EP2533109A1 - Mechanism preventing rate variations due to gravitation on an adjusting device with a spiral balance and timepiece equipped with such an improvement - Google Patents

Abstract

The mechanism has a regulating unit including a hairspring and an escape wheel mounted on a platform. The platform is mounted to rotate freely about an axis relative to a bottom plate of a clock such that the platform rotates under an effect of earth's gravity. A wheel system includes a kinematic drive chain to connect the wheel to a barrel system and a kinematic correcting chain to cancel an effect of movements and speed of the platform relative to the plate. A regulating device comprises a flywheel (50) connected to the platform and driven by the movements between the platform and the plate.

Description

Known mechanisms avoiding the variations of step due to gravitation on a spiral balance adjusting device such as described for example in the patent EP 2 124 111 of the proprietor, but also as described for example in the documents EP-A-2031465 or EP-A-1615085 have the disadvantage of subjecting the sprung balance to significant accelerations due to the movements of the mobile platform carrying the sprung balance during sudden movements of the wearer of the watch. These accelerations can cause a phenomenon of rebate of the balance causing a variation of this regulating organ, generally an advance thereof.

The object of the present invention is to improve these existing mechanisms by adding a device that prevents strong accelerations are transmitted to the sprung balance when the watch is subjected to movements of the user.

The subject of the present invention is a mechanism which avoids the differences of steps due to the effect of gravitation on a regulating member of a clockwork movement comprising a balance-spring and an escape wheel mounted on a platform. said platform having an unbalance and being mounted in free rotation about at least a first axis with respect to a platen of movement so that said platform rotates about said first axis under the effect of earth gravitation; said mechanism comprising a train comprising a driving kinematic chain connecting the escape wheel to a cylinder of the watch movement and a corrective kinematic chain which compensates for the movements and the speed of the platform relative to the plate, characterized in that it comprises a regulating device comprising an organ regulator connected to the platform and driven by the relative movements between the platform and the turntable of the watch movement.

The additional features of this device constituting the improvement are specified in the dependent claims.

• La figure 1 illustre partiellement et schématiquement une forme d'exécution d'un mécanisme évitant les variations de marche dues à la gravitation permettant une stabilisation du balancier autour d'un axe parallèle à l'axe de ce balancier et apte à se combiner avec un dispositif régulateur.
• La figure 1a est un schéma d'une variante du mécanisme illustré à la figure 1.
• La figure 2 illustre une construction correspondant au schéma de la figure 1a mettant en évidence la chaîne motrice principale.
• La figure 3 illustre la construction illustrée à la figure 2 mettant en évidence la chaîne correctrice.
• La figure 4 est une vue en coupe de la construction illustrée aux figures 2 et 3.
• La figure 5 illustre partiellement et schématiquement une seconde forme d'exécution du mécanisme permettant une stabilisation du balancier autour d'un axe orthogonal à celui du balancier et apte à se combiner avec un dispositif régulateur.
• La figure 6 illustre partiellement et schématiquement une troisième forme d'exécution du mécanisme permettant une stabilisation du balancier autour de deux axes orthogonaux à l'axe du balancier et apte à se combiner avec un dispositif régulateur.
• La figure 7 est une perspective partielle du mécanisme illustré aux figures 1a, 2 et 3 en combinaison avec le dispositif régulateur comprenant une chaîne cinématique inertielle entraînant un volant d'inertie selon une forme d'exécution de l'invention.
• La figure 8 est une perspective correspondant à celle de la figure 7 vue sous un autre angle.

The accompanying drawing illustrates schematically and by way of example various embodiments of the device according to the invention.

