EP3483664A1 - Clockwork mechanism for displaying the lunar day and the phase of the moon, with correction system with dual drive train - Google Patents

Abstract

Mechanism (8) watchmaker for displaying the lunar day and the moon phase, in which the moon is represented by a sphere (9) mounted on a meridian wheel, and which comprises: - A first rotating element meshing with a drive mechanism; - A second element (42) rotating frictionally mounted on the first rotating element; - A moon mobile (52) coupling the first rotating element to the meridian wheel; - A jumper wheel (57) (59); - A system (66) for correcting the lunar day display via a first correction wheel bypassing the transmission wheel (57) and comprising the meridian wheel; - A system (66) for correcting the display of the moon phase via a second correction wheel including the transmission wheel (57).

Description

Technical area

• Le jour lunaire, dont la durée sépare deux passages successifs par un méridien donné (qui peut être figuré, dans l'horloge ou la montre équipée du mécanisme, par deux passages successifs à midi) ;
• et la phase de lune, c'est-à-dire la portion (variable) de la lune éclairée par le soleil.

The invention relates to the field of watchmaking. It concerns, more precisely, a mechanism, commonly referred to as an astronomical complication, making it possible to display at the same time:

• The lunar day, the duration of which separates two successive passages by a given meridian (which can be figured, in the clock or watch equipped with the mechanism, by two successive passages at noon);
• and the moon phase, that is, the (variable) portion of the moon illuminated by the sun.

Technological background

The astronomical characteristics of the moon are known for a long time, and described in particular by James Ferguson in "Astronomy Explained on Sir Isaac Newton's Principles", the fifth edition of which was published in 1772 .

The average value of the lunar day (separating two passages on the meridian) is 24 hours, 50 minutes, 28.328 seconds.

The ratio of the solar day to the lunar day is therefore: $$\frac{86400s}{89428,328s}=0,96613682$$

As for the average value of the lunation (duration separating two full moons), it is 29 days, 12 hours, 44 minutes, 2.8 seconds.

Claiming to be inspired by Ferguson, E. Cloux, in his watchmaking course given at the vocational school of the Vallée de Joux in 1949, was drawing a mechanism for displaying the lunar day and the moon phase, superimposed on the solar day (averaging 24 hours).

• Un palier 101 de lune pourvu d'une roue 102 de méridien (à 59 dents) et monté en rotation autour d'un axe X1 principal ;
• Une sphère 103 figurant la lune, montée en rotation par rapport au palier 101 de lune autour d'un axe X2 radial perpendiculaire à l'axe X1 principal, l'axe Y1 radial portant un pignon 104 de lune (à 20 dents) ;
• Un premier élément 105 tournant (à 57 dents) monté en rotation autour de l'axe X1 principal et dont on comprend qu'il doit engrener un mécanisme d'entraînement (non représenté) employé par ailleurs pour l'affichage des minutes et/ou des heures du jour solaire ;
• Un mobile 106 de lune (à deux roues solidaires de 57 dents chacune) couplant en rotation, avec réduction, le premier élément 105 tournant à la roue 102 de méridien ;
• Une roue 107 centrale (à 20 dents), solidaire du premier 105 élément tournant et engrenant le pignon 104 de lune.

The mechanism designed by E. Cloux, represented on the figure 1 , had the following elements:

• A moon bearing 101 provided with a meridian wheel 102 (59 teeth) and rotatably mounted about a main axis X1;
• A sphere 103 in the moon, rotated relative to the moon bearing 101 about a radial axis X2 perpendicular to the main axis X1, the radial axis Y1 carrying a moon gear 104 (20 teeth);
• A first rotating element (57 teeth) rotatably mounted about the main axis X1 and which is understood that it must mesh with a drive mechanism (not shown) used elsewhere for the display of minutes and / or solar daylight hours;
• A mobile moon 106 (with two integral wheels of 57 teeth each) coupling in rotation, with reduction, the first element 105 rotating at the wheel 102 of meridian;
• A central wheel 107 (20 teeth), integral with the first 105 rotating element and meshing with the pinion 104 moon.

This very clever mechanism can display a passage from the moon to the meridian in 24 hours, 50 minutes, 31.58 seconds, and a lunation in 29.5 days.

We see that both are approximations of the average lunar day and the average lunation, imposed by the choice of the gear ratio: $$24h\times \frac{59}{57}=24\mathit{<figure-callout\; id="50"\; label="h"\; filenames="imgf0004.png"\; state="\{\{state\}\}">h</figure-callout>}50\mathit{<figure-callout\; id="31"\; label="min"\; filenames="imgf0003.png,imgf0004.png"\; state="\{\{state\}\}">min</figure-callout>}31,58s$$

However, the mechanism designed by E.Cloux does not include any device that makes corrections to the display visible. necessary either by the drifts resulting from the aforementioned approximations, or, quite simply, by the stopping of the mechanism following the exhaustion of the energy source (most frequently a mainspring in the mechanical watches, which, failing reassembly ends up relaxing completely).

An object of the invention is therefore to provide a solution for simply and reliably correcting the lunar day and lunation in a mechanism as presented above.

Summary of the invention

• un premier élément tournant monté en rotation autour d'un axe principal et engrenant un mécanisme d'entraînement,
• un palier de lune pourvu d'une roue de méridien et monté en rotation autour d'un axe principal,
• une sphère figurant la lune, montée en rotation par rapport au palier de lune autour d'un axe radial perpendiculaire à l'axe principal, l'axe radial portant un pignon de lune,
• un mobile de lune couplant en rotation, avec réduction, le premier élément tournant à la roue de méridien,
• une roue centrale, montée en rotation autour d'un axe principal sur le premier élément tournant et engrenant le pignon de lune,
• un deuxième élément tournant, engrenant le mobile de lune et monté avec friction, à une interface, sur le premier élément tournant pour lui être solidaire en rotation autour de l'axe principal tant que le couple résultant d'efforts circonférentiels différents s'exerçant respectivement sur le premier élément tournant et sur le deuxième élément tournant est inférieur à un couple de friction déterminant la limite d'adhérence à l'interface, le deuxième élément tournant ensemble avec le mobile de lune et le palier de lune formant une première chaîne cinématique en aval du premier élément tournant,
• une roue de transmission, solidaire en rotation de la roue centrale et pourvu extérieurement d'une denture et intérieurement d'au moins un sautoir en prise d'encliquetage avec une roue étoilée solidaire en rotation du deuxième élément tournant, pour coupler en rotation ce deuxième élément tournant avec la roue centrale tant que le couple résultant d'efforts circonférentiels différents s'exerçant respectivement sur la roue étoilée et sur la roue de transmission est inférieur à un couple de saut, au-delà duquel le sautoir est déporté radialement par glissement sur la roue étoilée jusqu'à s'en décliqueter, ledit au moins un sautoir et la roue étoilée étant configurés de sorte que le couple de saut est inférieur audit couple de friction, la roue de transmission ensemble avec la roue centrale et le pignon de lune formant une deuxième chaîne cinématique en aval de la roue étoilée,
• un système de correction de l'affichage du jour lunaire, qui comprend un premier élément d'entraînement apte à présenter au moins momentanément une relation d'engrènement avec la première chaîne cinématique pour forcer la rotation du palier de lune autour de l'axe principal, via un premier rouage de correction formé partiellement par au moins une partie de la première chaîne cinématique, lorsqu'un premier couple de correction, supérieur audit couple de friction, est appliqué à ce premier rouage de correction par un utilisateur, et
• un système de correction de la phase de lune, qui comprend un deuxième élément d'entraînement apte à présenter au moins momentanément une relation d'engrènement avec la deuxième chaîne cinématique pour forcer la rotation de la sphère autour dudit axe radial, via un deuxième rouage de correction formé partiellement par au moins une partie de la deuxième chaîne cinématique et indépendant de la première chaîne cinématique, lorsqu'un deuxième couple de correction, supérieur audit couple de saut, est appliqué à ce deuxième rouage de correction par un utilisateur.

