HK1174696B - Governor for a timepiece wheel set or strike wheel set - Google Patents

Description

Manager for a timepiece wheel set or chronograph wheel set

Technical Field

The invention relates to a supervisor/regulating control (governor) for a timepiece wheel set or striking wheel set for regulating the pivoting speed of the wheel set about a first pivot axis about a reference speed value, wherein the wheel set is driven by an energy source providing mechanical torque via transmission means, the wheel set comprising at least one inertia block pivotally mounted about a first pivot axis about a second pivot axis parallel to and at a distance from the first pivot axis.

The invention also relates to a spring comprising an inertia manager for adjusting the pivoting speed of a wheel set about a first pivot axis about a reference speed value, wherein the wheel set is driven by an energy source via a transmission, the energy source providing a variable torque at a variable angular speed, the wheel set comprising a main pivot or spindle about the first pivot axis, the wheel set comprising at least one inertia block pivotally mounted about a first pivot about a second pivot axis parallel to and at a distance from the first pivot axis, the inertia block comprising a second pivot defining a third pivot axis parallel to the first pivot axis and the second pivot axis.

The invention also relates to a musical or striking mechanism for a timepiece or musical box, comprising an energy source or barrel and means for transmitting a mechanical torque from said energy source or barrel to a wheel set or striking wheel set for producing music.

The invention also relates to a timepiece or musical box including a wheel set or striking wheel set for producing music.

The present invention relates to the field of mechanical speed regulation for rotating assemblies.

More specifically, the invention relates to the field of horology, in particular timepieces comprising a striking mechanism or a musical mechanism, such as a striking watch, a musical box or the like.

Background

The manufacture of timepieces or music boxes comprising a musical movement and/or striking mechanism with complex functions requires the use of mechanisms whose regularity of operation is of comparable quality to the timepiece movement in which they are included, at least during the music or striking cycle during which the beats imposed on the music or striking sequence must be observed, although not for the constant duration of the cycle time. In fact, any drawback can be audible and unpleasant for the user, especially if the timepiece is expensive.

The energy source, usually formed by a striking barrel, usually provides the energy to lift one or several hammers to strike gongs, resonators or bells, or even a sound box in the case of a music box. The vibrations of these gongs or the like are transmitted to the middle part of the timepiece, to the bezel and to the crystal, and are radiated into the air. Energy is usually required by a cam or toothed device, such as a simple or complex striking wheel set, actuated by a lever or trigger device controlled by the timepiece movement, or by the user in the case of an alarm clock function or alarm. The amount of energy used to wind the hammers is much higher than that necessary for the operation of the timepiece movement. Furthermore, the energy source of the striking mechanism (which is usually a barrel spring) must be of a large size to avoid the user winding up or reloading too frequently, whether the energy source is mechanical, electrical or of another type.

The energy utilized by the striking mechanism is characterized by transient peaks in consumption, which also affect the large size of the energy source to ensure fatigue resistance.

Furthermore, it is not uncommon for a striking mechanism to walk fast (hunting) under the combined influence of the large amount of energy burst and inertia widely available in the energy source. The consequences are detrimental, especially in terms of the nature of the subsequent time sequence, which may be incorrect. Or subsequent time ticks may not occur at the correct time, which is even more serious.

In order to prevent the pendulum clock and the clock from going fast, it is known to use a flywheel (fly), which brakes the rotation by air friction. These devices require space and cannot be properly integrated in a watch.

The regulation of the striking rhythm (tempo) or melody (where appropriate) can be achieved by a manager that stabilizes the relaxation speed of the barrel for striking, which can be the barrel of the movement, or a separate barrel, as is often the case with pendulum clocks.

Known regulators for striking mechanisms are thus based on friction, or on vibration. They are often difficult to manufacture, inaccurate in speed, and often very noisy, which is unacceptable for expensive musical or grand strike watches.

Any adjustment of the speed, if any, is conventionally achieved by a lever system or by a mechanical governor with inertial mass, for example of the type disclosed in swiss patent No.34 in the name of Barbezat-Baillot, which uses a large amount of energy and may be bulky. The known managers are not sufficiently accurate and cannot accurately limit the deviation of the angular velocity.

The most compact is a pole organizer that uses simple stop pins, which are easy to manufacture and adjust. Typically, such managers run at high speed, about 100-. These impacts generate vibrations that are transmitted to the middle portion, bezel, and crystal, and radiated into the air as a ringing and with noise that interferes with the ringing's sound.

Furthermore, these shock or friction based governors are difficult to manufacture, inaccurate in adjusting speed, and often noisy.

In short, in timepieces or musical boxes comprising striking mechanisms, and in particular in musical watches or quiz watches, the rhythmic variation is closely related to the relaxation curve of the barrel spring. As a result, in many cases, ringing or music is slowed down at the end of the function, which is unpleasant for the user. The known managers require a lot of space and/or are noisy.

Disclosure of Invention

The present invention proposes to overcome these drawbacks and to propose a manager for a timepiece or a musical box including a striking mechanism, in particular for a musical watch or a minute repeater watch, which makes it possible to obtain a constant speed while absorbing the differences in torque in the regulating train and keeping it absolutely silent.

The invention thus provides a new solution to the problem of walking quickly, which is particularly suitable for watches.

In short, a portion of the energy released during the strike cycle is used to prevent walking up.

The present invention solves the above problems in an original way by integrating a mechanism for utilizing energy. The invention therefore relates to an adjustment device for a striking mechanism of a timepiece, said adjustment device being arranged to adjust the power consumption to a level that is just suitable for the striking mechanism, and comprising energy dissipation means for this purpose.

The invention therefore relates to an administrator for a timepiece wheel set or striking wheel set for adjusting the pivoting speed of the wheel set about a first pivot axis about a reference speed value, wherein the wheel set is driven by an energy source providing a mechanical torque via transmission means, the wheel set comprising at least one inertial mass pivotally mounted about a first pivot axis about a second pivot axis parallel to and at a distance from the first pivot axis.

According to the invention, the manager comprises means for returning the at least one inertial mass towards the first pivot axis, and the at least one inertial mass is arranged: said at least one inertial mass remaining confined in a first internal revolution space about said first pivot axis when said wheel set is pivoted at a speed lower than or equal to said reference speed, said at least one inertial mass engaging at least in its peripheral portion in a second revolution space about said first pivot axis when said wheel set is pivoted at a speed higher than said reference speed, said second revolution space being adjacent to and external to said first revolution space, said peripheral portion cooperating within said second revolution space with adjustment means arranged to brake said wheel set and to bring the pivoting speed of said wheel set back to said reference speed, and to dissipate excess energy.

According to one feature of the invention, the timepiece wheel set or striking wheel set manager comprises braking means which are active when the peripheral portion of the inertia mass passes from the first space to the second space, the braking means being formed by: an air brake device, or a pneumatic brake applied when a reference speed is exceeded, or a dry brake device, or a friction device having a surface that applies a braking torque to the peripheral portion of the inertia mass and is disposed such that the applied braking torque intersects a radius from the first pivot axis.

According to one characteristic of the invention, the peripheral portion is electrically conductive and the adjustment means are constituted by means of generating at least one variable magnetic field comprising field lines oriented so that the interaction between the peripheral portion and the magnetic field generates eddy currents (eddy current) which brake the wheel set by resisting the pivoting of the wheel set.

According to one feature of the invention, the return means are arranged to keep the at least one inertial mass confined in the first internal rotation space when the wheel set is pivoted at a speed lower than or equal to the reference speed, and to allow the at least one inertial mass to engage in the second rotation space at least at a peripheral portion thereof when the wheel set is pivoted at a speed higher than the reference speed.

According to one feature of the invention, the return means are mechanical return means and exert a return force in the direction of the first pivot axis on a second pivot comprised in the at least one inertial mass, the second pivot defining a third pivot axis parallel to the first and second pivot axes.

According to one feature of the invention, said return means are elastic return means comprising a first pivot guide about a main pivot or arbour included in said wheel set about said first pivot axis, and comprising at least one second pivot guide about said second pivot included in said at least one inertial mass about said third pivot axis.

According to one feature of the invention, the wheel set comprises a plurality of said inertia blocks arranged equidistantly about said first pivot axis, the elastic return means comprise a first pivot guide about a main pivot or arbour comprised in the wheel set about said first pivot axis, and comprise a second pivot guide about said second pivot comprised in each of said inertia blocks about said third pivot axis specific to each of said inertia blocks.

According to one feature of the invention, said elastic return means are formed by at least one spring.

According to one feature of the invention, the spring comprises a preload corresponding to the radial travel of the second pivot guide in a radial direction with respect to the first pivot axis when the spring is guided by the first pivot guide on the main pivot between a non-coupled position of the spring and a coupled position of the spring with the second pivot of the inertial mass, wherein the wheel set and the inertial mass are in a stop position, and in the coupled position of the spring the preload draws the second pivot of the inertial mass radially towards the first pivot axis.

According to one feature of the invention, the stiffness of the spring is defined so that the value of the radial force applied to the inertial mass returned by the second pivot is substantially a linear function of the angular position of the inertial mass about the first pivot on the second pivot axis with respect to the rest position of the inertial mass, the value of the radial force having an absolute value of zero corresponding to the preload stroke.

According to one characteristic of the invention, the spring is made of a micro-machinable material, or silicon, or quartz or a composite thereof, or an alloy derived from MEMS technology, or an alloy obtained by the DRIE or LIGA method, or of an at least partially amorphous material.