• The figure 1 illustrates partially and schematically a form of execution of a mechanism avoiding the movements due to gravitation allowing stabilization of the balance about an axis parallel to the axis of the beam and adapted to combine with a regulating device.
• The figure 1a is a diagram of a variant of the mechanism shown in figure 1 .
• The figure 2 illustrates a construction corresponding to the schema of the figure 1a highlighting the main driving chain.
• The figure 3 illustrates the construction illustrated in the figure 2 highlighting the correcting chain.
• The figure 4 is a sectional view of the construction shown in Figures 2 and 3 .
• The figure 5 illustrates partially and schematically a second embodiment of the mechanism for stabilizing the balance about an axis orthogonal to that of the balance and adapted to combine with a regulating device.
• The figure 6 illustrates partially and schematically a third embodiment of the mechanism for stabilizing the balance about two axes orthogonal to the axis of the beam and adapted to combine with a regulating device.
• The figure 7 is a partial perspective of the mechanism illustrated in figures 1a , 2 and 3 in combination with the regulating device comprising an inertial kinematic chain driving a flywheel according to one embodiment of the invention.
• The figure 8 is a perspective corresponding to that of the figure 7 seen from another angle.

The Figures 1 to 6 partially and schematically illustrate three examples of mechanisms that avoid gravity-induced changes in travel, avoiding variations or variations in the operation of a spiral balance-type regulating device of a timepiece such as a wristwatch or a watch the Earth's gravitational effect resulting from changes in the spatial orientation of the regulating device. To do this, the mechanism comprises means allowing the regulating device to remain in a stable spatial position despite the movements imposed by the wearer to the timepiece while avoiding disrupting the display of time. Preferably, the stable spatial position of the regulating device is a position for which the balance remains in a horizontal or vertical reference plane whatever the position of the watch.

According to the present invention, such a mechanism further comprises a regulating device comprising at least one regulating member connected to the platform carrying the regulating device (preferably via an inertial kinematic chain), as described below with reference to to the figures 7 and 8 . However, to facilitate the understanding of the present invention, three examples of mechanisms avoiding gravitational shift are described first with reference to Figures 1 to 6 .

The principle of such mechanisms avoiding gait deviations consists in mounting the regulating member, generally the sprung balance, the anchor and the escape wheel on a mobile platform rotated along one or two orthogonal axes with respect to the platinum of the watch movement, this platform being subjected to the action of an unbalance which thus makes it possible to maintain said platform in a fixed reference plane (either horizontal, vertical or possibly inclined), by the action Earth's gravity whatever the position of the watch and therefore its movement.

A mechanism of this mechanism includes a driving kinematic chain connecting the escape wheel to the barrel system and a corrective kinematic chain that compensates the movements and speeds of the platform relative to the plate so that these movements of the plate -form do not disrupt chronometry of the timepiece. In particular, as will be seen below, thanks to this corrective kinematic chain when the platform rotates under the effect of its unbalance, it is possible to cancel the effect of displacements and the speed of the plate -form on the main driving kinematic chain.

A particularity of the mechanisms illustrated in Figures 1 to 6 is that in each case the cog, and in particular the motor and corrective kinematic chains, has the peculiarity of including only epicyclic gear trains whose mobiles meshing in a straight manner. Another important feature of these mechanisms lies in the fact that a mobile main driving kinematic chain is mounted in a satellite carrier rotating around two coaxial motor axes embedded or not on a mobile equipment comprising the platform carrying the pendulum and a cage pivoted on the plate of the movement on which is rotated said platform. In this way, these mechanisms consume little energy which reduces the weight of the unbalance of the platform and does not significantly reduce the power reserve of the watch movement.

According to another particularity of the mechanisms illustrated in Figures 1 to 6 , the corrective kinematic chain connects the escape wheel to the plate and comprises at least one mobile which pivots on the plate, which advantageously reduces the effect of the weight of this corrective chain on the unbalanced platform. According to yet another particularity of these mechanisms, the second wheel is on board the platform, which greatly minimizes the influence that the rotation of the platform can have on the torque transmitted to the exhaust by the driveline. main driving force.

Notwithstanding the foregoing, it is pointed out that the various embodiments and variants of the mechanism avoiding the deviations of the running device of a clockwork movement, which will now be described are by way of non-limiting example.

The first embodiment of the mechanism avoiding the deviations of a clocking device is illustrated in FIG. figure 1 . This is a simplified mechanism in that the platform carrying the regulating device is rotatably mounted on the plate of movement along a single axis of rotation AA perpendicular to the plane of the plate 1 of the clockwork movement.