To achieve the aforementioned objective, there is provided a clock mechanism for displaying the lunar day and the moon phase, which comprises:

• a first rotating element rotatably mounted about a main axis and meshing with a drive mechanism,
• a moon bearing provided with a meridian wheel and rotatably mounted about a main axis,
• a sphere representing the moon, mounted in rotation with respect to the moon bearing about a radial axis perpendicular to the main axis, the radial axis carrying a moon gear,
• a moon mobile coupling in rotation, with reduction, the first element rotating at the meridian wheel,
• a central wheel, rotatably mounted about a main axis on the first rotating element and meshing with the moon gear,
• a second rotating element, meshing with the moon wheel and frictionally mounted, at an interface, on the first rotating element to be secured to it in rotation around the main axis as long as the torque resulting from different circumferential forces exerting respectively on the first rotating element and on the second rotating element is less than a friction torque determining the adhesion limit at the interface, the second element rotating together with the moon mobile and the moon bearing forming a first kinematic chain downstream of the first rotating element,
• a transmission wheel, integral in rotation with the central wheel and provided externally with a toothing and internally with at least one jumper in latching engagement with a star-shaped wheel rotating in rotation with the second rotating element, for rotatingly coupling this second element rotating with the central wheel as the resulting torque of different circumferential forces exerted respectively on the star wheel and the transmission wheel is less than a jump torque, beyond which the jumper is radially offset by sliding on the star wheel until unclamped, said at least one jumper and the star wheel being configured so that the jump torque is less than said friction torque, the transmission wheel together with the center wheel and the moon gear forming a second kinematic chain downstream of the star wheel,
• a system for correcting the lunar day display, which comprises a first driving element capable of at least momentarily presenting a meshing relationship with the first kinematic chain to force the rotation of the moon stage around the main axis , via a first correction wheel partially formed by at least a portion of the first kinematic chain, when a first correction torque, greater than said friction torque, is applied to this first correction wheel by a user, and
• a moon phase correction system, which comprises a second driving element adapted to present at least momentarily a meshing relationship with the second kinematic chain to force the rotation of the sphere about said radial axis via a second wheel of correction formed partially by at least a part of the second kinematic chain and independent of the first kinematic chain, when a second correction torque, higher jump torque audit is applied to this second correction wheel by a user.

Thanks to this double correction system, which acts via two distinct kinematic chains, it is possible to simply and reliably correct the display of the lunar day and the moon phase.

• une position de réglage du jour lunaire, dans laquelle le pignon baladeur engrène le mobile de lune pour forcer la rotation du palier de lune autour dudit axe principal via ladite au moins une partie de la première chaîne cinématique ;
• une position de réglage de la phase de lune, dans laquelle le pignon baladeur engrène la roue de transmission pour forcer la rotation de la sphère autour dudit axe radial via ladite au moins une partie de la deuxième chaîne cinématique.

According to a main embodiment, the moon day display correction system and the moon phase correction system comprise a joint correction device for operating the lunar day display and without operating the display. of the lunar day, the moon phase. This joint correction device comprises a sliding pinion which forms only the first and second drive elements, this sliding pinion being adapted to adopt two adjustment positions, namely:

• an adjustment position of the lunar day, wherein the sliding pinion meshes with the moon wheel to force the rotation of the moon bearing about said main axis via said at least a portion of the first kinematic chain;
• a moon phase adjusting position, wherein the sliding pinion meshes with the transmission wheel to force the rotation of the sphere about said radial axis via said at least a portion of the second kinematic chain.

The correction device advantageously comprises a carrier pinion which meshes with the sliding pinion, and at least one connecting rod which couples the axes of rotation of the sliding pinion and the pinion carrier.

The first rotating element comprises for example a toothed wheel which extends perpendicular to the main axis, secured to a barrel which extends along the main axis. As for the second rotating element, it then comprises an auxiliary wheel which extends perpendicularly to the axis main, secured to a socket fitted with friction on the barrel of the first rotating element.

The friction connection between the second rotating element and the first rotating element is advantageously carried out by a lantern, which is for example. in the form of a point deformation of the inside diameter of the tube of the second rotating element, so as to ensure friction on the conical groove formed in the barrel of the first element.

• une roue inférieure, qui engrène la roue auxiliaire du deuxième élément tournant, et
• une roue supérieure, qui engrène la roue de méridien du palier de lune.

According to a preferred embodiment, the moon mobile comprises two superimposed integral wheels, namely:

• a lower wheel, which meshes with the auxiliary wheel of the second rotating element, and
• an upper wheel, which meshes with the meridian wheel of the moon landing.

• la roue auxiliaire du deuxième élément tournant comprend 64 dents,
• la roue inférieure du mobile de lune comprend 43 dents,
• la roue supérieure du mobile de lune comprend 37 dents, et
• la roue de méridien du palier de lune comprend 57 dents.

According to a particular embodiment:

• the auxiliary wheel of the second rotating element comprises 64 teeth,
• the lower wheel of the moon mobile has 43 teeth,
• the upper wheel of the moon mobile includes 37 teeth, and
• the meridian wheel of the moon stage has 57 teeth.

The central wheel preferably has a crown gear meshing with the moon gear; in addition, the central wheel is advantageously fitted on the barrel of the first rotating element.

The moon bearing is, for its part, preferably mounted on the central wheel, being for ex. fitted on it with the interposition of a plain bearing.

The transmission wheel advantageously comprises a pair of diametrically opposed jumpers.

Finally, the star wheel typically comprises 29 or 30 teeth, or in a preferred variant, 59 teeth.

