EP3475764B1 - Timepiece movement - Google Patents

Description

Technical area

The present invention relates to the field of watchmaking. More particularly, it relates to a timepiece movement provided with an adjusting member mounted in a pivoting mobile support.

State of the art

Ever since Breguet mounted a balance on a rotating support at the end of the 18th century, the watchmaking world has been fascinated by the tourbillon and all its variants. In the late 1970s, Anthony Randall and Richard Good developed their famous bi-axial and triaxial tourbillons, upon which modern developments of complicated multi-axis tourbillons have been built. The integration of such bi-axial and triaxial tourbillons in wristwatches presents difficulties in terms of the complexity and the thickness necessary to implement them. Moreover, these types of vortices, in which the regulating member pivots around two or three axes, are energy intensive and require a high torque for their drive, this energy being supplied by the finishing gear.

More recently, the document EP2729849 proposed a tourbillon in which the regulating member is mounted in a cage in a conventional manner, the cage being pivoted inside a first ring, itself pivoted inside a second ring, in order to form indeed a triaxial tourbillon with limited angular displacement for the second and third axes. The cage, which performs full rotations, is thus forced to move in a compound movement that resembles the precession of a gyroscope. Since the angular displacements around the second and third axes are not complete, the height required for the system can be significantly decreased, and the complexity can also be reduced.

Nevertheless, all the movements of this device remain driven by the finishing gear train, which still requires a higher torque than for a conventional unified axial tourbillon.

Another document of interest in the context of the present invention is the EP 1980920 . This document describes a single axis tourbillon system, this axis of rotation being perpendicular to that of the balance. Once an hour, the frame, which supports the regulating organ as well as part of the finishing gear, rotates by one step under the effect of a buffer cylinder, this pivoting also serving to advance the indication. hours. The latter is located on a ribbon that drives said rotating frame. In doing so, the frame always pivots in the same direction of rotation, since it is involved in driving the belt bearing the hour digits. Rotation of the frame in a single direction of rotation is thus compulsory, without which the display of the hours would not function. Even if each rotational step stops at a predetermined angular position, there is no limit to the pivot angle of the rotating frame. The latter performs a complete rotation every six hours, without a limit pivot angle, that is to say without a pivot angle which cannot be exceeded by the frame. Indeed, the pivot angle increases to infinity at the rate of a step of 60 degrees each hour of operation.

This arrangement requires that a large part of the finishing gear is in the movable frame, and makes full turns. This has the result that either the balance must be small, which is detrimental to the isochronism of the movement, or the pivoting frame must have a large diameter, which increases the thickness of the movement undesirably. Furthermore, the sudden pivoting of the movable frame generates significant undesirable shocks.

Disclosure of the invention

A main aim of the present invention is to alleviate the drawbacks of the prior art, by proposing a clockwork movement which makes it possible to present chronometric advantages, without requiring a significant thickness in the movement, and without using the finishing gear train. as a power take-off for certain movements of the regulating organ.

To this end, the present invention relates more particularly to a timepiece movement comprising at least one driving member, consisting for example of one or more driving springs housed in one or more barrels, one or more electric motors, and a member. regulating such as a sprung balance member associated with an escapement, a tourbillon, a carousel, a flywheel or the like, kinematically linked to said at least a motor member via a finishing gear in order to maintain it in a known manner. The at least one motor member is in kinematic connection with a first power take-off which drives the finishing gear train (the latter therefore starting with this power take-off).

According to the invention, the movement comprises a movable support, such as a cradle, a ring, a cage, a board or the like, pivoted on a frame element and carrying said regulating member and adapted to pivot between two limit pivot angles , which therefore cannot be exceeded. The movable support is arranged to be pivoted along at least one axis between said limit pivot angles in a predetermined sequence by means of a pivot control device arranged to rotate said movable support in a back and forth movement. come. A control gear connects said pivoting control device to a second power take-off (where the control gear therefore begins), separate from the first, and which is in kinematic connection with said at least one motor member. The pivoting control gear is therefore separate from said finishing gear, at least at the level of the transmission of torque between the finishing gear and the pivoting control gear. The pivotings of the mobile support are therefore not driven by a torque emanating from the finishing gear train, and thus do not represent an additional torque load on the latter, which minimizes, or even eliminates, the disturbances on this gear train due to these pivotings.

