EP2124111B1 - Mechanism preventing movement variations due to gravity on a sprung balance and timepiece equipped with such a mechanism - Google Patents

Description

The subject of the present invention is a mechanism that avoids the variations, or deviations, of travel due to the effect of gravitation on a spiral balance adjusting device as well as a timepiece comprising such a mechanism.

Known so-called swirling control systems in which the regulating device, the balance spring, is mounted in a rotating cage on one, two or three orthogonal pivot axes permanently driven by a clockwork movement, for example by a wheel on average.

The disadvantage of such systems is mainly that the rotation of said cage consumes energy permanently so even when it would not be necessary, for example at night the watch being placed flat, horizontal balance-spring.

In addition, the movements of the cage can theoretically statistically compensate for the differences in walking. However, when the watch is worn on the wrist it undergoes random movements and the deviations can not be fully offset by the constant regular movements imposed on the sprung balance by the rotating cage.

Document is known EP 1615085 a trim correction mechanism of a balance-sprung adjusting device which is held horizontal by the action of a counterweight. The balance spring is carried by a platform secured to a counterweight rotatably mounted about a first axis, pivoted in a cage rotatably mounted about a second axis perpendicular to the first. The escapement wheel of the regulating device is engaged with a driving wheel integral with the first axis and forming the output of a first differential gear train using three conical satellites, and therefore comprises two bevel gears. The inputs of this differential are a first corrective kinematic chain and a second drive kinematic chain itself connected to the output of a second differential gear train having at the input the barrel wheel and a second corrective kinematic chain engaged with a wheel integral with the cage. This second differential still uses three conical satellites, including two bevel gears, and in total the gear train has at least six bevel gears. Note also that all the wheels of the first corrective kinematic chain pivot on the platform is concentrically to its axis of rotation or on a fixed axis which is parallel to the latter. Similarly, all the wheels of the second corrective kinematic chain pivot on the cage either concentrically to its axis of rotation or on a fixed axis which is parallel to this axis.

According to the document EP 1615085 this mechanism effectively keeps the regulating organ in a horizontal plane under the sole action of gravity regardless of the position of the watch.

However, a major disadvantage of this mechanism is the complexity of its gear train containing two corrective kinematic chains and a high number of bevel gears, in particular in its gear differential gears, which causes significant power losses and therefore requires the presence of a large counterweight and a large power reserve. In addition, since all the mobiles of these corrective kinematic chains pivot on the platform or the cage, the weight of this balanced system is high which reduces the stabilization effect of the counterweight.

The object of the present invention is to provide a mechanism that avoids the gait deviations due to the effect of gravitation on a regulating member, in particular a timepiece, such as a balance-spring that allows said balance to be maintained. -spiral in a reference plane, preferably horizontal, under the only earth gravity action that is simple, free of conical gears consumer energy or understanding a minimum and thus reducing the weight of the counterweight, the size of the mechanism and the power reserve.

The subject of the present invention is a mechanism that avoids variations or variations in operation due to the effects of gravitation on a regulating device, sprung balance and a timepiece provided with such a device that obviates the aforementioned drawbacks of the existing devices.

This mechanism avoids the deviations due to the effect of gravitation on a regulating member of a watch movement of a timepiece, whose regulating member comprises a balance spring and an escape wheel mounted on a platform, said platform having an unbalance and being mounted in free rotation around at least a first axis (AA) relative to a movement plate so that said unbalance maintains said balance-spring in a plane fixed reference when said platform rotates about said first axis (AA) under the effect of terrestrial gravitation; is distinguished by the fact that the mechanism comprises a train comprising a driving kinematic chain connecting the escape wheel to a barrel system of the timepiece and a corrective kinematic chain which compensates for the movements and speed of the platform. shape with respect to a turntable of the watch movement so that these movements of the ptate-form do not disturb the chronometry of the timepiece, this work train comprising one or more epicyclic gear trains and each of said trains in said work train containing mobiles that mesh rightly only.

The invention also relates to a mechanism that avoids gait deviations due to the effect of gravitation on a regulating member of a timepiece movement of a timepiece, the regulating member of which comprises 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 by relative to a platen of movement so that said unbalance maintains said sprung balance in a fixed reference plane when said platform rotates about said first axis under the effect of earth gravitation; which is distinguished by the fact that the escape wheel is connected on the one hand to a barrel system of the timepiece by a driving kinematic chain and on the other hand to the platen of the movement by a corrective kinematic chain.