Brief description of the figures

• La figure 1 est une vue en coupe d'un mécanisme connu d'affichage du jour lunaire et de la phase de lune, tel que proposé par E.Cloux;
• la figure 2 est une vue en perspective éclatée illustrant une montre équipée d'un mécanisme d'affichage du jour lunaire et de la phase de lune, selon l'invention ;
• la figure 3 est une vue en perspective, à plus grande échelle, du mécanisme d'affichage de la figure 2 ;
• la figure 4 est une vue en coupe partielle du mécanisme de la figure 3, selon le plan de coupe IV-IV ; dans un médaillon est montré un détail à plus grande échelle ;
• la figure 5 est une vue en plan du mécanisme de la figure 4 (pour rendre visibles des composants sous-jacents, on a retiré le palier de lune) ;
• la figure 6 est une vue d'un détail, à plus grande échelle, du mécanisme, pris à la fois dans le médaillon VI en haut à gauche de la figure 5;
• la figure 7 est une de dessus du mécanisme, illustrant la correction du jour lunaire ;
• la figure 8 est une vue similaire à la figure 5, illustrant la correction de la phase de lune ;
• la figure 9 est une vue d'un détail, à plus grande échelle, du mécanisme, pris dans le médaillon IX en haut à gauche de la figure 8.

Other objects and advantages of the invention will become apparent in the light of the description of an embodiment, given hereinafter with reference to the accompanying drawings, in which:

• The figure 1 is a sectional view of a known mechanism for displaying the lunar day and the moon phase, as proposed by E.Cloux;
• the figure 2 is an exploded perspective view illustrating a watch equipped with a mechanism for displaying the lunar day and the moon phase, according to the invention;
• the figure 3 is a perspective view, on a larger scale, of the display mechanism of the figure 2 ;
• the figure 4 is a partial sectional view of the mechanism of the figure 3 according to section plane IV-IV; in a medallion is shown a detail on a larger scale;
• the figure 5 is a plan view of the mechanism of the figure 4 (to make visible underlying components, the moon bearing was removed);
• the figure 6 is a view of a detail, on a larger scale, of the mechanism, taken at the same time in the medallion VI in the upper left of the figure 5 ;
• the figure 7 is a top of the mechanism, illustrating the correction of the lunar day;
• the figure 8 is a view similar to the figure 5 , illustrating the correction of the moon phase;
• the figure 9 is a view of a detail, on a larger scale, of the mechanism, taken in the medallion IX at the top left of the figure 8 .

Detailed description of the invention

On the figure 2 is represented a timepiece. It could be a clock or a pendulum, but, in the example shown, it is a watch 1 - and more precisely a wristwatch, able to be worn on the wrist. Typically, this watch 1 comprises a housing 2 which includes a middle part 3, a bottom and an ice (not shown), and, fixed on the horns 4 of the middle part, a bracelet 5 for the wrist.

The watch 1 comprises, housed in the case 2, a watch movement 6 which includes a plate 7 and, mounted on the plate, at least one watch mechanism 8 designed to ensure the display of the lunar day and the moon phase .

As will be seen, the mechanism 8 is also designed to display the minutes and the time of the average solar day, but such a display is optional and could be realized by a separate mechanism.

Mechanism 8 belongs to the family of so-called astronomical complications; it is organized around a main axis A1 perpendicular to the general plane of the plate 7.

• révolution autour de l'axe A1 principal pour donner l'indication du jour lunaire ;
• rotation autour d'un axe A3 propre (radial) pour donner l'indication de la phase de lune.

The moon is displayed in volume, in the form of a sphere 9 animated by a double movement:

• revolution around the main A1 axis to give the indication of the lunar day;
• rotation about a proper A3 axis (radial) to give the indication of the moon phase.

According to an embodiment illustrated on the figure 4 , the main axis A1 is materialized by a shaft 10 which, in this example, is formed on a mobile 11 center, itself mounted on the plate 7. This mobile center is here provided with a wheel 12 whose function does not intervene in this frame.

• Une grande roue 14, pourvue d'une denture périphérique comprenant typiquement un nombre de dents Z1=72 ;
• Une roue 15 moyenne, pourvue d'une denture périphérique comprenant typiquement un nombre de dents Z2=24 ;
• Une petite roue 16, pourvue d'une denture périphérique comprenant typiquement un nombre de dents Z3=12.

As we see on the figure 4 , the display mechanism 8 is attacked by a drive mechanism 13, hereinafter referred to as a timer mobile, which comprises a plurality of superposed wheels integral in rotation with a common axis A2 offset relative to the main axis A1 and parallel to this one. In the example shown, the mobile 13 timer comprises three superimposed wheels, namely:

• A large wheel 14, provided with a peripheral toothing typically comprising a number of teeth Z1 = 72;
• An average wheel 15 provided with a peripheral toothing typically comprising a number of teeth Z2 = 24;
• A small wheel 16, provided with a peripheral toothing typically comprising a number of teeth Z3 = 12.

The timer mobile 13 is rotated by a motor device (not shown) including a power source and a transmission. The astronomical complications being customarily associated with the mechanical watches, it is preferable that the energy source is a mainspring associated with a balance spring regulator. Nevertheless, that the energy source is a battery associated with a quartz regulator would not be outside the scope of the present invention.

As discussed, mechanism 8 is designed to display the minutes and times of the average solar day.

For the display of the minutes, the mechanism 8 comprises a roadway 17, mounted in rotation about the main axis A1 and provided with a pinion 18 minutes meshing the big wheel 14, and a tube 19 fitted (with possibility rotation) on the shaft 10 of the mobile 11 center. The floor 17 carries a minute hand 20 which, as illustrated on the figure 4 , is driven on the tube 19 at an upper end thereof. The pinion 18 minutes is provided with a peripheral toothing typically comprising a number of teeth Z4 = 16. The pavement 17 rotates around the main A1 axis in one hour.

For the display of the hours, the mechanism 8 comprises a mobile 21 hours, mounted in rotation about the main axis A1 and provided with a wheel 22 hours meshing the average wheel 15, and a shaft 23 fitted (with possibility rotation) on the tube 19 of the floor 17. The mobile 21 hours carries a 24 hour hand which, as illustrated on the figure 4 , is driven on the shaft 23, at an upper end thereof.

The wheel 22 hours is provided with a peripheral toothing typically comprising a number of teeth Z5 = 64, so that the reduction ratio (that is to say the ratio of rotational speeds) between the wheel 22 hours and the pinion 18 minutes is: $$\frac{Z4}{\mathrm{<figure-callout\; id="1"\; label="Z"\; filenames="imgf0002.png"\; state="\{\{state\}\}">Z</figure-callout>}1}\times \frac{Z2}{\mathrm{<figure-callout\; id="5"\; label="Z"\; filenames="imgf0002.png"\; state="\{\{state\}\}">Z</figure-callout>}5}=\frac{16}{72}\times \frac{24}{64}=\frac{1}{12}$$

In this way, the mobile 21 hours performs a revolution around the main axis A1 in 12 hours.