Since the pivoting control gear does not receive any torque from the finishing gear, the movement of the movable support does not represent any load on the latter, and therefore cannot influence the operation of the regulating member. Moreover, the fact that the mobile support performs a back-and-forth pivoting requires less height in the movement than a tourbillon whose / a cage pivots around an axis perpendicular (or almost) to the axis. rotation of the balance. A larger regulating member can therefore be used in the case of such a tourbillon, which improves isochronism, while retaining the “tourbillon” or even “double tourbillon” effect, depending on the construction of the member. regulating (namely a conventional sprung balance, respectively a conventional tourbillon). In fact, it is not compulsory to make complete rotations to present a positive effect on isochronism provided by changes in angular positions as in a "classic" tourbillon.

Advantageously, said at least one driving member comprises a first driving member arranged to drive said finishing gear train via said first power take-off and a second driving member arranged to drive said pivoting control gear train via said first power take-off. second power take-off. The two cogs mentioned can thus be completely isolated from each other at the level of the torque transmission, each having its own energy source. The pivoting control gear therefore does not contribute to the disarming of the motor member used by the finishing gear.

Advantageously, the pivoting of said movable support is engaged by an element driven by said finishing gear, such as a cam, a lever or the like. The movements of the movable support can therefore be synchronized with the operation of the regulating member, without requiring a transfer of torque between the finishing gear and the pivoting control gear. Alternatively, the pivoting control gear can be autonomous, or can be triggered and / or blocked manually.

Advantageously, said control device comprises a speed controller, such as a flywheel, a winged flywheel, a sprung balance or the like. This speed controller is provided with at least one brake, such as a balance stop, a friction brake or the like. This brake can thus be used to block and trigger the operation of the pivot control gear train in a simple manner. This brake can, for example, be arranged to be released by means of said element driven by said finishing train. This element may be a cam arranged to actuate a release member such as a lever, this release member being arranged to release said brake.

Advantageously, said brake is designed to be activated, that is to say to stop the speed controller, by means of an element of said pivot control device. The pivoting of the movable support is thus stopped by the control device, which prevents these pivotings from becoming desynchronized, particularly in the case where they are triggered by an element driven by the finishing gear train. In such In this case, if the period between two actuations of a pivot is longer than the period in which the movable support pivots, the pivotings will remain synchronized with the progress of the finishing gear.

Advantageously, said finishing gear train comprises a differential gear having a first input arranged to be driven by said motor member, a second input arranged to be driven directly or indirectly as a function of the angular position of said movable support, for example via a toothed member integral in rotation with the movable support or moved by the latter, and an outlet arranged to drive said regulating member. This differential is used to isolate the finishing train from the pivoting of the mobile support, in order to avoid variations in torque due to the latter. The pivoting speed of the mobile support can thus be chosen freely, because the counter-force generated by the movements of the regulating member is canceled and therefore has no influence on the finishing gear train.

As an alternative to said differential gear, said finishing gear may comprise a torque compensator comprising a shaft integral in rotation with an input arranged to be driven directly or indirectly by said first power take-off, a second input arranged to be driven as a function of the angular position of said movable support, said second input comprising a wheel mounted loose on said shaft and linked to the latter by means of an elastic element, and an output arranged to directly or indirectly drive said regulating member. Said output comprises another wheel also mounted loose on said shaft and linked to the latter by means of its own elastic element. This solution requires fewer parts than a differential gear.

Advantageously, said control device comprises at least one control cam integral in rotation with the movable support, said control cam comprising at least one actuation surface arranged to cooperate with an actuation cam driven by said control gear in order to drive said movable support in pivoting. This system makes it possible to drive the movable support in pivoting. As a result, the system does not require any jumper to ensure the positioning of the mobile support when stationary. Energy consumption is thus reduced. Alternatively, a partial tooth system can also be used.

Advantageously, said pivot control device comprises a safety lever integral in rotation with said movable support, said safety lever comprising a plurality of limiting pins (ideally three, but two, four or even more are still possible) which take place in tracks comprised by a track disc arranged to be rotated by said pivoting control gear, said tracks being shaped so as to prevent inadvertent pivoting of said movable support. When the movable support is intended to remain stationary, the interaction of at least one of the limiting pins with the wall of a track blocks the pivoting of the movable support reliably, regardless of the weight and inertia of the support. The exact shape of the tracks, the angular speed of rotation of the track disc and the arrangement of the pins on the safety lever can be defined according to the geometry of the system as well as the sequence of pivoting of the movable support in order to lock and lock. release the support at the desired times.

