WO2017220246A1

WO2017220246A1 - Timepiece movement

Info

Publication number: WO2017220246A1
Application number: PCT/EP2017/060952
Authority: WO
Inventors: David Bernard; Stephen Forsey; Florian Corneille; Thomas Dietrich
Original assignee: Complitime S.A.
Priority date: 2016-06-23
Filing date: 2017-05-08
Publication date: 2017-12-28
Also published as: CN109313411A; EP3475764A1; CH712601A1; EP3475764B1

Abstract

The invention relates to a timepiece movement (1) comprising: - at least one driving member (3; 3a, 3b); - a first power take-off (3c) and a second power take-off (3d), each kinematically connected to said at least one driving member; - a regulating member (7) kinematically connected to said first power take-off (3c) via a going train (5). According to the invention, the movement (1) also comprises: - a movable support (11) carrying said regulating member (7) and designed to be pivotable between two limiting pivoting angles with reference to a frame element (12); - a pivot control device (13) designed to reciprocally pivot said movable support (11) between said limiting pivoting angles; and - a control gear train (15a) connecting said pivot control device (13) to said second power take-off (3d), said pivot control gear train (15b) being distinct from said going train (5).

Description

Clockwork movement

Technical area

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

State of the art

Since Breguet mounted a pendulum 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 vortices, on which the modern developments of complicated multi-axis vortices were built. The integration of such bi-axial and triaxial eddies in wristwatches presents difficulties in terms of complexity and the thickness necessary to implement them. Moreover, these types of vortices, in which the regulating member pivots about two or three axes, are energy-intensive and require a high torque for their training, this energy being provided by the finishing gear.

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

However, all movements of this device remain driven by the gear train, which still requires a higher torque than for a conventional uni-axial vortex.

Another interesting document in the context of the present invention is ΙΈΡ 1980920. This document describes a single axis vortex system, this axis of rotation being perpendicular to that of the balance. Once per hour, the frame, which supports the regulating member and a part of the work train, performs a pivoting step by the action of a buffer barrel, this pivoting also serving to advance the indication hours. The latter is on a ribbon that causes 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. A rotation of the frame in one direction of rotation is thus mandatory, without which the display of hours would not work. Even if each rotation 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, with no pivot angle limit, that is to say no pivot angle that can not be exceeded by the frame. Indeed, the pivot angle increases to infinity at a rate of 60 degrees each hour of operation.

This arrangement requires that a large part of the gear train is in the mobile frame, and performs complete turns. This has the result that either the pendulum 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. Moreover, the sudden pivoting of the mobile frame generates significant unwanted shocks.

Disclosure of the invention

A main object of the present invention is to overcome the disadvantages of the prior art, by proposing a watch movement that allows to present chronometric benefits, without requiring a significant thickness in the movement, and without using the cog as a power take-off for certain movements of the regulating member.

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

According to the invention, the movement comprises a mobile support, such as a cradle, a ring, a cage, a board or the like, pivoted on a frame member and carrying said regulating member and adapted to pivot between two angles. pivoting limits, which can not 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 pivot said movable support in a gated movement. comes. A control train connects said pivot control device to a second power take-off (where the control gear train begins), distinct from the first, and which is in kinematic connection with said at least one motor unit. The pivot control train is therefore distinct from said work train, at least at the level of the torque transmission between the work train and the work train. The pivoting of the mobile support is not driven by a torque emanating from the work train, and thus do not represent additional torque load on the latter, which minimizes, or eliminates, the disturbances on the wheel due to these pivoting.

Since the slewing control wheel does not receive any torque from the finishing train, the movement of the mobile support does not represent any load on the latter, and therefore can not influence the progress of the regulating member. Furthermore, the fact that the mobile support performs a back and forth pivoting requires less height in the movement than a vortex whose / a cage pivots about an axis perpendicular (or almost) to the axis. rotation of the balance. A larger regulating organ can therefore be used in the case of such a vortex, which improves the isochronism, while keeping the "whirlwind" or even "double vortex" effect, according to the construction of the vortex. regulating member (namely a conventional balance-spring, respectively a conventional vortex). Indeed, it is not obligatory to carry out complete rotations to present a positive effect on the isochronism provided by changes of angular positions as in a "classic" vortex.