The regulating device comprising a rocker 2, an anchor (not shown) and an escape wheel 3 is carried by a platform 4 pivoted on the plate 1 of the movement concentrically to the axis A-A. As illustrated in the figures, the axis of rotation AA of the platform 4 comprises a first motor shaft 20 and a second motor shaft 22, the platform being constructed so that these two motor shafts rotate around the same axis AA . In this embodiment, the axis of the balance 2 is parallel to this axis of rotation A-A of the platform 4.

The escape wheel 3, rotated coaxially with the axis AA on the platform 4, is secured to a drive wheel or second driving wheel 5 connected to the escape wheel by the second drive shaft 22. This second driving wheel 5 is engaged with the first mobile 6.2 of a satellite 6 rotated crazy in a satellite holder 7 which is itself pivoted on the platform 4 and rotated about the axis AA by a wheel of satellite door 7.1. In this way, the satellite gate 7 effectively constitutes a cage rotating concentrically with the platform 4 and in which the satellite mobile 6 is mounted crazy. As will be seen below, the rotational speed of this satellite carrier 7 is a function of the speed of rotation of the platform 4 about the axis A-A.

The second mobile 6.1 of the satellite 6, integral and coaxial with the first mobile 6.2 of the satellite 6 is engaged with a first driving wheel 8 integral with the first motor shaft 20 pivoted on the plate 1 of the movement. The wheel 8 and the shaft 20 are integral with the second wheel 9 of the clockwork motor of the watch movement. In a conventional manner, this second wheel 9 is kinematically connected to the barrel system 10 of the clockwork movement via the middle wheel 12 and the center wheel 11 all pivoted on the plate 1 of the following watch movement axes parallel to the AA axis.

The escape wheel 3 is thus connected to the barrel 10 by a main driving kinematic chain comprising a straight epicyclic gear train formed of the driving wheel 5, the first 6.1 and second mobile 6.2 of the satellite 6, of the first wheel. 8, of the second wheel 9, the average wheel 12, the center wheel 11 and the cylinder 10. This drive main drive train has no conical return and therefore has a very good performance, for example a yield which is substantially equal to the engine power of a conventional mechanical watch.

When a displacement of the timepiece carrying this mechanism causes the platform 4 to rotate about the axis AA, in the absence of a corrective kinematic chain, the mobiles of the main driving kinematic chain are rotated in rotation. which would cause disturbances in the display of the time and in particular on the exhaust.

To cancel the effects of these disturbances, a mobile of the main driving driveline, in this case the mobile 6, is mounted idle in the satellite holder 7, the latter being part of a correction kinematic chain also comprising the satellite gate wheel 7.1, a mobile idler 13, pivoted on the platform 4 along an axis parallel to the axis AA, and a fixed wheel 14 concentric with the axis AA and integral with the plate 1 of the movement. The idler 13 comprises a first wheel 13.1 meshing with the satellite gate wheel 7.1 and a second wheel 13.2 (integral and coaxial with the wheel 13.1) engaged with the fixed wheel 14.

Thus, thanks to the corrective kinematic chain comprising the fixed wheel 14, the idler 13, the satellite gate wheel 7.1, and the satellite carrier 7 carrying the satellite 6, when the platform 4 rotates, the satellite door 7 is rotated with a speed V ⁷ which is a function of the speed of the platform 4 V ⁴ (these speeds being relative to a fixed reference). This relationship depends on the transmission ratio between the wheels 14, 13.2, 13.1 and 7.1, in particular: $${\mathrm{<figure-callout\; id="7"\; label="V"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">V</figure-callout>}}^{\mathrm{7}}\mathrm{=}\left(\mathrm{1}\mathrm{-}{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_{\mathrm{1}}\right)\mathrm{.}{\mathrm{<figure-callout\; id="4"\; label="V"\; filenames="imgf0001.png,imgf0004.png"\; state="\{\{state\}\}">V</figure-callout>}}^{\mathrm{4}}\mathrm{or}{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_{\mathrm{1}}\mathrm{=}\frac{{\mathrm{<figure-callout\; id="14"\; label="R"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">R</figure-callout>}}_{\mathrm{14}}\mathrm{.}{\mathrm{R}}_{\mathrm{13.1}}}{{\mathrm{R}}_{\mathrm{13.2.}}{\mathrm{R}}_{\mathrm{7.1}}}$$

Rx being the number of teeth of wheel X.