The invention also relates to a mechanism that avoids gait deviations due to the effect of gravitation on a regulating member of a timepiece movement of a timepiece, the regulating member of which comprises 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 relative to a platen of the movement so that said unbalance maintains said balance-spring in a fixed reference plane when this platform rotates about said first axis under the effect of earth gravitation; said mechanism comprising a driving kinematic chain connecting the escape wheel to a barrel system of the timepiece and a corrective kinematic chain compensating the movements and the speed of the platform relative to a platinum of the movement of watchmaker for these movements of the platform do not disrupt the chronometry of the timepiece, and wherein the second wheel of the clockwork of the clockwork is embarked on the platform.

The additional features of this mechanism are specified in the dependent claims.

The invention also relates to a timepiece provided with such a mechanism.

• La figure 1 illustre schématiquement une forme d'exécution du mécanisme selon l'invention permettant une stabilisation du balancier autour d'un axe parallèle à l'axe de ce balancier.
• 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 schématiquement une forme d'exécution du mécanisme selon l'invention permettant une stabilisation du balancier autour d'un axe orthogonal à celui du balancier.
• La figure 6 illustre schématiquement une forme d'exécution du mécanisme selon l'invention permettant une stabilisation du balancier autour de deux axes orthogonaux à l'axe du balancier.
• La figure 7 est une vue en perspective d'une construction correspondant au schéma de la figure 6.
• La figure 8 est également une perspective de la construction illustrée à la figure 7 vue sous un autre angle.
• La figure 9 est une vue de côté de la construction illustrée à la figure 7 ou 8.
• La figure 10 est une coupe de la construction illustrée à la figure 9 suivant un plan contenant les axes A-A et B-B.
• La figure 11 est une coupe de la construction illustrée à la figure 9 suivant un plan contenant l'axe A-A et perpendiculaire à l'axe B-B.
• La figure 12 illustre schématiquement une forme d'exécution du mécanisme selon l'invention dans laquelle la chaîne correctrice est au moins partiellement à l'extérieur de la cage portant le balancier.

The attached drawing illustrates schematically and by way of example different embodiments of the mechanism according to the invention.

• The figure 1 schematically illustrates an embodiment of the mechanism according to the invention for stabilizing the balance about an axis parallel to the axis of the balance.
• 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 schematically illustrates an embodiment of the mechanism according to the invention for stabilizing the balance about an axis orthogonal to that of the balance.
• The figure 6 schematically illustrates an embodiment of the mechanism according to the invention for stabilizing the balance about two axes orthogonal to the axis of the balance.
• The figure 7 is a perspective view of a construction corresponding to the diagram of the figure 6 .
• The figure 8 is also a construction perspective illustrated at the figure 7 seen from another angle.
• The figure 9 is a side view of the construction shown in the figure 7 or 8 .
• The figure 10 is a section of the construction shown in the figure 9 following a plan containing the axes AA and BB.
• The figure 11 is a section of the construction shown in the figure 9 following a plane containing the axis AA and perpendicular to the axis BB.
• The figure 12 schematically illustrates an embodiment of the mechanism according to the invention wherein the corrective chain is at least partially outside the cage carrying the balance.

The subject of the present invention is a mechanism that avoids the variations or variations of a setting device of the spiral-balance type of a timepiece such as a wristwatch or a pocket watch due to the effect of the Earth gravitation resulting from changes in spatial orientation of the regulating device. To do this, the mechanism according to the invention 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.

The principle of the mechanism avoiding gait deviations according to the invention 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. relative to the platen 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 of 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 disturb the 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 completely cancel the effect of the displacements and the speed of the platform on the main drive train. Thus, despite the rotation of the platform to maintain the balance in a reference plane, for example horizontal, the The operation of the escapement and the time display of the watch movement are not disturbed.

Preferably, the gear train, and in particular the motor and corrective kinematic chains, has the particularity of including only epicyclic gear trains whose wheels mesh in a straight manner. The gear thus excluded any epicyoloïdal train containing conical gears whose performance is very unfavorable. Moreover, even in embodiments where the gearing includes bevel gears elsewhere in these motor and corrective kinematic chains, the latter are still of a reduced number compared to comparable gear systems of the state of the art.