Advantageously, said pivoting control device comprises a locking eccentric arranged to be driven by said pivoting control gear, said locking eccentric being arranged to cooperate with a stop lever arranged to stop said speed controller. The pivoting of the mobile support is thus stopped under the control of the pivoting control gear train, which prevents the pivoting of the mobile support from becoming out of synchronization.

Advantageously, said pivot control device is arranged such that said movable support has periods of movement when said movable support is moving, and periods of stopping when said movable support is stationary. Even more advantageously, said displacement periods are of longer duration than said stopping periods, which implies a limited, or even moderate, pivoting speed. This limited speed reduces the impact to various components when stopping.

Advantageously, said locking eccentric is arranged to cooperate with a stop lever arranged to directly or indirectly stop said speed controller.

The invention also relates to a timepiece comprising such a movement.

Brief description of the drawings

• la figure 1 représente un diagramme schématique d'un mouvement d'horlogerie selon l'invention ;
• la figure 2 représente un diagramme schématique d'une variante d'un mouvement d'horlogerie selon l'invention ;
• la figure 3 représente une vue partielle en perspective simplifiée d'un mode de réalisation concret d'une variante d'un mouvement d'horlogerie selon l'invention, illustrant particulièrement le rouage de commande de pivotement ainsi que le dispositif de commande de pivotement ;
• la figure 4 représente une vue en plan de la variante de la figure 3 ;
• les figures 5 et 6 représentent des vues partielles en perspective du dispositif de commande de pivotement de la variante de la figure 3 ;
• les figures 7 à 9 représentent des vues partielles en perspective du rouage de finissage et de l'engrenage à différentiel de la variante de la figure 3
• les figures 10a à 10c représentent des vues d'un système de sécurité que comporte le mode de réalisation des figures 3 à 9 ; et
• la figure 11 représente un diagramme schématique d'une solution alternative pour compenser les déplacements du support mobile.

Other characteristics and advantages of the present invention will emerge more clearly on reading the detailed description given with reference to the appended drawings given by way of non-limiting examples and in which:

• the figure 1 represents a schematic diagram of a timepiece movement according to the invention;
• the figure 2 represents a schematic diagram of a variant of a timepiece movement according to the invention;
• the figure 3 represents a partial simplified perspective view of a concrete embodiment of a variant of a timepiece movement according to the invention, particularly illustrating the pivoting control gear train as well as the pivoting control device;
• the figure 4 shows a plan view of the variant of the figure 3 ;
• the figures 5 and 6 represent partial perspective views of the pivot control device of the variant of the figure 3 ;
• the figures 7 to 9 show partial perspective views of the finishing gear train and differential gear of the variant of the figure 3
• the figures 10a to 10c represent views of a security system included in the embodiment of the figures 3 to 9 ; and
• the figure 11 represents a schematic diagram of an alternative solution to compensate for the displacements of the movable support.

Mode (s) for carrying out the invention

The figure 1 schematically illustrates the principle of the invention in its simplest form, in the context of a timepiece movement 1. This movement 1 comprises one or more driving members 3, such as one or more driving springs housed in one or more. several barrels. This or these engine member (s) 3 is associated with a first power take-off 3c as well as a second power take-off 3d. In the case of a single barrel, these sockets force 3c, 3d can simply be moving bodies meshing with a toothing that the barrel comprises (for example a toothing extending from a drum), or outputs of a differential gear whose input is in kinematic connection with the barrel . From the first of these power take-offs 3c extends a finishing gear 5 which kinematically links the motor member to a regulating member 7 and ensures its maintenance. This regulating member can be a balance-spring assembly, a tourbillon, a carousel, or any other suitable regulating member, conventional or inclined.

The finishing train passes through a first input 9a and an output 9c of a differential gear 9 or of an alternating system, the operation of which will be better understood hereinafter.

The regulating member 7 is carried by a movable support 11 mounted to pivot along at least one axis relative to a frame 12, the movable support 11 performing a reciprocating pivoting between limit pivot angles under the control of 'a pivot control device 13 by means of a control gear 15a. The latter connects the second power take-off 3d of the engine member 3 to the pivoting control device 13, which controls the pivoting of the movable support 11. Consequently, the finishing gear 5 and the control gear 15a are independent at the level. of the torque transmission downstream of the power take-offs 3c, 3d. The pivoting of the movable support 11 can take place along a single axis, or alternatively along several axes, cutting the movable support 11 or not, for example in order to effect a gimbal or ball joint movement.