For the display of the lunar day and the moon phase, the mechanism 8 comprises, firstly, a first rotating member rotatably mounted about the main axis A1 and meshing with the timer wheel 13.

More precisely, in the example illustrated in particular on the figure 4 the first rotating element comprises a gearwheel, called the solar wheel 26 (or 24-hour wheel), which extends perpendicularly to the main axis A1, and a gun 27, integral with the sun gear and which extends according to the main A1 axis.
According to an embodiment illustrated on the figure 4 , the barrel 27 is fitted (with possibility of rotation) on the barrel 23 of the mobile 21 hours.

In the example shown, the barrel 27 is staggered, and comprises a lower stage 28, which is secured to the solar wheel 26, and a higher stage 29, of diameter less than that of the lower stage 28. The lower stage and the upper stage are separated by a shoulder 30.

The solar wheel 26 meshes with the small wheel 16 of the mobile 13 timer. This sun gear is provided with a peripheral toothing typically comprising a number of teeth Z6 = 64, so that the reduction ratio between the first rotating element and the mobile 21 hours is: $$\frac{Z5}{Z2}\times \frac{Z3}{Z6}=\frac{64}{24}\times \frac{12}{64}=\frac{1}{2}$$

In this way, the first rotating element makes a revolution around the main A1 axis in 24 hours. In other words, the first rotating element can serve as a measure of the average solar day. It can be used to display the average solar day. Thus, in the illustrated embodiment (cf. figure 3 ), the first rotating element carries, at an upper end of the upper stage 29 of the barrel 27, a solar needle 31 (also called a 24 hour hand), which, in order to represent the sun, may be round in shape and / or have an opening circular.

The mechanism 8 comprises, secondly, a moon bearing 32 rotatably mounted about the main axis A1. The moon landing is provided with a wheel 33 of meridian. The moon bearing is also provided with a lid 34 moon, fixed on the meridian wheel to be integral in rotation. Alternatively, the meridian wheel and the moon cover form a single piece.

The meridian wheel 33 is provided with a peripheral toothing typically comprising a number of teeth Z7 = 57.

• Un hémisphère 36 sombre (grisé sur les dessins), figurant la portion de la face de la lune non éclairée par le soleil ;
• Un hémisphère 37 clair (blanc sur les dessins), figurant la portion de la lune éclairée par le soleil.

As we see on the figure 4 , the moon bearing 32 is hollow, and has an internal cavity 35 formed in the lid 34 of the moon.
The mechanism 8 comprises, thirdly, a sphere 9 representing the moon, mounted in rotation with respect to the moon bearing 32 about a radial axis A3, perpendicular to the main A1 axis. The sphere 9 advantageously comprises two hemispheres of contrasting colors, namely:

• A dark hemisphere 36 (grayed out in the drawings), showing the portion of the moon's face not illuminated by the sun;
• A clear hemisphere 37 (white on the drawings), showing the portion of the moon illuminated by the sun.

The hemispheres 36, 37 can be made distinct by applying a paint. However, according to a preferred embodiment, the hemispheres are hemispherical caps made of different materials and assembled to form the sphere 9. Thus, the dark hemisphere 36 can be made of biotite mica, obsidian or any other mineral of dark color, while the light hemisphere 37 can be made of metal (eg silver or gray gold), or in a light colored mineral (eg moonstone).

Furthermore, in the example shown, the radial axis A3 is formed by a pin 38 which passes through the sphere 9 and is integral with it in rotation. At an inner end, the spindle is mounted in a sleeve 39 fitted into a hole 40 formed in the moon bearing 32.

As we see on the figure 4 , the radial axis A3 (that is to say the pin 38) carries, at an inner end, a pinion 41 moon, which is integral in rotation. The moon gear is housed in the inner cavity of the moon bearing 32.

The moon gear 41 is provided with a peripheral toothing typically comprising a number of teeth Z8 = 14.

The mechanism 8 comprises, fourthly, a second rotating element 42, rotatably mounted about the main axis A1. According to an embodiment illustrated on the figure 4 , the second rotating element comprises an auxiliary wheel 43, which extends perpendicularly to the main axis A1, and a sleeve 44 integral with the auxiliary wheel and which extends along the axis A1 main. The auxiliary wheel 43 is provided with a peripheral toothing typically comprising a number of teeth Z9 = 64 teeth.

The second rotating element 42 is mounted on the first frictionally rotating element at their interface, denoted 45 (the interface is the surface where the first rotating element and the second rotating element make contact).

More specifically, the sleeve 44 is frictionally fitted on the barrel 27 of the first rotating element. More specifically still, the sleeve is friction-fitted on the lower stage of the barrel. This assembly with friction aims to make the second element 42 rotating (in rotation about the main axis A1) of the first rotating element, as long as the torque, noted C1, resulting from different circumferential forces exerted respectively on the first rotating element and on the second rotating element is less than a friction torque, noted CF, determining the adhesion limit at the interface 45.

• tant que C1 < CF, le premier élément 25 tournant et le deuxième élément 42 tournant sont solidaires en rotation, sans glissement à leur interface 45, et se comportent comme une pièce monobloc ;
• dès lors que C1 ≥ CF, la limite d'adhérence à l'interface 45 entre le premier élément 25 tournant et le deuxième élément 42 tournant est atteinte, et ils se désolidarisent en rotation, de sorte que le deuxième élément tournant peut pivoter indépendamment du premier élément tournant autour de l'axe A1 principal, avec glissement à l'interface 45.

In other words:

• so long as C1 <CF, the first rotating element and the second rotating element 42 are integral in rotation, without sliding at their interface 45, and behave as a single piece;
• when C1 ≥ CF, the adhesion limit at the interface 45 between the first rotating element and the second rotating element 42 is reached, and they dissociate in rotation, so that the second rotating element can pivot independently of the first element rotating around the main axis A1, with sliding at the interface 45.

The friction connection at the interface 45 between the second rotating element and the first rotating element can, in practice, be achieved by a lantern 46, which is for example, as illustrated in the detail medallion of the figure 4 , in the form of a conical groove made in the barrel 27 of the first rotating element.

The second rotating element 42 is provided with a star wheel 47. This star-shaped wheel 47, formed peripherally, is e.g. cut externally in the sleeve 44. It comprises a series of triangular teeth 48, which here are 30 in number but could be 29, or 59 in number (which corresponds to the approximate number of half-days in a row). lunaison).

