Clock mechanism for actuating flexible hands

Abstract

This invention relates to an actuation mechanism for a flexible pointer, the flexible pointer comprising a first tube and a second tube connected to a tip via flexible arms. In an operating position, the first and second tubes are coaxial about an output axis. The first tube is mounted at a first defined prestress angle, and the second tube is mounted at a second defined prestress angle in the opposite direction. The actuation mechanism is arranged to actuate the flexible pointer so as to change the angular position of the second tube relative to the first tube by pivoting about the output axis, thereby changing the shape and length of the flexible pointer in a desired manner. Each flexible arm of the flexible pointer performs an angular rotation (θ1) applied to the actuation mechanism by a watch movement wheel pair. This angular rotation is modulated by the actuation mechanism with an additional angle. The additional angles applied in opposite directions to the two flexible arms of the flexible pointer determine the shape and length changes of the flexible pointer in two closely successive rotations, such that the tip performs two distinct successive complete rotations.

Description

Technical Field

[0001] This invention relates to a clock mechanism for actuating flexible hands. Background Technology

[0002] Hands are the most common display mode used to represent time, especially in an analog manner. The applicant reinterprets this display mode by proposing a flexible hand, modifying the shape and length of the hand so that, for example, the tip of the hand follows the oval outer circumference of the watch dial as closely as possible. Because the shape of the hand changes over time, the displayed information can be measured intuitively. This flexible hand is particularly the subject of the applicant's European patent applications EP 3159751A1 and EP 3605243A1.

[0003] For two decades, flexible structures have represented a valuable research topic in watchmaking. These flexible structures consist of rigid elements interconnected by elastically deformable flexible elements to achieve a guiding function. Because their working principle is based on achieving elastic deformation of the structure by preventing any plastic deformation of the material, these structures can be manufactured with the high precision and integrated nature characteristic of watchmaking processes.

[0004] Compared to traditional guiding mechanisms, flexible structures can achieve very precise motion without friction, thus requiring no lubrication. The stiffness of a structure refers to the relationship between the applied force and the structure's motion. Motion subjected to a return force does not contain backlash or hysteresis.

[0005] The applicant studied the principles of flexible structures and applied them to the minute display of the Reine de Naples "Heart" model. This iconic timepiece is one of Breguet's most representative designs. Paying homage to the world's first wristwatch, it features an oval-shaped central section and an off-center time ring pointing towards the bottom of the dial.

[0006] While the traditional path of a hand's tip is perfectly circular, the use of a flexible structure allows the minute hand of the Reine de Naples "Heart" watch to have a variable length and shape. The tip of the minute hand can then follow the oval outer circumference of the dial. Therefore, the minute hand itself acts as a flexible guide. In the case of the hour display, this is achieved through a hole in the center of the dial.

[0007] Figure 1A and 1B The watch displays two different states. Figure 1A In this case, the watch indicates 9:00. The flexible minute hand 1 is elongated, with a length L of 16.8 mm; the tip 2 of the flexible hand 1 points to the "60" mark on the time ring. Figure 1BIn the clock face, the watch indicates 9:23; the flexible hand 1 elastically deforms to form a heart shape, with its tip 2 pointing to the "23" mark on the time ring. The length L of the hand is only 7.7mm.

[0008] The geometry of the flexible pointer 1 during its manufacturing process is Figure 2A As shown in the diagram. In its heart-shaped form, the flexible pointer 1 consists of tips 2 connected to two arms 4 and 6, each arm 4 and 6 including flexible portions 4A, 6A, rigid portions 4B, 6B, and cannons 4C, 6C. It is manufactured according to the LIGA process and is preferably made of a nickel-phosphorus alloy-type material, whose properties are particularly suited to the desired specificity. In fact, this material has a sufficiently low Young's modulus to ensure flexibility, and its high yield strength minimizes the risk of plastic deformation. The material's resistance to fatigue cycles also ensures the stability of its mechanical and physical properties over time. Another advantage is that this material is insensitive to magnetic fields.

[0009] The deformation principle of flexible pointer 1 is in Figure 2B As shown in the diagram. Once assembled on the movement, the two tubes 4C and 6C of the flexible pointer 1 are stacked and actuated via two coaxial geared shafts (not shown). Figure 2B In the illustrative example shown, the flexible pointer 1 changes its shape and length but does not rotate; it switches from a first resting position with a length L of 16.8 mm to a second elastically deformed position with a length L of 7.7 mm. To switch the flexible pointer 1 from its first position to its second position, the same rotation with an angle φ but in the opposite direction is applied to each of the arms 4 and 6 of the flexible pointer 1. Therefore, the angle φ of the pipes 4C and 6C to be applied to the flexible pointer 1 can be accurately determined, for example, by finite element simulation, to obtain the desired length change ΔL.

[0010] The actuation principle of the flexible pointer 1 is described in the appendix to this patent application. Figures 3A to 3C As shown in the figure. It should be understood that the complexity of the actuation mechanism of the flexible pointer 1 lies in determining the rotation to be applied to its two tubes 4C, 6C to obtain the desired length change ΔL. In fact, in order to modify the shape and length of the flexible pointer 1, each of its two arms 4, 6 must be actuated individually.

