person skilled in the art knowing how to implement them by means of conventional gear trains (for example), which also applies to FIGS. 9 to 14.

In this architecture, the regulating member 7 comprises a balance-spring assembly 7a which cooperates with an anchor 7b and an escapement wheel set 7c in a known manner. Actuator 9 is a differential gear comprising an input 9a and two outputs 9b, 9c. In the variant illustrated, this differential is of the spherical type, of which a first sun wheel acts as an input and is arranged to be driven by a barrel 3 acting as a power source. A second sun wheel acts as the first output 9b, which drives the regulating member 7. The second output 9c is a planet carrier, which carries a plurality of bevel gears 101 meshing simultaneously with each of the sun wheels 9a, 9b of known way.

The control device 13 comprises a constant radius cam 13a forming part of a mobile having a maximum diameter of 2.5 mm driven directly or indirectly by the escapement pinion 7d so that it is driven permanently when movement 1 is running. This cam 13a takes place in a first fork 13b of a double-fork 13c, which is pivoted ad hoc on a frame element. A second fork 13d enters an external toothing 9d that comprises the planet carrier 9c of the differential. This toothing 9d can be a conventional toothing, edged, a double edged toothing, or any other suitable toothing or any other arrangement with similar functionality.

[0030] When the cam 13a rotates, the double-fork 13c oscillates between two extreme positions which are arranged in such a way as to release the planet carrier 9c in steps, typically in steps of one tooth per alternation of the double-fork. Each time the planet carrier 9c is released, the latter is rotated at the rate of one step by the torque supplied to the first input 9a by the barrel 3, without substantial influence on the torque supplied by the first output 9b to the regulating organ 7.

Since the display 11 is in kinematic connection with the planet carrier 9c, it is thus driven in steps each time the planet carrier 9c is released. By these means, the control device 13 controls the distribution of the torque to the display 11, blocking it and releasing it successively.

[0032] It is also noted that a relatively weak force is necessary to block the planet carrier 9d, and consequently the control device 13 can be of reduced size. Depending on the gear ratio between the escape pinion 7d and the cam 13a, the display 11 can be stepped forward with a desired period. For example, the manufacturer can plan to advance the display 11 at the rate of one step per second, per minute, per hour, per day, or according to any other desired period, substantially without influencing the torque supplied to the regulating member. 7. The isochronism can thus be improved.

[0033] Furthermore, this arrangement makes it possible to create a step-by-step display without requiring any spring to be loaded, or a jumper to be overcome, as is typically the case in such conventional displays. The torque requirement is thus reduced, which increases the power reserve of movement 1.

[0034] Figure 2 illustrates a variant of a movement 1 which is not the subject of the invention, which differs from that of Figure 1 in that the control device 13 is itself controlled by an action of a user, represented schematically by the dotted arrow 15. In this variant, the user can press, for example, a push-button, a bolt, or the like, or can rotate a crown or the like. The torque which drives the control device 13 is thus provided by the user, and there is therefore no power take-off on the regulating member or on the going train for the operation of the control device 13.

[0035] In this context, the actuator 9 can be a conventional or differential clutch allowing the starting of a counter such as a chronograph or a countdown, a tachometer or the like. Still alternatively, the actuator 9 can be a gearbox, for example composed of an epicyclic gear train, which makes it possible to advance or reverse (depending on the gear ratios) the display member 11 at a or several speed(s) higher than that of its normal operation, in order to carry out a rapid correction of the display member 11, for example in the context of setting the time.

For this variant, the same comments with respect to the size of the mobiles constituting the kinematic links 10 and 14 also apply here.

Figure 9 schematically illustrates an architecture which corresponds to the block diagram of Figure 2. This construction has been shown very schematically, and is not to scale in any way.