The mechanism 8 comprises, fifthly, a central wheel 49, mounted on the first element 25 rotating and in gear engagement with the pinion 41 of the moon. This central wheel advantageously has a toothing 50 in a ring (that is to say, whose teeth extend parallel to the main axis A1) engaged by the pinion 41 of the moon. This tooth is e.g. cycloidal and comprises a number of teeth Z10 equal to the number of teeth Z8 of the moon gear (here, Z10 = 14).

In the example shown on the figure 4 the central wheel 49 is fitted on the barrel 27 of the first rotating element. More specifically, the central wheel is fitted on the shoulder 30. The interface between the central wheel and the first rotating element is slippery, so that the central wheel can rotate independently of the first rotating element.

According to a preferred embodiment illustrated on the figure 4 , the moon bearing 32 is mounted on the central wheel 49. To allow rotation of the moon bearing 32 relative to the central wheel, a smooth bearing 51 is interposed between them.

The mechanism 8 comprises, sixthly, a mobile moon 52 which couples in rotation, with reduction, the first element 25 rotating at the meridian wheel 33 (and therefore at the moon bearing 32) to allow the rotation drive of the moon bearing by the first rotating element. More specifically, the mobile 52 moon rotates the second rotating element 42 (integral in rotation of the first element 25 rotating as C1 <CF) to the meridian wheel.

• Une roue 53 inférieure, qui engrène la roue 43 auxiliaire du deuxième élément 42 tournant ;
• Une roue 54 supérieure, qui engrène la roue 33 de méridien du palier 32 de lune.

The mobile moon 52 is remote, mounted in rotation about an axis A4 parallel to the main axis A1. According to an embodiment illustrated on the figure 4 , the moon mobile includes two superimposed solid wheels, namely:

• A lower wheel 53 which meshes with the auxiliary wheel 43 of the second rotating element 42;
• An upper wheel 54, which meshes with the meridian wheel 33 of the moon bearing 32.

The lower wheel 53 is provided with a peripheral toothing typically comprising a number of teeth Z11 = 43. The upper wheel 54 is provided with a peripheral toothing typically comprising a number of teeth Z12 = 37 teeth. In this way, the reduction ratio, denoted R, of the solar wheel 26 to the meridian wheel 33 (equal to the ratio of the speeds of rotation of the moon bearing 32 and the first rotating element) is: $$R=\frac{Z9}{Z11}\times \frac{Z12}{Z7}=\frac{64}{43}\times \frac{37}{57}=0,96613627$$

This reduction ratio provides the value of the average lunar day displayed, noted J: $$J=\frac{24\mathit{h}}{R}=24\mathit{<figure-callout\; id="50"\; label="h"\; filenames="imgf0004.png"\; state="\{\{state\}\}">h</figure-callout>}50\mathit{<figure-callout\; id="28"\; label="min"\; filenames="imgf0004.png"\; state="\{\{state\}\}">min</figure-callout>}28,378s$$

This is an excellent approximation of the actual average lunar day. In fact, the delay of the lunar day displayed on the actual lunar day is only 5 / 100th of a second per solar day (one day late every eight years).

The display of the lunar day is provided by the circular path (that is to say the revolution) of the sphere 9 around the main axis A1. The passage from the moon to the zenith is represented by the passage from sphere 9 to twelve o'clock.

According to a preferred embodiment, illustrated in dotted lines on the figure 3 , the watch is advantageously provided with a bar 55, visible to the wearer, and which is the terrestrial horizon line.

The course of about 180 ° of the sphere 9 above the bar 55 (from the point of view of the carrier) is the course of the moon in the visible sky (lunar day), while the course of 180 ° of the sphere 9 below the bar represents the race of the moon in the non-visible sky (lunar night).

The mobile moon 52 is advantageously mounted on a bridge 56 itself fixed to the plate 7. Its axis A4 rotation is eg. formed by a screw in helical engagement with the bridge 56.

The mechanism 8 comprises, in seventh place, a transmission wheel 57 secured to the central wheel 49, designed to secure it in rotation to the second element 42 rotating in normal operation of the mechanism 8, and to allow on the contrary their relative rotation when correction of the display, under conditions which will be explained below.

The transmission wheel 57 is externally provided with a toothing 58 and internally with at least one jumper 59.

According to an embodiment illustrated on the figure 8 the transmission wheel 57 is provided with a pair of diametrically opposed jumpers 59. This number is not limiting. Thus, three jumpers distributed at 120 ° could be provided.

As illustrated on figure 6 and figure 9 , the (or each) jumper 59 comprises a leaf spring 60 (curve in the example shown), which extends in a notch 61 formed in the wheel 57 of transmission. When seen from above, the spring blade 60 is deployed from a fixed end 61 to a free end 63 in the counterclockwise direction (cf. figure 6 ). The jumper 59 is also provided, at the free end of the leaf spring, a triangular head 64 of size and shape complementary to the space between two teeth 48 adjacent to the star wheel 47.

The (or each) jumper 59 is in latching engagement (by its head 64) with the star wheel 47. In its equilibrium position (in the absence of any constraint), the jumper 59 would occupy a position in which the head 64 would be spaced from the main axis A1 by a distance less than the radius of the star wheel.

In normal operation, the (or each) jumper 59 is latched by its head 64 between two teeth 48 adjacent the star wheel 47. The jumper 59 is held in this position by its own elastic return force which tends to urge the head 64 towards the main axis A1.

In normal operation, the second rotating element 42, integral with the first rotating element (and therefore driven by it in rotation) rotates about the main axis A1 clockwise (when viewed from above). The star wheel 47 therefore exerts on the head 64 of (or each) jumper 59 a force which urges the latter to buttress, which tends to hold the head 64 between two teeth 48 adjacent to the star wheel. Under these conditions, the second rotating element (with the first rotating element) and the transmission wheel 57 (with the central wheel 49) are integral in rotation around the main axis A1, and rotate jointly in the clockwise direction around that -this ( figure 6 ).

The central wheel 49 is made integral with the transmission wheel 57 for example by means of feet 65, formed projecting on the central wheel, driven into holes drilled in the wheel 57 of transmission. Alternatively, this attachment can be made by screwing.

During a correction of the display of the moon phase, a driving torque is applied to the transmission wheel 57 to drive it in rotation around the main axis A1 (counterclockwise when seen from above, cf. . Figure 8 and Figure 9 ), but this rotation is not transmitted by the star wheel 47 to the second rotating element 42.

The second rotating element, frictionally mounted on the first rotating element, opposes a resistance to the rotation of the transmission wheel 57, and C2 is noted the torque resulting from the circumferential forces. different which are exerted respectively on the second rotating element 42 and the wheel 57 transmission.

