CH716525B1 - Self-starting mechanical watch regulator. - Google Patents

Abstract

The present invention relates to a mechanical watch regulator (1) comprising: an oscillator (10) comprising an elastic member (11, 12) and an inertial body (13); an escapement (50) counting the alternations of the oscillator (10); a mechanical impeller (30) powered by an energy source (41); the regulator (1) comprising an amplitude detector (20) responsive to the amplitude of oscillation of the oscillator (10); the amplitude detector (20) being also configured to activate the impeller (30) when the amplitude of oscillation of the inertial body (13) is zero or less than an amplitude of oscillation threshold; the impulse mobile (30) transmitting its energy to the oscillator (10) when the impulse mobile (30) is activated. The regulator is self-starting.

Description

Technical area

The present invention relates to a self-starting mechanical watch regulator. More particularly, the present invention relates to a regulator comprising an oscillator, in which a quantity of energy is supplied to the oscillator as needed, that is to say when its amplitude of oscillation is too low.

State of the art

[0002] Mechanical watch regulators comprising a high quality factor oscillator require by definition that only a small quantity of energy is supplied per alternation to maintain the amplitude of oscillation of the oscillator balance wheel. It then seems possible to design a regulating mechanism consuming very little energy. Unfortunately, the energy that must be supplied to the escapement for this type of oscillator to reach an amplitude such that the mechanism starts by itself, in other words for it to be self-starting, is much greater. This contradiction implies either giving up, at least partially, the advantage of the low energy consumption of the system, or the self-starting property of the mechanism.

[0003] An oscillator of the "flexible guide" type, that is to say an oscillator whose function of guiding the balance wheel and the elastic return function are ensured by flexible blades, is an example of a mechanical oscillator which can have a very high quality factor if the pivot stiffness is high enough. Such a flexible guide oscillator is described in patent application EP2911012 by the present applicant. The high stiffness of the flexible pivot means that a large torque must be generated at the escape wheel to start the regulator. This last constraint added to the fact on the one hand that the frequency of such an oscillator is high (for a watchmaking mechanical oscillator) and on the other hand, that the starting torque and the operating torque are identical in a conventional regulator, implies that energy consumption will be high. On the other hand, the fact that this type of oscillator has a high quality factor implies that it is necessary to supply them with little energy at each halfwave.

[0004] One way of resolving this contradiction is not to supply energy to the oscillator at all half-waves. One obvious way to achieve this is to use a so-called “lost shot” escapement, but this type of system is not self-starting.

Brief summary of the invention

According to the invention, a mechanical watch regulator comprises an oscillator comprising an elastic member and an inertial body which can oscillate under the effect of the restoring force of the elastic member; an escapement counting the alternations of the oscillator; a mechanical impulse wheel energized by a power source; the regulator comprising an amplitude detector responsive to the oscillation amplitude of the oscillator; the amplitude detector being configured to activate the impeller when the oscillation amplitude of the inertial body is zero or less than an oscillation amplitude threshold; when activated, the pulse wheel transmitting its energy to the oscillator.

[0006] In one embodiment, the escapement is configured to cooperate with an escape wheel; the impulse mobile transmitting its energy to the inertial body so as to provide the inertial body with an oscillation amplitude at least greater than the oscillation amplitude threshold of the inertial body. The impulse mobile can transmit its energy directly to the inertial body.

[0007] The regulator according to the invention is completely self-starting (the regulator can restart even if the oscillator is completely stopped) and brings a large quantity of energy to the oscillator only when it needs it. that is, when its amplitude is too low. This makes it possible to work with high torques, thus guaranteeing self-starting without expending a lot of energy.

The invention therefore provides a solution to the aforementioned energy contradiction by supplying a large quantity of energy to the oscillator, not at each alternation but only when its amplitude is too low and a small quantity of energy, or even no energy at all, when the amplitude of the pendulum is sufficient to guarantee its proper functioning. Such a mechanism is self-starting while having low energy consumption.