So that the pivoting of the mobile support 11 does not exert any influence on the finishing gear train and therefore does not interfere with the operation of the regulating member 7, a second input 9b of the differential gear is kinematically linked to the mobile support, so that the second input pivots as a function of the angular displacements of the movable support 11. In doing so, the torque supplied by the part of the finishing gear 5b downstream of the differential gear 9 remains independent of the pivotings of the movable support. The differential gear 9 has the effect of isolating the torque transmission along the finishing gear 5 from the movements of the movable support 11. In the absence of the differential gear 9, the movements of the support movable 11 would result in a counter-force due to the fact that the regulating member 7 is carried by the movable support 11 and is also moving relative to the frame.

An alternative solution to the differential gear 9 is a 9z torque compensator as shown schematically on figure 11 . The same reference signs have been used in this figure in order to make as clear as possible the equivalence between the operation of the differential gear 9 and that of the torque compensator 9z. The arrangement illustrated in this figure comprises a shaft 9k, integral in rotation with an input 9a comprising a wheel 9d driven by the first part 5a of the finishing gear 5. A second input 9b comprises a wheel 9l mounted loose on the shaft. 9k. This wheel 9l is pivoted as a function of the movements of the pivoting support 11, and is linked to the shaft 9k by means of an elastic element 9m such as a spiral spring or the like. The latter is fixed to the shaft by means of a ferrule 9n. The output 9c also consists of a wheel 9o in kinematic connection with the regulating member 7 and linked to the shaft 9k by means of a second elastic element 9m and a ferrule 9n. The ferrules 9n can be omitted if the elastic elements are otherwise secured to the shaft 9k, for example by means of a weld.

When installing the torque compensator 9z, the elastic elements 9m must be preloaded. During operation of the system, when the movable support 11 remains stationary, the torque arriving on the wheel 9d is transmitted to the wheel 9o by means of its elastic element 9m. The wheel 9l remaining stationary, its elastic element is stretched or relaxed according to its winding direction.

When the movable support 11 rotates, the elastic element 9m of the wheel 9l stretches or relaxes, as the case may be, and by adding or subtracting to the torque transmitted by the shaft 9k to the wheel 9o. In doing so, the counter-force resulting from the pivoting of the regulating member 7 arranged on the movable support 11 is compensated for.

In order to prevent the elastic element 9m of the wheel 9l from winding up or unwinding too much, its ferrule 9n can be arranged to be able to act as friction, and thus allow relative rotation with the shaft 9k. Alternatively, a Any friction can be incorporated between the wheel 91 and the movable support 11.

The pivot control device 13 can be autonomous, and / or can control the operation following actions of a user, for example by means of a push button 14 or the like, and / or controlled by the gear train. finishing 5. These last two possibilities are represented on the figure 1 by dotted arrows.

The figure 2 illustrates a variant in which each gear train 5, 15a is provided with its own motor member 3a respectively 3b each having its own power take-off 3c, 3d respectively, and are therefore completely independent as regards the transmission of torque.

In this variant, the pivot control device 13 is associated with a speed controller 17, which can take the form of a sprung balance assembly, a flywheel, a winged flywheel, or the like. , in kinematic connection with the pivot control device 13 via a second gear 15b. The speed controller 17 is blocked and / or released under the control of the finishing gear train 5, for example by means of a brake controlled by a cam, a wheel, or one or more levers. The speed controller 17 can also be released by the finishing gear 5 and locked under the control of the pivot control gear 15a, as is the case in the concrete embodiment which will be described later.

The figures 3 to 9 illustrate a concrete embodiment of a timepiece movement according to the invention, corresponding to the diagram of the figure 2 . In view of the complexity of the mechanism, certain elements have not been shown in certain figures in order to avoid overloading them.

The figures 3 and 4 particularly illustrate the control gear 15a, the pivot control device 13, the movable support 11, as well as the speed controller 17. The latter is formed of a balance-spring regulator 17a associated with a conventional escapement 17b. This escapement 17b has no influence on the course of the movement and acts exclusively in connection with the pivoting control device 13. The alternative forms of regulator mentioned above may well. intended to be used instead of the escapement 17b and the sprung balance 17a.

The pivoting control gear 15a simply links the second barrel 3b to the pivoting control device 13, and the second gear 15b is in branch of this gear 15a. The pivot control device 13 is kinematically linked to the movable support 11, which is pivoted on the frame of the movement (not shown). The movable support 11 supports the regulating member 7, which is a simple tourbillon in the illustrated variant, but can also be a simple sprung balance associated with an escapement, or even any other type of regulating member known to those skilled in the art. job.

The pivot control device 13 will now be described in detail in connection with the figures 3 to 6 .