[001 1] Advantageously, said at least one motor member comprises a first motor unit arranged to drive it end gear issage through said first power take-off and a second motor member arranged to drive said control gear of pivoting through the second PTO. The two wheels mentioned can thus be totally isolated from one another at the torque transmission, each having its own source of energy. The slewing control train therefore does not contribute to the disarming of the motor unit used by the gear train.

Advantageously, the pivoting of said movable support is engaged by a member driven by said work train, such as a cam, a lever or the like. Movements of the movable support can therefore be synchronized with the running of the regulating member, without requiring transfer of torque between the work train and the slewing control train. Alternatively, the pivot control train can be autonomous, or can be triggered and / or blocked manually.

Advantageously, said control device comprises a speed controller, such as a flywheel, a finned flywheel, a sprung balance or the like. This speed controller is provided with at least one brake, such as a rocker stop, a friction brake or the like. This brake can thus be used to block and trigger the operation of the pivot control wheel in a simple manner. This brake may, for example, be arranged to be released via said element driven by said work 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 arranged to be activated, that is to say to stop the speed controller, via an element of said pivot control device. The pivoting of the mobile support is thus stopped by the control device, which prevents these pivoting can be out of sync, particularly in the case where they are triggered by a member driven by the work train. In such a case, if the period between two actuations of a pivot is longer than the period in which the movable support pivots, the pivoting will remain synchronized with the running of the gear train.

Advantageously, the movement may comprise a brake arranged to be actuated manually, said brake being also arranged to allow and selectively prevent the operation of said speed controller. This brake may be the same as mentioned above, or an additional brake. In any case, this allows the user to stop the mobile support in a desired position, for example to observe it.

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

As an alternative to differential gearing, said finishing gear train 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 according to the angular position of said movable support, said second input comprising a wheel mounted idle on said shaft and connected thereto via an elastic member, and an output arranged to drive directly or indirectly said regulating organ. Said output comprises another wheel also mounted idle on said shaft and connected thereto via its own elastic element. This solution requires mo insdep parts that 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 actuating surface arranged to cooperate with an actuation cam driven by said control train. to drive said movable support pivotally. This system makes it possible to drive the mobile support pivotally. Therefore, the system does not require any jumper to ensure the positioning of the mobile support when it is stopped. The energy consumption is thus reduced. Alternatively, a system with partial teeth can also be used.

Advantageously, said pivoting control device comprises a safety lever secured to rotate 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 that comprises a track disc arranged to be rotated by said pivot control train, said tracks being shaped to prevent inadvertent pivoting of said movable support. When the mobile support is supposed to remain stationary, the interaction of at least one of the imitation pins with the wall of a track reliably blocks the pivoting of the movable support, notwithstanding the weight and inertia of the support. The exact shape of the tracks, the rotational angular velocity of the track disk 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 block and release the media at the desired moments.

Advantageously, said pivot control device comprises a locking eccentric arranged to be driven by said pivot control wheel, 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 slewing control gear, which prevents the pivoting of the movable support can desynchronize.

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

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

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

Brief description of the drawings

Other features and advantages of the present invention will appear more clearly on reading the detailed description given with reference to the accompanying drawings given by way of non-limiting examples and in which: FIG. 1 represents a schematic diagram of a watch movement according to the invention;

FIG. 2 represents a schematic diagram of a variant of a watch movement according to the invention;

FIG. 3 represents a simplified perspective partial view of a concrete embodiment of a variant of a clockwork according to the invention, particularly illustrating the pivoting control gear as well as the pivot control device;

Figure 4 shows a plan view of the variant of Figure 3; Figures 5 and 6 show partial perspective views of the pivot control device of the variant of Figure 3;

Figures 7 to 9 show partial perspective views of the gear train and the differential gearing of the variant of Figure 3

Figures 10a to 10c show views of a security system that includes the embodiment of Figures 3 to 9; and

FIG. 11 represents a schematic diagram of an alternative solution for compensating the displacements of the mobile support.