[0011] For this purpose, the actuation of the flexible pointer 1 is illustrated schematically. Figure 3A As shown, the actuation mechanism is driven, for example, by the gear shaft of a watch movement, which applies a rotation of angle θ1 to the input end of the auxiliary plate 7, which includes the entire actuation mechanism. The actuation mechanism must convert the input angle θ1 into a rotation of angle α(θ1) of the right tube 4C of the flexible pointer 1, and a rotation of angle β(θ1) of the left tube 6C.

[0012] The appendix to this patent application Figure 3B The rotation angles of the tubes 4C and 6C of the flexible pointer 1 are indicated so that the tip 2 of the flexible pointer 1 travels along an angle θ1, where angle θ1 corresponds to the rotation applied by the watch movement to the input of the actuation mechanism. Figure 3B As can be seen, in order to make the tip 2 of the flexible pointer 1 pivot by an angle θ1 and change the flexible pointer 1 from an approximately almond shape to a heart shape, the right tube 4C must be rotated by an angle α(θ1), and the left tube 6C must be rotated by an angle β(θ1).

[0013] The appendix to this patent application Figure 3C The evolution of the rotation angles α and β of the tubes 4C and 6C of the flexible pointer 1 with the rotation angle θ1 is shown. The rotation angle θ1 corresponds to the rotation applied by the watch movement to the input end of the actuation mechanism.

[0014] In order for the flexible hand 1 to change its shape and length while indicating minutes by means of its tip 2, each tube 4C, 6C must be rotated by an angle θ1, which corresponds to the angle applied by the minute gear axis of the watch movement to the conventional minute hand. This angle θ1 is modulated by an actuation mechanism by an angle φ so that the flexible hand 1 changes its shape and length in the desired manner. The angle φ(θ1) applied to the two tubes 4C and 6C in opposite directions determines the amount of change in the shape and length of the flexible hand 1, ΔL(φ).

[0015] Therefore, the output angles α(θ1) and β(θ1) of the actuation mechanism follow the following relationship:

[0016] α(θ1) = θ1 + φ(θ1)(1)

[0017] β(θ1) = θ1 – φ(θ1)(2)

[0018] The flexible pointer 1 shown here is symmetrical. The angular position θ2 of the tip 2 of the flexible pointer 1 is defined as the bisector of the two arms 4 and 6, that is, the average of the angles α(θ1) and β(θ1) according to the following formula:

[0019] (3)

[0020] Therefore, the angular position θ2 of the tip 2 of the flexible pointer 1 is the same as θ1.

[0021] All the complexity lies in determining the value of the modulation angle φ(θ1). This value depends on the deformability of the flexible pointer 1, which determines the modulation angle φ(θ1) to be applied to obtain the desired change in shape and length ΔL. Figure 3C The diagram shows the evolution of angles α, β, and θ2 as a function of θ1.

[0022] Several actuation mechanisms for the flexible pointer 1 can be conceived. A first example of such an actuation mechanism is provided in the appendix to this patent application. Figures 4A to 4C As shown in the figure. The actuation mechanism, generally indicated by general reference numeral 8, comprises first and second shaped gear trains 10 and 12, respectively. As described in more detail below, these first and second shaped gear trains 10, 12 comprise gear trains with non-circular teeth and are designed to add to the right tube 4C and subtract the modulation angle φ(θ1) from the left tube 6C for the input angle θ1 to obtain angles α(θ1) and β(θ1).

[0023] The appendix to this patent application Figure 4A This is an exploded perspective view of the first embodiment of the actuation mechanism 8 of the flexible pointer 1. A movement gear 14 is arranged at the watch movement at the bottom of the figure to drive two shaped gear trains 10 and 12. The first shaped gear train 10 is configured to drive the first right tube 4C, and the second shaped gear train 12 is configured to drive the second left tube 6C. The first and second arrows indicate the motion transmission to the first tube 4C and the second tube 6C, respectively. Figure 4A As seen, the first shaped gear train 10 and the second shaped gear train 12 include shaped gear trains arranged to introduce a phase shift into the rotation of one tube relative to the other tube.

[0024] More specifically, to drive the first right tube 4C, the first shaped gear train 10 includes multiple wheels mounted around the first axis DA and multiple wheels coaxially mounted around the main pivot axis D. As for the second shaped gear train 12 for driving the second left tube 6C, it includes multiple wheels mounted around the second axis DB and one wheel mounted on the main pivot axis D. It should be noted that in its assembled state, the flexible pointer 1 is prestressed, causing the entire actuation mechanism 8 to be tensioned, which allows for compensation of any backlash in the gear train.

[0025] The appendix to this patent application Figure 4B This is a partial cross-sectional view of a watch movement that drives the aforementioned type of actuation mechanism, and is appended to this patent application. Figure 4C It is based on Figure 4A A perspective view of the actuation mechanism of the first alternative embodiment shown in the assembled state. In these... Figure 4B and 4C In this design, the input wheel of the actuation mechanism is arranged to mate with the output wheel of the watch movement. This input wheel is coaxial with the drive shaft and the gear train. The first tube of the flexible hand is shown mounted on the gear train, while the second tube is shown in its free state before being coaxially positioned with the first tube on the drive shaft. Each shape wheel includes an angular guide mark to ensure proper action of the shape wheel train.