As will be seen later also, another important feature of the mechanism according to the invention resides in the fact that a mobile main drive kinematic chain is mounted in a satellite door rotating about two coaxial motor axes embarked or not on a mobile unit comprising the platform carrying the balance and a cage pivoted on the plate of the movement on which is pivoted said platform.

Thus, a mechanism is provided which avoids the operating deviations of the regulating member which consumes little energy, which makes it possible to reduce the weight of the unbalance of the platform and not to reduce significantly the power reserve of the movement of the watchmaking.

According to another preferred aspect of the invention, 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 correction chain on the unbalanced platform. According to yet another preferred aspect of the invention, the second wheel is on board the platform, which greatly minimizes the influence that the rotation of the platform may have on the torque transmitted to the exhaust by the driving main kinematic chain.

In the following, several embodiments and variants of the mechanism to avoid gait of the adjusting device of a clockwork movement will be described 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 mounted free to rotate on the platen of the 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 tree 20 are integral with the second wheel 9 of the clockwork 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 drive wheel 5, the first 6.1 and second 6.2 mobile satellite 6, 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 crazy 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, including: $${\mathrm{<figure-callout\; id="7"\; label="V"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">V</figure-callout>}}^{\mathit{7}}=\left(1-{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">k</figure-callout>}}_{\mathit{1}}\right)\cdot {\mathrm{<figure-callout\; id="4"\; label="V"\; filenames="imgf0001.png,imgf0004.png"\; state="\{\{state\}\}">V</figure-callout>}}^{\mathit{4}}\mathrm{or}{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">k</figure-callout>}}_1=\frac{{\mathrm{<figure-callout\; id="14"\; label="R"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">R</figure-callout>}}_{14}\mathrm{.}{R}_{13.1}}{R_{13.2}\mathrm{.}{R}_{7.1}}$$

Rx being the number of teeth of wheel X.

Pour rendre v⁹ indépendant de V⁴ , il suffit d'annuler le terme (k ₁ + k ₂ - k ₁.k ₂). La relation à satisfaire devient donc: $$\begin{array}{cc}\left(k_1+k_2-k_1\mathrm{.}{k}_2\right)=0& \mathrm{avec}{k}_1\ne 1\mathrm{et}\end{array}{k}_2\ne 1$$

A judicious choice of the different gear ratios makes it possible to actuate the mobile 6 in rotation around the axis AA in order to cancel the effect of the displacements and the speed of the platform 4 on the chain, main driving kinematics . In particular, if we denote V ⁹ a speed of the average wheel at the output of the platform and V ^u the useful speed transmitted to the exhaust (these speeds being still relative to a fixed reference), we obtain the following relation: $${\mathrm{<figure-callout\; id="9"\; label="V"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">V</figure-callout>}}^9=\frac{1}{{\mathrm{<figure-callout\; id="2"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_2}\left[V^u+\left({\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">k</figure-callout>}}_1+k_2-{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">k</figure-callout>}}_1\mathrm{.}{\mathrm{<figure-callout\; id="2"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_2\right)\mathrm{.}{\mathrm{<figure-callout\; id="4"\; label="V"\; filenames="imgf0001.png,imgf0004.png"\; state="\{\{state\}\}">V</figure-callout>}}^4\right]\mathrm{or}{\mathrm{<figure-callout\; id="2"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_2=\frac{{\mathrm{<figure-callout\; id="8"\; label="R"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">R</figure-callout>}}_8\mathrm{.}{R}_{6.2}}{R_{6.1}\mathrm{.}{\mathrm{<figure-callout\; id="5"\; label="R"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">R</figure-callout>}}_5}$$

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: $$\begin{array}{cc}\left({\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">k</figure-callout>}}_1+k_2-{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">k</figure-callout>}}_1\mathrm{.}{\mathrm{<figure-callout\; id="2"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_2\right)=0& \mathrm{with}{\mathrm{<figure-callout\; id="1"\; label="k"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">k</figure-callout>}}_1\ne 1\mathrm{and}\end{array}{\mathrm{<figure-callout\; id="2"\; label="k"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">k</figure-callout>}}_2\ne 1$$

As can be seen, the corrective kinematic chain comprises a right epicyclic gear train excluding any conical gear that consumes a lot of energy.

The gear train of this mechanism therefore comprises only spur gear trains, and is therefore particularly powerful, which allows to obtain a better performance and reduce the weight of the unbalance of the platform 4 and therefore its size and therefore allows not to reduce the power reserve of the watch movement.