A judicious choice of the different gear ratios makes it possible to actuate the mobile 6 in rotation about the axis AA in order to cancel the effect of displacements and the speed of the platform 4 on the main drive kinematic chain. In particular, if we denote by V ⁹ a speed of the average wheel at the output of the platform V ^u the useful speed transmitted to the exhaust (these speeds being still relative to a fixed reference), we obtain the following relation: $${\mathrm{<figure-callout\; id="9"\; label="V"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">V</figure-callout>}}^{\mathrm{9}}\mathrm{=}\frac{\mathrm{1}}{{\mathrm{<figure-callout\; id="2"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_{\mathrm{2}}}\left[{\mathrm{V}}^{\mathrm{u}}\mathrm{+}\left({\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_{\mathrm{1}}\mathrm{+}{\mathrm{k}}_{\mathrm{2}}\mathrm{-}{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_{\mathrm{1}}\mathrm{\cdot }{\mathrm{<figure-callout\; id="2"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_{\mathrm{2}}\right)\mathrm{.}{\mathrm{<figure-callout\; id="4"\; label="V"\; filenames="imgf0001.png,imgf0004.png"\; state="\{\{state\}\}">V</figure-callout>}}^{\mathrm{4}}\right]\mathrm{or}{\mathrm{<figure-callout\; id="2"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_{\mathrm{2}}\mathrm{=}\frac{{\mathrm{<figure-callout\; id="8"\; label="R"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">R</figure-callout>}}_{\mathrm{8.}}{\mathrm{R}}_{\mathrm{6.2}}}{{\mathrm{R}}_{\mathrm{6.1}}\mathrm{.}{\mathrm{<figure-callout\; id="5"\; label="R"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">R</figure-callout>}}_{\mathrm{5}}}$$

To make V ⁹ independent of V ⁴ , it suffices to cancel the term (k ₁ + k ₂ - k ₁ .k ₂ ). The relation to satisfy thus becomes: $$\left({\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_{\mathrm{1}}\mathrm{+}{\mathrm{k}}_{\mathrm{2}}\mathrm{-}{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_{\mathrm{1}}\mathrm{.}{\mathrm{<figure-callout\; id="2"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_{\mathrm{2}}\right)\mathrm{=}\mathrm{0}\mathrm{with}{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_{\mathrm{1}}\mathrm{\ne }\mathrm{1}\mathrm{and}{\mathrm{<figure-callout\; id="2"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_{\mathrm{2}}\mathrm{\ne }\mathrm{1}$$

The unbalance of the platform 4 can be constituted by the regulating device, sprung balance and escapement, itself since it can be mounted on the platform 4 offset from the axis of rotation AA of it. This avoids weighing down the watch movement. Of course, in variants a weight or mass could be attached eccentrically to the axis A-A on the platform 4 to increase the unbalance thereof.

The figure 1a illustrates a variant of the mechanism described with reference to the figure 1 . In this variant, the second wheel 9 of the work train is loaded on the platform 4 and meshes with the pinion of the escape wheel 3. Thus, it is no longer the axis of the escape wheel 3 which is confused with the axis AA of rotation of the platform 4, but the axis of the wheel of second 9, the rocker 2 and the escape wheel 3 being pivoted on the platform 4 parallel to the axis AA.

In this embodiment it is the second wheel 9 which is integral and concentric with the drive wheel 5 via the second drive shaft 22. The first drive wheel 8 is secured to it by the first drive shaft 20, a third drive wheel 15 engaged with the average wheel 12.

By loading a mobile of the conventional power train, here the second wheel 9, on the platform 4, the influence that the rotation of the platform 4 can have on the torque transmitted to the exhaust by the chain is greatly minimized. main driving kinematics. We can of course embark a second, see a third mobile of the conventional power train on the platform 4, the greater the number of embedded mobile is, the less the rotation of the platform 4 has effect on the torque transmitted from barrel 10 to the escape wheel 3. Note that in this embodiment, the above-mentioned velocity V ^u becomes the useful speed transmitted to the first mobile unit on the platform 4, so the second wheel 9 in the figure 1 at.

