Coupling device for clock mechanism

Description

[0001] The invention relates to a pivoting member or watch lever. It also relates to a clutch device, in particular a unidirectional coupling device provided for engaging a first gear train with at least one second gear train, the device comprising such a lever. Finally, it relates to a watch movement or a timepiece, in particular a watch, comprising such a lever or such a clutch device.

[0002] Unidirectional coupling devices intended to engage a first gear train with at least one second gear train of a watch movement are known. Such devices are particularly known within correction or winding mechanisms of a watch movement.

[0003] By unidirectional coupling device, we mean a device that generally comprises two transmission wheels, one driving, the other driven, which are secured in one direction of rotation and disengage in the other. To achieve this, a degree of freedom conferred on the driving wheel makes it possible to vary the center distance of the two wheels and thus to achieve the meshing of the driven wheel according to the direction of rotation of the driving wheel. Solutions are known in which the driving wheel, possibly coupled to a clutch spring, is pivoted within a cutout or on a rocker so as to move its pivot axis relative to that of the driven wheel. These designs are however not optimal with regard to their reliability, their robustness, their size, or their assembly method.

[0004] Patent application EP1925996A1 discloses a unidirectional coupling device used in a rapid correction mechanism for two calendar indications. This consists of an intermediate correction wheel driven by a winding stem which is engaged with a correction sliding pinion arranged within a curved oblong cutout. Thus, the sliding pinion is capable of moving from a first stable correction position of a first display member to a second stable correction position of a second display member depending on the direction of rotation of the winding stem. Such a solution has the advantage of requiring few components. However, it is dependent on a significant number of assembly clearances. Thus, the axial and radial play of the correction pinion is particularly difficult to control.As a result, the pivoting torque of the sliding pinion is variable, to the point that its pivot may not be moved under the effect of reversing the direction of rotation of the winding stem, and may not allow one or other of the two correction functions.

[0005] One solution is to add a clutch spring, or friction spring, to the sliding pinion in order to ensure sufficient torque to allow the sliding pinion to move by torque effect due to its direction of rotation. This solution has the advantage of generating torque to the corrector independently of the way in which it is pivoted. However, it does not guarantee the axial and radial positioning of the corrector relative to its environment. Furthermore, this coupling device has the disadvantage of being bulky and not being able to be assembled independently of a large number of components of the watch movement. Thus, this coupling device can only be tested and validated once the movement assembly procedure is well underway.

[0006] One solution consists of pivoting a corrector pinion on a clutch lever whose axis of rotation coincides with that of the wheel which is engaged with this corrector pinion. Thus, the radial and axial play of this pinion is controlled by assembly means constituting the clutch lever. Application CH703697A2 discloses a correction device within which the correctors are pivoted on a lever of this type. The document specifies that it is the friction occurring between this lever and one of the correction wheels which makes it possible to bring the lever into one or other of these extreme correction positions depending on the direction of rotation of the corrector. However, it seems that conventional assembly means do not allow friction to be adequately controlled to the point of making such a coupling device reliable.As a result, the pivoting torques of the correctors are variable, to the point that the pivots may not be moved under the effect of reversing the direction of rotation of the winding stem, and may not allow one or other of the two correction functions.

[0007] One solution is therefore to place a friction shim at the pivot axis of the corrector so as to hold the latter against the rocker by imparting an axial support force to it, and thus guarantee adequate friction between the rocker and the corrector. Although this solution makes it possible to overcome the aforementioned drawbacks, it nevertheless seems not very robust in view of the manufacturing tolerances inherent in this type of spring, the number of parts involved in this assembly, and the assembly tolerances which must be particularly tight due to the mounting method of this spring.

[0008] Document JP S54118860 U discloses a clutch device which allows the meshing of a first wheel with a mobile external to the device.

[0009] Document US325536 discloses a device for implementing a winding mechanism in which the pivot axis of a ratchet drive wheel is guided on a clutch lever, and braked by a friction spring applying a radial force thereto. More particularly, an annular receiving surface formed on the lever is provided to guide in rotation a cylindrical pivot portion of the ratchet drive wheel, while a leaf spring, manufactured in one piece with the lever, is provided to press this cylindrical portion of the ratchet drive wheel against said receiving surface. A rotation of the winding stem in a first direction of rotation induces the rotation of the ratchet by driving the ratchet drive wheel, and therefore the winding of the barrel spring. In this configuration, the ratchet drive wheel is guided by the receiving surface of the lever under the effect of the leaf spring.In a second direction of rotation of the winding stem, the leaf spring flexes under the effect of the reversal of the direction of rotation of the ratchet drive wheel, so that the latter is disengaged from the ratchet. In this configuration, the ratchet drive wheel is no longer in contact with the receiving surface of the lever, and its rotational guidance is thus degraded. Furthermore, the disengagement of the winding mechanism is not generated by the rotation of the clutch lever, but rather by the flexing of the leaf spring which gives a degree of freedom to the ratchet drive wheel. In view of the state of the art, there is no simple solution making it possible to propose a unidirectional coupling device whose driving wheel, for example a corrector pinion, is pivoted in such a way that its guidance, as well as its pivoting torque, are perfectly controlled.Furthermore, there is no simple solution for optimizing, in particular increasing, the resistant or resistive torque opposing the pivoting of the drive wheel in order to guarantee the proper functioning of the one-way coupling device.