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 coincides with the axis AA of rotation of the platform 4, but the axis of the second wheel 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 at the wheel 3. In this embodiment, it is noted that the above-mentioned speed V ^u becomes the useful speed transmitted to the first mobile unit on the platform 4, so the second wheel 9 in the figure 1a .

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 secured to the lower end of the first drive shaft 20 pivoted by a bearing 21 in the plate 1, the shaft 20 being free to rotate relative to the plate 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 bridge 4.3, meshes with the wheel of the satellite door 7.1 of the lower hub of the door satellite 7 pivoted in the lower bridge 4.3 concentrically to the axis AA around the first motor shaft 20. The satellite 6 is pivoted crazy on the satellite door 7, the second wheel 6.1 of the satellite 6 is engaged with the first driving wheel 8 while that the first wheel 6.2 of the satellite 6 meshes with the drive wheel or second drive wheel 5 which is integral with 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 linking has been highlighted the third driving wheel 15, connected by the engine train to the barrel, to the escape wheel 3 via the satellite 6 and the second wheel 9.

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

Thanks to this mechanism avoiding the gates 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 A-A no longer have any 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, parasitic couples that can come from the movements of the platform 4 on the escape wheel are reduced to a negligible value, or zero.

Moreover, as has already been seen, according to this embodiment, the kinematic and corrective drive chains comprise exclusively geared planetary gear trains with a very good efficiency making it possible not to reduce the power reserve of the movement and of minimize the weight and bulkiness of platform 4 unbalance.

According to yet another variant (not shown) of the first embodiment, instead of loading the seconds wheel 9 on the platform 4, a constant force escapement can be installed on the platform in order to avoid the influence that the rotation of the platform can have on the torque transmitted to the exhaust.

The figure 5 illustrates an 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 2. In this embodiment the axis of the balance 2, the axis of the escape wheel 3 and the axis of the second wheel embedded 9 are all three perpendicular to the axis of rotation AA of the platform 4. In this embodiment, in addition to the elements already described with reference to the Figures 1 to 4 , the correction mechanism comprises a conical return 25 secured to the drive wheel or second driving 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 1 In this embodiment, the axis AA around which the platform is rotated can for example be the 3 o'clock - 9 o'clock axis of the watch.

The embodiment of the mechanism avoiding gait deviations of a regulating member of a clockwork movement schematically illustrated 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. A practical embodiment or construction of such an embodiment is illustrated in Figures 7 to 10 for exemple. In these figures the mechanism represented differs from that illustrated schematically in figure 6 by adding mobiles 36; 37.1; 37.2 and 15.2 to reduce the bulk of the third drive wheel 15.

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 of which the 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 embodiment, the platform 4 which carries the regulating device 2, 3 thus has two degrees of freedom, rotation about a first axis A-A and rotation about a second axis B-B orthogonal to the first axis A-A. The platform 4 having an unbalance, formed by the regulating device 2, 3 or by an 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 all 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.

Here also the workings of this mechanism including including these two motor and corrective kinematic chains comprise only gear trains epicyclic right with good efficiency. In addition, although the mechanism gear includes bevel gears elsewhere in these kinematic and corrective drive chains, these gears are still of a reduced number compared to comparable gear systems of the state of the art. For example, in comparison with the machinery mechanism described in the document EP 1615085 , that of the figure 6 comprises considerably fewer links and in particular half the number of bevel gears used in the mechanism of EP 1615085 . Moreover, according to the form of execution of the figure 6 , correction of the displacements of the cage 30 and the platform 4 are made using a single continuous correction kinematic chain.

The figure 12 illustrates yet another embodiment of the mechanism with two axes of rotation in which part of the correction kinematic chain, including in particular the mobile 6 and its satellite door 7, is located outside the platform 4 and the cage 30.

The platform 4 carrying the regulating device, sprung balance 2 and escape wheel 3 is, just as in the figure 6 , pivoted on the cage 30 along a first axis of rotation AA perpendicular to the axes of the balance 2 and the escape wheel 3. Also, the cage 30, it is rotated on the plate 1 along a second axis of rotation BB perpendicular at the first axis of rotation AA of the platform 4 on the cage 30 and perpendicular to the axes of the balance 2 and the escape wheel 3.