The regulator according to the invention is particularly suitable for oscillators with a high quality factor and a high frequency. Indeed, these two properties are obtained on the one hand by minimizing the energy losses at the level of the inertial body and on the other hand by increasing the stiffness of the elastic member of the oscillator. In the case where the inertial body is a horological balance wheel, the energy losses are minimized by using a flexible pivot rather than a rubbing pivot.

Brief description of figures

[0010] Examples of implementation of the invention are indicated in the description illustrated by the appended figures in which: FIG. 1 illustrates a mechanical watch regulator, according to one embodiment; Figure 2 shows the regulator, according to another embodiment; Figure 3 shows a top view of a possible implementation of the controller, according to one embodiment; and Figure 4 shows a bottom view of the regulator of Figure 3.

Example(s) of embodiment of the invention

Figure 1 shows a schematic representation of a mechanical watch regulator 1, according to one embodiment. The regulator 1 comprises an oscillator 10 comprising an elastic member and an inertial body 13 able to oscillate under the effect of the restoring force of the elastic member. In the example of Figure 1, the elastic member comprises a first oscillator spring 11 connected in series with a second oscillator spring 12 via an intermediate mobile 14. The first oscillator spring 11 connects the intermediate mobile 14 to a fixed base 15 and the second oscillator spring 12 connects the intermediate mobile 14 to the inertial body 13. Note that the oscillator can comprise a mechanical oscillator adapted to a timepiece, such as an oscillator of balance-spring type in which the second oscillator spring 12 is the balance spring and the inertial body 13 is the balance. Regulator 1 also includes an exhaust 50 driven by a first energy source 40 (exhaust energy source), for example via a gear train (reduction, not shown). The escapement 50 counts the alternations of the oscillator 10. The escapement 50 can for example cooperate with an escape wheel (not shown), such as an escape wheel. Regulator 1 further comprises an impeller 30 comprising at least one degree of freedom in rotation or translation and being supplied with energy by a second energy source 41 (energy source of impeller 30). The force/torque supplied to the escapement wheel set by the first energy source 40 is significantly lower (between 50 and 100 times lower) than the force/torque supplied to the impulse wheel set by the second energy source 41 .

[0012] According to an embodiment not shown, the first energy source is supplied via the second energy source 41 coupled to a torque reduction. The torque reduction is configured in such a way as to supply a force or a torque to the escape wheel which is significantly lower (between 50 and 100 times lower) than the force or the torque supplied to the impulse wheel by the second source energy 41.

The regulator 1 also includes an amplitude detector 20 sensitive to the oscillation amplitude of the oscillator 10. The amplitude detector 20 and the pulse wheel 30 cooperate with the oscillator 10 as follows. The amplitude detector 20 is configured to activate the pulse mobile 30 when the oscillation amplitude of the inertial body 13 is zero or less than an oscillation amplitude threshold. When the impulse mobile 30 is activated, the impulse mobile 30 transmits its energy to the oscillator 10.

[0014] Still according to the particular configuration of FIG. 1, the amplitude detector 20 comprises a passive detection mobile 21, that is to say one that does not require an external energy supply to fulfill its function, which can be move at least according to one degree of freedom in rotation or in translation. The detection mobile 21 is magnetically coupled to the oscillator 10 so that the movement of the detection mobile 21 is defined by the amplitude of oscillation of the oscillator 10.

[0015] More particularly, the amplitude detector 20 comprises at least one detection magnet 23. Preferably, the latter is integral with the detection mobile 21, for example rigidly linked to the detection mobile 21. The oscillator 10 comprises at least one triplet of magnets 24. The triplet of magnets 24 can also be integral with the intermediate stage 14, for example rigidly linked to the intermediate stage 14. Alternatively, the amplitude detector 20 comprises the triplet d magnets 24 while oscillator 10 includes sensing magnet 23. Triplet of magnets 24 includes a central magnet 241 and two peripheral magnets 242, each having an opposite polarity to that of central magnet 241. detection magnet 23 has the same polarity as that of the central magnet 241.