[0010] The aim of the invention is to provide a clutch device making it possible to overcome the drawbacks mentioned above and to improve the known rockers of the prior art. In particular, the invention proposes a solution making it possible to produce a unidirectional coupling device in a simple, reliable and robust manner, in particular for a correction or winding mechanism.

[0011] A device according to the invention is defined by independent claims 1, 4, 18 and 19.

[0012] Different embodiments of the device are defined by claims 2, 3, 5 to 17.

[0013] In the various embodiments and / or variants, at least one bearing surface of the at least one friction element can be produced by a flank portion of the slot.

[0014] In the various embodiments and / or variants, at least one friction element may comprise at least one bearing surface, in particular two or three or four bearing surfaces, in particular at least one point bearing surface, in particular two or three or four point bearing surfaces.

[0015] In the various embodiments and / or variants, the rocker may comprise two bearing surfaces, at least one of the bearing surfaces being at least generally concave to match the shape of the first mobile, in particular the shape of the at least substantially cylindrical portion of the first mobile.

[0016] In the various embodiments and / or variants, the at least one elastic element is preferably made: made of steel, especially Durnico steel, or CuBe2 alloy, or nickel or nickel-phosphorus, or silicon.

[0017] The attached drawings represent, by way of example, three embodiments of a scale according to the invention. THE figures 1 et 2 are top views of a first embodiment of a clockwork movement comprising a first embodiment of a clutch device provided with a first embodiment of a lever. The figure 3 is a sectional view of the first embodiment of the rocker according to a plane III-III of the figure 4 . There figure 4 is a sectional view of the first embodiment of the rocker according to a plane IV-IV of the figure 3 . There figure 5 is a sectional view of the first embodiment of the clutch device according to a plane VV of the figure 2 . There figure 6 is a bottom view of the first embodiment of the clockwork movement. The figure 7 is a top view of the first embodiment of the clockwork movement comprising the first embodiment of the clutch device provided with a variant of the first embodiment of the lever. figure 8 is a top view of the first embodiment of the clockwork movement comprising the first embodiment of the clutch device provided with a variant of the first embodiment of the clutch lever which is locked in a neutral angular position. figure 9 is a detailed view of the first embodiment of the clockwork movement comprising the first embodiment of the clutch device provided with a variant of the first embodiment, the clutch lever being positioned in an adjustment position of the clockwork movement. figure 10 is a view of a variant of the first embodiment of the device according to the invention. The figure 11 is a view of a second embodiment of the device according to the invention. The figure 12 is a sectional view of the second embodiment of the device according to the invention according to a plane XII-XII of the figure 11 . There figure 13 is a view of a third embodiment of the device according to the invention. The figure 14 is a sectional view of a third embodiment of the device according to the invention according to a plane XIV-XIV of the figure 13 .

[0018] A first embodiment of a clockwork movement 8 according to the invention is described below with reference to figures 1 et 2 The movement preferably includes a calendar corrector mechanism 9 provided to correct, for example, the date and day of the week indications.

[0019] The correction mechanism may comprise a correction wheel set 1 acting as a driving wheel set capable of selectively engaging with two driven wheels to produce two separate unidirectional coupling devices. This correction wheel set is an integral part of a correction kinematic chain which is driven by the rotation of a control stem 5 of a conventional calendar movement when the latter is positioned in a predefined axial position, via a clutch device 7.

[0020] The correction kinematic chain consists of a control pinion 4 which is rotationally fixed to the control rod 5, an intermediate return 3, and an intermediate correction return 2 which is engaged with the correction wheel set 1. The wheel set 1 comprises a first shaft 11. The wheel set 2 rotates around a second shaft 21.

[0021] This correction wheel set 1 is capable of moving from a first stable position for correcting the dates 10 to a second stable position for correcting the day indication 100 depending on the direction of rotation of the stem 5. More particularly, when the stem is driven in a clockwise direction, a date corrector 1a of the correction wheel set 1 is positioned so that its teeth can drive a toothing of a date disc Dq. When the stem is driven in a counterclockwise direction, a correction wheel 1b of the wheel set 1 is positioned so that its teeth can drive the kinematic chain for correcting the day indication in order to rotate the day disc Dj.

[0022] In a preferred embodiment shown in figures 1 et 2 , the correction mobile 1 is pivoted on a clutch rocker 6 which is designed to combine the functions of coupling rocker, or horizontal clutch rocker, and also that of friction spring. More particularly, this rocker is shaped so as to pivot the mobile 1 while imparting to it a radial or substantially radial clamping force, which, due to a friction phenomenon, creates a braking or friction torque opposing the rotation of the correction mobile 1 relative to the rocker and thus drives this rocker in rotation.