A second wheel 9 secured to a first drive shaft 40 is connected to the barrel by the usual engine gear of the watch movement. This first motor shaft 40 is pivoted on the plate 1 and one of its ends carries a second hand 39 cooperating with a second fixed dial relative to the plate 1.

The conical return 25 meshes with the escape wheel 3 and meshes with the first wheel 41.1 of a first driving mobile 41 pivoted on the platform 4 coaxially with the axis of rotation AA of the platform 4. The second 41.2 wheel of the first driving mobile meshes with the first wheel 42.1 of a second driving mobile 42 pivoted on the cage 30 and the plate 1 coaxially with the axis of rotation BB of the cage 30. The second wheel 42.2 of the second mobile coach 42 meshes with a third driving wheel 43 secured to a second motor shaft 44 pivoted on the plate 1 in a direction parallel to the axis of rotation BB of the cage 30 on the plate 1. This second motor shaft 44 is integral with a second drive wheel 45 in engagement with the first satellite wheel 6.1 of the satellite 6 whose second wheel 6.2 meshes with a first drive wheel 46 integral with a first drive shaft 40 and thus the second wheel 9. These first and second trees mo 40, 44 are coaxial.

According to this embodiment, the satellite 6 is rotated crazy in the satellite carrier 7 concentrically to the first and second motor shafts 40, 44 on the plate 1. The satellite gate wheel 7.1 is engaged with the first wheel 47.1 of a mobile corrector 47 pivoted on the plate 1 concentrically to the pivot axis BB of the cage 30 on the plate 1, the second wheel 47.2 is engaged with a correction wheel 48 secured to the platform 4 and concentric to the axis AA of rotation of this platform 4 on the cage 30.

In this embodiment, the main drive train comprises the second wheel 9, the first drive shaft 40, the first driving wheel 46, the satellite 6, the second driving wheel 45, the second driving shaft 44, the third wheel 43, the second driving mobile 42, the first driving mobile 41 and the conical return 25 secured to the escape wheel 3.

Although this drive main drive train comprises bevel gears, all epicyclic gear trains which constitute it are straight and therefore of high efficiency. In addition, the number of bevel gears used elsewhere in the gear train is still of a reduced number compared to the state of the art.

In this embodiment, the corrective kinematic chain comprises the correction wheel 48, the correction wheel 47, the satellite gate wheel 7.1, and the satellite gate 7. This correction chain also comprises only a limited number of bevel gears as well as planetary gear trains which meshes in a straight manner only (excluding any epicyclic bevel gear train); this chain is still relatively good.

In variants of this embodiment, the second wheel 9 can also be embarked on the platform 4 reducing or canceling the effects of the movements of the platform 4 on the torque transmitted to the regulating device 2, 3.

By this embodiment it is seen that it is possible to lighten and reduce the size of the platform 4 carrying the regulating device 2, 3 by placing the satellite 6 and its satellite door 7 outside the plate form 4.

In all possible embodiments of this mechanism, it is necessary that the center of gravity of the mobile equipment formed by the platform 4 and the cage 30 is located away from the axes of rotation AA and BB of this platform 4 relative to the plate so that the mobile element has an unbalance to position the regulating member in the reference plane regardless of the movements of the plate 1.

It should also be noted that even in the embodiments where the platform 4 is articulated about two orthogonal axes A-A and B-B on the plate, the mechanism comprises only one and the same correction kinematic chain which is continuous.

It is obvious that in watch movements equipped with such a self-winding correction mechanism, it is possible to use the mobile equipment formed of the cage 30 and / or the platform 4 as a winding mass to wind the barrel by means of a winding kinematic chain connecting the platform 4 or the cage 30 to the barrel ratchet and comprising a reverser of direction for example of the Pellaton type. The cage 30 and the platform 4 can be unbalanced separately or the entire mobile equipment, platform 4 and cage 30 can be balanced.