According to a feature of the invention, the inertial mass is made of electrically conductive material or gold, copper or silver, or comprises, in the portion subjected to the magnetic field in the chamber, a portion made of electrically conductive material or gold, or silver or copper, in a direction parallel to the first pivot axis.

The invention also relates to a spring for an inertia manager for adjusting the pivoting speed of a wheel set about a first pivot axis about a reference speed value, wherein the wheel set is driven by an energy source via a transmission, the energy source providing a variable torque at a variable angular speed, the wheel set comprising a main pivot or arbour about the first pivot axis, the wheel set comprising at least one inertia block pivotally mounted about a first pivot about a second pivot axis parallel to and at a distance from the first pivot axis, and the inertia block comprising a second pivot defining a third pivot axis parallel to the first pivot axis and the second pivot axis, characterized in that the spring is arranged to exert a return force on the second pivot in the direction of the first pivot axis, and returning said at least one inertia block towards said first pivot axis, and in that said spring comprises a first pivot guide around said main pivot and comprises at least one second pivot guide around said second pivot of said at least one inertia block.

The invention also relates to a musical or striking mechanism for a timepiece or musical box, comprising an energy source or barrel and means for transmitting a mechanical torque from said energy source or barrel to a wheel set or striking wheel set for producing music, characterized in that said transmission means drive at least one of said wheel sets included in said timepiece wheel set or striking wheel set manager.

The invention also concerns a timepiece or a musical box including a wheel set or striking wheel set for producing music, characterized in that it includes a music or striking mechanism of the type described above, and/or a timepiece wheel set or striking wheel set manager of the type described above.

Drawings

Other features and advantages of the invention will become apparent upon reading the following description with reference to the drawings, in which:

fig. 1 shows a schematic side view of a timepiece wheel set or striking wheel set manager according to the invention.

Fig. 2 shows a schematic cross-section through a first pivot axis of a first embodiment of the timepiece wheel set or striking wheel set manager of the invention, said manager being integrated in a partially shown striking mechanism integrated in a partially shown timepiece.

Fig. 3 shows a schematic top view of a part of the organizer of fig. 2, wherein the moving inertial mass contained in the organizer shows a first collapsed down position (collapsed down position) in solid lines and a second expanded position (deployed position) in dashed lines.

Fig. 4 shows a schematic top view of the organizer of the first embodiment, wherein the inertial mass moves in the annular chamber.

Fig. 5 shows an exploded view of the manager in fig. 4.

Fig. 6 shows an exploded view of the organizer of fig. 4, said organizer being equipped with means for elastically returning the inertial mass according to the first variant.

Fig. 7 shows a schematic top view of a portion of the organizer of fig. 4, said organizer being equipped with means for elastically returning the inertial mass according to a second variant.

Fig. 8 shows a schematic top view of a portion of the organizer of fig. 4, said organizer being equipped with means for elastically returning the inertial mass according to a third variant.

Fig. 9 shows a schematic top view of a part of the organizer in fig. 6 with a different number of inertial masses.

Figure 10 shows a schematic view of a variant of the manager comprising several superposed wheel sets.

Fig. 11 shows a schematic top view of the portion of the organizer in fig. 8, equipped with means for elastically returning the inertial masses according to the second variant in a preferred embodiment of said return means, the return means shown being in the uncoupled condition, not coupled to their inertial mass for return.

Fig. 12 shows the mechanism of fig. 11 with a return device coupled to the inertial mass, the wheel set shown being stopped.

Fig. 13 shows the mechanism of fig. 11 with a return device coupled to the inertial mass, the wheel set shown pivoting with its inertial mass in the deployed position.

Fig. 14 schematically shows, in a sectional view through the first pivot axis of the wheel set, the different turnaround spaces of the inertia blocks included therein.

Fig. 15 is a graph representing the braking torque as a function of the pivoting speed for two different types of speed managers.

Fig. 16 depicts the appearance of the braking torque curve C as a function of the pivoting speed ω for two different regulation characteristics.

Figure 17 is a graph representing the variation of the radial return force as a function of the angle a, which is the variation of the position of the attachment spindle of the inertial mass return device comprised in the manager according to the invention with respect to the rest position, with respect to the pivot axis of the inertial mass.

Fig. 18 is a schematic perspective view of a modification of the invention.

Figure 19 is a graph representing the variation of eddy current losses as a function of the angular position of the inertial mass on its respective pivot in the embodiment of figure 18.

Fig. 20 is a graph representing the variation of eddy current losses as a function of the angular offset of a row of top magnets relative to a row of bottom magnets, all else being equal, which together generate a magnetic field for adjusting the speed according to the invention.

Detailed Description

The present invention relates to the field of mechanical speed regulation for rotating assemblies.

The invention relates in particular to the field of horology, in particular including chronograph mechanisms, and will be described more particularly for this preferred application. However, the present invention is applicable to the adjustment of the pivot speed of any rotating assembly, regardless of its scale.

In the description of this preferred application of the invention, the invention relates to an adjustment mechanism for a timepiece wheel set or striking wheel set 1, said timepiece wheel set or striking wheel set 1 being intended for a timepiece or musical box, which will be denoted below by the generic term "timepiece".

The manager for a timepiece wheel set or striking wheel set 1 is intended for regulating the operation of a mechanism, in particular a music or striking mechanism 10, in the particular application explained in detail below and illustrated by the figures. "timepiece or striking wheel set manager 1" means hereinafter the manager for a timepiece wheel set, in particular for a striking wheel set or a musical movement wheel set, and "striking mechanism 10" means a musical or striking mechanism. Those skilled in the art will know how to apply the invention to the adjustment of other timepiece wheel sets.

The exemplary application on the striking mechanism takes into account the particular limitations inherent in the adjustment which must be very precise, preferably better than 3%, since any deviation can be heard and is unpleasant for the user and the noise level must be kept very low with respect to the volume of the chime. The invention thus combines precision of adjustment and quietness.

Striking mechanism 10 comprises, in a conventional manner, an energy source or barrel, and means 3 for transmitting mechanical torque from the energy source or barrel towards a wheel set or striking wheel set for producing music, said wheel set being formed by a hammer, a lever or the like. The energy source, barrel or the like typically provides a torque that varies as a function of the relaxation of the spring. Of course, the manager 1 according to the invention described below can also be used with energy sources that provide a torque that is considered constant at a speed that is considered constant, the only purpose being to guarantee the accuracy of the regulation of the speed and to prevent hazards such as shocks.

The relaxation of the barrel is associated with a significant reduction in torque as a function of time, for example by a factor of about 4. The variation of the residual torque envelope (torque envelope) on the manager wheel set is due to the variation of the barrel load. High frequency torque peaks may be associated with loading music pieces (loading music pieces). These high frequency torque variations have little effect on the speed level and are therefore ignored due to their brief nature and system inertia.

The amount of energy received as torque at the user wheel set (in this case the striking wheel set) is thus quite variable. By stabilizing the pivoting speed of the wheel set on the one hand and using the excess energy when the barrel starts to relax on the other hand, the most uniform energy possible is provided to the user's wheel set.

The desired speed manager for a particular application is characterized by low speed variation (less than 3% of rated speed) and high power dissipation (greater than 6 mW). Ideally, below the rated speed, the braking torque induced by the governor should be zero. Above the rated speed, the braking torque as a function of speed must increase drastically. The higher the characteristic slope, the lower the change in velocity. FIG. 15 illustrates an exemplary torque feature of the speed manager. The dashed curve is for a speed manager with high speed variation. In contrast, the solid curve reduces speed variation and has a high slope to reduce speed sensitivity with respect to torque, which the present invention is directed to achieve.

It is desirable to obtain energy dissipation characteristics as a function of time, in the form of power, expressed inThe relation P ═ f (ω)ⁿ) Where n > 2, the value n-2 corresponds to a power equal to the square of the torque (homogeneous), and therefore proportional to the square of the angular velocity. The invention therefore proposes to improve this dissipation as much as possible.

In order to achieve this in an optimal manner, in a first variant, the invention uses an inertia block which can pivot relative to a wheel set powered by an energy source via a transmission and/or a return, in particular an elastic return. In a second variant, the invention uses eddy currents, generated by the interaction between these inertial masses and the variable magnetic field, which makes it possible to exploit the excess energy by releasing heat, without using more energy than necessary.

Preferably, the invention combines the use of these pivoting inertia blocks returned by the return means with the use of eddy currents generated by the interaction between the inertia blocks and the variable magnetic field.

The invention thus establishes a passively regulated braking, which is effective despite the constraints of the small space available in the timepiece movement.

In another embodiment of the invention, the use of a pivoting inertia block is combined with a centrifugal force compensation device and a braking device.

Timepiece wheel set or striking wheel set manager 1 is designed to regulate the pivoting speed ω of wheel set 3 about first pivot axis D1 about a reference speed value ω c. This wheel set 3 is driven by an energy source providing mechanical torque via the transmission 2. This wheel set 3 comprises at least one inertial mass 4 pivotally mounted about a first pivot 6, the first pivot 6 defining a second pivot axis D2, the second pivot axis D2 being parallel to and spaced a distance from the first pivot axis D1.

According to the invention, the organizer 1 comprises means 6 for returning the inertial mass 4 towards the first pivot axis D1. This inertial mass 4 is set:

on the one hand, when wheel set 3 pivots at a speed lower than or equal to reference speed ω c, inertial mass 4 remains confined in first revolution space VI about first pivot axis D1;

and on the other hand, when wheel set 3 pivots at a speed higher than said reference speed ω c, inertial mass 4 is located, at least on its peripheral portion 30, in a second revolution space VE around said first pivot axis D1, contiguous to said first revolution space VI.