[0023] As represented in the figures 3 à 6 , the lever 6 comprises at least a first element 61 for guiding the rotation of the first mobile 1, in particular the correction mobile 1, in particular the first shaft 11 of the first mobile 1, at least one friction element 62 intended to cooperate with an at least substantially cylindrical portion 10c of the first mobile, in particular the first shaft 11 of the first mobile, and at least one elastic element 63 intended to elastically return the at least one friction element into a state of cooperation with the portion of the first mobile, in particular in contact with the portion of the first mobile.

[0024] The at least one friction element applies at least one radial or substantially radial force to the first shaft portion of the first mobile, in order to produce the braking or friction torque opposing the rotation of the correction mobile 1 relative to the rocker.

[0025] In the first embodiment, the rotational guide element and the at least one friction element are merged.

[0026] The rocker 6 is provided with two elastic arms 6a, 6b which, once elastically deformed, are provided to receive the first shaft 11 of the correction wheel set 1 and define its pivot axis 1d. The arms preferably extend longitudinally to one end of the rocker. The arms are separated from each other by an opening 6d, in particular a slot-shaped opening, in particular a slot-shaped through opening. This opening 6d makes it possible to receive the first shaft 11. This opening preferably extends from the previously mentioned end. Each of the two elastic arms comprises at least one bearing surface 60a, 60b, 60c, 60d intended to cooperate with the cylindrical portion 10c of the shaft 11.Preferably, each of the two elastic arms comprises at least one bearing surface 60a, 60b, 60c, 60d intended to cooperate punctually with the cylindrical portion 10c of the shaft 11 (i.e. according to a point of contact or according to a surface of limited area). Thus, the axis of rotation 1d of the mobile 1 is advantageously defined unequivocally by at least two bearing surfaces intended to cooperate punctually (i.e. according to a point of contact) with the cylindrical portion 10c of the shaft 11. Preferably, there are two bearing surfaces 60a, 60b and 60c, 60d on each of the elastic arms 6a, 6b. The bearing surfaces are, for example, bosses made on the arms, but can also be confused with the arms. In other words, the bearing surfaces have, for example, a negative radius of curvature on the side of the opening 6d which is substantially distinct from the radius of curvature of the arms.The radii of curvature of the bearing surfaces may also be the same as the radii of curvature of the arms. Alternatively, the bearing surfaces may be rectilinear, i.e., they may have an infinite radius of curvature. Alternatively, the bearing surfaces may have a positive radius of curvature. The bearing surfaces of each of the arms are, for example, symmetrical to each other with respect to an axis of symmetry S of the opening 6d of the rocker 6. The elastic arms 6a, 6b are, for example, symmetrical to each other with respect to the axis of symmetry S of the opening 6d of the rocker 6. Preferably, this symmetry is maintained regardless of the degree of opening of the arms 6a, 6b. Thus, the axis of rotation 1d of the mobile 1 is defined unequivocally, regardless of the variations in diameter of the cylindrical portion 10c of the shaft 11, and therefore of the elastic deformation of the arms 6a, 6b.This definition is obtained by the geometry of the arms and the bearing surfaces which cooperate by contact on the cylindrical portion 10c. This definition is such that the axis 1d is positioned at the appropriate location allowing the correct operation of the gearing of the correction wheel set 1 with the intermediate correction return wheel set 2. Thus, the center distance between the wheels 1 and 2 is determined independently of the variations in diameter of the cylindrical portion 10c of the shaft 11. The tightening torque of the cylindrical portion 10c is, for its part, controlled by the elastic properties and the pre-arming of the arms 6a and 6b.

[0027] Advantageously, each of the ends 60e, 60f of the respective elastic arms 6a, 6b is shaped to allow the engagement of the shaft 11 of the mobile 1 within the opening 6d of the rocker 6, in particular the engagement of the portion 10c of the shaft within the opening 6d of the rocker 6, and thus allow the cooperation of the bearing surfaces 60a, 60b, 60c, 60d with the shaft 11, while adequately pre-arming the arms 6a and 6b of the spring 6. In particular, the two ends form a V allowing the engagement of the first mobile by elastically deforming the arms. The ends of the arms can be rounded for this purpose.

[0028] Preferably, the portion 10c of the shaft 11 which is in contact with the bearing surfaces 60a, 60b, 60c, 60d is delimited by bearing surfaces 10d, 10e which axially hold the correction wheel set 1. Thus, this correction wheel set 1 can be pre-assembled on the lever 6 before mounting the movement, and be guided by a frame 7a, 7b of the clockwork movement after mounting within the movement. In an alternative embodiment, the bearing surfaces 10d, 10e can also define an axial clearance of the correction wheel set 1 in operation.

[0029] In this first embodiment, an opening 66, in particular a bore, formed on the rocker 6 is also provided so as to radially guide the rocker and pivot it around an axis of rotation 6f which coincides with that of the intermediate correction return 2. Thus, the rocker comprises a second element 66 for guiding the rocker in rotation around the second shaft 21.

[0030] In this first embodiment, the rocker comprises two guide elements 61, i.e. one guide element on each of the arms. Each guide element comprises, for example, two bosses whose bearing surfaces 60a, 60b, 60c and 60d are intended to cooperate by contact with the cylindrical portion 10c. Preferably, the bearing surfaces 60a, 60b, 60c and 60d are intended to cooperate by point contact with the cylindrical portion 10c. Thus, thanks to these contacts, the shaft 11 of the first mobile 1 can be guided in rotation around the axis 1d.