In the nominal position, that is to say when the inertial body 13 is in its rest position and the oscillation amplitude is zero, the central magnet 241 of the magnet triplet 24 is aligned with the detection magnet 23 of the detection mobile 21. The polarity of the central magnet 241 is reversed with respect to those of the two outer magnets 242 of the magnet triplet 24. This arrangement of magnets makes it possible to generate an instantaneous variation of the magnetic torque/force on the detection wheel set 21 when the inertial body 13 oscillates along its axis of oscillation 16, as well as an average variation of the torque/magnetic force on the detection wheel set 21 when the oscillation amplitude of the inertial body 13 varies.

[0017] Preferably, the amplitude detector 20 is configured so that the position of the detection mobile 21 is practically not sensitive to the instantaneous variation of the torque/magnetic force and as sensitive as possible to the average variation torque/force. The detection mobile 21 is rendered insensitive to variations in the torque/instantaneous magnetic force on the one hand thanks to its high inertia/mass and, on the other hand, thanks to a viscous damping of the movement of the detection mobile 21. For example, the amplitude detector 20 may comprise damping means represented schematically in FIG. 1 by a lubricated pivot (or viscous pivot) 25. The amplitude detector 20 is therefore configured to activate the pulse wheel set 30 when the oscillation amplitude of inertial body 13 is zero or less than an oscillation amplitude threshold.

In the configuration of Figure 1, the triplet of magnets 24 is not positioned directly on the inertial body 13 of the oscillator 10, but on the intermediate mobile 14 of low inertia / mass.

According to one embodiment, the first oscillator spring 11, which connects the intermediate mobile 14 to the fixed base 15, is advantageously much more rigid than the second oscillator spring 12. The reason is that the detector of amplitude 20 also generates a counter torque/magnetic force on oscillator 10 and the nature of this torque/force is highly non-linear, which will considerably degrade the isochronism of oscillator 10. Placing the magnet triplet 24 on the intermediate mobile 14 of the oscillator 10 rather than on the inertial body 13 makes it possible to greatly reduce the harmful effects on the isochronism of the torque/magnetic force.

[0020] A decrease in the amplitude of oscillation of oscillator 10 will therefore generate a displacement of detection mobile 21 in the direction of oscillator 10. Amplitude detector 20 can then be configured in such a way that that the pulse wheel 30 is activated when the detection wheel 21 is moved to a threshold position in the direction of the oscillator 10. In other words, the amplitude detector 20 is triggered in the threshold position.

[0021] Still according to the particular configuration of FIG. 1, a trigger 22 having at least one degree of freedom collaborates with the detection mobile 21 and moves with the latter in the direction of the oscillator 10 when the amplitude of oscillation of oscillator 10 decreases. In the threshold position of the detection mobile 21 (when the oscillation amplitude of the inertial body 13 becomes lower than the oscillation amplitude threshold), the trigger 22 releases the impulse mobile 30 which then gives an impulse to the inertial body 13. When the oscillation amplitude of the inertial body 13 is greater than the oscillation amplitude threshold, the trigger 22 blocks the pulse rotor 30. The displacement amplitude detector 20 is designed so as to never release pulse wheel 30 above the oscillation amplitude threshold of oscillator 10 and always release pulse wheel 30 below this same threshold.

According to one embodiment, the displacement amplitude detector 20 comprises adjustment means for adjusting a threshold amplitude of the oscillator 10 from which the pulse wheel 30 is activated.

The adjustment means may comprise an adjustment spring 26 having one end attached to the mobile detection 21 and the other end attached to a fixed support 27 during operation of the system, but whose position is adjustable. The adjustment can then be carried out by adjusting the torque/preload force of the adjustment spring 26. Adjusting the position of the fixed support 27 will therefore modify the torque/preload force of the adjustment spring 26 and determine the amplitude alone of the oscillator 10.