In the first configuration, see fig. 14, the second space VE is located outside the first space VI.

In a second configuration, not shown in the figures, the second space VE is located inside the first space VI.

Of course, other configurations are possible with a plurality of adjacent spaces, each having specific characteristics for interacting with the inertial mass 4 or not interacting with the inertial mass 4.

The peripheral portion 30 cooperates in the second revolution space VE with an adjustment device arranged to cause braking of the wheel set 3 and to return the pivoting speed ω of the wheel set 3 to the reference speed ω c and to dissipate the excess energy.

In a particularly advantageous manner peculiar to the invention, the return means 7 are arranged to keep said at least one inertial mass 4 confined in the first internal rotation space VI when the wheel set 3 is pivoted at a speed lower than or equal to the reference speed ω c, and to allow said inertial mass 4 to be located in the second rotation space VE at least on its peripheral portion 30 when the wheel set 3 is pivoted at a speed higher than said reference speed ω c.

Preferably, the return device 7 is a mechanical return device and exerts a return force on the second pivot 72 in the direction of the first pivot axis D1, said second pivot 72 being comprised in said at least one inertia block 4 and defining a third pivot axis D3 parallel to the first pivot axis D1 and the second pivot axis D2.

Advantageously, the return means 7 are elastic return means comprising a first pivot guide 74 about a main pivot 15 or arbour comprised in said wheel set 3 about said first pivot axis D1 and at least one second pivot guide 73 about a second pivot 72, said second pivot 72 being comprised in said at least one inertial mass 4 about said third pivot axis D3.

As will be explained below, this elastic return means 7 preferably comprises at least one spring 71 with a preload. The precise manufacture of these springs with a preload accurately calculated from the reference speed to be maintained overcomes the lack of precision in the prior art. The combination with eddy current dissipation provides a steady rate very quickly by dissipating a large amount of energy in a very short time.

In a particular embodiment, timepiece wheel set or striking wheel set manager 1 comprises braking means which act when peripheral portion 30 of inertia mass 4 passes from first space VI to second space VE. This braking means is formed by an air braking means, or by an air brake (aero brake) applied above the reference speed ω c, or by a dry braking means, or by a friction means having a braking torque surface applied to the peripheral portion 30 of the inertia block 4 and arranged such that the applied braking torque intersects the radius from the first pivot axis D1.

Thus, the braking means act when the peripheral portion 30 of the inertia block 4 passes from the first space VI to the second space VE to apply a braking torque to the peripheral portion 30 of the inertia block 4, so that the applied braking torque intersects the radial position of each said inertia block from the first pivot axis D1, at the centre or inside of the second space VE.

The preferred energy dissipation principle as shown in the figure is the eddy current loss principle. An electrically conductive wheel set, in particular a disk or the like, pivoting in a variable or alternating magnetic field, is the seat (seat) of the induced eddy currents, which causes joule effect losses according to the expression:

(2.1)P_{eddy}≈ρ.BC².Ω².e，

where ρ is the resistivity of the pivoting conductive material, BC is the induction peak seen through the material, Ω is the pivoting velocity, e is its thickness,

also, the eddy current braking torque may be expressed as:

(2.2)M_{eddy}≈ρ.BC².Ω.e

in a very simple embodiment of the invention, the speed manager studied comprises a conductive disc or wheel set, for example made of silver, which pivots in a variable, preferably alternating magnetic field and whose braking torque follows expression 2.2.

The torque-speed relationship of this system is a purely linear characteristic, with the slope depending on the parameter ρ, BC²And e.

However, this system has a rated speed braking torque. Furthermore, the slope can be adjusted by the above parameters, but with a limit value. In fact, silver has a minimum resistivity value. The induction value cannot be increased infinitely. It is therefore difficult to obtain a very steep slope in an acceptable space, which results in the need to consider a preferred embodiment of the invention as shown in fig. 4.

The timepiece wheel set or striking wheel set manager 1 according to the invention is designed to adjust the pivoting speed ω of at least one user wheel set about the first pivot axis D1 about a reference speed value ω c. Timepiece wheel set or striking wheel set manager 1 comprises at least one wheel set 3 arranged to be pivoted by transmission 2 about said first pivot axis D1.

As can be seen in fig. 1, this wheel set 3 comprises, directly or indirectly, at least one peripheral portion 30 made of electrically conductive material, at least a portion of this peripheral portion 30 being subjected to at least one variable magnetic field in a chamber 8 or in a slot 21 between the poles 22 and 23, at least when the wheel set 3 is not in the rest position, said chamber 8 being comprised in the manager 1, at least partially defined by a magnetized component comprised in the manager 1.

By driving of the torque-transmitting means 2, the wheel set 3 is pivoted and the peripheral portion 30 is moved into a variable magnetic field, in particular into said chamber 8 in a preferred embodiment, so that the pivoting speed of the wheel set 3 is regulated by eddy currents induced by the interaction between said magnetic field and said peripheral portion 30 (or peripheral portions 30 if the wheel set 3 has a plurality of said magnetic fields), as is preferred in fig. 2 to 9 and 11 to 13.

In fact, when the wheel set 3 pivots, an electric current is generated in the conductor formed by the peripheral portion 30, which tends to oppose the relative movement between the wheel set and the magnetic field according to the eddy current braking principle, and the braking torque increases when the constant surface speed increases. Of course, if the peripheral surface 30 of the wheel set is increased, the braking torque is also increased. When the various elements of the manager 1 are suitably dimensioned, the relaxation speed of the barrel constituting the energy source is suitably stabilized by the manager 1. Wheel set 3 is synchronized with the music-producing wheel set or striking wheel set, the rhythm of which is thus well regulated.

In a preferred version of the invention, as can be seen in fig. 2 to 9, the wheel set 3 comprises at least one inertia block 4, preferably a plurality of said inertia blocks 4, each inertia block 4 being pivotally mounted about an eccentric first pivot 6, said first pivot 6 being fixed to the wheel set 3, in particular on the pivot flange 31, being directly or indirectly driven by the transmission means 2, and defining a second pivot axis D2 parallel to and at a distance from the first pivot axis D1. It is clear that in the case of a plurality of inertial blocks 4A, 4B. The pivoting of each inertia block 4 takes place in a guide 5, for example a hole, said guide 5 cooperating with a complementary guide 6, for example a pin, comprised in wheel set 3, or vice versa.

Preferably, the center of inertia of each inertia mass 4 is farther from the first pivot axis D1 than the first pivot shaft 6 of that inertia mass 4 is from the first pivot axis D1.

In a preferred version of the energy dissipation using eddy currents, according to the invention, at least one peripheral portion 30 of each inertial mass 4 or the entire inertial mass 4 is made of an electrically conductive or magnetized material.

According to the invention, at least one portion of each inertial mass 4 forms a peripheral portion 30, said at least one portion of each inertial mass 4 being subjected, in the case in which at least one peripheral portion 30 of each inertial mass 4 is formed of an electrically conductive material, to the action of at least one variable or alternating or sinusoidal magnetic field, preferably in the chamber 8 in which the inertial mass 4 moves, at least when the inertial mass 4 concerned is not in the rest position, and preferably outside a specific pivoting speed threshold of the wheel set 3, so that the pivoting speed of the wheel set 3 is regulated by the action of eddy currents induced by the interaction between the chamber 8 and the peripheral portion 30 of the inertial mass 4.

In the alternative case where at least one peripheral portion 30 of each inertial mass 4 is made of a magnetized material, the pivoting movement of wheel set 3 and, consequently, of inertial mass 4, generates a variable or alternating or sinusoidal magnetic field in chamber 8, said chamber 8 being defined at least in part by electrically conductive members whose interaction with said magnetic field generates eddy currents which tend to brake the wheel set by resisting the pivoting of the wheel set.

The inertial mass 4 must be subjected to or generate a magnetic field with variable amplitude. Of course, if the magnetic field is alternating, the amplitude of the variation is even greater and the conditions are optimal. It should be noted, however, that simple changes in the magnetic field between the non-magnetized regions with zero magnetic field and the regions subjected to the magnets will also produce the eddy current dissipation conditions required by the present invention.

In one embodiment, described in more detail below, peripheral portion 30 is electrically conductive, and the speed regulation means are constituted by means of generating at least one magnetic field comprising magnetic field lines oriented so that the interaction between this peripheral portion 30 and the variable magnetic field generates eddy currents which tend to brake wheel set 3 by resisting pivoting of wheel set 3.

A person skilled in the art will know how to implement the reverse configuration, in which the peripheral portion 30 is made of a magnetised material and the chamber 8 comprises electrically conductive surfaces, and therefore this alternative embodiment is not described in detail in the description.

According to the invention, the inertial mass 4 (preferably each inertial mass 4) is arranged so that, on the one hand, when the wheel set 3 is pivoted at a speed lower than or equal to the reference speed ω c, the inertial mass 4 remains confined in a first turnaround space VI about a first pivot axis D1, and, on the other hand, also so that, when the wheel set 3 is pivoted at a speed higher than said reference speed ω c, the inertial mass 4 is located, at least at its peripheral portion 30, in a second turnaround space VE about said first pivot axis D1, which second turnaround space VE is adjacent to and preferably outside said first turnaround space VI. The peripheral portion 30 cooperates in the second revolution space VE with an adjustment device arranged to cause braking of the wheel set 3 and return the pivoting speed ω of the wheel set 3 to the reference speed ω c, as well as to dissipate the excess energy.

It is clear that this device can also operate in a second configuration, in which the second space VE is inside the first space VI, however, this is less efficient than the first configuration, in which the second space VE is outside the first space VI, because of less dissipation.