In the variant shown, the pivoting control device 13 drives the movable support 11 in pivoting such that it performs the predetermined sequence of pivotings of -35 ° - 0 ° - + 35 ° - 0 ° - -35 ° etc. . around its axis of rotation 11a relative to the plane of movement. The angles of -35 ° and + 35 ° represent limit and extreme pivot angles in this case, and the 0 ° represents an intermediate pivot stop angle, distinct from the limit position angles. The latter are absolute and can never be exceeded by the mobile support 11, while any intermediate pivoting stop angles are exceeded during the next pivoting of the mobile support 11. The mobile support is stopped for five seconds at each angle in the sequence, and pivoting for fifteen seconds. Modifications to the movement in order to control the movable support 11 according to other pivoting sequences are within the abilities of those skilled in the art. More generically, the periods of movement of the movable support 11 are advantageously longer than the periods of stopping, which reduces the shocks to which the various components of the pivot mechanism are subjected. However, this system is also suitable for travel periods equal to or shorter than those of stop, and it is also possible to provide different periods of immobilization in each stop position, according to the arrangements of the cams.

Fixed in rotation with the movable support 11 is a first control cam 11b as well as a second control cam 11c.

The first control cam 11b comprises three safety surfaces 11d each contiguous with an actuating surface 11e.

When the control gear is running, a wheel 21 is in kinematic connection with another wheel 23, which is rotatably attached to an actuating cam 25. The wheels 21, 23 have been omitted from the figure. figure 6 in order to better visualize the locking eccentric 19 (here in the form of a cam, but which can alternatively be a finger or a pin mounted eccentrically on a mobile) as well as the actuation cam 25, which rotates counterclockwise in order to drive the first control cam 11b clockwise. As such, the actuation cam 25 comprises two fingers 25a, angularly spaced by 90 °, and which drive the movable support 11 according to its two clockwise rotation steps (depending on the orientation of the figures 5 and 6 ).

In order to drive it counterclockwise, the second control cam 11c takes on a shape similar to that of the first control cam 11b, but inverted and angularly offset by an ad hoc angle defined according to the construction. The second control cam 11c has an inverted shape with respect to the other control cam 11b and is rotated by its own actuation cam 27 (see figure 6 ). The latter is coaxial and integral with the wheel 21 and therefore pivots in the same direction, and serves to drive the mobile support 11 in the counterclockwise direction (depending on the orientation of the figures 5 and 6 ).

When one of the fingers 25a, 27a of one of the actuation cams 25, 27 is in contact with one of the actuating surfaces 11e, the angular position of the movable support 11 is ensured by the interaction of these elements. However, when the movable support 11 is stationary between two movements, these fingers 25a, 27a are remote from the control cams 11b, 11c. In order to block the movable support 11 in each of its stop positions and thus prevent any untimely displacement of the support 11, a safety system 42 is provided. This security system 42 is illustrated in more detail in the form of exploded diagrams in the figures 10a to 10c .

The safety system 42 comprises a track disc 43, integral in rotation with the wheel 21. A safety lever 45 is integral in rotation with the movable support 11 as well as the control cams 11b, 11c, and consequently follows the movement of reciprocation of the support 11. This safety lever 45 also comprises three limiting pins 45a arranged at the end of the lever 45, which take place in tracks 43a with which the track disc is provided. The position of the pins 45a and the shape of the tracks 43a can be chosen ad hoc according to the sequence of movements of the components, so that the safety lever 45 is locked when the movable support 11 is stationary (the walls tracks 43a serving as stops for the pins 45a), and can pivot when the fingers 25a, 27a drive the control cams 11b, 11c (the pins being at this time in recessed areas 43b of the tracks which do not prevent not tilting the safety lever 45).

As a second safety, stop surfaces 25b, 27b are provided on the actuating cams 25, 27, adjacent to the fingers 25a, 27b respectively. These stop surfaces 25b, 27b are positioned opposite the safety surfaces 11d when the movable support 11 is at rest so that, during an impact which could overcome the effect of the safety system 42, the safety surface 11d opposite a stop surface 25b, 27b, abuts against the latter.

This arrangement avoids the use of a jumper to maintain the movable support in each angular stop position, which is advantageous since the use of a jumper is energy intensive during pivoting.

Alternatively, the pivoting control device 13 can use toothed segments with interrupted teeth instead of the control cams 11b, 11c, as well as interrupted tooth wheels instead of the actuating cams 25, 27. Still alternatively, the device control 13 can drive the movable support 11 in a single direction of pivoting, then release it to return to its starting position by means of an elastic return member. An example of such a sequence would be -30 ° - 0 ° - +30 - -30 ° ... Still alternatively, the downtimes could be different in each of the stop positions, depending on the shape and arrangement of the various cams.