[0024] Still according to one embodiment, the amplitude detector 20 may comprise positioning means making it possible to determine a nominal position of the mobile detection device 21. More particularly, the positioning means comprise a stop spring 28 connecting the mobile detection 21 to a fixed stop 29, make it possible to define a nominal position of the mobile detection 21. In other words, when the amplitude of oscillation of the oscillator 10 increases, the mobile detection 21 moves away from the oscillator and comes into contact with the stop spring 28 until it presses against the fixed stop 29, then gradually moves away from it when the amplitude of oscillation decreases. In other words, when the detection mobile 21 is in its nominal position, the stop spring 28 is very close to the detection mobile 21 but is not in contact with the latter. The stop spring 28 makes it possible to ensure that the detection wheel set 21 does not remain in static equilibrium against the fixed stop 29. In the configuration of FIG. 1, the stop spring 28 and the fixed stop 29 are placed on the side of detection mobile 21 opposite to oscillator 10.

When it is activated, the pulse wheel 30 transmits its energy to the oscillator 10. In this way, the pulse wheel 30 transmits its energy to the oscillator 10 only when the amplitude of the oscillator 10 is too weak. Pulse wheel 30 can transmit its energy directly to oscillator 10 (according to the example of FIG. 1 and illustrated in more detail in FIG. 3) or indirectly via an escapement (see FIG. 2).

[0026] Pulse mobile 30 can also be configured to return detection mobile 21 to its nominal position and release it once the pulse has ended, that is to say, once detection mobile 21 transmitted its energy to the oscillator 10. An exemplary embodiment is discussed below, in connection with Figures 3 and 4.

The regulator 1 according to the invention can be used for different watchmaking applications. Depending on the application, the way in which the impulse mobile 30 will interact with the oscillator 10 may differ.

According to one embodiment, the impeller 30 acts directly on the inertial body 13 of the oscillator 10, that is to say, transmits its energy directly to the inertial body 13, so as to provide the inertial body 13 with an oscillation amplitude at least greater than the oscillation amplitude threshold of the inertial body 13.

[0029] For example, the exhaust 50 of the regulator 1 according to the configuration of FIG. 1 may not be self-starting. In this case, regulator 1 can operate as a secondary escapement in the event of blockage of escapement 50. oscillation at least greater than the oscillation amplitude threshold of the inertial body, thus allowing the escapement 50 to unblock (in the case where the escapement 50 is blocked following an oscillation amplitude of the inertial body 13 below the threshold of oscillation amplitude) or to the escapement 50 not to block (in the case where the impeller 30 maintains the oscillation of the inertial body 13 at an oscillation amplitude at least greater than the threshold of amplitude of oscillation).

[0030] The non-self-starting escapement 50 may, for example, comprise a Genequand type escapement (not shown) comprising flexible blades fulfilling the role of impulse and rest pallets, cooperating with the escapement wheel set.

According to one embodiment, the first spring 11 corresponds to a flexible pivot of the "remote center of rotation" (RCC) type and the second oscillator spring 12 corresponds to a flexible pivot of the Wittrick type.

[0032] An RCC-type flexible pivot is typically a flexible pivot made up of two straight flexible blades each included in separate, non-parallel planes, the line of intersection of which does not physically meet either of the two blades. The axis of the RCC-type flexible pivot coincides approximately with the line of intersection between the two planes defined by the blades at rest (i.e. the non-flexed blades).

[0033] A pivot of the Wittrick type is a flexible pivot consisting of two straight flexible blades crossing at an angle of between 60° and 120°, typically at 90°; the flexible blades of a Wittrick pivot are physically separated by a plane orthogonal to their own planes; the flexible blades of a Wittrick pivot intersect with a crossover ratio between 6% and 18%, typically 12.5%; the axis of a Wittrick-type pivot coincides approximately with the line of intersection between the two planes defined by the flexible blades at rest (i.e. the unflexed blades). An example of a Wittrick type pivot is described in European patent application EP2911012

The Genequand escapement, named after its inventor, is a Grasshopper type escapement having the following specificities: a flexible pivot, typically of the RCC type, ensures the pivoting of the lever; a flexible pivot, typically of the Wittrick type, ensures the pivoting of the oscillator; flexible blades carried by the anchor fulfill the role of impulse and rest paddles; the oscillator is carried by the anchor (i.e. the Wittrick pivot of the oscillator is connected in series with the RCC pivot of the anchor). Examples of implementation of the Genequand escapement are described in European patents EP1736838 and EP2090941.