In this second configuration, the inertia mass 4 can be made in the form of a lever-type inertia mass, with a larger mass on the first lever arm subjected to the circumferential centrifugal force and a less inertial conductive part on the second lever arm close to the pivot axis of the wheel set.

According to the invention, the organizer 1 comprises means 7 for returning at least one inertial mass 4 (preferably each inertial mass 4 when the organizer has a plurality of inertial masses 4) towards the first pivot axis D1.

Each inertial mass 4 is therefore returned towards the first pivot axis D1 by the return means 7 (preferably by the elastic return means 7). Each inertia mass 4 moves between a folded-down rest position, corresponding to the stop position of wheel set 3, and a maximum unfolded eccentric position, corresponding to the highest pivoting speed of wheel set 3, peripheral portion 30 of each inertia mass 4 tending to move away from first pivot axis D1 under the effect of centrifugal force.

Preferably, the elastic return means 7, in particular formed by at least one spring 71, connect each elastic block 4 to the first pivot axis D1, or to the flange 31, or to the other inertial block 4. Advantageously, according to the invention, the elastic return means 7 have a preload determined so as to enable the inertial mass 4 to move off-centre when the nominal speed ω c is reached. The stiffness of the elastic return means 7, in particular the spring 71, is calculated so as to compensate the centrifugal force of the inertial mass 4 at any angular position of the inertial mass 4.

Below the nominal speed ω c, the inertial mass 4 remains in the folded-down position close to the first pivot axis D1 and outside the magnetic field applied in the chamber 8. The magnetic field is generated by one or more magnets 12, said magnets 12 being mounted on a stator yoke (yoke)19, on yoke flanges 16, 17, as can be seen in fig. 2, 6 and 13.

When the nominal speed ω c is reached, the inertial mass 4 moves off-center and enters the magnetic field generated by the permanent magnet 12.

The eddy current braking increases as a function of the angular position of the inertia blocks 4 on their respective pivots. Thus, the elastic return means 7, in particular the spring 71, is dimensioned such that, when the nominal speed ω c is reached, small variations in speed significantly change the braking torque. The stiffness of the spring 71 must be slightly greater than that required for balancing the centrifugal force only at any angular position. Thus ensuring a certain self-regulating speed stability for the system.

Therefore, the present invention establishes only the condition of the radial movement of the inertia mass 4 above the reference velocity ω c. To achieve this, the means in the form of a preload spring 71, which returns radially towards the axis of the mechanism, form a particularly reliable solution: this spring exactly compensates the centrifugal force applied to the inertial mass 4 at its point of application to said mass, at a reference speed ω c.

The curve in fig. 16 describes the appearance of the braking torque curve C as a function of the pivoting speed ω. Curve C1 is an ideal theoretical curve, all power being used only at the reference speed ω C. Curve C2 is the actual curve, which is offset from the previous curve by an angle θ. This angle θ must be minimized to be as close as possible to the ideal. The greater the stiffness of the spring, the greater the angle θ. The advantage is that a spring 71 with a sufficiently low stiffness is used to obtain a very steep characteristic curve: so that a small increase in the pivoting speed above the reference speed θ results in a large radial travel of the respective inertial mass 4, and a dissipation of a large amount of energy, proportional to the surface of the inertial mass 4, said inertial mass 4 interacting with the variable magnetic field to generate eddy currents. More particularly, this magnetic field is generated in the circumferential annular chamber 8, so that the adjustment is effective regardless of the angular position of the wheel set to be adjusted.

Taking the barrel shown in the figures as an example, it must be able to dissipate several mW, about 5mW for a regulation of about 3000 revolutions per minute. The embodiment of the invention with dimensioning of the components in fig. 2 and in particular the selection of a variable magnetic field is able to dissipate 8mW, which is particularly advantageous.

In the embodiment of fig. 2, the timing train drives the adjustment pinion 29, thereby forming the torque transmitting device 2. Wheel set 3 comprises a flange 31 carrying two inertia blocks 4A, 4B, each freely mounted on a pin 6, said pin 6 being located in a hole 5 comprised in each inertia block 4. In this figure, the inertia blocks 4A, 4B are connected to each other by a spring 71, the spring 71 constituting the return means 7 and being freely mounted on an arbour 15 included in the wheel set 3 carrying the adjustment pinion. The penetration depth of the inertial mass 4 below the magnet 12 varies as a function of the pivoting speed of the wheel set, said magnet 12 generating a variable magnetic field 8. The greater the radial penetration depth of the peripheral portion 30 of the inertial mass 4, the greater the braking torque generated by the eddy currents.

Preferably, as shown in fig. 4 to 13, the organizer 1, in particular the wheel set 3, comprises a plurality of inertial masses 4. These inertia blocks are preferably distributed about the first pivot axis D1 in order to dynamically balance the assembly of wheel set 3 and inertia blocks 4 at the maximum pivoting speed of wheel set 3.

The return means 7 are arranged to keep the or each inertial mass 4 confined in the first internal revolution space VI when the wheel set 3 pivots at a speed lower than or equal to the reference speed ω c, the return means 7 being arranged to enable said inertial mass 4 to be located in said second revolution space VE at least on its peripheral portion 30 when the wheel set 3 pivots at a speed higher than said reference speed ω c.

The return means 7 are preferably mechanical return means exerting a return force on the second pivot 72 in the direction of the first pivot axis D1, said second pivot 72 being comprised in each inertia block 4 and defining a third pivot axis D3 parallel to the first pivot axis D1 and the second pivot axis D2.

Preferably, the second pivot 72 of each inertia block 4 is further from the first pivot axis D1 than the first pivot of that inertia block 4 is from the first pivot axis D1.

Preferably, the return means 7 are elastic return means and comprise a first pivot guide 74 and at least a second pivot guide 73, said first pivot guide 74 surrounding the main pivot 15 or arbour, said main pivot 15 or arbour being included in the wheel set 3 about a first pivot axis D1, said second pivot guide 73 surrounding the second pivot 72 or, when the radial elastic return means 7 are common to all the inertia blocks 4, each second pivot 72, as shown in fig. 11 to 13.

The effect of the elastic return means 7 is therefore to keep the inertia mass 4 close to the axis D1 when the wheel set 3 is stopped and to limit the pivoting of the inertia mass 4 about its respective second pivot axis D2 as the wheel set 3 accelerates, during the brief phase in which the modulated eddy currents start to be generated. The design of the elastic return means 7 determines a reference speed above which the centrifugal force is greater than the return force and moves the inertial mass 4 away from the axis D1 so that said inertial mass, or at least its peripheral portion 30, enters the magnetic field of the chamber 8. Said reference speed is preferably equal to the reference pivoting speed ω c of wheel set 3. Eddy currents induced in the inertia mass 4 brake the inertia mass at this time and convert kinetic energy into thermal energy. Preferably, the elastic return means 7 are formed by one or more springs 71. By appropriately dimensioning each spring 71 and the attachment position between the inertia mass 4 and its support, it is possible to obtain a pivoting speed for the unfolded position of the inertia mass 4 that is slightly higher than for the folded-down position of the inertia mass. This difference in speed is equivalent to the speed adjustment accuracy of the manager 1. The depth of penetration of the inertial mass 4 into the magnetic field varies according to the torque to dissipate more or less energy.

When there are several inertia blocks, the elastic return means 7 also have the effect of balancing the effect and the position of said inertia blocks. In fact, wheel set 3 preferably has a plurality of inertial masses 4 equally distributed about first pivot axis D1. The elastic return means 7 also comprise a first pivot guide 74 around a main pivot 15 or arbour included in the wheel set 3 around a first pivot axis D1, the elastic return means 7 also comprising a second pivot guide 74 around said second pivot 72, said second pivot 72 being included in each inertial mass 4 around a third pivot axis D3 specific to each inertial mass 4.

Preferably, these inertia blocks 4 are identical to each other, their respective second pivot axes D2 are equidistant from the first pivot axis D1 and are distributed equidistantly, and all the elastic return means 7 are identical, fixed in a similar manner to the inertia blocks 4. Advantageously, these inertia blocks 4 are distributed about the first pivot axis D1 in order to dynamically balance the assembly constituted by wheel set 3 with inertia blocks 4 at the maximum pivoting speed of wheel set 3.

Preferably, the return means 7 are confined in the first revolution space VI, as is the second pivot 72, regardless of the position of the inertial mass or masses 4.

Of course, different variants can be envisaged.

In the first variant of fig. 3, the inertial mass 4 (here the two inertial masses 4A and 4B) is connected in pairs by elastic return means 7, said elastic return means 7 being dimensioned so as to dynamically balance the assembly constituted by wheel set 3 and inertial mass 4 at the maximum pivoting speed of wheel set 3.

In the second variant of fig. 4, the inertia blocks 4 are all connected to each other by a single elastic return means 7, said elastic return means 7 being dimensioned so as to dynamically balance the assembly constituted by wheel set 3 and inertia blocks 4 at the maximum pivoting speed of wheel set 3.

In a third variant of fig. 5, each inertial mass 4 is connected by an independent elastic return means 7 to a spindle 15, said spindle 15 being included in wheel set 3 along a first pivot axis D1. These elastic return means 7 are dimensioned so as to dynamically balance the assembly constituted by wheel set 3 and inertial mass 4 at the maximum pivoting speed of wheel set 3.

The preferred embodiment shown in fig. 11 to 13 is formed by combining the second and third modifications.