[0026] More specifically, Figure 4B The actuation mechanism 8 for the flexible pointer 1 to display minutes is shown. Figure 4C A watch movement driving this actuation mechanism 8 is shown. In this embodiment, the input wheel 32 is guided on a fixed tube 34, the center of which is located on the main pivot axis D. The input wheel 32 is arranged to cooperate with the movement transmission 14 formed by the output wheel assembly of the watch movement. The input wheel 32, for example, a geared pinion, drives the coaxial drive geared pinion 38 directly or via frictional indentations that allow for pointer setting.

[0027] The drive gear shaft 38 is rotatable and drives a first shape wheel 40, which in turn engages with a complementary second shape wheel 42 mounted around a first axis DA. The second shape wheel 42 is pivotally fixed to the first shape wheel 44 and engages with a complementary fourth shape wheel 46 mounted around a main pivot axis D, the fourth shape wheel 46 including a gear shaft 48 for fastening the first pipe fitting 4C.

[0028] The same drive gear shaft 38 drives a fifth shape wheel 50, which in turn engages with a complementary sixth shape wheel 52 mounted around a second axis DB. The sixth shape wheel 52 is pivotally fixed to a seventh shape wheel 54 and engages with a complementary eighth shape wheel 56 pivoting around a main pivot axis D, the eighth shape wheel 56 including a gear shaft 58 to which a second tube 6C is fastened.

[0029] Each shape wheel may include angular guide marks to ensure that it... Figure 5 The correct indexing and positioning are shown. Figure 5 A shape wheel system with a seventh shape wheel 54 and an eighth shape wheel 56 is shown in detail. These shape wheels 54, 56 are not rotary and each includes guide marks 60, 62 for their indexing relative to each other, and elongated holes 64, 66 to facilitate their positioning.

[0030] The aforementioned actuation mechanism 8 meets its specifications and offers numerous advantages, particularly its simple, robust operation and accurate display. However, the shape-gear actuation also has some limitations. The design is not easily modified because changes in the path of the tip 2 of the flexible pointer 1 imply modifications to the two shape-gear systems 10 and 12. Furthermore, the modulation of the angular movement φ of the arms 4 and 6 of the flexible pointer 1 is limited to modest values, as larger values ​​would require shape-gear systems that deviate too much from a circular shape.

[0031] Refer to the above Figure 2BIn the described example, the ratio between the length of the flexible pointer 1 in its resting position and the length of the flexible pointer 1 in its elastically deformed position is close to 2.2, which exceeds the technical feasibility related to the modulation φ(θ1) of the actuation mechanism 8 with the gear trains 10, 12. Therefore, a novel actuation mechanism was developed to enable the tip 2 of the flexible pointer 1 to accurately follow the oval outer periphery of the dial of the Reine de Naples "Heart" watch.

[0032] The second embodiment of the actuation mechanism, generally indicated by general reference numeral 68, is appended to this patent application. Figure 6A and 6B As shown in the diagram. The actuation mechanism 68 is arranged to drive the flexible pointer 70, as... Figure 6C As shown, the flexible pointer 70 consists of a tip 72 connected to two arms 74 and 76, which are respectively fastened to the toothed shafts 78 and 80. The operating position of the flexible pointer 70 is a stress position, in which the two arms 74 and 76 of the flexible pointer 70 are fastened to the first toothed shaft 78 and the second toothed shaft 80, respectively, so that they are coaxial with each other about the output axis D'.

[0033] The actuation mechanism 68 includes a first drive unit 82 around a first gear shaft 78 and a second drive unit 84 around a second gear shaft 80.

[0034] The first drive unit 82 and the second drive unit 84 are arranged to change the angular position of the second toothed shaft 80 relative to the first toothed shaft 78 by pivoting about the output axis D', so as to deform the flexible pointer 70, which has the effect of changing the radial position of the tip 72 relative to the output axis D'.

[0035] The actuation mechanism 68 includes a first differential device 90 and a second differential device 86. The first input end of the first differential device 90 is composed of a first cam 92, and the first input end of the second differential device 86 is composed of a second cam 88. Depending on the configuration adopted, these first cams 92 and second cams 88 can be fixed or movable.

[0036] The actuation mechanism 68 is accomplished by a planetary gear retaining frame 94, which forms the second input end of the first differential device 90 and the second differential device 86. The planetary gear retaining frame 94 carries the first planetary gear 96 and the second planetary gear 98, each of which is equipped with cam follower fingers 100 and 102, which are arranged to follow the contours 104 and 106 of the corresponding cams 88 and 92.

[0037] Finally, the first differential device 90 has a first gear shaft 78 as an output end, and the second differential device 86 has a second gear shaft 80 as an output end.

[0038] like Figure 6B As seen, the second planetary gear 98 is assembled to rotate freely on the top pivot 108 of the planetary gear retaining frame 94, which is assembled to rotate freely about the output axis D'.

[0039] The second tooth 110, carried by the second toothed shaft 80, forms the sun pinion.

[0040] On the surface opposite to the surface supporting the second planetary gear 98, the first planetary gear 96 is mounted so as to be freely rotatable on the planetary gear retaining frame 94, particularly as appended to this patent application. Figure 6D As shown in the figure, the planetary gear retaining frame 94 includes countersunk holes 112 on the top and bottom surfaces, as well as a top pivot 108 and a bottom pivot 114. Finally, the sun pinion is formed by the first tooth 116 carried by the first indexing shaft 78.