In this variant, the actuator 9 is illustrated as an epicyclic gearbox 9f, which makes it possible to drive the display 11 at different speeds under the control of the control member 13, which comprises one or several mobiles (not shown) of reduced size which are controlled by the pusher 13z. This gearbox 9f takes force on a 9th axis that comprises the going train 5a, 5b, and can take an appropriate form.

In this regard, mention may be made of epicyclic bicycle gearboxes, such as those described in documents US 2301852, US 3021728, DE 3440067 and others. A person skilled in the art knows how to adapt these systems to a timepiece, in particular by modifying them for a relatively flat construction.

Another type of gearbox particularly suitable for this role is a differential gear having a first input arranged to be driven by the barrel 3, a second input arranged to be blocked or released by the control member 13, as well only one output which drives the display 11. By blocking or releasing the second input, the speed of rotation of the output is modified, according to the selected gear ratios. The second input is provided with a disengageable connection such as a pawl, a friction or the like, which serves to link it kinematically with the first input when the second input is not blocked.

[0041] For example, if it is desired to be able to reverse the direction of rotation of the display 11 following a command from the user, the differential can be arranged in such a way that its planet carrier acts as a said second entry. 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 therefore 1:1.

[0042] By blocking the second input, the planet gears serve as inverters, and the gear ratio between the first input and the output therefore becomes 1 to -1, or another negative ratio according to the numbers of teeth chosen and the architecture of the differential (spherical, flat, etc.). This kind of differential inverter is known for example in the document WO2017071887 and therefore belongs to the knowledge of those skilled in the art.

[0043] Such an inverter makes it possible, for example, to provide a countdown 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 perform small corrections via a push button if the movement is ahead.

[0044] If, on the other hand, the first input is the planet carrier and the second input is a sun wheel or a sun pinion, the speed of rotation 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.

[0045] By choosing the construction of the differential gear (spherical, flat, etc.) as well as the number of teeth, the gear ratios can be chosen at will by those skilled in the art.

[0046] Furthermore, by providing two such differential gears in series, the manufacturer can be given more choice as to the speed ratios, and even several different speeds if one, the other or even both are blocked. second inputs of the two differentials.

[0047] These kinds of gearboxes lend themselves to making corrections to the display in the clockwise direction, controlled by a push button. For example, in the case of an 11 display which indicates minutes and hours, if the gear ratio is 1:1 when the second input(s) is/are free and 1:1440 when is/are blocked, the display will complete a full 24-hour cycle in one minute. Of course, these gear ratios can be chosen at will, in particular in the case of a gearbox of reduced size (that is to say comprising mobiles having a diameter of 2.5 mm at most).

Figure 3 further illustrates a variant of a movement 1 according to the invention. This variant differs from that of FIG. 1 in that the actuator is not located in the going train 5, but has its own kinematic connection consisting of an additional train 17 extending from the motor member 3. As such, the drive member can divide its torque between the going train 5 and the additional train 17 via a differential gear (not shown). This differential can be arranged according to construction requirements, in order to distribute the torque symmetrically between the two cogs 5, 17, or asymmetrically, depending on the gear ratios used. In this way, the torque supplied to each gear train can be optimized for the operation of the regulating member on the one hand, and the display on the other. In doing so, it is possible, for example, to drive a display requiring a high torque and a regulating organ that consumes little energy or vice versa from a single barrel.

Alternatively, in a less complex motor member 3 construction, one of the cogs 5, 17 can be driven from the drum of a barrel, the other from its shaft. This variant has a reduced number of components compared to the differential solution described above. In order to manage the torque ratio distributed to the two cogs 5, 17, the diameters of the mobiles which serve as a power take-off on the drum and on the arbor of the barrel can be chosen ad hoc.

For this variant, the same comments with respect to the size of the mobiles constituting the kinematic links 8, 10 and 14 also apply here. Typically, the kinematic link 14 between the actuator 9 and the display member 11 would be of watchmaking size.

Figure 10 schematically illustrates an architecture which corresponds to the block diagram of Figure 3. This construction has been shown very schematically, and is not to scale in any way.