Mode (s) of realization of the invention Figure 1 schematically illustrates the principle of the invention in its simplest form, in the context of a watch movement 1. This movement 1 comprises one or more motor members 3, such as one or more motor springs housed in one or more barrels. This or these motor member (s) 3 is associated with a first PTO 3c and a second PTO 3d. In the case of a single barrel, these power take-offs 3c, 3d can simply be mobile meshing with a toothing that includes the barrel (for example a toothing extending from a drum), or outputs of a gear to differential whose input is in kinematic connection with the barrel. Since the first of these PTOs 3c extends a work train 5 which kinematically links the motor member to a regulating member 7 and ensures its maintenance. This regulating member may be a pendulum-balance assembly, a vortex, a carousel, or any other suitable regulating organ, conventional or inclined.

The work train passes through a first input 9a and an output 9c of a differential gear 9 or an alternative system, the operation will be better understood later.

The regulating member 7 is carried by a movable support 1 1 pivotally mounted at least one axis relative to a frame 1 2, the movable support 1 1 pivoting back and forth between angles of pivoting limits under the control of a pivot control device 13 through a control wheel 15a. This latter connects the second power take-off 3d of the drive member 3 to the pivot control device 1 3, which controls the pivoting of the movable support 1 1. As a result, the work train 5 and the drive train 15a are independent at the torque transmission downstream of the power take-offs 3c, 3d. The pivoting of the movable support 1 1 can be made in a single axis, or alternately along several axes, cutting the movable support 1 1 or not, for example in order to perform a cardan movement or patella.

So that the pivoting of the mobile support 1 1 exert no influence on the work train and therefore do not interfere with the running of the regulating member 7, a second input 9b of the differential gear is kinematically linked to the mobile support, so that the second entry rotates according to the angular displacements of the movable support 1 1. In doing so, the torque provided by the part of the finishing gear 5b downstream of the differential gear 9 remains independent of the pivoting of the movable support. The differential gear 9 has the effect of isolating the torque transmission along the work train 5 displacements of the movable support 1 1. In the absence of the differential gearing 9, the movements of the movable support January 1 would cause a counter-force due to the fact that the regulating member 7 is carried by the movable support 1 1 and is also moving relative to the frame .

An alternative solution to the differential gear 9 is a torque compensator 9z as schematically illustrated in Figure 1 1. The same reference signs have been used in this figure 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 inlet 9a comprising a wheel 9d driven by the first part 5a of the finishing train 5. A second inlet 9b comprises a wheel 91 mounted idle on the shaft 9k. This wheel 91 is rotated according to the movements of the pivoting support 1 1, and is linked to the shaft 9k by means of an elastic element 9m such as a spiral spring or other. The latter is fixed on the shaft via 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 via 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 prestressed. During operation of the system, when the mobile support 1 1 remains stationary, the torque arriving on the wheel 9d is transmitted to the wheel 9o through its elastic member 9m. The wheel 91 remaining stationary, its elastic element is stretched or relaxed in its winding direction.

When the mobile support 1 1 pivots, the elastic member 9m of the wheel 91 is stretched or expands, if necessary, and adding or subtracting 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 disposed on the movable support 1 1 is compensated

To prevent the elastic element 9m of the wheel 91 wraps or unrolls too much, its ferrule 9n can be arranged to act as friction, and thus allow a relative rotation with the shaft 9k . Alternatively, any friction may be incorporated between the wheel 91 and the movable support January 1.

The pivot control device 13 may be autonomous, and / or may control the operation following actions of a user, for example by means of a pushbutton 14 or the like, and / or controlled The last two possibilities are shown in FIG. 1 by dashed arrows.

[0034] FIG. 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 with respect to the transmission. of couple.

In this variant, the pivot control device 13 is associated with a speed controller 17, which may take the form of a balance-balance assembly, a flywheel, a finned flywheel , or the like, in kinematic connection with the pivot control device 13 via a second gear 15b. The speed controller 17 is locked and / or released under the control of the work 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 train 5 and locked under the control of the pivot control train 15a, as is the case in the specific embodiment which will be described later.

Figures 3 to 9 illustrate a concrete embodiment of a clockwork according to the invention, corresponding to the diagram of Figure 2. Given the complexity of the mechanism, some elements have not been represented in some figures to avoid overloading them.