On each quarter turn of the locking eccentric 19, one of its wings interacts with a stop lever 29, as will be explained below. If the second gear 15b is free to rotate, the locking eccentric will complete one revolution in 60 seconds in the variant shown.

As already mentioned above, the speed controller 17 comprises a sprung balance 17a assembly as well as an escapement. The escape wheel forms the last mobile of the second gear 15b, in branch of the control gear 15a. The movement 1 is provided with a brake, in particular a balance stop 17c, integral with one end of a balance stop lever 29b which is subjected to a return force by means of a return member (not shown) which serves to bring the balance stop 17c into contact with the periphery of the balance. This rocker is pivoted on a frame element (not shown), and interacts with an intermediate rocker 29a which forms the link between the stop lever 29 and the stop rocker rocker 29b. In the illustrated variant, every fifteen seconds, the locking eccentric 19 actuates the stop lever 29, and brings the balance stop 17c into contact with the periphery of the balance under the effect of its return spring (not illustrated) , and prevents it from oscillating until it is released by the balance stop 17c.

Turning now to the finishing gear 5, as shown in the figures 7 , 8 and 9 , this train connects on the one hand (via part 5a) the first barrel 3a to a first input 9a of a differential gear 9 via the first power take-off 3c, and on the other share (via part 5b of the finishing gear train 5 which is mounted on the movable support 11), an output 9c of the differential gear 9 to the regulating member 7 carried by the movable support 11. The first entry 9a consists of a planet carrier frame carrying at least one planet gear (invisible) in a known manner. The frame is integral in rotation with a pinion 9d driven by the first barrel 3a. Said outlet 9c consists of a barrel comprising an edge set 9h meshing with the planet gears, as well as a second edge set 9i which meshes with a toothed mobile 39 pivoted on the movable support 11 and which is in kinematic connection with the regulating member 7. The toothed mobile 39 as well as the other mobile units downstream of the latter form the second part 5b of the finishing gear 5 and drive the regulating member 7.

When the mobile support 11 is stationary, the second inlet 9b remains stationary, and the satellites act as references kinematically connecting the pinion 9d and the barrel acting as output 9c.

In order to compensate for the pivoting of the mobile support 11, the latter is in kinematic connection with said second input 9b of the differential gear 9. In the variant shown, the second input 9b is formed by a mobile comprising a first edge teeth. 9f constituting another solar mobile of the differential gear 9, as well as a second set of teeth 9g which meshes with a reference 41a, itself driven by means of a toothed segment 41b integral in rotation with the movable support 11.

The pivotings of the movable support 11 are transmitted to the second input 9b and are “subtracted” from those of the finishing gear 5 so as not to influence the torque supplied to the regulating member 7 and not to disturb it. A pivoting of the mobile support rotates the second input 9b, and thus the satellites, which results in the frame of the planet carrier 9a not pivoting as a function of the pivoting of the mobile support 11.

In the absence of such a differential gear 9, a pivoting of the movable support 11 in one direction would "wind" the finishing gear 5, thus applying a positive counter-force (that is to say in the direction of rotation of the finishing gear 5), thus causing a higher application of torque to the regulating member 7. A pivoting in the other direction would "unwind" the finishing gear, thus applying a negative counter force (that is, i.e. in the opposite direction to that of the rotation of the finishing gear 5). This latter situation would reduce the torque transmitted to the regulating member, and would even run the risk of stopping the regulating member 7. Furthermore, such an arrangement would in any case be limited to significantly limited angular pivoting speeds of the movable support. The use of a differential gear 9 effectively isolates the finishing gear 5 from the pivoting of the movable support 11, which can thus pivot at any angular speed.

The planet carrier frame is also provided with a peripheral toothing 9j, which serves to drive a return 31, which in turn drives a pinion 33a integral in rotation with an actuating cam 33b. This cam 33b therefore rotates continuously and performs one revolution in one minute, independently of the position of the mobile support. Three times per revolution, one of the three peaks that the cam comprises actuates a release member 35, in the form of a rocker in the present case. The latter is provided at a first end with a roller 35a in order to minimize friction with the cam 33b. The other end 35b of the release member 35 rests against a block 29c integral with the stop balance lever 29b.