[0041] As described above, the first planetary gear 96 includes a cam-following finger 100 arranged to travel along the profile 104 of the first cam 88, and held against the profile 104 by the elasticity of a flexible pointer 70. Similarly, the second planetary gear 98 includes a cam-following finger 102 arranged to travel along the profile 106 of the second cam 92, and elastically reset by the elasticity of the flexible pointer 70.

[0042] It is advantageous to use the elasticity of the flexible pointer 70 to ensure that the cam follower fingers 100, 102 are elastically reset against the corresponding contours 104, 106 of the cams 88, 92, because this saves the reset components that would be needed to press the cam follower fingers 100, 102 against the contours 104, 106 of the cams 88, 92.

[0043] The operation of the aforementioned actuation mechanism 68 is as follows. The actuation mechanism 68 rests on a planetary gear retaining frame 94, which is capable of rotating, for example, together with the drive gear shaft 118 of a watch movement to which it is fixed. Except for the cams 88 and 92, which are the only fixed elements, the planetary gear retaining frame 94 drives the entire actuation mechanism 68 to rotate about an angle θ1. On the planetary gear retaining frame 94, two gear shafts 78 and 80, to which the arms 74 and 76 of the flexible hands 70 are fastened, interact with the first planetary gear 96 and the second planetary gear 98. Each planetary gear carries fingers 100 and 102 arranged to follow the corresponding contours 104 and 106 of the cams 88 and 92.

[0044] The flexible pointer 70, which is elastically prestressed, keeps the entire actuation mechanism 68 taut, so that the cam follower fingers 100, 102 are always in contact with the corresponding contours 104, 106 of the cams 88, 92.

[0045] The indexing shaft 80 corresponding to the right arm 76 of the flexible pointer 70 is directly driven in engagement with the second planetary gear 98. The indexing shaft 78 corresponding to the left arm 74 of the flexible pointer 70 is directly driven in engagement with the first planetary gear 96. The first indexing shaft 78 and the second indexing shaft 80, which are fixed to the arms 74 and 76 of the flexible pointer 70, are interconnected via the planetary gear retaining frame 94. When the planetary gear retaining frame 94 rotates at an angle θ1, the first planetary gear 96 and the second planetary gear 98 pivot on their respective bottom pivot 114 and top pivot 108, and rotate at an angle φ(θ1) under the influence of their interaction with the cams 88 and 92. The indexing shaft 80, to which the right arm 76 of the flexible pointer 70 is fixed, increases the rotation θ1 of the planetary gear retaining frame 94 by this angle φ(θ1) to obtain the angle α(θ1). Conversely, the left arm 74 of the flexible pointer 70 is fastened to the toothed shaft 78 thereon to obtain the angle β(θ1) by subtracting the angle φ(θ1) from the rotation θ1.

[0046] Assembly of the additional plate, including the entire actuation mechanism 68, is relatively straightforward. Special attention should be paid to the atypical pointer assembly using a specific protocol. As described above, the flexible pointer 70 is continuously tensioned to elastically compensate for backlash in the gear train of the actuation mechanism and to keep the cam follower fingers 100, 102 abutting against the cams 88, 92. When assembling the flexible pointer 70, the fittings must be pre-positioned so that the cam follower fingers 100, 102 abut against the cams 88, 92. The right arm 76 of the flexible pointer 70 is then press-fitted onto the corresponding gear shaft 80 at a defined prestress angle, and the left arm 74 is then press-fitted onto the gear shaft 78 at the same prestress angle, but in the opposite direction to the right arm 76 relative to line D'', which passes through the output axis D' and the tip 72 of the flexible pointer 70.

[0047] The actuation mechanism 68, consisting of several components, is simple and robust. Manufacturing tolerances have minimal impact. The actuation mechanism 68 can also be adapted to design variations, as modest changes in the path of the tip 72 of the flexible pointer 70 can be achieved by simply altering the geometry of the cams 88 and 92.

[0048] The innovative design of the Breguet Reine de Naples "Heart" watch is immediately apparent to the wearer. Beyond its aesthetic appeal, the watch, equipped with the aforementioned horological mechanism, primarily addresses the technical challenges of non-circular dials while adhering to traditional horological norms. The allure perceived through the mysterious movement of the gear train seen at the case back shifts here to the dial side, where the movement of the flexible hands and the variations in their shape and length create true charm.

[0049] The appendix to this patent application Figure 7A and 7BAnother embodiment of the actuation mechanism for the flexible pointer is shown. Generally indicated by general reference numeral 120, this actuation mechanism is arranged to drive, for example, a flexible pointer 122, which consists of a tip 124 connected to two arms 126 and 128, each arm including a tube 130, 132. The operating position of the flexible pointer 122 is a stressed position, wherein the first tube 130 and the second tube 132 are coaxial with respect to each other about the output axis D'''.