Figures 3 and 4 particularly illustrate the drive train 15a, the pivot control device 13, the movable support 1 1, and the speed controller 1 7. The latter is formed of a regulating member spiral balance 17a associated with a classic exhaust 17b. This exhaust 17b has no influence on the movement and acts exclusively in connection with the pivot control device 13. The alternative control forms mentioned above can of course be used in place of the exhaust 17b and sprung balance

17a.

The slewing control gear 1 5a l ie simply the second barrel 3b to d ispositif pivot control 1 3, and the second gear 15b is branch of the gear 15a. The pivot control device 13 is kinematically connected to the movable support 11, which is pivoted to the movement frame (not shown). The movable support 1 1 supports the regulating member 7, which is a simple tourbillon in the illustrated variant, but can also be a simple balance-spring associated with an exhaust, or any other type of regulating member known to man of career.

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

In the variant shown, the pivot control device 13 drives the movable support 1 1 pivotally so that it performs the predetermined sequence of pivoting -35 ° - 0 ° - + 35 ° - 0 ° - -35 ° etc. around its axis of rotation 1 1 a relative to the plane of the movement. The angles of -35 ° and + 35 ° represent extreme and extreme angles of rotation in this case, and that of 0 ° represents an intermediate pivoting stop angle, which is the same as the position angles imitated . These are absolute and can never be exceeded by the movable support 1 1, the ndisqued awake you angels of stopping intermediate pivoting are exceeded at the next pivoting of the movable support 1 1. The mobile support is stopped for five seconds at each corner of the sequence, and pivoted for fifteen seconds. Changes to the movement to control the mobile support 1 1 according to other sequences of pivoting are within the reach of the skilled person. More generically, the periods of displacement of the movable support 1 1 are advantageously longer than the stopping periods, which reduces the impact experienced by the various components of the pivot mechanism. Nevertheless, this system is also suitable for periods of displacement equal or shorter than those stop, and it is also possible to provide different periods of immobilization in each stop position, according to the provisions of the cams.

Solidarity in rotation of the movable support 1 1 is a first control cam 1 1b and a second control cam 1 1 c.

The first control cam 1 1b comprises three safety surfaces

1 1 contiguous each of an actuating surface 1 1 e.

When the control train is running, a wheel 21 is in kinematic connection with another wheel 23, which is integral in rotation with an actuation cam 25. The wheels 21, 23 have been omitted from the figure 6 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) and the actuation cam 25, which turns in the direction counterclockwise to drive the first control cam 1 1b clockwise. As such, the actuation cam 25 comprises two fingers 25a, angularly spaced 90 °, and which drive the movable support 1 1 in its two clockwise rotation steps (according to the orientation of Figures 5 and 6) .

In order to drive it counterclockwise, the second control cam 11c resumes a shape similar to that of the first control cam 11b, but inverted and angularly offset by an ad hoc angle defined in FIG. function of the construction. The second control cam 11c has a shape inverted with respect to the other control cam 11b and is rotated by its own actuating cam 27 (see Figure 6). The latter is coaxial and integral with the wheel 21 and thus rotates in the same direction, and serves to drive the mobile support 1 1 counterclockwise

(according to the orientation of Figures 5 and 6).

When one of the fingers 25a, 27a of one of the actuating cams 25, 27 is in contact with one of the actuating surfaces 1 1 e, the angular position of the movable support 1 1 is ensured. by the interaction of these elements. Nevertheless, when the mobile vehicle 1 1 is stationary between two movements, these fingers 25a, 27a are remote from the control cams 11b, 11c. In order to block the mobile support 1 1 in each of its stop positions and thus prevent inadvertent movement of the support 1 1, a security system 42 is provided. This security system 42 is illustrated in more detail in the form of exploded diagrams in FIGS. 10a to 10c.

The security 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 1 1 as well as the control cams 1 1 b, 1 1 c, and therefore follows the reciprocating movement of the support January 1. This safety lever 45 also comprises three limiting pins 45a arranged at the end of the lever 45, which take place in tracks 43a which is provided with the track disc. 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 blocked when the mobile support 1 1 is stopped (the tracks walls 43a serving as stops for the pins 45a), and can pivot when the fingers 25a, 27a drive the control cams 1 1b, 1 1c (the pins are at this time in recessed areas 43b of the tracks that do not prevent tilting of the safety lever 45).