In this variant, the torque of 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 exiting in two directions by each of the two outputs 3e (which leads to the regulating organ 7) and 3f (which drives the display 11). The shape of this differential is not significant and should not be described in more detail. Furthermore, the aspects which are identical to the variant of FIG. 8 bear no reference signs and will not be described again.

[0053] The control device 13 is driven by the escapement pinion 7d and is similar to that illustrated in Figure 8. Consequently, it therefore need not be described a second time. However, the actuator 9 includes a toothed wheel 9g which interacts with the second fork 13d in order to be blocked and released step by step at each alternation of the double-fork 13c.

This toothed wheel 9g is driven by the second output 3f of the differential, and is blocked and released step by step at each alternation of the double fork 13c. The control device 13c thus controls the distribution of torque between the barrel 3 and the display 11. The advantages of this variant are the same as those of FIG. 9.

The variant of Figure 4 differs from that of Figure 3 in that the motor member 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 going train 5, and cannot in any way disturb the regulating member 7. Furthermore, the size of the two energy sources 3a, 3b can be chosen according to their respective roles. The same comments with respect to kinematic links 8, 10 and 14 also apply here.

[0056] Figure 11 illustrates a construction which corresponds to the diagram of Figure 4, and will be described exclusively by its differences with respect to that of Figure 10. Again, this construction has been represented very schematically, and is only in no measurements to scale.

In this variant, the energy source 3 comprises a first barrel 3a which drives the regulating organ, as well as a second barrel 3b which drives the display 11. A particularity of the construction illustrated here is that a toothing carried by the barrel meshes directly with the escapement pinion 7d of the regulating member, which makes the going train 5 as compact as possible, and minimizes the number of components. This is made possible by the fact that the display 11 is not driven by the going train 5, but is only controlled by the latter. Indeed, the control device 13 takes information only on the regulating member 7 (more particularly on the escapement pinion 7). The drive of the display is therefore situated entirely outside the going train under the control of the control device 13, which regulates the speed of rotation of the display under the effect of the torque supplied by the second barrel 3b and regulates thus the gear ratios for display 11.

As in the variant of 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.

This variant makes it possible to adapt the torque provided by each of the barrels according to its role since the first barrel 3a can be adapted for driving the regulating member 7, while the second barrel 3b can be more powerful in order to drive the display device 11. The control device 13 again comprising mobiles having a maximum diameter of 2.5 mm, it consumes very little energy and therefore hardly disturbs the regulating member 7. However, it can control larger torques from the second barrel 3b.

[0060] Figure 5 illustrates a variant based on that of Figure 3, but which differs from the latter in that the control device 13 takes information on the going train 5 upstream of the regulating member 7. This variant makes it possible to supply more torque to the control device 13, which can thus in turn supply more torque and/or force to the actuator 9 to activate/deactivate it. By doing so, the control device 13 can operate with an actuator 9 which requires more force to trigger its operation. The same comments with respect to kinematic links 8, 10 and 14 also apply here.

[0061] Figure 12 illustrates a construction which corresponds to the diagram of Figure 5, and will be described exclusively by its differences with respect to that of Figure 11. This construction has been represented very schematically, and is not to be scale.

In this variant, a single barrel 3 is present, and has a first PTO 3m on its drum, as well as a second PTO on its axis 3n. The first power take-off 3m again drives the regulating member 7, and the second drives the actuator 9 via the additional kinematic chain 17. Otherwise, this variant operates in the same way as that of FIG. 11. However , it is also noted that the control device 13 can alternatively be driven by the drum of the barrel 3m, or by any possible mobile in a kinematic chain linking the drum 3m to the escapement pinion 7d.

Figure 6 illustrates yet another variant of a movement 1 according to the invention. In this variant, the actuator 9 is located directly in the going train 5a, 5b, 5c, and the control device 13 is also located in the same going train 5a, 5b, 5c, upstream of the regulating organ 7 and downstream of the actuator 9. In doing so, the control device 13 controls the actuator 9 by transmitting time information to it from the regulating member 7.