The regulator 1 according to the configuration of FIG. 1 can be used in parallel with a conventional exhaust system which is not self-starting (for example, as a secondary exhaust). An intrinsically blocking escapement system (for example a Genequand escapement) can therefore become self-starting while only very slightly increasing the energy consumption of the assembly, in particular thanks to the absence of contact in the amplitude detector 20, provided that the system must not restart too often (i.e. must not unblock the escapement 50 and restart the oscillations of the inertial body 30 too often).

In the case where the mobile detection 21 is a wheel, it may be advantageous to couple the mobile detection 21 with a second wheel 60 (see Figure 3) called balancing to make the assembly insensitive to shocks in rotation. Moreover, these two wheels 21, 60 must be balanced (center of mass at the center of rotation) so that the amplitude detector 20 is not disturbed by linear shocks. The inertia of the balancing wheel 60 attached to the detection wheel set 21 is advantageously substantially identical to the inertia of the detection wheel set.

[0037] Figure 2 shows the regulator 1 according to another embodiment. In this configuration, regulator 1 can be used as a torque regulator at wheel 32 of an escapement 50 in a conventional watch movement. In this case, the impeller 30 acts on an escapement wheel 32 (for example, the impeller 30 transmits its energy to the escapement wheel 32) which itself transmits its energy directly, or indirectly via an anchor (not shown), to the oscillator 10. In this implementation, without the action of the impeller 30, the torque to the escapement wheel 32 would be very low, which would prevent it from catching up with the oscillator 10 and to produce its pulse. In the latter case, the pulse then takes place only when the pulse wheel set 30 is released and transmits its torque to the escapement wheel 32. The latter then has enough torque to catch up with the oscillator 10 and transmit its torque to it. energy. In this configuration and contrary to the configuration of FIG. 1, the first energy source 40 does not supply the oscillator 10 at all, which is only supplied by the second energy source 41 via the pulse rotor 30. The first energy source 40 therefore only serves to rotate the escape wheel 32 to count the oscillations of the oscillator 10, to actuate the gear train and the watch hands of the watch movement.

In the configuration of the regulator 1 of FIG. 2, and contrary to the configuration of FIG. configuration of figure 2 against 1 or 2 per day for the configuration of figure 1). This implies that triggering of the amplitude detector 20 must disturb the oscillator 10 as little as possible. To this end, the amplitude detector 20 comprises a fixed magnet 243, in addition to the detection magnet 23 (or the triplet of magnets 24, depending on the configuration). The fixed magnet 243 has the same polarity as the detection magnet 23. In this way, when the amplitude detector 20 is triggered, the mobile detection 21 moves away from the triplet of magnets 24 (or from the detection magnet 23, depending on the configuration) instead of getting closer to it, as in the example of FIG. 1. Note that the detection magnet 23 has an opposite polarity to that of the central magnet 241 so that mobile detection 21 moves away from oscillator 10 when the amplitude of oscillation of oscillator 10 decreases. Note also that the first part of the removal of the detection magnet 23 can be accomplished only thanks to the interaction with the triplet of magnets 24. On the other hand, the release of the impulse mobile 30 requires a certain force/ torque due to friction between impeller 30 and detent 22. As in the implementation of Figure 2 the magnets 23, 24 move away from each other, the torque/magnetic force may not be sufficient to release the pulse wheel 30. The fixed magnet 243 makes it possible to ensure the release of the pulse wheel 30. Thus, when the amplitude detector 20 is triggered, the disturbing magnetic torque on the oscillator 10 decreases instead to increase critically. Indeed, the magnetic torque applied to the intermediate mobile 14 can be such that this mobile can be practically stopped in its oscillation. This effect is negligible in the case of the configuration of FIG. 1 where the impulse mobile 30 only triggers once or twice a day (ideally even less). The stop spring 28 and the fixed stop 29 can advantageously be placed on the same side of the detection mobile 21 as the oscillator 10. The polarity of the central 241 and peripheral 242 magnets of the triplet 24 is reversed with respect to the polarity of these magnets in the case of the configuration of figure 1.