[0031] In this first embodiment, the rocker comprises two friction elements 62, i.e. one friction element 62 on each of the arms. Preferably, each friction element comprises two bosses whose bearing surfaces 60a, 60b, 60c and 60d are intended to cooperate by contact with the cylindrical portion 10c. The friction elements are produced on the flanks of the slot, in particular, the bearing surfaces of the friction elements are produced by flank portions of the slot. Each friction element comprises two bearing surfaces 60a, 60b and 60c, 60d. At the contacts, radial or substantially radial forces are applied to the cylindrical portion 10c. When the mobile 1 is rotated, these forces create a mechanical friction torque opposing the rotation of the mobile 1.The intensity of this torque is determined by the coefficient of friction of the bearing surfaces on the portion 10c and by the intensity of the forces exerted. This intensity of the forces is itself determined by the at least one elastic element 63 intended to elastically return the at least one friction element into contact with the portion 10c of the first shaft 11.

[0032] In this first embodiment, the rocker comprises two elastic elements 63 intended to elastically return the at least one friction element into contact with the portion 10c of the first shaft. Thus, each elastic element comprises an arm 6a, 6b. As seen previously, the arms are delimited by sides of the slot. The geometries of the arms 6a, 6b are of course defined so as to generate admissible and minimized stresses for the material constituting them. The thickness and the shape of these arms 6a, 6b are defined, for example, following an optimization carried out using a digital simulation program such as ANSYS.

[0033] The arms are made of any suitable material, such as steel, for example Durnico steel, i.e., a nickel, cobalt, and molybdenum steel, or CuBe2. They can also be made of, for example, nickel, nickel-phosphorus, or silicon. These arms can be manufactured, for example, using conventional machining techniques such as stamping, wire cutting, or laser cutting. They can also be manufactured using well-known micro-fabrication techniques, such as UV-LIGA or DRIE processes.

[0034] In the first embodiment, the rocker 6 is preferably a single piece. By "single piece" is meant that the rocker 6 is manufactured in one piece. The entire rocker is therefore made with the material constituting the arms. The rocker can thus be produced as described in the previous paragraph. The rocker is in this case preferably made of elastic material and can also be referred to as a spring.

[0035] Preferably, the rocker 6 is flat. However, it is conceivable to implement a stepped rocker so as to optimize the elasticity of the arms 6a, 6b in a given construction context.

[0036] In the first embodiment described, the rocker therefore comprises two friction elements each comprising two bearing surfaces 60a, 60b, 60c, 60d. The rocker thus comprises four bearing surfaces. In alternative embodiments, the number of these bearing surfaces can of course be different. The rocker may in particular have three bearing surfaces, or even two bearing surfaces, or even a single bearing surface. In the latter case, another means is provided to ensure the rotational guidance of the first shaft.

[0037] In the first embodiment described, the rocker comprises two guide elements each comprising two bearing surfaces 60a, 60b, 60c, 60d. The rocker therefore comprises four bearing surfaces providing the guidance. In alternative embodiments, the number of these bearing surfaces can of course be different. The rocker may in particular have three bearing surfaces, or even two bearing surfaces. In the latter case, at least one of the two bearing surfaces has an at least generally concave shape to match the shape of the first shaft. In this case also, the two bearing surfaces are diametrically opposed or substantially diametrically opposed, at least a first point of a first bearing surface being diametrically opposed to a second point of the second bearing surface.

[0038] Of course, the embodiments of the rocker described above are not limiting. In addition to the number of bearing surfaces of the arms which are in contact with the shaft 11 of the correction wheel set 1, the geometry of the rocker and the arms can of course be modified. In particular, the arms may not be symmetrical. In particular, the number of bearing surfaces on each of the arms may be different.

[0039] The rocker preferably does not include the first and second mobile, nor the first axis of the first mobile and the second axis of the second mobile.

[0040] As represented in the figures 1, 2 , 5 et 6 , an embodiment of a clutch device 7 comprises the lever 6 as described above, the first mobile 1 and the second mobile 2. The first shaft is integral with the rest of the first mobile 1 and the second mobile as well as the lever rotate around the second shaft. By "integrated with", we mean in particular "rotationally linked to", or even "fixed on" or "in embedded connection with". The first mobile is capable of coming directly into engagement with a third mobile of a first kinematic chain, in particular with a kinematic chain for correcting the date disc Dq, or with a fourth mobile of a second kinematic chain, in particular with a kinematic chain for correcting the day disc Dj, depending on the state of the clutch, in particular depending on the position of the lever.Indeed, in a first position of the rocker, the first mobile is a driving mobile driving a first kinematic chain and, in a second position of the rocker, the second mobile is a driving mobile driving a second kinematic chain.