If we consider that the sprung balance 17a is currently at rest and is stopped by the balance stop 17c, every 20 seconds, one of the tops of the actuating cam 33b lifts the release member 35, which lifts up to in turn, the pendulum stop rocker 29b, which moves the pendulum stop 17c away from the balance. In view of the geometry of the rockers 29a and 29b, the balance stop rocker 29b can be lifted (by pivoting clockwise on the figure 4 ) by the release member 35, and this independently of the position of the intermediate lever 29a.

The sprung balance 17a is thus released and the control gear 15a is started. The control cams 11b, 11c and the actuation cams 25, 27 begin to pivot as described above, which rotates the movable support 11 to its next position in the predetermined sequence. When the locking eccentric 19 has rotated a small angle, it moves the stop lever 29, which rotates counterclockwise on the figure 3 . The intermediate lever 29a thus pivots clockwise on the figures 3 and 4 under the effect of a return spring (not shown) which is strong enough to overcome the effect of the return spring of the stop balance lever 29b. The end 29d of the intermediate lever approaches the pivot of the balance stop lever 29b, and slides along its side 29th, which prevents the stop balance lever from falling on the balance. Immediately thereafter, the top of the actuating cam 33b has passed the roller 35a and releases the release member 35 and thus the block 29c. Until the next passage of a top of the actuating cam 33b, the balance stop 17c is under the control of the locking eccentric 19. Fifteen seconds after the start of the control gear 15a by the actuating cam 33b , one of the wings of the locking eccentric 19 moves the locking lever 29, which rotates counterclockwise on the figure 3 . The intermediate lever 29a thus pivots clockwise on the figures 3 and 4 , and the end 29d of the intermediate lever 29a approaches the pivot of the balance stop lever 29b, which falls on the balance, stopping it by means of the balance stop 17c. Five seconds later, this operating cycle restarts following the next intervention of a top of the control cam 33b on the release member 35.

Although the control gear 15a is triggered by means of the actuation cam 33b, there is no transmission of torque between the finishing gear 5 and the control gear 15a, and they are therefore independent of each other. on the other at the kinematic level. The rate of movement 1 is thus independent of the rate of the control gear 15a. If, for example, the second motor member 3b is disarmed so that the control gear 15a no longer operates, the movable support 11 remains stationary and the finishing gear 5 continues to operate.

By adding a second brake to stop the sprung balance 17a, said brake being actuated by any manual control member, the pivoting of the movable support can be stopped manually. Alternatively, the control member can act on only the brake 17c already described. The user can thus stop the balance in a desired position, for example in order to observe the regulating member 7 in a precise position. If the user stops the movable support 11 in an intermediate position, once the second brake no longer stops the balance, on the next passage of a top of the actuating cam 33b, the balance will be released and the mobile support will pivot to the next stop angle in the predetermined sequence before the pendulum is stopped again via the set of levers 29, 29a, 29b.

In order to form an operating indicator of the control gear 15a, a needle 37 is in kinematic connection with the second gear 15b. In the illustrated variant, the gear ratios are chosen such that it performs one revolution per minute when the control gear 15a is operating. In fact, this needle travels 120 ° in fifteen seconds when the mobile support is in the process of being pivoted, then pauses for five seconds when the mobile support is at rest, and then repeats this sequence as long as the mobile support continues its sequence. of swivels. In doing so, hand 27 acts as a second hand not conventional, which brings additional interest to movement 1 for the user.

In view of the above, it is clear that the regulating member can travel through a series of different angular positions. In terms of isochronism, this system has a vortex effect on an additional axis which the regulating member 7 itself presents, without the mobile support 11 making complete rotations. In comparison with the layout of the document EP 1980920 mentioned above, a balance of larger diameter can thus be used in the same thickness of the movement, and / or the thickness of the movement can be significantly reduced for a balance of the same size. A larger balance wheel can, for example, contribute to an improvement in the isochronism of the movement. In the illustrated variant, which comprises a uni axial tourbillon mounted on the movable support 11, the movement of the invention provides the effect of a bi-axial tourbillon, without requiring as much height in the movement as a bi-axial tourbillon. -axial "classic" having a balance having the same dimensions. In the case of a regulating member with a simple sprung balance, the movement provides a uniaxial tourbillon effect, the axis of rotation of which is perpendicular to that of the balance.