In the case of the regulator 1 according to the configuration of FIG. 2, a strong impulse from the mobile impulse 30 has the advantage of being better controlled than a small impulse. This implies that the isochronism defect induced by the pulse of the pulse wheel 30 will be more stable and better defined. It will then be easier to compensate for the isochronism disturbance generated by the pulse.

Another substantial advantage of the regulator 1 according to the configuration of FIG. 2 in the case where the oscillator 10 is of the flexible guide type, is the fact of being able to use more rigid flexible pivots than for a regulator equipped with a self-starting conventional mechanical escapement, which makes it possible, indirectly, to increase the mass of the inertial body 13 without sacrificing the rate difference in flat-hanging mode. Thus the dimensions of the inertial body 13 can be smaller and therefore the oscillator 10 less bulky. Similarly, a more rigid flexible pivot implies that the elastic blades that make it up will be less slender (thickness/blade height ratio) which is favorable for the linearity of the elastic return torque of oscillator 10. Finally, at an amplitude given, an oscillator with a stiffer flexible pivot has also greater internal energy. Such an oscillator is less disturbed when carrying.

[0041] Figure 3 shows a top view of a possible implementation of the regulator 1 and Figure 4 shows a bottom view of this implementation. The regulator 1 is used to make self-starting an exhaust system (not shown) which is not in the absence of the regulator 1 (such as the configuration of FIG. 1). In the example of FIG. 3, the oscillator 10 comprises a rotary oscillator for a timepiece in which the inertial body 13 is a rim, and in which the first oscillator spring 11 is a flexible pivot of the RCC type comprising 4 blades and the second oscillator spring 12 is a Wittrick-type flexible pivot comprising two blades. The Wittrick pivot 12 connects the rim 13 to the intermediate mobile 14, itself connected to the base 15 via the RCC pivot 11. The base 15 is intended to allow the assembly of the oscillator 10 on a frame (not shown) of a mechanical watch. The non-self-starting escapement which is not shown in detail in FIGS. 3 and 4 may, for example, be an escapement as described in European patents EP1736838 and/or EP2090941. For example, this non-self-starting escapement may comprise an anchor whose two pallets each consist of a flexible blade. The anchor can be pivoted by a pivot consisting of a flexible guide in rotation of the RCC (Remote Compliance Center) type and carry a pendulum pivoted in rotation by a flexible guide of the Wittrick type as described in patent EP2911012.

The impeller 30 comprises a wheel having a locking tooth 33 at its periphery. The trigger 22 is formed of a rigid part pivoting on an axis 220 and comprising a trigger tooth 221 which comes into engagement with the locking tooth 33 so as to lock the impeller 30.

The detection mobile 21 of the amplitude detector 20 is a wheel rigidly mounted on an axis guided by a pivot 25. This pivot 25 is lubricated so as to limit dry friction and to dampen the oscillations of the detection mobile. 21 in order to make it less sensitive to instantaneous torque variations. In normal operation, these instantaneous torque variations are magnetic in nature and are generated by the interactions between the detection magnet 23 and the triplet of magnets 24. However, instantaneous torque variations can also be generated by the combination of a imbalance of the detection mobile 21 and an external shock or a change in orientation of gravity. The adjustment spring 26 is linked on the one hand to the axis (pivot) 25 of the detection mobile 21 and on the other hand to a spring preload adjustment system (not shown). The detection mobile 21 also comprises a detection magnet 23 and the triplet of magnets 24 is placed on the intermediate mobile 14 of the oscillator 10.