[0041] Thus, the lever 6 acts as a horizontal clutch lever for each of the correction devices of the clockwork movement 8. When the stem 5 is turned clockwise, seen from the back of the watch dial, the correction wheel set 1 rotates counterclockwise so that a torque is transmitted to the lever to rotate it clockwise around its axis 6f, thus engaging the corrector 1a with the teeth of the date disc Dq as shown in figure 6 This stable position 10 for correcting the dates can be defined by a portion 10f of the axis 11 of the mobile 1 which comes into contact with a stop B10 of the frame 7b of the clockwork movement.

[0042] When the stem is turned in the opposite direction, seen from the back of the watch dial, a torque is transmitted to the lever to make it turn counterclockwise around its axis 6f, thus putting the correction wheel 1b of the wheel set 1 into engagement with a day correcting wheel set 81 which drives the day disc Dj in a clockwise direction. This stable position 100 for correcting the day indication is defined by the portion 10f of the axis 11 which comes into contact against a stop B100 of the frame 7b of the clockwork movement.

[0043] Advantageously, an oblong opening 70b, provided to cooperate with the portion 10f of the shaft 11 of the wheel set 1, can be shaped within the frame 7b of the clockwork movement so as to optimize the radial guidance of the correction wheel set 1.

[0044] Alternatively, the lever 6 may be provided with an arm 600 of which a flank 600a, in particular an end 600a, is provided to be actuated by an additional control mechanism in order to disengage the correction wheel set 1 from the date disc Dq or from the day corrector wheel set 81 when the latter are likely to be actuated by a related adjustment device, in particular a time-setting mechanism. Thus, such a conformation makes it possible to significantly increase the resistive torque opposing the pivoting of the correction wheel set in order to guarantee the proper functioning of the unidirectional coupling device, without however degrading a related adjustment device for time information, in particular a time-setting mechanism capable of driving the day corrector and / or the date disc potentially engaged with a correction wheel set 1 on which the torque acts.

[0045] THE figures 7, 8 , 9 et 10 illustrate such a variant of the first embodiment of the device according to the invention. As shown in the figure 7 , the clutch rocker 6 is free to oscillate between the correction positions 10 and 100. For this purpose, the end 600a of the arm 600 is released from the contact of the pin 12a carried by the rocker 12 of the additional control mechanism, which is controlled in particular by the translation of the rod. figure 8 illustrates the clutch lever locked in a neutral position by the additional control mechanism. For this purpose, the end 600a of the lever 6 is capable of coming into abutment against the pin 12a regardless of the direction of rotation of the lever 6. Thus, the wheel 1 is positioned such that the corrector 1a is out of range of the date disc Dq and the wheel 1b is out of range of the day corrector wheel. The arm 600 can also make it possible to immobilize the lever in another position, in particular a position in which the wheel or wheels carried by the lever mesh with other elements.

[0046] In this first embodiment, in particular in this variant of the first embodiment, the resistive torque to the pivoting of the correction wheel set 1 which is produced by the friction elements 61, 62, is greater than 2, 3, or even 5, or even 6 times the resistive torque to the pivoting of the correction lever around the axis of rotation 6f.

[0047] A second embodiment of flip-flop 6' is described below with reference to figures 11 et 12 . This second embodiment differs from the first embodiment in that the rocker comprises a body 64' and a component 65' attached to the body. This component comprises at least one friction element 62' and at least one elastic element 63'. Preferably, the friction elements and / or the elastic elements are only present on the component 65'. In the figures illustrating this second embodiment, a "'" has been added to the numerical references designating the elements which are identical or provide the same functions as in the first embodiment. Thus, for example, the first mobile referenced "1" in the first embodiment is referenced "1'" in the second embodiment. In the second embodiment, the component also comprises at least one rotational guide element 61' of the first shaft.

[0048] Thus, in this second embodiment, the switch combines: a component, in particular a spring-type component providing rotational guidance of the first shaft and friction by generating radial clamping of the shaft of the mobile 1', and a conventional horizontal clutch rocker body.

[0049] This allows a distribution of the functions of the rocker on the rocker body and on the component and therefore to adapt as best as possible to a given construction context.

[0050] For example, the component 65' can be embedded or fixed or mounted integrally with the rocker body 64'. As in the first embodiment, the geometries of the arms 6a', 6b' are shaped so as to define the axis of rotation 1d' of the first mobile 1' while imparting an adequate tightening torque to its shaft 11' to obtain a desired friction torque.

[0051] However, the pivoting of the rocker 6' in the plane is carried out by means of the rocker body 64' around an axis of rotation 6f'. This pivoting and this axis are defined by an opening 66', in particular a bore, made in the rocker body 64'. The axis thus defined coincides with that of the intermediate return wheel set 2' which is engaged with the driving wheel set 1'.

[0052] As represented in the figures 11 et 12 , an embodiment of a clutch device 7' comprises the rocker 6' as described previously, the first mobile 1' and the second mobile 2'. The first mobile is capable of coming directly into engagement with a third mobile of a first kinematic chain or possibly with a fourth mobile of a second kinematic chain depending on the state of the clutch, in particular depending on the position of the rocker. Indeed, in a first position of the rocker, the first mobile is a driving mobile driving a first kinematic chain and, in a second position of the rocker, the first mobile is a driving mobile capable of driving a second kinematic chain.