[0050] The actuation mechanism 120 is accomplished by a planetary gear retaining frame 134 equipped with a first pivot 136 on which planetary gears 138 are mounted to rotate. As described above, the planetary gears 138 are equipped with cam follower fingers 140 arranged to travel along the profile 142 of the cam 144, which is held against the profile 142 by means of the elasticity of the flexible pointer 122. The cam 144 is the only fixed element of the actuation mechanism 120. The planetary gear retaining frame 134 is also equipped with a fixed tube 146 on which a first drive gear shaft 148 and a second drive gear shaft 150 are mounted to rotate freely concentrically. The right arm 126 of the flexible pointer 122 is press-fitted onto the second drive gear shaft 150 at a defined prestress angle, while the left arm 128 of the same flexible pointer 122 is press-fitted onto the first drive gear shaft 148 at the same prestress angle, but in the opposite direction to the right arm 126. Finally, the actuation mechanism 120 includes a first sun pinion 152 formed by teeth carried by the first drive gear shaft 148 and a second sun pinion 154 formed by teeth carried by the second drive gear shaft 150. When the planetary gear retaining frame 134 is driven to rotate, for example clockwise, by the watch movement, it drives the planetary gear 138 in the same direction, and the planetary gear 138 rotates along its cam follower finger 140 as it travels along the profile 142 of the cam 144. The first drive gear shaft 148, which directly meshes with the planetary gear 138, therefore rotates relative to the planetary gear retaining frame 134. As for the second drive gear 150, it rotates relative to the planetary gear retaining frame 134 at the same speed as the first drive gear 148, but in the opposite direction, because the rotation of the planetary gear 138 is transmitted to the second drive gear 150 via the intermediate gear 156, which is mounted on the second pivot 158 ​​in a rotatable manner.

[0051] To switch the flexible pointer 122 from the first position to the second position, the actuation mechanism 120 applies rotations of the same angle φ but in opposite directions to each arm 126, 128 of the flexible pointer 122. For this purpose, the actuation mechanism 120 is driven by the watch movement, which applies a rotation of angle θ1 to the input end of the planetary gear retaining frame 134. This rotation of angle θ1 is converted by the actuation mechanism 120 into rotations of angle α(θ1) of the right tube 130 and angle β(θ1) of the left tube 132 of the flexible pointer 122. The output angles α(θ1) and β(θ1) of the actuation mechanism therefore obey the following relationship:

[0052] α(θ1) = θ1 + φ(θ1)(1)

[0053] β(θ1) = θ1 – φ(θ1)(2)

[0054] Assuming the flexible pointer 122 is symmetrical, the angular position θ2 of the tip of the flexible pointer 122 is defined as the bisector of the two arms 126 and 128, i.e., the average of angles α(θ1) and β(θ1) according to the following formula:

[0055] (3)

[0056] The three actuation mechanisms described above enable the tip of the flexible pointer to trace a non-circular path during a full rotation. Summary of the Invention

[0057] The object of the present invention is to provide a mechanism driven by a watch movement and designed to actuate a flexible hand whose shape and length change in two closely successive rotations, such that the tip of the flexible hand traces two distinct paths.

[0058] Therefore, the present invention relates to an actuation mechanism for a flexible pointer, wherein a wheel assembly of a watch movement applies a first angular rotation θ1 to the actuation mechanism. The flexible pointer includes a first tube and a second tube connected to the tip of the flexible pointer via flexible arms. When the flexible pointer is in a stress-free free state, the first and second tubes are separated from each other. The operating position of the flexible pointer, having a defined shape and length, is a stressed position. In this stressed position, the first and second tubes are coaxial about an output axis. The first tube is assembled at a first defined prestress angle, and the second tube is assembled at a second defined prestress angle opposite to that of the first tube. The actuation mechanism is arranged to actuate the flexible pointer so as to change the angular position of the second tube relative to the first tube by pivoting about the output axis, thereby changing the shape and length of the flexible pointer in a desired manner. Each flexible arm of the flexible pointer performs an angular rotation θ1 applied to the actuation mechanism by the wheel assembly of the watch movement. The angular rotation θ1 applied by the wheel assembly of the watch movement is actuated by the actuation mechanism with an additional angle. Modulation is performed, applying this additional angle in opposite directions to the two flexible arms of the flexible pointer. The changes in the shape and length of the flexible pointer during two closely successive rotations were determined so that the tip of the flexible pointer traces two distinct paths. The change in shape and length ΔL(φ) is performed by rotating the gear train of the watch movement at an angle 2xθ1 to the input of the actuation mechanism.

[0059] According to a specific embodiment of the present invention:

[0060] - The cam follower finger senses the profile of the cam, which determines the shape and length changes of the flexible pointer. While the cam follower finger travels along the entire length of the cam profile, the flexible pointer performs its two distinct successive rotations.

[0061] - The gear train of the watch movement that applies an angle rotation θ1 to the actuation mechanism must perform two complete rotations, so that the cam follower finger travels along the entire cam profile, and the tip of the flexible hand traces the path corresponding to the two different complete rotations;

[0062] - Due to the mechanical tension caused by the stress assembly of the flexible pointer, the cam follower finger is held against the cam profile;

[0063] - The actuation mechanism includes at least one rotating planetary gear retaining frame, which is driven by the wheel assembly of the watch movement and carries cam follower fingers. While the wheel assembly of the watch movement performs two complete rotations by applying an angle rotation θ1 to it, the planetary gear retaining frame performs one complete rotation.

[0064] - The cam is fixed;

[0065] - The planetary gear retaining frame carries a first sun gear pair and a second sun gear pair arranged coaxially with each other. The first sun gear pair consists of a first sun pinion and a first sun gear, and the second sun gear pair consists of a second sun pinion and a second sun gear. The first pinion meshes with a planet gear carried by the planetary gear retaining frame. The planet gear carries a cam follower finger. The planet gear meshes with an intermediate gear. The intermediate gear itself meshes with the second sun pinion. The actuation mechanism also includes a first cannon-pinion and a second cannon-pinion arranged coaxially with each other. The first tube of the flexible pointer is fastened to the first cannon-pinion, and the second tube of the flexible pointer is fastened to the second cannon-pinion.