When the amplitude of oscillation of the inertial body 13 of the oscillator 10 decreases, the mobile detection 21, magnetically coupled to the oscillator 10, rotates clockwise (indicated by the arrow in Figure 3) so that the detection magnet 23 approaches the triplet of magnets 24. When the oscillation amplitude of the inertial body 13 becomes lower than the oscillation amplitude threshold, the detection mobile 21 is pivoted sufficiently (at the threshold position) so that a first lug 222 of the detection mobile 21 comes to rest against the trigger 22 and pivots it so as to separate the trigger tooth 221 from the locking tooth 33, releasing the mobile from impulse 30. Once released, the impulse wheel set 30 pivots in the clockwise direction indicated by the arrow in FIG. 3. The impulse wheel set 30 is provided with an impulse plane 34 which meets a pin of pulse 17 located on the inertial body 13 of the oscillator 10 and this, regardless of the position angular of the inertial body 13 provided that its amplitude is equal to or less than the amplitude of the trigger threshold. The impulse plane 34 will push the inertial body 13 to a minimum angular position via the impulse pin 17, so as to unlock the escapement mechanism 50. Once the impulse given by the impulse 34 on the inertial body 13 is completed, the impulse mobile 30 will continue its rotation and the plane 35 of the impulse mobile 30 will push the detection mobile 21 via a reset plane 223 of the detection mobile 21 , so as to reposition the detection mobile 21 in its initial position. It should be noted that this repositioning phase of the detection mobile 21 could just as well be done before the impulse of the impulse mobile 30 on the inertial body 13. Finally the detection mobile 21 will complete its rotation by locking on the tooth relaxation 221.

The amplitude detector 20 also comprises positioning means making it possible to determine the nominal position of the mobile detection device 21. More particularly, the amplitude detector 20 comprises a stop spring 28 taking the form of a leaf spring which bears against the fixed stop 29. The detection wheel set 21 comprises a second lug 281 integral with the detection wheel set 21 which bears against the leaf of the stop spring 28 when the amplitude of oscillation of the oscillator increases and that mobile detection 21 pivots in the anti-clockwise direction. The detection mobile 21 is permanently meshed, via a toothing 210, with a pinion 61 integral with the balancing wheel 60, the purpose of which is to prevent false detection when a rotational shock is exerted on the regulator 1 To this end, the inertia of the balancing wheel 60 relative to the detection mobile 21 must be identical to the inertia of the detection mobile.

The regulator 1 according to the invention is particularly suitable for oscillators with a high quality factor and a high frequency. Indeed, these two properties are obtained on the one hand by minimizing the energy losses at the level of the inertial body 13; for example in the case where the inertial body 13 is a pendulum, using a flexible pivot rather than a friction pivot. On the other hand, these two properties can be obtained by increasing the stiffness of the elastic member 11, 12 of the oscillator 10 (for example, the first and second oscillator springs 11, 12).

Reference numbers used in the figures

1 regulator 10 oscillator 11 first oscillator spring, elastic member 12 second oscillator spring, elastic member 13 inertial body, mass/inertia, pendulum 14 intermediate mobile 15 base 16 oscillation axis 17 impulse pin 20 amplitude detector 21 detection mobile 210 toothing 22 detent 220 axis 221 detent tooth 222 first lug 223 reset plane 23 detection magnet 24 triplet of magnets 241 central magnet 242 peripheral magnet 243 fixed magnet 25 lubricated pivot 26 adjustment spring 27 fixed support 28 stop spring 281 second lug 29 fixed stop 30 impulse mobile 32 escapement wheel 33 locking tooth 34 impulse plane of the impulse mobile 35 plane of the impulse mobile 40 first source of energy 41 second power source 50 primary escapement 60 balance wheel 61 pinion

Claims (21)