It is obviously difficult to arrange the inertial mass 4 and the return means 7 so that the inertial mass can only be deployed beyond a certain speed. The invention proposes an inventive solution in which the elastic return means 7 are constituted by at least one spring 71 comprising a preload. A comparison of fig. 11 and 12 shows that this preload corresponds to a radial preload stroke CP of the second pivot guide 73 in the radial direction with respect to the first pivot axis D1, when the spring 71 is guided by its first guide 74 on the main pivot 15 between the uncoupled position of the spring 71 and the position of the second pivot 72 in which the spring is coupled to the inertial mass 4, with the wheel set 3 and the inertial mass 4 in the rest position, and in the coupled position of the spring 71 said preload tends to pull the second pivot 72 of the inertial mass 4 radially towards the first pivot axis D1.

The spring 71 is made so that the return force on the inertia mass always passes through the first pivot axis D1, as shown in fig. 11 to 13, where the first guide 74 is an eye (eye) pivotally mounted without friction about the main pivot 15.

In short, said preload exerts a radial return force on the second pivot 72 of the inertial mass, which counteracts the centrifugal force exerted on the second pivot 72 due to the pivoting speed, and also prevents the deployment of the inertial mass 4 before the wheel set 3 reaches a critical speed, preferably chosen as the reference speed value ω c.

The stiffness of said spring 71 is defined so that the radial force value applied to the inertia mass 4 returning to the second pivot 72 is substantially a linear function of the angular position a of the inertia mass 4 about the first pivot 6 on the second pivot axis D2 with respect to the rest position of the inertia mass 4, for which a radial force value with an absolute value of zero corresponds to the preload stroke CP, as shown in fig. 17, which represents the variation of the radial return force as a function of the angle a, which is the variation of the position of the third pivot axis D3 with respect to the second pivot axis D2 with respect to the rest position of fig. 12.

In another expression, the radial force applied to the inertia mass beyond the preload stroke CP of the spring is a linear function of the radial position of the second pivot 72 relative to the pivot axis D1. It is also a linear function of the distance between the position of the second pivot 72 and the position of the point of attachment of the spring not assembled on the inertial mass 4 (as shown in fig. 11), or more simply expressed as a linear function of the distance over which the spring 71 extends, at any given time. This distance is equal to the radial preload stroke CP when the spring is coupled to the inertial mass 4 as shown in fig. 12.

This characteristic of the increase in the radial force applied to the inertia mass 4, which is substantially proportional to the increase in the radial position of the second pivot 72 of the inertia mass 4, is obtained by smoothing a curve obtained by calculating the centrifugal force balance regardless of the angle of the inertia mass to achieve an approximate result.

By the specific arrangement of the pivots with respect to each other to obtain a variable lever arm, an additional effect can be achieved which allows a large deployment (deployment) of the inertia mass 4 for a small increase in speed above the reference speed ω c.

The arms of the spring 71 may advantageously be made in a coiled or spiral form, so that the spring is sufficiently flexible to obtain the required precise rigidity.

Preferably, in order to achieve perfect repeatability and perfect reproducibility of the phenomenon, the spring 71 is made of: micro-machinable material, or silicon, or quartz or a composite thereof, or an alloy derived from MEMS technology, or an alloy obtained by DRIE or LIGA methods, or an at least partially amorphous material. The method and/or the choice of material also provide a non-magnetic and non-magnetizable spring 71, which is not affected by the magnetic field or diffuses the magnetic field to the timepiece movement surrounding the manager 1. Another advantage is that the young's modulus of the spring varies little with temperature and therefore there is no deviation from the regulation speed.

Of course, it is also possible to manufacture the spring 71 in a conventional manner using spring material, in particular spring steel, such as is used in horology for mainsprings or barrel springs.

However, it may be desirable to adjust the reference speed. This can be achieved by varying the stiffness of the spring or its preload or both. Therefore, the mechanism can be provided with a static element (static element), for example an index, for example for pivoting an intermediate flange (not shown in the figures), in order to shift the curve by performing a zero offset corresponding to another value of the reference speed, as shown in fig. 16, in which characteristic C' 2 replaces characteristic C2. The use of such an index in the factory enables precise adjustment to the desired value. In an advantageous alternative, not shown in the figures, the spring 71 comprises a plurality of pivot guides 73 side by side, each pivot guide 73 being formed by an eyelet arranged to cooperate with the second pivot 72 of the inertial mass 4, each eyelet representing a specific, memorable and repeatable adjustment, which makes factory pre-adjustment simple. The holes 73 may be arranged in a line, staggered or otherwise arranged and preferably are referenced to facilitate assembly. This arrangement is preferred for the indexing arrangement as it avoids any compression on the spring.

The means for generating at least one variable magnetic field for the watch are preferably constituted by permanent magnets 12 arranged on both sides of the chamber 8, in which chamber 8 the peripheral portion 30 of each inertial mass 4 moves at a certain speed range, on both sides of said chamber 8 pairs of said permanent magnets 12 having opposite polarity.

Preferably, to avoid interference with the timepiece movement or mechanism, the chamber 8 in which the magnetic field is generated is defined by a magnetically insulating screen 9. Preferably, these permanent magnets 12 are arranged at the inner periphery 11 of a yoke 19 surrounding the chamber 8, said yoke 19 preferably being defined by said magnetically insulating screen 9, said permanent magnets 12 being aligned in a direction substantially parallel to the first pivot axis D1 on both sides of the chamber 8. In the non-limiting example shown in fig. 2 and 3-5, the chamber 8 is defined by a yoke 19 comprising two top and bottom yoke flanges 16, 17 connected by a yoke ring 18.

In one particular embodiment shown in these figures, the chamber 8 rotates about a first pivot axis D1.

The variable magnetic field generated inside the chamber may be generated by various methods. For a stationary timepiece, such as a pendulum clock, or for a music box, it is conceivable to use a power-operated or battery-powered electromagnet.

Therefore, preferably, the chamber 8 comprises a plurality of permanent magnets 12 at its inner periphery 11, said permanent magnets 12 being arranged to generate a magnetic field. Preferably, these permanent magnets 12 are arranged to produce magnetic field lines in chamber 8 parallel to first pivot axis D1 of wheel set 3. The magnetic field in the chamber 8 or in the air gap is therefore axial and the manager has an axial flux.

In one particular embodiment, shown in figure 6, the permanent magnets 12 are arranged in pairs on opposite surfaces 13, 14 of the chamber 8 and facing each other to generate magnetic field lines in the chamber 8 parallel to the first pivot axis D1 of the wheel set 3. Preferably, each inertial mass 4 is also movable between these two opposite permanent magnets 12 arranged on either side of its trajectory.

In another variant (also shown in fig. 6), an integer number of permanent magnets 12 are mounted on the same surface 13 or 14, with alternating magnetic poles, so that the magnetic field traversed by each inertial mass 4 during its trajectory is an alternating magnetic field with maximum intensity. The magnetic field is in a first direction below a given pole and in the opposite direction below the immediately adjacent pole. Thus, each inertial mass 4 is subjected to a periodic harmonic magnetic field having a sinusoidal shape when wheel set 3 is pivoted. In particular, on both sides of the chamber 8, the yoke 19 comprises a first flange 16 carrying a first series of permanent magnets 12 and a second flange 17 carrying a second series of permanent magnets 12, and the first flange 16 and the second flange 17 each comprise an integer number of permanent magnets 12, said permanent magnets 12 being mounted with alternating polarity at the periphery of the respective flange, so that the magnetic field is an alternating magnetic field, as seen from the peripheral portion 30 of the moving inertial mass 4.

In another variant, not shown in the drawings, the permanent magnets 12 are mounted on the same surface 13 or 14 with non-alternating polarity, in a form repeating from a central ring, with variable overall angle, radius and incidence, so that the magnetic field is an alternating variable magnetic field, seen from the peripheral portion 30 of the moving inertial mass 4 during its trajectory.

As already indicated previously, the variability of the magnetic field seen from the peripheral portion of the inertial mass is a condition for generating eddy currents and energy dissipation. Thus, while the preferred embodiments are described herein, it should be understood that the system can function with a non-integer number of magnets or even with magnets all of the same polarity. The examples given here are in particular those which enable the best and most uniform dissipation, which is by no means limiting.

In a particular embodiment, the first flange 16 and the second flange 17 are pivotally movable relative to each other about a first pivot axis D1 to align the magnetic field lines parallel to said pivot axis D1 or to orient the magnetic field lines obliquely relative to the first pivot axis D1 on a surface of a cone or cylinder of revolution about the first pivot axis D1 depending on their relative position. Obtaining helical or conical magnetic field lines allows to vary the energy dissipation and to adjust the regulation as best as possible. This arrangement also allows for better deployment of the inertial mass 4. The graph of fig. 20 describes the variation of eddy current losses as a function of the angular offset of the first flange 16 with respect to the second flange 17, all else being equal, in the fully deployed position of the inertial mass.

In another particular embodiment, the first and second flanges 16, 17 are translationally or pivotally movable relative to each other in the direction of the first pivot axis D1, thereby modifying their air gap values.

In another particular embodiment, due to the effect of the peripheral portion 30 of the inertial mass 4 interposing their air gap, the first flange 16 and the second flange 17 can move translationally and/or pivotally with respect to each other in the direction of the first pivot axis D1, for example, the double conical portion or corner of said peripheral portion tends to move the flanges apart, in particular resisting the spring that returns them towards each other up to the stop position.

In another particular embodiment, the first flange 16 and the second flange 17 pivot with respect to each other in the direction of the first pivot axis D1 due to the effect of the peripheral portion 30 of the inertial mass 4 interposing their air gap, which tends, for example, to pivot one movable flange with respect to the other flange that remains stationary.