[0064] In this variant, the actuator may for example be a cam arranged in the going train 5a, 5b, or alternatively in a branch of the latter, to cause the display member 11 to advance by jumps, and the regulating member 7 can itself be of reduced size. In this case, the regulating member 7 may comprise a balance having a diameter equal to or less than 5 mm, depending on the material chosen for its production, and the control device 13 acts as an interface between the parts of the going train 5a, 5b which have a conventional watchmaking size and the regulating member 7 of reduced size.

Of course, other possibilities are possible.

In this variant, the part of the going train 5b which is located between the actuator 9 and the control device 13 can be composed of mobiles of watchmaking or reduced size, and the part 5c which links the control device 13 to the regulating organ is of course of reduced size in order to cooperate with the regulating organ 7 of reduced size.

[0067] Figure 13 illustrates a construction which corresponds to the diagram of Figure 6. This construction has been shown very schematically, and is not to scale in any way.

[0068] In this variant, the overall construction of movement 1 is conventional, barrel 3 being kinematically linked to regulating organ 7 via a going train 5.

[0069] On one of the mobiles of the going train which forms part of the actuator 9 and of the control device 13 is mounted a cam 9j with a constant radius. This cam interacts with a wolf toothed wheel 103 via a hook 105 carried by a flexible arm 107. The latter is integral with a rigid arm 109 extending from a fork 111 which cooperates with the cam 9j . When the cam 9j rotates, the rigid arm 109 oscillates around its pivot axis 113, which causes the wolf toothed wheel 103 to advance clockwise (in the figure) in steps of one tooth, the wheel 103 being 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 the teeth as it moves to the left. The wolf toothed wheel 103 being in kinematic connection with the display 11, the latter is also driven in turn.

FIG. 7 further illustrates a variant of a movement 1 according to the invention.

In this variant, the regulating member 7 is in direct kinematic connection with the motor member 3 through the going train 5, and an additional display member 12 is provided downstream of the regulating member 7 .

[0072] This time, the control device 13 takes information downstream of the regulating member 7, or alternatively directly from the latter, and the actuator takes force from a wheel set of the going train 5 or alternatively directly from the energy source.

[0073] 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.

In this variant, the kinematic connection 8 between the regulating member 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 going train 5 to the Actuator 9 can be of horological or reduced size.

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

[0076] Figure 14 illustrates a construction which corresponds to the diagram of Figure 7. This construction has been shown very schematically, and is not to scale in any way.

The construction comprises a single barrel 3, the torque of which is divided by a differential gear 3c in a known manner. The torque arrives on a first sun wheel 3g, and leaves on a first output 3h (a second sun wheel) to drive the regulating member 7, and on a second output 3i (a planet carrier) to drive the actuator 9. Good Of course, other arrangements are possible, such as those of Figures 10 and 12 among others.

The actuator 9 shown here is a wheel carrying a single finger 9h, which is retained by a retention spout 13i that includes a lever 13g.

The control device 13 is made up of this lever 13g, which also provides the kinematic connection 10 between the regulating member 7 and the actuator 9.

The lever 13g is actuated by a pin 8a carried by the rim of the balance 7a, or by another element such as a plate which is integral in rotation with the balance 7a. It is therefore clear that the pin 8a constitutes the kinematic connection 8 between the regulating member 7 and the control device 13. It is also possible to have the lever 13g actuated by the escapement pinion 7d or by an element driven by this latest.

The lever 13g pivots around a point 13h, chosen here at one of the ends of the lever 13g in order to simplify the figure. However, a pivot at an intermediate point associated with a more realistic geometry of the mechanism is preferable.

[0082] In the sense of the invention, the "diameter" of the lever is twice its maximum radius measured from its pivot point 13 o'clock, and is at most 2.5 mm.