[0066] -The second sun gear is multiplied by a factor of 2 and by an angle The first rotating gear shaft meshes, and the first sun gear meshes with the gear at an angle with a multiplication factor of 2. The rotating second toothed shaft engages;

[0067] -The actuation mechanism includes: The gear reduction ratio is coupled to a first planetary gear retainer, which carries a concentric first and second index gear shaft. Each flexible arm of a flexible pointer is press-fitted onto one of the index gear shafts. The first and second index gear shafts are kinematically correlated to each other so that they rotate in opposite directions. The second planetary gear retainer carries a sun gear pair coupled to the second index gear shaft. The second planetary gear retainer also carries planet gears coupled to the sun gear pair. These planet gears are equipped with cam follower fingers arranged to travel along a cam profile. These cam follower fingers sense the profile of a fixed cam. The planet gears rotate at an angle... The rotation angle θ1 applied to the sun gear pair of the watch movement is modulated, and the sun gear pair then drives the second gear shaft at an angle with a multiplication factor of 2. Rotation, the second gear shaft drives the first gear shaft at an angle Rotate;

[0068] - The cam is movable;

[0069] The actuation mechanism includes an intermediate reduction gear pair driven by the watch movement's gears. This intermediate reduction gear pair, in turn, drives a planetary gear retainer frame to rotate at an angle θ1. The planetary gear retainer frame carries a first gear shaft and a second gear shaft concentric with the first gear shaft. The planetary gear retainer frame also carries a first planetary gear, which meshes with both the first and second gear shafts. The second planetary gear meshing with the second gear shaft is equipped with a cam follower finger arranged to travel along the contour of a rotating cam and is elastically held against the contour of the rotating cam, which is driven by the watch movement at a reduction ratio. Driven such that when the planetary gear holding frame rotates at angle θ1, the rotating cam rotates at angle θ2. The second planetary gear, therefore, rotates together with the planetary gear frame about the output axis at an angle θ1, while simultaneously rotating on its own axis at a certain rotational angle, which is defined as an angle... The rotation of the two flexible arms of the flexible pointer is modulated so that the flexible pointer changes its length and shape in a desired manner.

[0070] In order for the flexible hand to perform two successive, distinct full rotations by changing its shape and length, each arm of the hand must rotate by an angle θ1, which corresponds to the angle that the minute hand is subjected to by the minute gear of the watch movement. This angle θ1 is modulated by an actuation mechanism at an angle φ, causing the flexible hand to change its shape and length in the desired manner. This angle φ(θ1), applied in opposite directions to the two arms of the flexible hand, determines the amount of change in the shape and length of the flexible hand, ΔL(φ). Attached Figure Description

[0071] Further features and advantages of the invention will become more apparent from the following detailed description of a clock mechanism for actuating flexible hands, an example given by way of illustration only and not limitation with reference to the accompanying drawings, in which:

[0072] - quoted above Figure 1A The watch shown indicates 9:00, with a flexible hand that is elongated and its tip points to the "60" mark on the hour ring.

[0073] - quoted above Figure 1B The watch shows the time at 9:23; the flexible hands are elastically deformed to form a heart shape, with the tip pointing to the "23" mark on the hour ring;

[0074] - quoted above Figure 2A The geometry of the flexible pointer during its manufacturing process is shown;

[0075] - quoted above Figure 2B The principle of the deformation of the flexible pointer is shown;

[0076] - quoted above Figure 3A This is a schematic diagram of flexible pointer actuation;

[0077] - quoted above Figure 3B This indicates the rotation angle of the tube and the flexible pointer, so that the tip of the flexible pointer travels along an angle θ1, which corresponds to the rotation applied by the watch movement to the input of the actuation mechanism;

[0078] - quoted above Figure 3C The evolution of the rotation angles α and β of the flexible hand as a function of the rotation angle θ1 is shown. The rotation angle θ1 corresponds to the rotation applied by the watch movement to the input of the actuation mechanism.

[0079] - quoted above Figure 4A This is an exploded perspective view of the first embodiment of the actuation mechanism for the flexible pointer;

[0080] - Figure 4B It is a partial cross-sectional view of the watch movement that drives the actuation mechanism;

[0081] - quoted above Figure 4C It is in the assembly state. Figure 4A A perspective view of the actuation mechanism;

[0082] - quoted above Figure 5 A shape wheel is shown, on which angular guide marks are mounted to ensure the correct indexing and positioning of the shape wheel;

[0083] - quoted above Figure 6A A second embodiment of the actuation mechanism for a flexible pointer in an assembled state is shown;

[0084] - quoted above Figure 6B It is in a disassembled state. Figure 6A Perspective view of the actuation mechanism in the middle;

[0085] - quoted above Figure 6C It is arranged as follows: Figure 6A and 6B A perspective view of the flexible pointer actuated by the actuation mechanism in the middle;

[0086] - quoted above Figure 6D A planetary gear retaining frame is shown, which includes countersunk holes on the top and bottom surfaces, as well as a top pivot and a bottom pivot;