In another particular embodiment, under the action of the spring barrel constituting the energy source, the first flange 16 and the second flange 17 can be translated relative to each other in the direction of the first pivot axis D1 or pivotally moved relative to each other in the direction of the first pivot axis D1 in order to compensate for striking spring barrel energy losses in a similar manner to the energy storage mechanism.

Such relative pivoting and/or translational movement of these flanges, which carry magnets as described above, or conductive elements when they are carried by the inertial mass 4, enables in particular the adjustment of the cadence, as is the case in the application of the striking mechanism as shown in the figures.

In a specific embodiment not shown in the figures, the permanent magnet 12 is radially movable with respect to the first pivot axis D1. Thus, if the magnetic field layer (which is substantially cylindrical about the first pivot axis D1) becomes progressively further away from the axis D1 as the pivoting speed of the wheel set 3 increases, the braking torque will also increase as the pivoting speed of the wheel set 3 increases. Advantageously, the organizer 1 comprises means arranged to allow the permanent magnets 12 and/or the chamber 8 to move radially with respect to the first pivot axis D1 as a function of the pivoting speed of the wheel set 3, for example by using centrifugal forces, or by using electro-motorization (electric motorization) powered by induced eddy currents.

In a particular embodiment, not shown in the figures, the organizer 1 comprises means arranged to allow a swivelling movement of the permanent magnets 12 and/or the chamber 8 about the first pivot axis D1 as a function of the pivoting speed of the wheel set 3. In an advantageous embodiment, this swivelling movement occurs in the opposite direction to the pivoting direction of wheel set 3, so as to double the current induced and therefore the associated braking.

In a particular embodiment, the dissipation of energy can be further improved by axially motorizing the flanges or yokes carrying the permanent magnets. In particular, the use of a differential gear enables the inertial mass 4 and the permanent magnet 12 to pivot simultaneously in opposite directions, which means that the same dissipation and regulation can be achieved using a lower rotational speed, which is advantageous in terms of wear. Alternatively, when maintaining the same speed, eddy current dissipation can be doubled if the differential gear is, for example, designed such that the respective speeds of the magnet and inertial mass are equal and in opposite directions.

Preferably, at least one inertial mass 4 (advantageously each inertial mass 4) is made of electrically conductive material or gold, or copper or silver, throughout the entire thickness traversed by the magnetic field in a direction parallel to the first pivot axis D1, or comprises, in the portion subjected to the magnetic field in the chamber 8, a portion made of electrically conductive material or gold, or silver or copper.

In one particular arrangement, as shown in fig. 10, the organizer 1 comprises a plurality of pivoting integral wheel sets 3, stacked in the direction of the first pivot axis D1, and each carrying at least one inertial mass 4, said inertial mass 4 being movable in a single chamber 8 or a chamber common to the other inertial masses 4. This arrangement is advantageous if the horizontal space in the timepiece movement is limited.

In one particular embodiment of timepiece wheel set or striking wheel set manager 1 shown in fig. 1, at least a portion of peripheral portion 30 of wheel set 3 is movable, not in a chamber, but in a slot 21 comprised between two opposite poles 22, 23 in a permanent magnet or electromagnet, said slot 21 defining a plane orthogonal to first pivot axis D1. Adjustment can be achieved by applying, near the periphery of wheel set 3, an electromagnet 24 to one surface of wheel set 3, said electromagnet 24 being supplied by a current induced by the pivoting of wheel set 3. Preferably, this manager 1 comprises a frame, for example made of steel or iron, constituting a magnetic loop, and a magnetic circuit/loop (magnetic circuit) surrounding the slot 21, which is arranged in said frame. On both sides of the slot 21 the magnetic circuit has magnetic poles of opposite polarity. The magnetic poles of the magnetic circuit are disposed in the vicinity of the periphery of the movable rotor 3. The mobile rotor 3 constitutes a rotary striking wheel set or is coupled to it directly or via a wheel train or other direct transmission means. Pivoting of the striking wheel set under the action of the energy source causes the rotor to pivot, thereby generating a variable magnetic field in the air gap between the poles. This variable magnetic field generates induced currents which are also variable in rotors made of electrically conductive or magnetic material.

Depending on the type of assembly, the current may be used to drive a motor (the spindle of which is coupled directly or indirectly to the rotor) in order to drive or brake the rotor. The current may also be used to trigger an electromagnet or be applied to the surface of the rotor near its periphery in order to brake the pivoting of the rotor according to Laplace's law or to trigger the braking means of the striking wheel set.

Preferably, in order to be as compact as possible and with a minimum number of component parts, the rotor and striking wheel set, when assembled, form a single element, said frame comprising, on both sides of its slot, permanent magnets of opposite polarity, the regulation being carried out by means of electromagnets applied to the surface of the rotor in the vicinity of its periphery, said electromagnets being supplied by the current induced by the pivoting of the rotor.

The braking achieved by Laplace force (Laplace force) and electromagnets is substantially proportional to the pivoting speed of the rotor. In the case of a striking mechanism walking fast, the speed difference causes a braking difference which returns the pivoting speed of the rotor and therefore of the striking wheel set to a reference value, which not only counteracts the effect of the mechanism walking fast, but also adjusts the pivoting speed of the striking wheel set so that the musical or striking sequence has a perfect pace, pleasant to the user.

As shown in fig. 18, a simplified embodiment includes the following elements:

two ferromagnetic yoke flanges, 13mm in diameter, made of "Mumetal", with 12 "recama 25" permanent magnets mounted with alternating axial magnetization, and 1.7mm in diameter and 0.25mm in thickness.

Two copper inertia blocks with an internal diameter of 2mm, an external diameter of 5.6mm and a thickness of 0.9 mm.

A brass inertial mass support, 6mm in diameter, into which a brass pin is pressed as inertial mass pivot.

An outer yoke ring in the form of a steel tube "CK 45" with a length of 2.5mm to ensure continuity of the magnetic flux induced by the permanent magnets. The yoke ring thus forms a shield.

Two pins pressed into the inertial mass for fixing the return spring.

Two return springs of the rubber O-ring type, which connect the spindle to the respective fixing pins.

Although simplified, this solution, which comprises a return spring not having a specific size, still operates in a stable manner in terms of the self-adjustment speed of the system.

It is important to note that the symmetry of the inertial mass and the return spring is important to prevent imbalance and oscillation. In fact, due to the lack of symmetry, the inertial mass may move off-center with different angular movements, in the worst case only one inertial mass making an angular movement. Further, a spring is coupled to the central spindle. This solution prevents any asymmetry and prevents the two inertia blocks from oscillating around the central spindle, unlike the case where a single spring connects the two inertia blocks but not the central spindle.

A specific, more elaborate solution, which is able to satisfy the regulation conditions to be guaranteed by the present invention, is shown in fig. 18 and comprises:

two ferromagnetic stator yoke flanges made of "AFK 502" FeCo. Each yoke flange carries 14 permanent magnets of 1.3mm diameter and 0.25mm thickness, of the "VACODYM 655 HR" NdFeB type, arranged with alternating axial magnetisation.

The two inertial masses are chosen to be made of silver, because their electrical conductivity is very low.

The magnetic air gap, i.e. the axial distance between the two magnet layers, is reduced to increase the induction of the inertial mass in the air gap. The thickness of the inertial mass is 0.3mm and the mechanical air gap between the magnet and the inertial mass is 0.12 mm.

The dimensions of the device are adapted to the available space in the musical watch, and the outer diameter is limited to 8.4mm and the height to 1.35 mm.

The spring is dimensioned to balance the centrifugal force for any inertial mass angular position at a speed of 3100 tr/mn.

The results were consistent with expectations: low speed variation, less than 3% of rated speed, and high power dissipation, higher than 6 mW.

The graph of fig. 19 depicts the variation of eddy current losses as a function of angular position of the inertial mass on its respective pivot axis in this preferred embodiment.

It can be seen that when the inertial masses are close together, the power dissipated by the eddy currents is zero. Therefore, the system does not brake below rated speed.

The properties of the return spring are determined by balancing the centrifugal force acting on the inertial mass at the nominal speed at the attachment point of the spring. Thus, the desired spring rate and spring preload values in this example are 0.0014N/mm and 0.006N, respectively.

The radial position of the end of the spring at rest and the preload distance can also be determined, having values of 0.93mm and 0.44mm, respectively. It should also be noted that the spring is held by the central spindle, but is free to rotate. Thus, the return force of the spring is always towards the center of rotation of the system.

Fig. 20 shows the power dissipated as a function of angular offset of the top yoke magnet for a rated speed of 3100rpm, with the inertial mass fully extended. The angular offset corresponds to a magnetic phase offset between the top and bottom yoke magnets. It should be noted that the maximum dissipated power change (magnitude) varies significantly as a function of the magnetic phase offset (up to 90 °). This action enables fine adjustment of the adjustment speed interval by allowing a spring with a slightly greater stiffness than that required to balance the centrifugal force at the rated speed. Thus, the eddy current dissipated power behavior can vary as a function of the angular position of the inertial mass on its respective pivot. Thus, for the same dissipated power, the phase shift of the top magnet relative to the bottom magnet means that the inertial mass must be moved further off-center. With a suitable spring, the speed must be increased in order for the inertial mass to reach its angular position for dissipating the required power.

The magnetic interference in the timepiece balance spring caused by the manager is less than 1 nT.