• demeurer encliqueté avec la roue 47 étoilée tant que le couple C2 est inférieur à un couple CS de saut ;
• être déporté radialement par glissement sur la roue 47 étoilée (et plus précisément par glissement de la tête 64 sur les dents 48) jusqu'à s'en décliqueter, comme illustré en pointillés sur la figure 9, dès lors que le couple C2 est supérieur au couple CS de saut. On notera que ce déport radial est permis par la flexibilité de la lame ressort 60.

It is then that the elasticity of (or) jumpers 56 intervenes. Each jumper 59 is indeed calibrated - that is to say dimensioned - for:

• remain locked with the starwheel 47 as long as the pair C2 is less than a jumping torque CS;
• be radially offset by sliding on the star wheel 47 (and more precisely by sliding the head 64 on the teeth 48) until it is unclipped, as shown in dotted lines on the figure 9 when the pair C2 is greater than the jump pair CS. It will be noted that this radial offset is permitted by the flexibility of the spring blade 60.

The jump CS couple is less than the friction torque CF, that is: $$\mathrm{CS}<\mathrm{CF}$$

As a result, the application of the single pair C2 can never cause the sliding of the second rotating element 42 relative to the first rotating element. The first element and the second rotating element therefore remain integral in rotation (and therefore fixed) during a correction of the moon phase.

In normal operation, the central wheel 49 (with the toothing 50 crown) rotates integrally with the second rotating element (and therefore the first rotating element) due to a complete revolution around the main axis A1 in 24 hours.

Taking into account the reduction ratio R presented above, the moon bearing 32 (with the sphere 9) performs its own complete revolution more slowly (in 24h, 50 min, 28.378 s), and, considering the fact that the pinion 41 lunar moon and the ring gear 50 comprise the same number of teeth (Z8 = Z10), the sphere 9 is driven slowly in rotation about the radial axis A3 (in the clockwise direction when the mechanism 8 is observed by the wafer, in the direction of the radial axis A3).
The sphere 9 performs a complete rotation about its axis A3 in a number L of days corresponding to the value of the displayed lunation, namely: $$\mathrm{The}=\frac{1}{1-R}=29,53012048=29\mathit{j}12\mathit{<figure-callout\; id="43"\; label="h"\; filenames="imgf0004.png,imgf0006.png"\; state="\{\{state\}\}">h</figure-callout>}43\mathit{<figure-callout\; id="22"\; label="min"\; filenames="imgf0004.png"\; state="\{\{state\}\}">min</figure-callout>}22,4\mathit{s}$$

This is an excellent approximation of the actual lunation, with a delay of about 7 minutes per month (ie one day late every 17 years only).

We have seen that the gaps between the displayed lunar day and the actual lunar day, on the one hand, and the displayed moon phase and the actual moon phase on the other hand, are low. A correction of the lunar day and a correction of the lunation would be necessary after uninterrupted operation of the watch 1 for several years.

Moreover, wearers sufficiently diligent not to let the power reserve of a mechanical watch run out are rare. Also the corrections due to the need to readjust the displays after a stop of the watch 1 due to the distraction of the wearer are they more frequent than the corrections due to the need to make up for the delays accumulated by the mechanism 8 during a uninterrupted operation.

To correct the display of the lunar day, the mechanism 8 is equipped with a correction device 66 comprising a pinion 67 capable of meshing the moon mobile 52 to force the rotation of the moon bearing 32 around the main axis A1 via a first correction wheel which bypasses the transmission wheel 57 and which comprises the moon mobile 52 and the meridian wheel 33.
To correct the display of the moon phase, the mechanism 8 is equipped with a correction device 66 which comprises a pinion 67 adapted to mesh the transmission wheel 57 to force the rotation of the sphere 9 around the axis A3 radial via a second train which includes the transmission wheel, the central wheel 49, and the moon gear 41.

The mechanism 8 could include two separate correction devices for separately correcting the lunar day display and the moon phase display. To operate separately, the watch 1 could be equipped with two separate winders that the wearer (or a watchmaker) would handle independently of one another.

However, in a preferred embodiment illustrated in the drawings, and more particularly in the figure 5 , figure 7 and figure 8 the mechanism 8 comprises a single device 66 for correcting the display of the lunar day and the moon phase.

• Une position de réglage du jour lunaire, dans laquelle le pignon 67 baladeur engrène le mobile 52 de lune pour forcer la rotation du palier 32 de lune autour de l'axe A1 principal via la première chaîne cinématique (figure 7) ;
• Une position de réglage de la phase de lune, dans laquelle le pignon 67 baladeur engrène la roue 57 de transmission pour forcer la rotation de la sphère 9 autour de l'axe A3 radial via la deuxième chaîne cinématique (figure 8).

This correction device 66 comprises a sliding gear 67 capable of adopting two adjustment positions, namely:

• A setting position of the lunar day, in which the sliding gear 67 meshes with the moon 52 to force the rotation of the moon bearing 32 around the main axis A1 via the first kinematic chain ( figure 7 );
• A setting position of the moon phase, in which the sliding gear 67 engages the transmission wheel 57 to force the rotation of the sphere 9 about the radial axis A3 via the second kinematic chain ( figure 8 ).

In the example shown on the figure 7 and figure 8 , the correction device 66 comprises a carrier pinion 68 which meshes with the sliding pinion 67, and at least one connecting rod 69 which couples the axes of rotation of the sliding pinion and the pinion. In practice, the correction device 66 comprises a pair of superimposed rods 69, arranged on either side of the carrier pinion and the sliding pinion.

The pinion 68 carrier is mounted on the bridge 56 in rotation about an axis A5 parallel to the main axis A1 and advantageously formed by a screw helically engaged with the bridge 56.

The correction device 66 comprises a winding device 70 provided with a rod 71 pivotally mounted around and along a winding axis A6 perpendicular to the main axis A1, and a ring 72 integral in rotation with the stem. 71. The rod passes through the middle part 3, the crown being accessible to the wearer.

According to a particular embodiment illustrated on the figure 8 , the correction device 66 comprises a gearwheel gear (hereinafter more simply referred to as a 73 phase gear) which meshes with the transmission wheel 57 and via which, in the moon phase adjustment position, the gearwheel 67 walkman meshes the transmission wheel. The phase deflection is rotatably mounted on the bridge about an axis A7 in the form of a screw in helical engagement with the bridge 56.

• une position de correction (figure 7 et figure 8) dans laquelle le pignon 76 coulant est accouplé au pignon 68 porteur, et
• une position de libération dans laquelle le pignon 76 coulant est désaccouplé du pignon 68 porteur (et dans laquelle le pignon 75 de remontoir est accouplé à un pignon de remontoir non représenté, via lequel le ressort de barillet de la montre 1 est réarmé par rotation de la couronne 72 de remontoir).