[0087] - quoted above Figure 7A This is an exploded perspective view of a third embodiment of an actuation mechanism for a flexible pointer according to the prior art, the actuation mechanism including a differential type device carried by a planetary gear retaining frame, and two tubes of the flexible pointer coaxially around the first and second indexing gear shafts;

[0088] - quoted above Figure 7B yes Figure 7A A view of the actuation mechanism in its assembled state;

[0089] - Figure 8A This is a schematic diagram of a first embodiment of the actuation mechanism of the flexible pointer according to the present invention;

[0090] - Figure 8B yes Figure 8A Perspective view of the actuation mechanism in the middle;

[0091] - Figure 8C yes Figure 8A Top view of the actuation mechanism in the middle;

[0092] - Figure 9A This is a schematic diagram of a second embodiment of the actuation mechanism of the flexible pointer according to the present invention;

[0093] - Figure 9B yes Figure 9A Perspective view of the actuation mechanism in the middle;

[0094] - Figure 9C yes Figure 9A Top view of the actuation mechanism in the middle;

[0095] - Figure 10A This is a schematic diagram of a third embodiment of the actuation mechanism of the flexible pointer according to the present invention;

[0096] - Figure 10B yes Figure 10A Perspective view of the actuation mechanism in the middle;

[0097] - Figure 10C yes Figure 10A Top view of the actuation mechanism in the middle;

[0098] - Figure 11A and 11B The diagram illustrates two distinct, closely following paths of the flexible pointer when it is driven by one of the actuation mechanisms according to the invention. Detailed Implementation

[0099] The present invention originates from the following general inventive concept: that is, to provide a mechanism driven by a watch movement and intended to actuate a flexible hand in which the shape and length change in two closely successive rotations, such that the tip of the hand traces two mutually different paths.

[0100] According to a first embodiment of the actuation mechanism of the present invention, Figures 8A-8C As shown in the figure. The actuation mechanism, generally indicated by general reference numeral 160, is arranged to drive a flexible hand 162 of the type described above, which consists of a tip 164 connected via corresponding flexible arms 166 to a first tube 166A and a second tube 166B. In order for the flexible hand 162 to perform two successive and distinct full rotations by changing its shape and length, each flexible arm 166 of the flexible hand 162 must rotate by an angle θ1, which corresponds to the angle applied to the conventional minute hand by the minute gear shaft of the watch movement. This angle θ1 is modulated by the actuation mechanism 160 by an angle φ so that the flexible hand 162 changes its shape and length in a desired manner. This angle φ, applied in opposite directions to the two flexible arms 166 of the flexible hand 162, determines the amount of change in the shape and length of the flexible hand ΔL(φ). For this purpose, the first tube 166A corresponding to the right flexible arm 166 of the flexible pointer 162 is fastened to the second gear shaft 170, and the second tube 166B corresponding to the left flexible arm 166 of the flexible pointer 162 is fastened to the first gear shaft 168, with the two gear shafts 168 and 170 being concentrically arranged around the output axis D0.

[0101] The actuation mechanism 160 includes a planetary gear retaining frame 172. The wheel 174 of the watch movement is rotated by an angle θ1 at the input end of the planetary gear retaining frame 172, such that when the wheel 174 rotates by angle θ1, the planetary gear retaining frame 172 rotates by an angle θ1. Rotation. The planetary gear retaining frame 172 carries a first sun gear 176 and a second sun gear 178 coaxially arranged. The first sun gear 176 carries a first sun gear 180, and the second sun gear 178 carries a second sun gear 182. The first sun gear 176 meshes with a planet gear 184, which carries a cam follower finger 186 arranged to travel along the profile 188 of the fixed cam 190 and is held against the profile 188 by means of the elasticity of a flexible pointer of the type described in detail above. The planet gear 184 meshes with an intermediate gear 189, which in turn meshes with the second sun gear 178. It can be understood that the gear 174 must perform two full rotations such that the cam follower finger 186 travels along the entire profile 188 of the fixed cam 190, and the tip 164 of the flexible pointer 162 traces a path corresponding to the two different full rotations. The second sun gear 182 is multiplied by a factor of 2 and by an angle θ1+ The first rotating gear shaft 168 engages, and the first sun gear 180 engages with the first sun gear at an angle θ1 with a multiplication factor of 2. The rotating second gear shaft 170 engages. The right flexible arm 166 of the flexible pointer 162 is press-fitted onto the second gear shaft 170, and the left flexible arm 166 of the flexible pointer 162 is press-fitted onto the first gear shaft 168. The right and left flexible arms 166 of the flexible pointer 162 thus define the following angles:

[0102]

[0103]

[0104] Assuming the flexible pointer 162 is symmetrical, the angular position θ2 of the tip 164 of the flexible pointer 162 is defined as the bisector of the two flexible arms 166, that is, the average of the angles α(θ1) and β(θ1) according to the following formula:

[0105] (3)

[0106] A second embodiment of the actuation mechanism of the flexible pointer 162 according to the present invention is in Figures 9A-9C The diagram is schematically shown. The actuating mechanism, generally indicated by general reference numeral 191, includes a first planetary gear retaining frame 192, which... The gear reduction ratio engages with the second planetary gear retainer frame 194. For the flexible hand 162 to perform two successive and distinct full rotations by changing its shape and length, each flexible arm 166 of the flexible hand 162 must rotate by an angle θ1, corresponding to the angle applied to the conventional minute hand by the minute gear shaft of the watch movement. This angle θ1 is modulated by the actuation mechanism 191 via an angle φ so that the flexible hand 162 changes its shape and length in the desired manner. This angle φ(θ1) applied in opposite directions to the two flexible arms 166 of the flexible hand 162 around the output axis D0 determines the amount of change in the shape and length of the flexible hand 162, ΔL(φ).