1. Regulator (1) mechanical watchmaker comprising: an oscillator (10) comprising an elastic member (11, 12) and an inertial body (13) which can oscillate under the effect of the restoring force of the elastic member (11, 12); an escapement (50) counting the alternations of the oscillator (10); a mechanical impeller (30) energized by an energy source (41); characterized in that the regulator (1) comprises an amplitude detector (20) responsive to the oscillation amplitude of the oscillator (10); the amplitude detector (20) being configured to activate the impeller (30) when the oscillation amplitude of the inertial body (13) is zero or less than an oscillation amplitude threshold; when it is activated, the impulse mobile (30) transmitting its energy to the oscillator (10). 2. Regulator (1) according to claim 1, wherein the elastic member comprises a first oscillator spring (11) connected in series with an intermediate wheel set (14) and a second oscillator spring (12), the second oscillator spring (12) being connected to the body inertial (13). 3. Regulator (1) according to claim 1 or 2, wherein the amplitude detector (20) comprises a detection mobile (21) able to move at least according to one degree of freedom in rotation or in translation, the detection mobile (21) being coupled to the oscillator (10) so that the displacement of the detection mobile (21) is determined by the amplitude of oscillation of the oscillator (10). 4. Regulator (1) according to claim 3, wherein the detection mobile (21) is coupled to the oscillator (10) via a magnetic coupling (23, 24). 5. Regulator (1) according to claim 4, in which the magnetic coupling comprises at least one detection magnet (23) integral with the detection mobile (21) and an oscillator magnet (24) integral with the oscillator (10). 6. Regulator (1) according to claim 5, wherein the oscillator magnet (24) comprises a central magnet (241) and two peripheral magnets (242) having opposite polarity to the polarity of the central magnet (241). 7. Regulator (1) according to one of claims 1 to 6, wherein the amplitude detector (20) includes viscous damping means. 8. Regulator (1) according to claim 7, wherein said viscous damping means comprises a lubricated pivot (25). 9. Regulator (1) according to one of claims 3 to 8, wherein the amplitude detector (20) comprises a detent (22) cooperating with the detection wheel (21) and moving with the latter, the detent (22) blocking the pulse wheel (30) when the amplitude of oscillation of the inertial body (13) is greater than the oscillation amplitude threshold and releasing the impeller (30) when the oscillation amplitude of the inertial body (13) is zero or less than the threshold of amplitude of oscillation. 10. Regulator (1) according to one of claims 3 to 9, in which the amplitude detector (20) comprises adjustment means making it possible to adjust a threshold amplitude of the oscillator (10) below which the pulse wheel (30) is released by the detection wheel (21) . 11. Regulator (1) according to claim 10, wherein said adjustment means comprise an adjustment spring (26) having one end attached to the detection wheel set (21) and the other end attached to a fixed support (27) whose position is adjustable. 12. Regulator (1) according to one of claims 3 to 11, in which the amplitude detector (20) comprises positioning means making it possible to determine a nominal position of the detection mobile (21). 13. Regulator (1) according to claim 12, wherein said positioning means comprise a fixed stop (29) and a stop spring (28), the latter coming to bear against the fixed stop (29) when the detection wheel set (21) is in the nominal position. 14. Regulator (1) according to one of claims 1 to 13, in which the impulse wheel (30) comprises a wheel provided with an impulse plane (34). 15. Regulator (1) according to one of claims 12 to 14 wherein the pulse wheel (30) is configured to return the detection wheel (21) to its nominal position, once the pulse wheel (30) is activated. 16. Regulator (1) according to one of claims 1 to 15 wherein the escapement (50) is configured to cooperate with an escapement wheel set; And wherein the impeller (30) transmits its energy directly to the inertial body (13) so as to provide the inertial body (13) with an oscillation amplitude greater than the oscillation amplitude threshold of the inertial body (13 ). 17. Regulator (1) according to claim 16, wherein the exhaust (50) is non-self-starting, and in which, the impulse mobile (30) transmits its energy directly to the inertial body (13) so that the inertial body (13) regains an oscillation amplitude greater than the oscillation amplitude threshold of the inertial body, allowing the escapement (50) to unblock in the event of blockage of the latter; Or wherein the impeller (30) maintains the oscillation of the inertial body (13) at an oscillation amplitude greater than the oscillation amplitude threshold, so that the escapement (50) does not block. 18. Regulator (1) according to claim 17, in which the escapement (50) is of the Genequand type, comprising flexible blades configured to cooperate with the escapement wheel set. 19. Regulator (1) according to claim 18, wherein the oscillator (10) includes a Wittrick-type flexible pivot pivoting the oscillator (10). 20. Regulator (1) according to claims 2 and 19, wherein the first spring (11) corresponds to a flexible pivot of the offset center of rotation type and the second oscillator spring (12) corresponds to said flexible pivot of the Wittrick type. 21. Regulator (1) according to claim 16 or 17, wherein the oscillator (10) comprises a hairspring-balance type oscillator, wherein the second oscillator spring (12) corresponds to the hairspring and the inertial body (13) corresponds to the balance wheel.