The correction device 66 also comprises a shuttle 74 provided with a winding pinion 75 (eg with a Breguet toothing) and a sliding pinion 76 mounted pivotally around and along the winding axis A6. and coupled to the winder 70 e.g. by a conventional pull-and-tilt mechanism (not shown), between:

• a correction position ( figure 7 and figure 8 ) in which the sliding pinion 76 is coupled to the pinion 68 carrying, and
• a release position in which the sliding pinion 76 is uncoupled from the pinion 68 carrier (and in which the winding pinion 75 is coupled to a not shown winding pinion, via which the mainspring of the watch 1 is rearmed by rotation of the winding crown 72).

The transmission of the rotation of the winding 70 to the pinion 68 carrier is advantageously via a gear train, which typically comprises a first reference 77, meshing with the pinion 76 flowing, and a second reference 78, interposed between the first reference and the pinion carrier.

Finally, according to an embodiment illustrated in particular on figure 2 and figure 4 the mechanism 8 comprises a cover 79 in the form of a disc integral with the moon bearing 32 (and, for example, sandwiched between the meridian wheel 33 and the moon cover 34). The cover 79 has an opening 80 with a circular contour in which the sphere 9 is housed. This cover, which rotates with the moon bearing 32, is intended to symbolize the celestial vault. For this purpose, in the example shown, the cover 79 carries symbols 81 (engraved, painted, or formed protruding) constituting a starry constellation.

The correction of the display of the lunar day induces a rotation of the sphere 9 about its axis A3 and consequently a modification of the display of the moon phase. This is why the correction of the lunar day display must precede the correction of the display of the moon phase.

Before any correction, it is appropriate to place the shuttle 74 in the correction position, pulling (in a conventional manner for the wearer or watchmaker) on the winding crown 72, which pushes the pinion 76 flowing towards the first return 77 to put them in gear.

To correct the display of the lunar day, the winding crown 72 must be rotated in a specific direction which depends on the number of gears in the gear train 77, 78. In the embodiment illustrated in FIG. figure 7 , the winding crown must be turned clockwise when viewed along the winding axis A6.

The rotation of the crown 72 of winding then drives, via the gear train 77, 78, the pinion 68 carrier clockwise (when viewed from above), which tends to rotate the rods 69 also clockwise and causes (or maintains) the gearing of the sliding gear 67 with the moon 52 mobile.

• Le pignon 67 baladeur, engrené par le pignon 68 porteur, dans le sens antihoraire,
• Le mobile 52 de lune, engrené par le pignon 67 baladeur, dans le sens horaire,
• Le palier 32 de lune, dont la roue 33 de méridien est engrenée par la roue 54 supérieure du mobile de lune, dans le sens antihoraire.

Il en résulte que la sphère 9 est entraînée dans un mouvement de révolution autour de l'axe A1 principal dans le sens antihoraire. Tous ces mouvements sont illustrés par des flèches sur la figure 7.The clockwise rotation of the carrier pinion 68 then drives successively in rotation:

• The sliding gear 67, meshing with the pinion 68 bearing, counterclockwise,
• The mobile 52 moon, geared by the pinion 67 walkman, clockwise,
• The moon bearing 32, whose meridian wheel 33 is engaged by the upper wheel 54 of the moon wheel, counterclockwise.

As a result, the sphere 9 is driven in a revolution movement around the main axis A1 counterclockwise. All these movements are illustrated by arrows on the figure 7 .

It will be noted that, during the correction of the lunar day, the resulting torque C2 exerted on the auxiliary wheel 43 exceeds the friction torque CF, so that while the first rotating element remains fixed in rotation around the A1 axis (because it is blocked by the mobile 13 timer), the lantern 46 gives way and allows the sliding of the auxiliary wheel relative to the barrel 27 at their interface 45.

The rotation of the winding crown 72 is stopped when the angular position of the radial axis A3 of the sphere 9 around the main axis A1 is decreed correct, which completes the correction of the lunar day display.

It is then necessary to correct the display of the moon phase. To do this, the winding crown 72 must be turned in the opposite direction of the direction followed during the correction of the display of the lunar day. In the example shown on the figure 8 , the winding crown 72 must be rotated counterclockwise when viewed along the winding axis A6.

The rotation of the winding crown 72 drives, via the gear train 77, 78, the pinion 68 carrier counterclockwise (when seen from above), which causes the links 69 to swing counterclockwise to cause the gear take-off of the sliding gear 67 with the phase gear 73.

• Le pignon 67 baladeur, engrené par le pignon 68 porteur, dans le sens horaire,
• Le renvoi 73 de phase, engrené par le pignon baladeur, dans le sens antihoraire.

The rotation of the crown 72 of winding continuing, the counterclockwise rotation of the pinion 68 carrier successively rotates:

• The sliding gear 67, meshing with the pinion 68 carrying, clockwise,
• The return 73 phase, geared by the sliding gear, counterclockwise.

As soon as the torque C2 reaches the breakaway torque CS (which the fingers of the wearer or the watchmaker are able to produce), the transmission wheel 57, the gearing 58 of which is engaged by the phase gear 73, is itself rotated in the clockwise direction. All these movements are illustrated by arrows on the figure 8 .

However, the jump CS couple is less than the friction torque CF of the second member 42 rotating on the first rotating member. Therefore, despite the rotation of the transmission wheel 57, the second rotating element remains fixed because it is integral in rotation with the first rotating element, which is blocked by the mobile 13 timer.

Consequently, the jumper (s) 59 is (are) radially offset and jumps (s) from one tooth to the other as the transmission wheel 57 is rotated, as illustrated in dotted lines on the figure 9 .

The central wheel 49, integral in rotation with the transmission wheel 57, is driven, with its toothing 50, in rotation about the axis A1 in the clockwise direction. As the moon bearing 32 remains stationary, this rotation of the central wheel causes, via the moon pinion 41 which it meshes, the rotation of the sphere 9 around its radial axis A3, in the clockwise direction (when viewed according to the axis A3). In a first variant, for example by adding an additional mobile to the moon phase correction gear train between the transmission wheel and the sliding pinion, the sphere then rotates counterclockwise, which corresponds to its direction of rotation during operation. normal. In a second variant, by accepting during a correction of lunar day that the sphere 9 is driven in a revolution movement about the main axis A1 in the clockwise direction, then the additional mobile can be introduced into the kinematic chain of the correction device 66. As an alternative, in a third variant, it is provided to remove a mobile in the kinematic chain of the correction device 66. Finally, it is also possible to obtain a correction of the moon phase by inverting the relative position of the moon wheel and the transmission wheel, the correction of the moon phase being thus performed by a rotation of the crown in the clockwise while the correction of the lunar day is performed by a rotation of the crown counterclockwise.