[0053] As for the first embodiment, the lever 6' may be provided with an arm, one side of which, in particular one end, is designed to be actuated by an additional control mechanism in order to disengage the wheel set 1' from the third wheel set or the fourth wheel set when the latter are capable of being actuated by a related adjustment device. The arm may also make it possible to immobilize the lever in another position, in particular a position in which the wheel set or wheels carried by the lever mesh with other elements. In this second embodiment, the resistive torque to the pivoting of the correction wheel set 1' which is produced by the friction elements 61', 62', is greater than 2, 3, or even 5, or even 6 times the resistive torque to the pivoting of the correction lever around the axis of rotation 6f'.

[0054] A third embodiment of a 6" rocker is described below with reference to figures 13 et 14 . This third embodiment differs from the second embodiment in that the rotational guide element of the first shaft 11" of the first mobile 1" is produced on the rocker body 64" and not on the component 65". The component comprises at least one friction element 62" and at least one elastic element 63". Preferably, the friction elements and / or the elastic elements are only present on the component. In the figures illustrating this third embodiment, a " " has been added to the numerical references designating the elements which are identical or which provide the same functions as in the first embodiment. Thus, for example, the first mobile referenced "1" in the first embodiment is referenced "1" in the third embodiment.

[0055] Thus, the axis of rotation 1d" of the driving mobile 1" is defined by the rocker body 64". Indeed, a bore 61" makes it possible to guide the shaft in rotation around the axis 1d". On the other hand, the fictional torque opposing the free rotation of the first mobile 1" is defined by the component 65". Indeed, as illustrated in figures 13 et 14 , arms 6a", 6b" are pressed, at the level of bearing surfaces 60a" and 60b" which are merged with the arms 6a", 6b", on the portion 1c" of the shaft 11". Just as in the previous embodiment, the rotation of the rocker 6" in the plane is carried out by means of the rocker body 64" whose axis of rotation 6f" is defined by an opening 66", in particular a bore, made on the rocker body 64". This axis coincides with that of the return mobile 2" which is engaged with the driving mobile 1".

[0056] As represented in the figures 13 et 14, an embodiment of a 7" clutch device comprises the rocker 6" as described previously, the first mobile 1" and the second mobile 2". The first mobile is capable of coming directly into engagement with a third mobile of a first kinematic chain or possibly with a fourth mobile of a second kinematic chain depending on the state of the clutch, in particular depending on the position of the rocker. Indeed, in a first position of the rocker, the first mobile is a driving mobile driving a first kinematic chain and, in a second position of the rocker, the first mobile is a driving mobile capable of driving a second kinematic chain.

[0057] As for the first and second embodiments, the 6" rocker can be provided with an arm, one side of which, in particular one end, is designed to be actuated by an additional control mechanism in order to disengage the 1" mobile from the third mobile or the fourth mobile when the latter are capable of being actuated by a related adjustment device.

[0058] In this third embodiment, the resistive torque to the pivoting of the correction wheel 1" which is produced by the friction elements 61", 62", is greater than 2, 3, or even 5, or even 6 times the resistive torque to the pivoting of the correction lever around the rotation axis 6f".

[0059] The clutch device according to the invention can be used within any type of mechanism for which a unidirectional clutch device is required. For example, it can be implemented within a unidirectional correction chain of a time, calendar, or any other time-derived indication such as the moon phase indication. It can also be used within a manual winding chain of an automatic or non-automatic watch, or within an automatic winding chain of an automatic watch with unidirectional winding. For these winding applications, the second and third embodiments are preferred.The clutch device can be actuated, in particular the driving wheel 1, 1', 1" of this coupling device can be driven in rotation by a control member capable of being manipulated by the wearer of the timepiece or by the finishing chain, or even by the automatic winding chain of the timepiece.

[0060] The clutch device according to the invention can also be combined with related elements for angularly locking the lever independently of the direction of rotation of the driving wheel, to thus implement a bidirectional coupling device for at least one kinematic chain of a timepiece. This clutch device could cooperate with at least one lever so as to lock the spring or the lever when it is located in a predetermined angular position. Such an arrangement is described for example in patent application EP2012199A2. This discloses in particular a lever for correcting two calendar indications on which a correction wheel is frictionally mounted.The correction of the dates is possible in both correction directions by the cooperation of the correction lever and a correction lever, while the correction of the day indication is possible only in the chronological direction due to the pivoting torque of the correction wheel set. It is also conceivable to lock the angular position of a correction lever of a one-way coupling device directly by the pull of the watch movement.

[0061] The clutch device according to the invention can also implement a lever on which more than one corrective wheel set pivots, in particular two corrective wheels. Alternatively, it can also pivot at least one additional return which is engaged with the wheel set to, for example, reverse the direction of rotation of the corrective wheel set in order to adapt to a given application.