On the other hand, since there is no torque transmission between the finishing gear 5 and the pivot control gear 15a, the latter is independent of the former. The torque supplied for the pivoting of the movable support 11 therefore does not represent any additional load on the finishing gear train 5, and therefore does not influence the operation of the regulating member 7. The isochronism of the regulating member 7 is thus ensured. . The only interaction between the two cogs 5, 15a at the level of the torque is indirect via the toothed segment 41b integral with the movable support 11 and the second input at the level of the differential gear 9, which effectively serves to isolate the cog. finishing 5 of the pivotings of the movable support 11 and thus making it independent of the latter.

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.

Claims (16)

1. Timepiece movement (1) comprising:

   - at least one drive member (3; 3a, 3b);

   - a first power take-off (3c) and a second power take-off (3d), each kinematically linked to said at least one drive member;

   - a regulating member (7) kinematically linked to said first power take-off (3c) by means of a finishing gear train (5);

   - a movable support (11) holding said regulating member (7) and arranged to pivot between two limit pivot angles with reference to a frame element (12);

   - a pivot control device (13) arranged to pivot said movable support (11) between said limit pivot angles in a back-and-forth movement;

   - a control gear train (15a) connecting said pivot control device (13) to said second power take-off (3d), said pivot control gear train (15a) being distinct from said finishing gear train (5).
2. Movement (1) according to Claim 1, in which said at least one drive member (3; 3a, 3b) comprises a first drive member (3a) arranged to drive said finishing gear train (5) by means of said first power take-off (3c) and a second drive member (3b) arranged to drive said pivot control gear train (15a) by means of said second power take-off (3d).
3. Movement (1) according to any of the preceding claims, in which the pivoting of said movable support (11) is triggered by an element (33b) driven by said finishing gear train (5).
4. Movement (1) according to Claims 1 to 3, in which said control device (13) comprises a speed controller (17; 17a, 17b) provided with at least one brake (17c).
5. Movement (1) according to Claim 4, in which said speed controller (17) is a balance and spring assembly (17a) associated with an escapement (17b), and said brake is a balance stop (17c).
6. Movement (1) according to one of Claims 4 and 5 as dependent on Claim 3, in which said brake (17c) is arranged to be released by means of said element (33b).
7. Movement (1) according to Claim 6, in which said element is a cam (33b) arranged to actuate a release member (35), this release member (35) being arranged to release said brake (17c).
8. Movement (1) according to one of Claims 4 to 7, in which said brake (17c) is arranged to be activated by means of an element of said pivot control device (13).
9. Movement (1) according to one of the preceding claims, in which said finishing gear train (5) comprises a differential gear (9) having a first input (9a) arranged to be driven by said drive member (3; 3a), a second input (9b) arranged to be driven as a function of the angular position of said movable support (11), and an output (9c) arranged to drive said regulating member (7) .
10. Movement (1) according to one of Claims 1 to 8, in which said finishing gear train (5) comprises a torque compensator (9z) comprising a staff (9k) rotationally-integrated with an input (9a) arranged to be driven by said first power take-off (3c), a second input (9b) arranged to be driven as a function of the angular position of said movable support (11), said second input comprising a wheel (91) mounted idle on said staff (9k) and linked thereto by means of a resilient element (9m), and an output (9c) arranged to drive said regulating member (7), said output comprising a wheel (9o) mounted idle on said staff (9k) and linked thereto by means of a resilient element (9m).
11. Movement (1) according to one of the preceding claims, in which said pivot control device (13) comprises at least one control cam (11b, 11c) rotationally-integrated with the movable support (11), said control cam (11b, 11c) comprising at least one actuation surface (11e) arranged to interact with an actuating cam (25, 27) driven by said control gear train (13) in order to pivotally drive said movable support (11).
12. Movement (1) according to one of the preceding claims, in which said pivot control device (13) comprises a safety lever (45) rotationally-integrated with said movable support (11), said safety lever (45) comprising a plurality of limiting pins (45a) that are located in tracks (43a) comprised by a track disc (43) arranged to be rotated by said pivot control gear train (15a), said tracks (43a) being configured in order to prevent the untimely pivoting of said movable support (11).
13. Movement (1) according to Claim 8, in which said pivot control device (13) comprises a locking eccentric (19) arranged to be driven by said pivot control gear train (15a), said locking eccentric (19) being arranged to interact with a stop lever (29) arranged to stop said speed controller (17).
14. Movement (1) according to one of the preceding claims, in which said pivot control device (13) is arranged so that said movable support (11) has moving periods when said movable support (11) is moving, and stopped periods when said movable support (11) is stopped.
15. Movement (1) according to Claim 14, in which said moving periods are longer than said stopped periods.
16. Timepiece comprising a movement according to one of the preceding claims.

Images