The Figures 2, 3 and 4 illustrate by way of example a practical execution of the embodiment of the mechanism described with reference to the diagram of the figure 1a , that is to say for a stabilization around a single axis AA of the platform 4 carrying the regulating device 2, 3 and the second wheel 9.

The platform 4 is formed of an upper bridge 4.1, an intermediate bridge 4.2 carrying an exhaust bridge 3.1 and a lower bridge 4.3 pivoted on the plate 1 concentrically to the axis A-A.

The three bridges 4.1, 4.2 and 4.3 of the platform 4 are integrally connected together by columns 4.4 which ensures that all these elements of the platform rotate together freely in rotation relative to the plate.

The third drive wheel 15 is integral with the lower end of the first drive shaft 20 pivoted by a bearing 21 in the plate 1, the shaft 20 being free in rotation relative to the platen as indicated above. This first motor shaft 20 has at its upper end the first drive wheel 8.

The fixed wheel 14 of the plate 1 meshes with the second wheel 13.2 of the idler 13 while the first wheel 13.1 of this idler, rotated crazy on the lower deck 4.3 meshes with the wheel of the satellite door 7.1 of the lower hub of the satellite door 7 is pivoted in the lower axle 4.3 concentrically to the axis AA around the first drive shaft 20. The satellite 6 is idly rotated on the satellite carrier 7, the second wheel 6.1 of the satellite 6 is engaged with the first driving wheel 8 while the first wheel 6.2 of the satellite 6 meshes with the drive wheel or second drive wheel 5 which is secured to the lower end of the second drive shaft 22 pivoted on the intermediate bridge 4.2 of the platform 4. This second motor shaft 22 carries the second wheel 9 which is engaged with the pinion 3.2 of the escape wheel 3. On this figure 2 the path of the main driving kinematic chain M connecting the third drive wheel 15, connected by the engine train to the barrel, to the escape wheel 3 via the satellite 6 and the second wheel 9 has been highlighted. .

On the figure 3 the path of the corrective kinematic chain C linking the satellite gate 7 to the plate 1 has been highlighted by means of the satellite gate wheel 7.1, the idler 13 and the fixed wheel 14.

The figure 4 is a sectional view of the mechanism shown in figures 1a , 2 and 3 .

The second motor shaft 22 is extended beyond the intermediate bridge 4.2 of the platform 4 and is also pivoted in the upper deck 4.1 of this platform 4. In this variant of the first embodiment of the mechanism in which the second wheel 9 is embarked on the platform 4, the free upper end of the second motor shaft 22 is extended beyond the upper deck 4.1 and carries a second hand 23 cooperating with a second dial 24 carried by the upper face of the upper deck 4.1 of the platform 4.

In such an embodiment, the seconds dial 24 rotates about the axis AA at the mercy of the movements of the platform 4. The seconds hand 23, it, also rotates with the movements of the platform. form but is further driven by the main driving kinematic chain in rotation relative to the dial 24. In this way, at a given moment or if the movement of the watch is stopped, the seconds hand 23 remains stationary relative to the dial of 24 seconds although the dial rotates around the AA axis.

The display of the hour and minutes is done conventionally from a mobile of the clockwork motor drive, generally the center wheel 11 or the medium wheel 12, by a timer to train the hour and minute hands that cooperate with a fixed dial relative to the watch movement platinum.

The display of the seconds previously described in the frame of the mechanism is original and playful because it turns on itself with each movement of the platform, that is to say whenever the orientation of the watch in the frame. space change due to the movements of the wearer of this watch.

Thanks to this mechanism avoiding the deviations of a regulating device, it is possible to maintain by the effect of the gravity acting on the unbalance of the platform 4 the balance in a fixed reference plane, preferably horizontal or vertical but can also be inclined, regardless of the spatial orientation of the plate 1 about the axis AA. Thus the movements printed by the wearer of the watch around this axis AA generally have more influence on the operation of the regulating device which is still working under the same conditions. The presence of a single correction chain is sufficient to eliminate the influence of displacements and the speed of the platform 4 on the escape wheel 3 and therefore on the regulating device and on the time display because they are fully compensated. In the embodiment where the second wheel 9 is loaded on the platform, the parasitic couples that can come from the movements of the platform 4 on the escape wheel are further reduced.