[0062] In the various embodiments, the clutch device is arranged so that the rotation about its axis 1d, 1d', 1d", 6f, 6f', 6f" of the first mobile 1, 1', 1" and / or of the second mobile 2, 2', 2" involves the rotation of the rocker about its axis 6f, 6f', 6f" until the rocker or one of the first and second mobile comes into abutment against an element, in particular a mobile with which the first mobile or the second mobile meshes or a stop limiting the rotation or pivoting travel of the rocker. To do this, as seen previously, the resistive or resistant torque to the rotation of the first and / or the second mobile relative to the rocker, in particular the sum of the resistive or resistant torques to the rotation of the first and the second mobile relative to the rocker, must be greater than the resistant or resistive torque of rotation or pivoting of the rocker relative to the movement building.Preferably, the resistive torque to the rotation of the first and / or second mobile relative to the rocker is 2 times greater, or even 3 times greater, or even 5 times greater, or even 6 times greater, than the resistive torque to the pivoting of the rocker about its axis of rotation or pivoting. In order to be able to be compared, the values ​​of this torque must be brought back to the level of a common axis, for example the pivoting axis of the rocker.

[0063] In the various embodiments described above, the at least one friction element cooperates with the first shaft alone, in particular with a cylindrical portion of the first shaft or, more generally, with a cylindrical portion of the first mobile. However, as a variant, the at least one friction element may cooperate with the second shaft alone or, more generally, with a cylindrical portion of the second mobile, i.e. the mobile or the mobile shaft rotating around the axis around which the rocker pivots. Alternatively, a first friction element may be provided cooperating with the first mobile and a second friction element cooperating with the second mobile.

[0064] In the various embodiments described above, the portion of the first mobile with which the friction element(s) cooperate is cylindrical and concentric with the mobile. However, this portion or surface may only be substantially cylindrical. In particular, it may be slightly frustoconical and / or have a slightly elliptical cross-section. Furthermore, the portion or surface may also be eccentric relative to the axis of rotation of the mobile.

[0065] The invention also relates to a movement 8; 8'; 8" comprising a clutch device according to one of the embodiments described previously.

[0066] The invention finally relates to a timepiece movement, in particular a watch, comprising such a movement.

[0067] The invention has the advantage of providing a rocker of simple structure which is easy to mount in a movement and which also allows control of the friction torque applied to the clutch mobiles.

[0068] According to the invention, a friction spring is manufactured in one piece with a clutch rocker. The spring can be provided to generate a radial force at the pivot axis of the drive wheel.

[0069] The clutch device according to the invention allows the rocker to rotate in a first direction when the second wheel is rotated in the first direction and allows the rocker to rotate in a second direction when the second wheel is rotated in the second direction.

[0070] The at least one friction element preferably allows friction between the at least one friction element and the at least substantially cylindrical portion of the first mobile.

Claims

1. Coupling device (7; 7'; 7"), comprising: - a first wheel (1; 1'; 1"), - a second wheel (2; 2'; 2"), - a lever (6; 6'; 6") pivoted around a first axis (6f; 6f'; 6f") and comprising: o at least one first element (61; 61'; 61") for guiding in rotation of the first wheel (1; 1'; 1"), o at least one friction element (62; 62'; 62") which is designed to co-operate with an at least substantially cylindrical portion (10c; 10c'; 10c") of the first wheel (1; 1'; 1"), o at least one resilient element (63; 63'; 63") which is designed to return resiliently the at least one friction element (62; 62'; 62") to a state of co-operation with the said at least substantially cylindrical portion (10c; 10c'; 10c") of the first wheel (1; 1'; 1"), o a second element (66; 66'; 66") for guiding in rotation of the lever around the first axis (6f; 6f'; 6f"), the first guiding element (61; 61'; 61") comprising support surfaces (60a, 60b, 60c and 60d) which are designed to co-operate by contact with the said at least substantially cylindrical portion (10c; 10c'; 10c"), the support surfaces (60a, 60b, 60c and 60d): - having an infinite radius of curvature, or - being bosses or - being designed to co-operate by means of localized contact with the at least substantially cylindrical portion (10c; 10c'; 10c") of the first wheel (1; 1'; 1"), the lever (6; 6'; 6") being provided with two resilient arms (6a, 6b; 6a', 6b'; 6a", 6b") each comprising at least one of the support surfaces (60a, 60b, 60c and 60d), the first wheel (1; 1'; 1") being able, according to the state of the coupling, and in particular according to the position of the lever (6; 6'; 6"), to go: - into a first position in which it is directly engaged with a third wheel of a first kinematic chain, and - into a second position in which it is not directly engaged with the third wheel, and the first wheel (1; 1'; 1") and the second wheel (2; 2'; 2") being connected kinematically, and notably connected kinematically by meshing, and in particular connected kinematically by direct meshing, and the coupling device (7; 7'; 7") being arranged such that the rotation, around its axis, of the first wheel (1; 1'; 1") involves the rotation of the lever (6; 6'; 6") around the first axis (6f) until the lever (6; 6'; 6") or the first wheel (1; 1'; 1") abuts an element.

2. Device according to the preceding claim, characterized in that the at least one friction element (62; 62'; 62") applies at least one radial or substantially radial force on the said portion (10c; 10c'; 10c") of the first wheel (1; 1'; 1").