Claims (18)

1. Mechanism avoiding the rate variations due to the effect of gravitation on a regulating organ (2, 3) in a clockwork movement of a timepiece where the regulating organ comprises a sprung balance (2) and an escape wheel (3) mounted onto a platform (4), said platform (4) including an unbalance and being mounted so as to freely rotate about at least a first axis (A-A) relative to a plate (1) of the movement so that this platform (4) may rotate about said first axis (A-A) under the effect of terrestrial gravitation; the mechanism comprising a wheelwork including a driving kinematical chain (M) linking the escape wheel (3) to a barrel system (10) of the timepiece, as well as a corrective kinematical chain (C) canceling the effects of the movements and speed of the platform (4) relative to the plate (1) on the driving chain (M), the driving chain (M) comprising a first driving wheel (8,46) fast with a first driving shaft (20,40) and a second driving wheel (5,45) fast with a second driving shaft (22,44) coaxial to the first driving shaft (20,40), characterized by the fact that the wheelwork comprises one or several epicycloïdal gears each of said trains in said wheelwork containing wheels with straight thoothing exclusively and by the fact that the first drive wheel (8, 46) meshes straight with the second wheel (6.1) of planetary mobile (6) the first wheel (6.2) of which meshes straight with the second drive wheel (5, 45).
2. Mechanism according to claim 1, characterized in that the planetary mobile (6) is freely pivoted on a planetary wheel holder (7) which itself pivots coaxially with the first and second drive shafts (20, 22; 40, 44); and in that the planetary wheel holder (7) includes a wheel (7.1) of the planetary wheel holder that is part of the corrective kinematical chain (C).
3. Mechanism according to claim 2, characterized in that the corrective kinematical chain (C) links wheel (7.1) of the planetary wheel holder (7) to a fixed wheel (14) integral with the plate (1) of the clockwork movement.
4. Mechanism according to claim 3, characterized in that the fixed wheel (14) is coaxial with the axis of rotation (A-A) of the platform (4).
5. Mechanism according to claims 3 or 4, characterized in that the corrective kinematical chain (C) comprises planetary mobile (13) freely pivoted parallel to the axis A-A on the platform (4), and comprising a first wheel (13.1) meshing with the wheel (7.1) of the planetary wheel holder, and a second wheel (13.2) meshing with the fixed wheel (14).
6. Mechanism according to one of claims 1 to 3, characterized in that the platform (4) is suspended within a carriage (30) freely pivoted on the plate (1) about a second axis of rotation (B-B) orthogonal to the first axis of rotation (A-A).
7. Mechanism according to claim 6, characterized in that the corrective kinematical chain (C) links the wheel (7.1) of the planetary wheel holder (7) to a fixed wheel (14) integral with the plate (1), and coaxial with the second axis of rotation (B-B) of the carriage (30).
8. Mechanism according to claim 6 or 7, characterized in that the corrective kinematical chain (C) links the wheel (7.1) of the planetary wheel holder (7) to corrector mobile (32) integral with the platform (4) and coaxial with its first axis of rotation (A-A).
9. Mechanism according to claim 8, characterized in that the corrective kinematical chain (C) comprises planetary mobile (13) freely pivoted on the platform (4) along an axis A-A and comprising a first wheel (13.1) meshing with the wheel (7.1) of the planetary wheel holder, and a second wheel (13.2) meshing with a first wheel (32.1) of the corrector mobile (32), and in that a second wheel (32.2) of the corrector mobile (32) meshes with the fixed wheel (14).
10. Mechanism according to one of the preceding claims, characterized in that the axis of the balance (2) is parallel to the first axis of rotation (A-A) of the platform (4).
11. Mechanism according to one of claims 1 to 9, characterized in that the axis of the balance (2) is perpendicular to the first axis of rotation (A-A) of the platform (4).
12. Mechanism according to one of the preceding claims, characterized in that the fourth wheel (9) of the going train of the clockwork movement is placed upon the platform (4).
13. Mechanism according to claim 12, characterized in that the fourth wheel (9) meshes with the escape wheel (3), and its axis is parallel to the axis of the balance (2) and axis of the escape wheel (3).
14. Mechanism according to claim 13, characterized in that the axis of the fourth wheel (9) coincides with the second drive shaft (22), the free end of this shaft holding a seconds hand (23) cooperating with a seconds dial (24) integral with the platform (4) and coaxial with the fourth wheel (9).
15. Mechanism according to one of claims 2 to 14, characterized in that the planetary wheel holder (7) is pivoted on the platform (4).
16. Mechanism according to one of claims 1 or 6, characterized in that the planetary wheel holder (7) is pivoted on the plate (1) of the clockwork movement.
17. Mechanism according to one of the preceding claims, characterized in that the mobile assembly constituted by the platform (4) or by the platform (4) and carriage (30) is used as a winding mass for an automatic winding system of the timepiece.
18. Timepiece provided with a mechanism according to one of claims 1 to 17.

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