As a second security, abutment surfaces 25b, 27b are provided on the actuating cams 25, 27, adjacent to the fingers 25a, 27b respectively. These abutment surfaces 25b, 27b are positioned facing the safety surfaces 1 1 d when the mobile support 1 1 is at rest so that, during a shock that could overcome the effect of the security system 42, the safety surface 1 1d next to an abutment surface 25b, 27b, abuts against the latter.

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

Alternatively, the pivot control device 13 may use toothed segments with interrupted teeth instead of the control cams 1 1b, 1 1c, as well as interrupted wheels instead of the actuation cams 25, 27. Still alternately, the control device 13 can drive the mobile support 1 1 in a single pivoting direction, 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, downtime could be different in each of the stop positions, depending on the shape and arrangement of the various cams.

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 1 5b is free to rotate, the locking eccentric will perform a revolution in 60 seconds in the illustrated variant.

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

Passing now to the gear train 5, as shown in Figures 7, 8 and 9, the gear train connects firstly (through part 5a) the first barrel 3a to a first input 9a d ' a differential gear 9 via the first power take-off 3c, and on the other hand (through the part 5b of the work train 5 which is mounted on the movable support 1 1), an output 9c of the differential gear 9 to the regulating member 7 carried by the movable support 1 1. The first input 9a consists of a carrier chassis carrying at least one satellite gear (invisible) in a known manner. The chassis is secured in rotation with a pinion 9d driven by the first barrel 3a. Said output 9c consists of a barrel comprising a 9h edge toothing meshing with the planet gears, and a second edge toothing 9i which meshes with a toothed wheel 39 pivoted on the movable support 1 1 and which is in kinematic connection. with the regulating organ 7. The toothed wheel 39 and the others movable downstream of the latter form the second part 5b of the work train 5 and drive the regulating member 7.

When the mobile support 1 1 is stationary, the second input 9b remains stationary, and the satellites act as references kinematically connecting the pinion 9d and the output of the barrel 9c.

In order to compensate for the pivoting of the mobile support 1 1, the latter is in kinematic connection with said second input 9b of the differential gearing 9. In the variant shown, the second input 9b is formed of a mobile comprising a first ring gear 9f constituting another solar mobile differential gear 9, and a second set of teeth 9g engene with a 41a reference, itself driven via a toothed segment 41b integral in rotation of the mobile support 1 1.

The pivoting of the mobile support 1 1 is transmitted to the second input 9b and are "subtracted" from those of the work train 5 so as not to influence the torque supplied to the regulating member 7 and not to disturb it. Pivoting of the movable support rotates the second input 9b, and thus the satellites, which results in the chassis of the carrier 9a does not pivot according to the pivoting of the movable support 1 1.

In the absence of such a differential gear 9, a pivoting of the movable support 1 1 in a direction "would wind" the work train 5, thus applying a positive counter-force (that is to say in the direction of rotation of the work train 5), thus causing a higher application of torque to the regulating member 7. A pivoting in the other direction "unwind" the work train, thus applying a negative counterforce ( that is to say 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 could even stop the regulating member 7. Moreover, such an arrangement would in any case be limited to angular speeds of pivoting of the movable support significantly limited. The use of a differential gear 9 effectively isolates the work train 5 from the pivoting of the mobile support January 1, which can rotate at any angular speed.

The chassis of the carrier is also provided with a peripheral gear 9j, which serves to drive a gear 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, regardless of the position of the movable support. Three times per revolution, one of the three peaks that the cam actuates a release member 35, in the form of a rocker in this case. The latter is provided at one end with a roller 35a to minimize friction with the cam 33b. The other end 35b of the release member 35 rests against a block 29c integral with the rocker stop rocker 29b.

If it is considered that the spring balance 17a is currently at rest and is stopped by the balance stop 17c, every 20 seconds, one of the vertices of the actuating cam 33b raises the release member 35, which in turn raises the rocker stop lever 29b, which separates the balance stop 17c from the balance. In view of the geometry of the flip-flops 29a and 29b, the rocker stop rocker 29b can be lifted (by pivoting clockwise in FIG. 4) by the release member 35, and this independently of the position of the rocker intermediate 29a.