The shapes of the lever 13g and the pin 8a are chosen so that, when the pendulum 7a oscillates, the pin 8a strikes the lever 13h and causes it to pivot. If the lever acts in the same plane as the pendulum, this can be done without any particular difficulty. If, on the other hand, the lever acts in a different plane, as figure 14 implies, bevel surfaces, cam surfaces or the like may be provided to ensure that the lever 13g is actuated in a suitable manner.

[0084] When the lever is lifted, the beak 13i releases the finger 9h, and the wheel acting as an actuator 9 can turn at the rate of one revolution. An elastic 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, at each alternation of the pendulum 7a, the actuator 9 completes one revolution, and drives the display 11 at the rate of one step.

If the pin 8a is retractable in one direction of rotation of the balance 7a but not in the other, the lever 13g will be actuated once per oscillation of the balance 7a. Furthermore, it is possible to provide several fingers 9h (or even a set of teeth) on the actuator 9 in order to choose the desired gear ratio between the barrel and the display 11.

[0086] It is also noted that the additional display 12 is illustrated as being driven by the escapement pinion 7d that comprises the regulating member 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 in FIG. 13, in order to cause an additional display.

In each variant, it is possible for the actuator 9 and the control device 13 to be integrated with each other in a single unit taking up the two functions, as is the case with the variant of the figure 13. Furthermore, the actuator 9 and/or the control device 13 can act as a kinematic link, as is particularly the case in figure 14, and it is also possible for the actuator 9 to be integrated into a drum of a barrel constituting the driving member 3.

The reduced-size mobiles, that is to say those forming part of the control device 13, as well as certain kinematic chains as mentioned above, can be manufactured for example by micro-machining processes capable of define elements with voxels of the order of a few hundred nanometers, and thus create shapes with a precision of the order of a micrometer.

In this respect, mention may be made of LIGA processes, masking and etching processes from a material plate, the photostructuring of glass or quartz with a femtolaser, or high-resolution additive manufacturing in metal, epoxy, or ceramic. “Additive manufacturing” is the general term for all manufacturing processes by means of addition of material, more specifically 3D printing, including 3D photolithography, laser sintering, and others. A more extensive discussion of this topic is found in Swiss patent application CH360/16.

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

Claims (10)

1. Movement (1) for a timepiece, comprising: - at least one energy source (3, 3a, 3b); – a going 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; characterized in that said movement (1) further comprises: – 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), said control device (13) comprising mobiles all having a diameter less than or equal to 2.5 mm, said control device (13) being arranged to to be driven by said regulating member (7) or to be driven by said going train (5, 5a, 5b). 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 actuator (9) is located in said going train (5, 5a, 5b). 4. Movement (1) according to one of claims 1 and 2, wherein said actuator (9) is integrated into said energy source (3, 3a, 3b). 5. Movement (1) according to one of claims 1 and 2, wherein said actuator (9) is located in an additional kinematic chain (17) extending from said energy source (3, 3a, 3b), the control device (13) being controlled by said regulating member (7). 6. Movement (1) according to claim 5, wherein said energy source (3) comprises a single motor member (3). 7. Movement (1) according to claim 5, wherein said energy source (3, 3a, 3b) comprises a first motor member (3a) arranged to drive said going train (5), as well as a second member motor (3b) arranged to drive said additional kinematic chain (17). 8. Movement (1) according to one of claims 1 to 4, wherein said control device (13) is arranged to be driven by said going train (5, 5a, 5b), said control device (13) and said actuator (9) located in said going train (5a, 5b, 5c), said regulating member (7) comprising an oscillator having a diameter equal to or less than 5 mm. 9. Movement (1) according to one of the preceding claims, further comprising an additional display device (11a, 12) arranged to be driven from said going train (5, 5a, 5b) or by said regulating member (7). 10. Timepiece comprising a movement (1) according to one of claims 1 to 9.