The figure 5 partially illustrates a second exemplary embodiment of the mechanism avoiding the deviations of the setting device of a watch movement in which the platform 4 is stabilized about an axis of rotation AA orthogonal to the axis of the balance 2. In this embodiment the axis of the balance 2, the axis of the escape wheel 3 and the axis of the onboard second wheel 9 are all three perpendicular to the axis of rotation AA of the platform 4. In this form of execution, in addition to the elements already described with reference to Figures 1 to 4 , the correction mechanism comprises a conical return 25 secured to the drive wheel or second drive wheel 5 which meshes with the second wheel 9. For the rest, the mechanism is identical to that of the first embodiment in its variant described in Figures 1a to 4 . In this embodiment, the axis AA around which the platform is rotated may for example be the 3 o'clock - 9 o'clock axis of the watch.

The third exemplary embodiment of a mechanism that avoids the gapping of a regulating member of a clock movement illustrated schematically in FIG. figure 6 allows the stabilization of the platform 4 carrying the balance 2 around two axes of rotation AA and BB orthogonal to each other and with respect to the axis of rotation of the balance 2. Such a mechanism makes it possible to maintain the platform 4 carrying the setting device of the watch in a fixed reference plane regardless of the orientation of the plate 1 of the movement of the watch in space and no longer just with respect to a single axis of displacement.

This mechanism comprises a cage 30 pivoted on the plate 1 about a second axis of rotation BB. Platform 4 of the figure 5 , previously described is, it, rotatably mounted on this cage 30 around the first axis of rotation AA perpendicular to the second axis of rotation BB of the cage 30.

As in the embodiment described with reference to the figure 5 , the platform 4 carries the balance 2, the escape wheel 3 and the second wheel 9 whose axes are parallel to each other and orthogonal to the first AA and second BB axes of rotation.

The second wheel 9 meshes with the conical return 25 secured to the drive wheel or second drive wheel 5 pivoted on the platform 4 concentrically to the first axis of rotation AA around which said platform 4 rotates. Still as previously described , this drive wheel 5 meshes with the first wheel 6.2 of the satellite 6 whose satellite carrier cage 7 pivots about the first axis of rotation AA on the platform 4. The second satellite wheel 6.1 meshes with the first drive wheel 8 concentrically pivoted to the first axis of rotation AA on the cage 30, which itself is pivoted about the second axis of rotation BB on the plate 1. This first drive wheel 8 is integral with the third drive wheel 15 both pivoted on the cage 30 .

The satellite gate 7 is engaged by its satellite gate wheel 7.1 with the first wheel 13.1 of the idler mobile 13 pivoted mad on the platform 4, the second wheel 13.2 meshes with the first wheel 32.1 of a corrective mobile 32 whose second wheel 32.2 has a conical toothing. This corrective mobile 32 is pivoted on the platform 4, in particular around the first drive shaft 20, concentrically to its axis of rotation AA on the cage 30. This corrector mobile 32 meshes with its second wheel 32.2 with the fixed wheel 14 secured to the plate 1. In this embodiment the fixed wheel 14 thus has a conical toothing.

The third drive wheel 15 also has a conical toothing and meshes with the first bevel gear 34.1 of a second idler wheel 34 rotated crazy on the cage 30. The second wheel 34.2 of the second idler 34 is engaged with a fourth driving wheel 35 pivoted concentrically to the second axis of rotation BB on the cage 30. This fourth drive wheel 35 is integral with a fifth drive wheel 35A kinematically connected to the cylinder 10 by a drive train of the movement may comprise a center wheel 11 and a wheel of high average 12 for example (the latter not being shown in the figure 6 for simplicity).

In this third embodiment, the platform 4 which carries the regulating device 2, 3 thus has two degrees of freedom, rotation about a first axis AA and rotation about a second axis BB orthogonal to the first axis AA . The platform 4 having an unbalance, formed by the regulating device 2, 3 or by additional unbalance can thus move according to the any spatial orientation of the plate 1 of the movement to ensure the maintenance in a fixed reference plane balance 2 and avoid the deviations due to gravity regardless of the position of the watch or movements imposed on them.