3. Device according to one of the preceding claims, characterized in that the lever (6; 6'; 6") comprises an opening (6d; 6d'; 6d") for receipt of the first wheel (1; 1'; 1"), and notably a slot (6d; 6d'; 6d").

4. Coupling device, comprising: - a first wheel, - a second wheel, - a lever pivoted around a first axis and comprising: o at least one first element for guiding in rotation of the second wheel, o at least one friction element which is designed to co-operate with an at least substantially cylindrical portion of the second wheel, o at least one resilient element which is designed to return resiliently the at least one friction element to a state of co-operation with the said at least substantially cylindrical portion of the second wheel, o a second element for guiding in rotation of the lever around the first axis, the first guiding element comprising support surfaces which are designed to co-operate by contact with the said at least substantially cylindrical portion, the support surfaces: - having an infinite radius of curvature, or - being bosses or - being designed to co-operate by means of localized contact with the at least substantially cylindrical portion of the second wheel, the lever being provided with two resilient arms each comprising at least one of the support surfaces, the first wheel being able, according to the state of the coupling, and in particular according to the position of the lever, to go: - into a first position in which it is directly engaged with a third wheel of a first kinematic chain, and - into a second position in which it is not directly engaged with the third wheel, and the first wheel and the second wheel being connected kinematically, and notably connected kinematically by meshing, and in particular connected kinematically by direct meshing, and the coupling device being arranged such that the rotation, around its axis, of the second wheel involves the rotation of the lever around the first axis until the lever or the first wheel abuts an element.

5. Device according to the preceding claim, characterized in that the at least one friction element applies at least one radial or substantially radial force on the said portion of the second wheel.

6. Device according to one of Claims 4 and 5, characterized in that the lever comprises an opening for receipt of the second wheel, and notably a slot.

7. Device according to Claim 3 or 6, characterized in that the at least one friction element (62; 62'; 62") is arranged on a flank or on a flank portion of the slot (6d; 6d'; 6d").

8. Device according to Claim 3, 6 or 7, characterized in that the at least one resilient element (63; 63'; 63") comprises an arm (6a, 6b), a flank of which coincides at least partially with a flank portion of the slot (6d; 6d'; 6d").

9. Device according to the preceding claim, characterized in that the arm comprises at least one support surface (60a, 60b, 60c and 60d) of the at least one friction element (62; 62'; 62").

10. Device according to one of Claims 8 and 9, characterized in that the lever (6; 6'; 6") comprises two arms, ends (60e, 60f) of which are formed such as to permit the engagement of the shaft, and notably the two ends (60e, 60f) form a V permitting the engagement of the first wheel (1; 1'; 1"), respectively of the second wheel (2, 2', 2"), by deforming the arms resiliently.

11. Device according to one of the preceding claims, characterized in that the first guiding element (61; 61'; 61") and the at least one friction element (62; 62'; 62") are combined.

12. Device according to one of the preceding claims, characterized in that the lever (6) is in a single piece.

13. Device according to one of Claims 1 to 12, characterized in that the lever (6'; 6") comprises a body (64'; 64") and a component (65'; 65") which is added onto the body (64'; 64"), the component comprising the at least one friction element (62; 62'; 62") and the at least one resilient element (63; 63'; 63") and / or the component comprising the at least one first element (61; 61'; 61") for guiding in rotation.

14. Coupling device according to one of the preceding claims, characterized in that it makes it possible to correct a calendar indication, a time indication or an indication derived from the time, or it permits manual or automatic winding of an energy accumulator.

15. Coupling device according to one of the preceding claims, characterized in that the first wheel (1; 1'; 1") is able, according to the state of the coupling, and in particular according to the position of the lever (6; 6'; 6"), to go: - into a first position in which it is directly engaged with the third wheel, or - into a second position in which it is directly engaged with a fourth wheel of a second kinematic chain.

16. Movement (8) comprising a coupling device (7; 7'; 7") according to one of the preceding claims.

17. Horology piece, notably a watch, comprising a movement according to the preceding claim or a coupling device according to one of Claims 1 to 15.

18. Use, as a component of a coupling device according to one of Claims 1, 2, 3 and 7 to 15, of a lever (6; 6'; 6") comprising: - at least one first element (61; 61'; 61") for guiding in rotation of the first wheel (1; 1'; 1"), - at least one friction element (62; 62'; 62") which is designed to co-operate with an at least substantially cylindrical portion (10c; 10c'; 10c") of the first wheel (1; 1'; 1"), and - at least one resilient element (63; 63'; 63") which is designed to return resiliently the at least one friction element to a state of co-operation with the said portion of the first wheel (1; 1'; 1"), notably in contact with the said portion of the first wheel (1; 1'; 1").

19. Use, as a component of a coupling device according to one of Claims 4 to 15, of a lever comprising: - at least one first element for guiding in rotation of the second wheel, - at least one friction element which is designed to co-operate with an at least substantially cylindrical portion of the second wheel, and - at least one resilient element which is designed to return resiliently the at least one friction element to a state of co-operation with the said portion of the second wheel, notably in contact with the said portion of the second wheel.