Temperature affects the behavior of the device via three elements: a magnet, an inertial mass, and a spring. Which affects the residual induction of the magnet and the resistivity of the inertial mass. Therefore, as the temperature increases, the inertial mass must move slightly further away from the center to achieve the necessary power dissipation. If the stiffness/stability of the relationship between eddy current brake torque and rotational speed is high, the effect of temperature on the regulation speed via the magnets and inertia blocks is negligible. Materials of the "Enlivar" type can be advantageously used to reduce the effect of temperature on the elastic modulus of the spring and thus on the stiffness/stability of the spring preload.

In another embodiment of the invention, which does not rely on eddy currents, wheel set 3 comprises a similarly pivotally mounted inertial mass which returns towards the first pivot axis D1 of the centrifugal force compensation means constituted by the return means 7, in this case one or several springs 71 according to the characteristics set out previously. In addition to this structure, the device 1 also comprises braking means which are active when the peripheral portion 30 of the inertial mass 4 passes from the first space VI to the second space VE in fig. 14, and then it is no longer necessary to include the magnetic field 8.

This braking device may be constituted by an air braking device, for example by applying a pneumatic brake above the reference speed ω c; or by a dry braking device, for example by friction between the peripheral portion 30 of the inertia block 4 and the braking torque surface. In particular, the surface is arranged such that the applied braking torque increases with radius from the first pivot axis D1, for example with a roughness that increases with distance from the first pivot axis D1.

Here too, it is preferred that the centre of inertia of each inertia block 4 is at a greater distance from the first pivot axis D1 than the first pivot 6 of said inertia block 4 is at the first pivot axis D1.

Preferably, the second pivot 72 of each inertia block 4 is at a greater distance from the first pivot axis D1 than the first pivot of the inertia block 4 is at the first pivot axis D1.

Of course, this purely mechanical embodiment may also be combined with the eddy current braking torque embodiment.

The organizer 1 according to the present invention can be operated in two opposite pivoting directions, marked a and B in fig. 13. The direction of travel produces different effects in the sense that the forces applied to the system produce different results.

Returning to the exemplary embodiment shown in the figures, in which the second space VE is located outside the first space VI, the inertial mass 4 is at least partially conductive, and a magnetic field is present in the chamber 8 during pivoting in the direction a, the inertial mass 4 easily moves away and enters the variable magnetic field region, allowing eddy current energy to dissipate.

In the opposite pivoting direction B, in the temporary mode at the beginning of its rotation, the inertial mass 4 is held by a force due to the acceleration due to the resulting rotation of the inertial mass about its pivot point, which is different from its centre of inertia, which is added to the return force of the pre-wound spring 71 and opposes the centrifugal force. As a result, it is more difficult to move the inertia mass away from the pivot axis D1 of wheel set 3 and less easy to enter the magnetic field region. This dynamic action therefore counteracts centrifugal forces, which are different from the pivoting of wheel set 3 in direction a, in which the forces add up to one another.

The dimensioning of the system must take into account the magnetic field leakage, in particular at the axial portion of the manager 1. These leaks generate a magnetic origin force that tends to move the inertial mass away from axis D1 when the organizer 1 is pivoted in direction a, and in the opposite case tends to move the inertial mass closer to axis D1. The strength of this force increases with the pivoting speed, and is far from negligible at high rotational speed forces, especially at about 3000 rpm.

From the previous manager with air-brake inertia blocks, it is also noted that aerodynamic effects, although small, should not be ignored in the calculation of the magnets and inertia blocks.

The quality of the temporary wheel side acceleration phase depends on the proper setting of the spring size and the spring preload condition.

In a variant of the invention, which is not shown in the drawings, these dynamic forces and/or the forces associated with magnetic field leakage are used to allow the shape of the inertial mass to change during operation, which further extends the range of adjustment possibilities.

In another variant of the invention, the organizer 1 does not comprise return means 7, springs 71 or similar elements, and the centrifugal force on the inertial mass is calculated to compensate the force due to eddy currents.

In another variant, a portion of inertial mass 4 can be permanently maintained in the air gap at chamber 8, so that, once wheel set 3 starts to pivot, eddy currents are generated and enter the estimation of the force applied to inertial mass 4 and thus indirectly to wheel set 3.

In short, the invention provides conditions for a very good speed regulation by dissipating a large amount of energy using a simple and very reliable mechanism.

Depending on the dimensioning used, it is also possible to design a system according to the principles of the invention which on the contrary does not use too much energy, for which the main regulating effect is the net force generated by eddy currents.

At least two adjustment possibilities can thus advantageously be realized with a single mechanism, which has different characteristics depending on the selected pivoting direction.

In a particular variant of the invention, the energy dissipation takes place in a liquid medium, in particular in a viscous medium.

Thus, the organizer 1 according to the invention can be operated in a liquid, such as oil, since a friction-free sealed mechanical connection can be achieved between various dry and lubricated media. In practice, it is particularly advantageous to combine the variable magnetic field effect with the effect resulting from hydrodynamic phenomena.

The invention also relates to a musical or striking mechanism 10 for a timepiece or a musical box, comprising an energy source or a winding spring, and means 2 for transmitting a mechanical torque from the energy source or the winding spring to a wheel set or striking wheel set for generating music, wherein said transmission means 2 drive at least one wheel set 3 comprised in a timepiece wheel set or striking wheel set manager 1 according to the invention.

The invention also relates to a timepiece or musical box including a wheel set or striking wheel set for producing music, including a music or striking mechanism 10 of the type described above, and/or a timepiece wheel set or striking wheel set manager 1 of the type described above.

In a particular embodiment, the timepiece is a musical watch.

The invention also relates to an inertia management device having the same composition as the previously described timepiece wheel set or striking wheel set management device, for other applications than the regulation of striking or musical mechanisms, for example for regulating the movement in the field of horology, or for regulating the speed of any mechanism pivoted by an energy source providing a variable torque, in other fields than horology, and more generally any system for measuring and/or displaying time. The following mechanisms can be enumerated: chronographs, chronographs (chronographs), mechanisms for adjusting the speed of movement of the lever, for example in instantaneous date mechanisms, automatic mechanisms capable of varying the speed between different movements, alarm clocks, grand strike, chime or minute repeater mechanisms, music boxes and the like with a pin wheel set or air mechanism, or mechanisms with a mechanical centre of inertia. This list is in no way limiting.

The invention also relates to springs 71 of the same type as previously described, for applications other than those described herein, in particular for use in inertial management devices.

Briefly, the present invention proposes a preferred application of a magnetic manager for regulating a striking mechanism.

The application of the magnetic manager to the striking mechanism has novelty. Unlike the known regulators for control mechanisms and therefore unlike the transmitter circuits (transmitter circuits) intended to guarantee the set frequency of the horological mechanism, according to the invention the magnetic regulator operates as a receiver and uses energy. When the speed is above a reference value, the magnetic manager controls the rotational speed of the rotating striking train (particularly the striking wheel set) at the reference speed by reducing the speed and converts the excess kinetic energy into stored and/or used energy.

The magnetic manager must include magnets and/or electromagnets, which may result in the preferred use of certain materials that are less sensitive to magnetic fields to avoid the effects of interference. In particular, the use of a silicon balance is preferred here. This is also the reason for the particular solution of the preferred chamber 8, in which the chamber 8 is delimited by a magnetically insulating screen 9, said magnetically insulating screen 9 being made of non-magnetic material and constituting a magnetic shield and causing minimal interference in the horological environment without affecting the operation of the movement. Chamber 8 can also be made annular, with a hole limited for this purpose to the passage of spindle 15 of wheel set 9.

The manager according to the invention is advantageously constructed using design principles similar to those of known managers: with close pivot speeds and equal braking power, but this new manager does not have the drawbacks of the managers of the prior art.

The use of such a magnetic manager provides a muting mechanism with extremely accurate speed. In fact, the variable eddy current braking achieved by the invention is sufficient to stabilize the pivoting speed of wheel set 3 without any contact, so that it does not generate noise, or is very noisy.

The invention enables the watch manufacturer to adjust the braking torque, provided for example that the chamber 8 in the first embodiment is designed so that the distance between the surfaces 13 and 14 is adjustable, for example by: wherein one and/or the other of the yoke flanges 16, 17 is fitted or even better fastened to the yoke ring 18 with screws, or in the second embodiment, provided that the air gap of the slot 21 between the poles 22 and 23 is adjustable.

The repeatability of the adjusted speed during assembly is much better than in existing systems.

By eliminating friction and shock, speed stability during aging is made more reliable.

The speed of wheel set 3 is satisfactorily adjusted even if the barrel torque changes by half during the relaxation.

The key elements of this manager are: on the one hand, the inertial mass return spring that regulates the speed is determined, and on the other hand, the permanent magnet and the conductive inertial mass, which characterize the dissipated power and therefore the braking torque.

This manager is particularly reliable, which is of great importance for horological products.

This device with eccentric inertia mass is a novel design that characterizes the stiffness/stability of the relation between braking torque and regulating speed and disengages the rotating system from magnetic braking for speeds below the nominal speed.

In short, the advantages offered by the present invention are numerous:

very precise pivoting speeds, in particular adjusted to less than 3%;

-silent operation;

reliability by no wear;

easy adjustment during assembly;

-no defined uncertainty regarding amplitude/velocity during development/operation;

-having a wide range of operating torques for the same speed.