In this embodiment, the main drive train comprises the fifth drive wheel 35A, the fourth drive wheel 35, the second drive wheel 34, the third drive wheel 15, the first drive wheel 8, the satellite 6, the drive wheel drive (or second driving wheel) 5 and the conical return 25 as well as the second wheel 9 and the escape wheel 3.

The corrective kinematic chain, it comprises in this embodiment the fixed wheel 14, the correction mobile 32, the first mobile crazy 13, the wheel of the satellite door 7.1, and the satellite door.

For all these mechanisms, to better avoid that strong accelerations are transmitted to the regulating member, the sprung balance 2, during the movements of the platform 4 due to the change of orientation of the watch following the movements of the wearer of this watch a mechanism according to the invention, further comprises a regulator device connecting the platform 4 to a regulating member such as a flywheel 50, preferably through an inertial kinematic chain. This regulating device gives the platform greater rotational inertia, with the aim of making the operation of the balance more even, by opposing jolts due to the accelerations of the wearer.

According to one embodiment of the invention, the figures 7 and 8 partially illustrate the mechanism of Figures 1A to 4 equipped with a regulating device. This inertial kinematic chain comprises a toothed ring 51 integral with the platform 4 and coaxial with the latter meshing with a first mobile 52 pivoted on the plate 1 or a bridge of the watch movement. This first mobile 52 drives a flywheel 50 via a second mobile 53 and a third mobile 54 in engagement with a pinion 50.1 of the flywheel. The second movable 53 and third 54 of this inertial kinematic chain are also pivoted on the plate 1 or a bridge of the clockwork movement just like the flywheel 50. In a variant, the inertial kinematic chain may comprise only one mobile intermediate in between the ring gear 51 and the flywheel 50. In yet another variant, the wheel 50 can mesh directly with the ring gear 51, but in this case the steering wheel must be much larger.

Thanks to this regulator device it is possible to better avoid the rebate of the balance by greatly reducing the accelerations of the platform by increasing its inertia without increasing its mass.

In a variant it is possible to embark the flywheel 50 and its inertial kinematic chain on the platform 4. In this case it is necessary to introduce on the platform 4 a differential. The inputs of this differential are then a fixed wheel on the plate 1 and the toothed ring 51 integral with the platform 4 and the inertial kinematic chain leading to the flywheel 50 constitutes the output of this differential.

The regulator device comprising an inertial kinematic chain connecting the platform 4 to the flywheel 50 makes it possible to reduce the variations in acceleration of the movement of the platform 4 and prevents the balance 2 from reshuffling.

It should be noted that this inertial kinematic chain driving the regulating member by the relative movements between the platform and the turntable of the watch movement is independent of the motor kinematic or corrective mechanisms of the mechanism as well as of the automatic winding kinematic chain if the platform 4 acts as a winding mass. This device makes it possible to relate to the platform 4 the inertia of the flywheel 50 multiplied by the square of the reduction ratio of the inertial kinematic chain. This solution responds well to the problem of reducing the effects of accelerations of the platform by increasing the inertia without increasing its mass.

In a preferred manner, the multiplication ratio of the inertial kinematic chain is between 50 and 500, preferably equal to 100 for the embodiment previously described with reference to FIGS. figures 7 and 8 .

In general, the greater the multiplication ratio of this inertial kinematic chain, the smaller the flywheel can be and its low inertia.

For this regulating device the flywheel's inertia multiplied by the ratio of the inertial kinematic chain squared is from 10 to 50 times the inertia of the platform. Preferably, and for execution as described above, a value equal to 20 times the inertia of the platform is obtained.

In a variant, the flywheel 50 and the intermediate mobiles of the inertial kinematic chain can be loaded onto the platform 4, the first intermediate mobile 52 meshing with a wheel fixed on the plate or a bridge of the clockwork movement.

In the example shown, the platform 4 is provided with an automatic winding mass 55 and the mechanism comprises a conventional automatic winding kinematic chain (not illustrated) connecting the platform 4 to the barrel ratchet of the watch movement. .