The sprung balance 17a is thus released and the drive train 15a is turned on. The control cams 1 1b, 1 1c and the actuation cams 25, 27 begin to pivot as described above, which causes the movable support 11 to pivot to its next position in the predetermined sequence. When the locking eccentric 19 has pivoted by a small angle, it moves the stop lever 29, which pivots counterclockwise in FIG. 3. The intermediate lever 29a thus pivots clockwise in FIGS. 4 under the effect of a return spring (not shown) which is strong enough to overcome the effect of the return spring of the balance stop rocker 29b. The end 29d of the intermediate flip-flop approaches the pivot of the rocker stop rocker 29b, and slides along its flank 29e, which prevents the pendulum rocker from falling back on the balance. Immediately after, 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 wheel 15a by the actuating cam 33b , one of the wings of the eccentric blocking 19 moves the locking lever 29, which pivots counterclockwise in Figure 3. The intermediate lever 29a thus rotates clockwise in Figures 3 and 4, and the end 29d of the intermediate lever 29a is close to the pivot of the rocker stop 29b, which falls on the pendulum, stopping it by means of the stop ba la nier 1 7c. 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 actuating cam 33b, there is no torque transmission between the work train 5 and the work train 15a, and they are therefore independent from one another to the kinematic one. The movement of the movement 1 is thus independent of the operation of the drive train 15a. If, for example, the second drive member 3b is disarmed so that the drive train 15a no longer operates, the movable support 1 1 remains stationary and the work train 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 at a time. Alternatively, the control member can act on the only brake 17c already described. The user can thus stop the balance in a desired position, for example to observe the regulating member 7 in a precise position. If the user stops the mobile support 1 1 in an intermediate position, once the second brake no longer stops the balance, the next passage of a top of the actuating cam 33b, the balance will be released and the support The mobile will pivot to the next stopping angle in the predetermined sequence before the pendulum is stopped again via the set of levers 29, 29a, 29b.

To form an indicator of operation of the control train 15a, a needle 37 is kinematically connected with the second gear 15b. In the illustrated variant, the gear ratios are chosen such that it performs one revolution per minute when the drive train 15a is operating. Indeed, this needle travels 120 ° in fifteen seconds when the mobile support is rotating, 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 pivoting. In doing so, the needle 27 acts as unconventional second hand, which brings additional interest to the movement 1 for the user.

In view of the above, it is clear that the regulating member can traverse a series of different angular positions. At the level of the isochronism, this system has a tourbillon effect on an additional axis that the regulating member 7 presents itself, without the mobile support 1 1 performs complete rotations. In comparison with the above-mentioned EP 1980920 arrangement, a larger diameter rocker can thus be used in the same thickness of the movement, and / or the thickness of the movement can be significantly reduced for a rocker of the same size. A larger scale may, for example, contribute to an improvement of the isochronism of the movement. In the illustrated variant, which comprises a uni-axial vortex mounted on the movable support 1 1, the movement of the invention provides the effect of a bi-axial vortex, without requiring as much height in the movement as a vortex bi-axial "classic" having a balance having the same dimensions. In the case of a simple balance-spring regulating member, the movement provides a uniaxial vortex effect, whose axis of rotation is perpendicular to that of the balance.

Moreover, since there is no torque transmission between the work train 5 and the pivot control train 15a, the latter is independent of the first. The torque provided for the pivoting of the mobile support January 1 therefore represents no additional load on the work train 5, and therefore does not influence the operation of the regulating member 7. The isochronism of the regulating member 7 is thus assured. The only interaction between the two gear trains 5, 1 5a at the torque level is indirect via the toothed segment 41b integral with the movable support 11 and the second input at the differential gearing 9, which is effectively used to isolate the work train 5 of the pivoting of the movable support 1 1 and thus make it independent of the latter.

Although the invention has been described above in connection with specific embodiments, additional variants are also can be envisaged without departing from the scope of the invention as defined by the claims.