When the star wheel 47 comprises 29 or 30 teeth, each jump of the jumper (s) 59 from one tooth 48 to the other corresponds to a correction of one day. When the star wheel comprises 59 teeth, each jump of the jumper (s) from one tooth to the other corresponds to a correction of half a day. The wearer or watchmaker is warned of this correction (of a day or, respectively, half a day) by the sound click accompanying the jump of the jumper (s).

Once the corrections of the display of the lunar day and the display of the moon phase have been completed, the wearer pushes the winding crown 72, which translates the shuttle 74 by uncoupling the sprocket 76 flowing from the first return 77.

During the normal operation of the watch 1, it is not a problem that the sliding gear 67 remains meshing with the mobile 52 of the moon (as shown in FIG. figure 5 ) or with the return 73 of phase, since the winder 70 is uncoupled from the pinion 68 carrier.

It can be seen that the correction device 66 presented above makes it possible, in a simple, effective, precise and reliable manner, to correct the lunar day and the moon phase in the mechanism 8. For the wearer or the watchmaker, only the meaning rotation determines the applied correction.

Claims (15)

Mechanism (8) watchmaker of the lunar day and the moon phase, which includes: a first rotating element (25) rotatably mounted around a main axis (A1) and meshing with a drive mechanism (13), a moon bearing (32) provided with a meridian wheel (33) and rotatably mounted about the main axis (A1), a sphere (9) representing the moon, mounted in rotation with respect to the moon bearing about a radial axis (A3) perpendicular to the main axis, the radial axis carrying a moon pinion (41), - a mobile moon (52) coupling in rotation, with reduction, the first element rotating at the meridian wheel, - a wheel (49) central, rotatably mounted about the main axis (A1) on the first rotating element and meshing the moon gear; this mechanism (8) being characterized in that it comprises: - a second element (42) rotating, meshing the mobile (52) moon and mounted with friction, to an interface (45) on the first element (25) rotating to be secured to it in rotation about the axis (A1 ) as long as the torque (C1) resulting from different circumferential stresses exerted respectively on the first rotating element and the second rotating element is less than a friction torque (CF) determining the adhesion limit at the interface (45), the second element rotating together with the moon mobile and the moon bearing forming a first kinematic chain downstream of the first rotating element, - A transmission wheel (57) integral in rotation with the wheel (49) and provided externally with a toothing (58) and internally at least one jumper (59) in latching engagement with a wheel (47). starry integral in rotation with the second rotating element, for rotatingly coupling this second rotating element with the central wheel as long as the torque (C2) resulting from different circumferential forces acting respectively on the star wheel and the transmission wheel (57). is less than a jumping torque (CS), beyond which the jumper (59) is radially offset by sliding on the star wheel (47) until it is unclipped, said at least one jumper and the star wheel being configured so that the jump torque is less than said friction torque, the transmission wheel together with the center wheel and the moon gear forming a second kinematic chain downstream of the star wheel, a system for correcting the display of the lunar day, which comprises a first driving element (67) capable of presenting, at least momentarily, a meshing relationship with said first kinematic chain for forcing the rotation of the bearing (32) of moon around the main axis (A1), via a first correction wheel formed partially by at least a portion of the first kinematic chain, when a first correction torque, greater than said friction torque, is applied to this first gear correction by a user, and a moon phase correction system, which comprises a second driving element (67) capable of presenting at least one momentarily a meshing relationship with said second kinematic chain in order to force the rotation of the sphere (9) around the radial axis (A3), via a second correction wheel partially formed by at least a part of the second kinematic chain and independent of the first kinematic chain, when a second correction torque, greater than said jump torque, is applied to this second correction wheel by a user. Mechanism (8) according to claim 1, characterized in that the system for correcting the lunar day display and the moon phase correction system comprise a correction device (66). joint for activating the display of the lunar day and, without activating the moon day display, the moon phase, this joint correction device comprising a sliding pinion (67) which forms only the first and second drive elements, this sliding pinion being adapted to adopt two adjustment positions, namely: an adjustment position of the lunar day, in which the sliding pinion meshes with the moon mobile (52) to force the rotation of the moon bearing (32) around the main axis (A1) via said at least part of the first kinematic chain; a position for adjusting the phase, in which the sliding pinion meshes with the transmission wheel (57) to force the rotation of the sphere (9) around the radial axis (A1) via said at least part of the second kinematic chain. Mechanism (8) according to claim 2, characterized in that the device (66) of joint correction comprises a pinion (68) carrier which meshes the pinion (67) sliding, and at least one rod (69) which couples the axes of rotation of the sliding gear (67) and the drive gear. Mechanism (8) according to any one of the preceding claims, characterized in that the star wheel (47) and the second rotating element (42) are coaxial and integral; and in that the transmission wheel (57) and the central wheel (49) are coaxial and integral. Mechanism (8) according to any one of the preceding claims, characterized in that the first driving element is adapted to mesh the moon mobile at least during a correction of the lunar day display; and in that the second driving element is capable of meshing the transmission wheel at least during a correction of the moon phase. Mechanism (8) according to any one of the preceding claims, characterized in that the first element (25) rotating comprises a toothed wheel (26) which extends perpendicular to the main axis (A1), integral with a barrel (27) which extends along the main axis. Mechanism (8) according to claim 6, characterized in that the second rotating element (42) comprises an auxiliary wheel (43), which extends perpendicular to the main axis (A1), integral with a sleeve (44) frictionally fitted on the barrel (27) of the first element (25) rotating. Mechanism (8) according to claim 7, characterized in that the mobile (52) moon comprises two superimposed integral wheels, namely: - A lower wheel (53), which meshes the wheel (43) auxiliary second element (42) rotating; - An upper wheel (54) which meshes with the meridian wheel (33) of the moon bearing (32). Mechanism (8) according to claim 8, characterized in that : the auxiliary wheel of the second rotating element comprises 64 teeth, the lower wheel of the moon wheel includes 43 teeth, the upper wheel of the moon mobile comprises 37 teeth, - The meridian wheel of the moon stage comprises 57 teeth. Mechanism (8) according to any one of the preceding claims, characterized in that the wheel (49) carries a center gear (50) engaged by the pinion (41) moon. Mechanism (8) according to any one of the preceding claims, characterized in that the central wheel (49) is mounted free to rotate on the first element (25) rotating. Mechanism (8) according to any one of the preceding claims, characterized in that the moon bearing (32) is rotatably mounted on the central wheel (49). Mechanism (8) according to claim 12, characterized in that the bearing (32) of the moon is fitted on the central wheel with the interposition of a bearing (51) smooth. Mechanism (8) according to any one of the preceding claims, characterized in that the transmission wheel (57) comprises a pair of diametrically opposed jumpers (59). Mechanism (8) according to any one of the preceding claims, characterized in that the star wheel (47) comprises 29, 30 or 59 teeth.

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