In the same way (but not illustrated), if the mechanism of the figure 5 is provided with a regulating device comprising an inertial kinematic chain connecting the platform 4 to a flywheel 50, as described above, the platform 4 still carries the toothed ring 51 of the inertial kinematic chain of the regulating device connecting this platform 4 to the flywheel 50.

When the regulating device of the present invention is added to a mechanism with two axes of rotation AA and BB such as that of the figure 6 , the platform 4 carries the toothed ring 51 of a first inertial kinematic chain connecting it to the flywheel 50. The cage 30, it carries a second toothed ring 51a of a second inertial kinematic chain connecting the cage 30 to a second flywheel.

In a variant, the platform 4 and the cage 30 can be coupled using a differential whose output drives a single inertial kinematic chain and a single flywheel damping the accelerations of the platform 4 and the the cage 30.

According to variants, the regulating member may be other than a flywheel where the regulation is simply by the rotation of a mass. For example, a regulating member as used in minute repeats (where the regulation is by rotation of a mass and friction of this mass on a frame), a movable regulator with fins (where the viscosity of the air is used), or a regulating mobile similar to a clockwork escapement can be used.

Claims (11)

Mechanism that avoids the deviations due to the effect of gravitation on a regulating member (2, 3) of a timepiece of a timepiece, this mechanism comprising a regulating member comprising a balance-spring ( 2) and an escape wheel (3) mounted on a platform (4), said platform (4) having an unbalance and being mounted for free rotation about at least a first axis (AA) relative to a platen (1) of movement so that the platform (4) rotates about said first axis (AA) under the effect of earth gravitation; the mechanism comprising a gear train comprising a driving kinematic chain (M) arranged to connect the escape wheel (3) to a barrel system (10) of the timepiece and a correction kinematic chain (C) to cancel the effect of displacements and speed of the platform (4) with respect to the plate (1); characterized in that this mechanism further comprises a regulating device comprising a regulating member (50) connected to the platform (4) and driven by the relative movements between the platform (4) and the plate (1) of the movement watchmaking. Mechanism according to claim 1, characterized in that the regulating member (50) comprises a flywheel. Mechanism according to claim 1 or 2, characterized in that the regulating member (50) is connected to the platform (4) by means of an inertial kinematic chain (51, 52, 53, 54) comprising less an intermediate mobile. Mechanism according to claim 3, characterized in that a toothed ring (51) of the inertial kinematic chain is integral with the platform (4) while the regulating member (50) and at least one intermediate mobile (52, 53, 54) of the inertial kinematic chain are pivoted on the plate and / or a bridge of the clockwork movement. Mechanism according to claim 3, characterized in that a toothed wheel of the inertial kinematic chain is integral with the plate or a bridge of the movement while the intermediate wheel (s) (52, 53, 54) of the kinematic chain inertia and / or the regulating member (50) are pivoted on the platform (4). Mechanism according to one of claims 1 to 5, characterized in that the first axis (AA) is parallel to the axis of rotation of the sprung balance (2). Mechanism according to one of claims 1 to 6, characterized in that the platform (4) is rotatably mounted on a cage (30) pivoted on the plate (1) or a bridge of the movement along a second axis ( BB) perpendicular to the first axis (AA); and in that the regulating device further comprises a second regulator member connected to the cage (30). Mechanism according to one of claims 1 to 6, characterized in that the platform (4) is rotatably mounted on a cage (30) pivoted on the plate (1) or a bridge of the movement along a second axis ( BB) perpendicular to the first axis (AA); and in that the regulating device comprises a differential whose inputs are connected, one to the platform (4) and the other to the cage (30) and whose output is connected by one or more intermediate mobiles to the regulating member (50), these intermediate mobiles and / or this regulating member being pivoted on the plate (1) or a bridge of the clockwork movement. Timepiece comprising a mechanism according to one of claims 1 to 8. Timepiece according to claim 9, characterized in that it comprises an automatic winding kinematic chain connecting the platform (4) to the barrel ratchet of the watch movement. Timepiece according to one of claims 1 to 10, characterized in that the platform (4) carries or constitutes a winding mass (55).

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