Claims

claims

1. Clockwork movement (1) comprising:

at least one driving member (3; 3a, 3b);

a first power take-off (3c) and a second power take-off (3d), each in kinematic connection with said at least one driving member

a regulating member (7) kinematically connected to said first power take-off (3c) via a finishing gear train (5);

characterized in that the movement (1) further comprises:

- a movable support (1 1) carrying said regulating member (7) and arranged to pivot between two limits of pivoting angles with reference to a frame member (12);

a pivot control device (13) arranged to pivot said movable support (1 1) between said pivoted angles imitated in a reciprocating motion;

a control wheel (15a) connecting said pivot control device (13) to said second power take-off (3d), said pivot control gear (15b) being distinct from said finishing gear (5).

2. Movement (1) according to claim 1, wherein said at least one driving member (3; 3a, 3b) comprises a first driving member (3a) arranged to drive said finishing train (5) through said first power take-off (3c) and a second drive member (3b) arranged to drive said pivot control gear (15a) through said second power take-off (3d).

3. Movement (1) according to one of the preceding claims, wherein the pivoting of said movable support (1 1) is engaged by a member (33b) driven by said work train (5).

4. Movement (1) according to one of claims 1 to 3, wherein 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, wherein said speed controller (17) is a sprung balance member (17a) associated with an exhaust (17b), and said brake is a balance stop (17c).

6. Movement (1) according to one of claims 4 and 5, wherein said brake (17c) is arranged to be released through said element (33b).

7. Movement (1) according to claim 6, wherein said element is a cam (33b) arranged to actuate an organ liberation (35), this releasing member (35) being arranged to release said brake (17c).

8. Movement (1) according to one of claims 4 to 7, wherein said brake (17c) is arranged to be activated via an element of said pivot control device (15a).

9. Movement (1) according to one of claims 4 to 8, comprising a brake (17c) arranged to be manually operated action, said brake (17c) being also arranged to allow and prevent the operation of said speed controller ( 17).

10. Movement (1) according to one of the preceding claims, wherein said finishing train (5) comprises a differential gear (9) having a first inlet (9a) arranged to be driven by said motor member (3; ), a second inlet (9b) arranged to be driven according to the angular position of said movable support (1 1), and an outlet (9c) arranged to drive said regulating member (7).

1 1. Movement (1) according to one of claims 1 to 9, wherein said finishing train (5) comprises a torque compensator (9z) comprising a shaft (9k) integral in rotation with an inlet (9a) arranged to be driven by said first power take-off (5c), a second input (9b) arranged to be driven according to the angular position of said movable support (1 1), said second input comprising a wheel (91) idly mounted on said shaft ( 9k) and connected thereto via an elastic element (9m), and an outlet (9c) arranged to drive said regulating member (7), said output comprising a wheel (9o) idly mounted on said shaft (9k) and connected thereto via a resilient member (9m).

12. Movement (1) according to one of the preceding claims, wherein said pivot control device (13) comprises at least one control cam (1 1 b, 1 1 c) integral in rotation with the movable support (1 1 ), said control cam (1 1 b, 1 1 c) comprising at least one actuating surface (1 1 e) arranged to cooperate with an actuation cam (25, 27) driven by said control train (13). ) to drive said movable support (1 1) to pivot.

13. Movement (1) according to one of the preceding claims, wherein said pivot control device (13) comprises a safety lever (45) integral in rotation with said movable support (1 1), said safety lever (45). ) comprising a plurality of limiting pins (45a) which fit into tracks (43a) of a track disc (43) arranged to be rotated by said pivot control train (15a), said tracks (43a) ) being shaped to prevent inadvertent pivoting of said movable support (1 1).

The movement (1) according to claim 8, wherein said pivot control device (13) comprises a locking eccentric (19) arranged to be driven by said pivot control gear (15a), said locking eccentric ( 19) being arranged to cooperate with a stop lever (29) arranged to stop said speed controller (17).

15. Movement (1) according to one of the preceding claims, wherein said pivot control device (13) is arranged such that said movable support (1 1) has periods of displacement when said movable support (1 1 ) is in motion, and stopping periods when said movable support (1 1) is stopped.

16. Movement (1) according to claim 15, wherein said periods of displacement are of longer duration than said stopping periods.

17. Timepiece comprising a movement according to one of the preceding claims.