Claims (21)

1. A timepiece wheel set or striking wheel set manager (1) for regulating the pivoting speed (ω) of a wheel set (3) about a first pivot axis (D1) about a reference speed value (ω c), wherein the wheel set (3) is driven by an energy source providing mechanical torque via a transmission device (2), the wheel set (3) comprising at least one inertia block (4) pivotally mounted about a first pivot (6), the first pivot (6) defining a second pivot axis (D2) parallel to and at a distance from the first pivot axis (D1), characterized in that: the manager (1) comprises return means (7) to return the at least one inertial mass (4) towards the first pivot axis (D1); the at least one inertial mass (4) is arranged: on the one hand, when said wheel set (3) pivots at a speed lower than or equal to said reference speed (ω c), said at least one inertial mass (4) remains confined in a first revolution space (VI) about said first pivot axis (D1); and on the other hand, when said wheel set (3) pivots at a speed higher than said reference speed (ω c), said at least one inertial mass (4) engages, at least at its peripheral portion (30), in a second revolution space (VE) around said first pivot axis (D1), said second revolution space being contiguous with said first revolution space (VI), said peripheral portion (30) cooperating, inside said second revolution space (VE), with adjustment means arranged for braking said wheel set (3) and returning the pivoting speed (ω) of said wheel set (3) to said reference speed (ω c), and for dissipating the excess energy, characterized in that: -said peripheral portion (30) is electrically conductive and said adjustment means are constituted by means of generating at least one variable magnetic field in a chamber (8) defined at least in part by magnetized components, said variable magnetic field comprising field lines oriented so that the interaction between said peripheral portion (30) and said magnetic field generates eddy currents which tend to brake said wheel set by resisting pivoting of said wheel set, or characterized in that: the peripheral portion (30) is made of a magnetized material and the pivoting movement of the wheel set (3) and of the inertial mass (4) generates a variable, or alternating or sinusoidal, magnetic field in a chamber (8), the chamber (8) being defined at least in part by an electrically conductive member whose interaction with the magnetic field generates eddy currents that brake the wheel set by resisting pivoting of the wheel set; and in that said supervisor (1) comprises braking means acting to apply a braking torque to the peripheral portion (30) of the inertia blocks (4) when said peripheral portion (30) of the inertia blocks (4) passes from said first turnaround space (VI) to said second turnaround space (VE), so that the applied braking torque intersects, within said second turnaround space (VE), a radial position of each of said inertia blocks starting from a first pivot axis (D1).

2. A timepiece wheel set or striking wheel set manager (1) according to claim 1, characterised in that the second revolution space (VE) about the first pivot axis (D1) is adjacent to and outside the first revolution space (VI).

3. A timepiece wheel set or striking wheel set manager (1) according to claim 1, characterised in that the second revolution space (VE) about the first pivot axis (D1) is adjacent to and inside the first revolution space (VI).

4. Timepiece wheel set or striking wheel set manager (1) according to claim 1, characterised in that said chamber (8) is defined by a magnetically insulating screen (9), said magnetically insulating screen (9) being made of non-magnetic material and constituting a magnetic shield.

5. A timepiece wheel set or striking wheel set manager (1) according to claim 1, characterised in that the return means (7) are arranged to keep the at least one inertia block (4) confined in the first revolution space (VI) when the wheel set (3) pivots at a speed lower than or equal to the reference speed (ω c), whereas the return means (7) are arranged to allow the at least one inertia block (4) to engage in the second revolution space (VE) at least in a peripheral portion (30) thereof when the wheel set (3) pivots at a speed higher than the reference speed (ω c).

6. Timepiece wheel set or striking wheel set manager (1) according to claim 1, characterised in that said return means (7) are elastic return means and exert a return force to a second pivot (72) in the direction of said first pivot axis (D1), said second pivot (72) being comprised in said at least one inertia block (4) and defining a third pivot axis (D3) parallel to said first pivot axis (D1) and said second pivot axis (D2); the return means (7) comprise a first pivot guide (74) about a main pivot (15) or arbour, which main pivot (15) or arbour is comprised in the wheel set (3) about the first pivot axis (D1), and comprise at least one second pivot guide (73) about a second pivot (72), which second pivot (72) is comprised in the at least one inertial mass (4) about the third pivot axis (D3).

7. A timepiece wheel set or striking wheel set manager (1) according to claim 1, characterised in that said wheel set (3) comprises a plurality of said inertia blocks (4) arranged equidistantly about said first pivot axis (D1); the return means (7) comprise a first pivot guide (74) around a main pivot (15) or arbour comprised in the wheel set (3) around the first pivot axis (D1), and comprise a second pivot guide (73) around a second pivot (72), the second pivot (72) being comprised in each inertial mass (4) around a third pivot axis (D3) specific to each inertial mass (4).

8. Timepiece wheel set or striking wheel set manager (1) according to claim 6, characterized in that the return means (7) are constituted by at least one spring (71), the at least one spring (71) being assembled into a preload whose value corresponds to the radial travel of the second pivot guide (73) of the spring (71) in a radial direction with respect to the first pivot axis (D1) when the spring (71) is guided by the first pivot guide (74) of the spring (71) on the main pivot (15) between an uncoupled position of the spring (71) and a position in which it is coupled to the second pivot (72) of the inertial mass (4), wherein the wheel set (3) and the inertial mass (4) are in a stop position, and in the coupled position of the spring (71) the preload tends to move the second pivot (72) of the inertial mass (4) towards the first pivot axis (D1) Radially drawn about the first pivot axis (D1).

9. Timepiece wheel set or striking wheel set manager (1) according to claim 1, characterised in that when said adjustment means are constituted by said means generating at least one variable magnetic field, said means are constituted by permanent magnets (12) arranged on both sides of a chamber (8), said peripheral portion (30) of said at least one inertial mass (4) moving in said chamber (8), said permanent magnets (12) being arranged on the inner periphery of a yoke (19) surrounding said chamber (8).

10. Timepiece wheel set or striking wheel set manager (1) according to claim 9, characterised in that on both sides of the cavity (8) the yoke (19) comprises a first flange (16) carrying a first series of the permanent magnets (12) and a second flange (17) carrying a second series of the permanent magnets (12), the first flange (16) and second flange (17) being pivotally movable relative to each other about the first pivot axis (D1) so as to align the field lines parallel to the first pivot axis (D1) or on the surface of a cone or cylinder of revolution about the first pivot axis (D1) so as to be oriented obliquely relative to the latter, depending on the relative position of the first flange (16) and second flange (17).

11. Timepiece wheel set or striking wheel set manager (1) according to claim 9, characterised in that on both sides of the cavity (8) the yoke (19) comprises a first flange (16) carrying a first series of the permanent magnets (12) and a second flange (17) carrying a second series of the permanent magnets (12), the first flange (16) and the second flange (17) being able to translate with respect to each other in the direction of the first pivot axis (D1) to vary the value of the air gap between these flanges.

12. Timepiece wheel set or striking wheel set manager (1) according to claim 9, characterised in that on both sides of the cavity (8) the yoke (19) comprises a first flange (16) carrying a first series of the permanent magnets (12) and a second flange (17) carrying a second series of the permanent magnets (12), the first flange (16) and the second flange (17) being able to move in translation and/or in pivoting with respect to each other in the direction of the first pivot axis (D1) as a result of the action of the peripheral portion (30) of the at least one inertia block (4) inserted in the air gap between these flanges.

13. Timepiece wheel set or striking wheel set manager (1) according to claim 9, characterised in that on both sides of the cavity (8) the yoke (19) comprises a first flange (16) carrying a first series of the permanent magnets (12) and a second flange (17) carrying a second series of the permanent magnets (12), the first flange (16) and the second flange (17) being able to move in translation and/or in pivoting with respect to each other in the direction of the first pivot axis (D1) under the action of a spring barrel constituting the source of energy providing the mechanical torque.

14. Timepiece wheel set or striking wheel set manager (1) according to claim 9, characterised in that the permanent magnet (12) is mounted radially movable with respect to the first pivot axis (D1).

15. Timepiece wheel set or striking wheel set manager (1) according to claim 8, characterised in that said spring (71) is arranged to exert a return force on said second pivot (72) in the direction of said first pivot axis (D1) and towards said first pivot axis (D1) to return said at least one inertia block (4) towards said first pivot axis (D1); the spring (71) comprises a first pivot guide (74) arranged to cooperate with the main pivot (15) as an additional guide, and comprises at least one second pivot guide (73) arranged to cooperate with the second pivot (72) of the at least one inertial mass (4) as an additional guide.

16. A timepiece wheel set or striking wheel set manager (1) according to claim 15, characterized in that the stiffness of the spring (71) is defined such that the value of the radial force applied to the inertia mass (4) returning to the second pivot (72) is substantially a linear function of the angular position (a) of the inertia mass (4) about the first pivot (6) on the second pivot axis (D2) with respect to the rest position of the inertia mass (4), the value of the radial force having an absolute value of zero corresponding to the preload stroke.

17. Timepiece wheel set or striking wheel set manager (1) according to claim 8, characterised in that the spring (71) is made of a micro-machinable material.

18. Timepiece wheel set or striking wheel set manager (1) according to claim 8, characterised in that the spring (71) is made of silicon or quartz.

19. Timepiece wheel set or striking wheel set manager (1) according to claim 8, characterised in that the spring (71) is made of an at least partially amorphous material.

20. A musical or striking mechanism for a timepiece or musical box, comprising an energy source or barrel and transmission means (2) for transmitting a mechanical torque from said energy source or barrel to a wheel set or striking wheel set for producing music, characterized in that it comprises a timepiece wheel set or striking wheel set manager (1) according to any one of the preceding claims, and in that said transmission means (2) drive at least one of said wheel sets (3).

21. Timepiece or music box comprising a wheel set or striking wheel set for producing music, characterized in that it comprises a music or striking mechanism according to claim 20 and/or a timepiece wheel set or striking wheel set manager (1) according to any one of claims 1 to 19.