[0107] For this purpose, the first planetary gear retainer 192 carries a concentric first indexing shaft 196 and a second indexing shaft 198. The right flexible arm 166 of the flexible pointer 162 is press-fitted onto the second indexing shaft 198, and the left flexible arm 166 of the flexible pointer 162 is press-fitted onto the first indexing shaft 196. A first sun pinion 200 formed by the first teeth carried by the first indexing shaft 196 meshes with a first planetary gear 202, which is configured to rotate freely on the first planetary gear retainer 192. This first planetary gear 202 meshes with a second planetary gear 204, which is also configured to rotate freely on the first planetary gear retainer 192 and meshes with a second sun pinion 206 formed by the second teeth carried by the second indexing shaft 198. The function of these first planetary gears 202 and second planetary gears 204 is to cause the first indexing shaft 196 and the second indexing shaft 198 to rotate relative to the first planetary gear retainer 192 about the output axis D0 in opposite directions.

[0108] The second planetary gear retainer 194 carries a sun gear pair formed by a sun pinion 208 and a sun gear 210, the sun gear 210 engaging with the second sun pinion 206 of the second gear shaft 198. The second planetary gear retainer 194 also carries a third planetary gear 212, which engages with the sun pinion 208 and is equipped with a cam follower finger 214 arranged to travel along the profile 216 of a fixed cam 218 and held against the profile 216 by the elasticity of a flexible pointer, as described in detail above. When the first planetary gear retainer 192 rotates by an angle θ1, the second planetary gear retainer 194 also rotates by an angle θ1. Rotation. The third planetary gear 212, carried by the planetary gear retaining frame 194, rotates at an angle. ( The third planetary gear 212 rotates to sense the contour 216 of the fixed cam 218. As it follows the contour 216 of the fixed cam 218, the third planetary gear 212 rotates at an angle. ( The angle rotation θ1 applied to the sun gear 210 by the watch movement is modulated, and the sun gear 210 in turn drives the second gear shaft 198, which rotates by a multiplier of 2. It can be understood that the first gear shaft 196 and the second gear shaft 198 rotate relative to the first planetary gear retaining frame 192 in opposite directions.

[0109] Finally, the second gear shaft 198 drives the first gear shaft 196 to rotate by an angle. .

[0110] Therefore, the right flexible arm 166 and the left flexible arm 166 of the flexible pointer 162 depict the following angles:

[0111]

[0112]

[0113] Assuming the flexible pointer 162 is symmetrical, the angular position θ2 of the tip 164 of the flexible pointer 162 is defined as the bisector of the two flexible arms 166, i.e., the average of angles α(θ1) and β(θ1) according to the following formula:

[0114]

[0115] A third embodiment of the actuation mechanism of the flexible pointer according to the present invention is in Figures 10A-10C The actuation mechanism, generally indicated by general reference numeral 220, includes an intermediate reduction gear pair 222, which consists of an intermediate reduction gear 226 and an intermediate reduction pinion 224. A planetary gear retaining frame 228, driven by a wheel of the watch movement at an angle θ1, further drives the intermediate reduction gear 226. The planetary gear retaining frame 228 carries a first gear shaft 230 and a second gear shaft 232 concentric with the first gear shaft 230. The planetary gear retaining frame 228 also carries a first planetary gear 234, which is rotatably mounted on a pivot and meshes with the first gear shaft 230 on one hand and with a second planetary gear 236, which is rotatably mounted on another pivot. The second planetary gear 236, meshing with the second gear shaft 232, is equipped with a cam follower finger 238, which is arranged to travel along the profile 240 of the rotating cam 242 and is held against the profile 240 by the elasticity of the flexible pointer 162. The rotating cam 242 is guided by a runner 243 and engages with an intermediate reduction gear pair 222, such that when the planetary gear retaining frame 228 rotates at an angle θ1, the rotating cam 242 rotates at an angle θ1. Rotation. Therefore, the first gear shaft 230 rotates by the actuation mechanism 220 via an angle. The modulated angle θ1 rotates so that the flexible pointer changes shape and length in the desired manner. This angle is applied in the opposite direction to the two flexible arms 166 of the flexible pointer 162. The shape and length variation ΔL(φ) of the flexible pointer 162 were determined. Therefore, the right and left flexible arms 166 of the flexible pointer 162 are defined by the following angles:

[0116]

[0117]

[0118] at last, Figure 11A and 11B Two different positions of the flexible pointer 162 are shown. This flexible pointer 162 can be driven by one of the actuation mechanisms described above according to the invention, and the change in shape and length ΔL(φ) of the flexible pointer 162 is achieved by a rotation of an angle 2xθ1 applied to the input end of the actuation mechanism by the gear train of the watch movement. Figure 11A and 11B As can be seen, the tip 164 of the flexible pointer 162 is able to draw two roughly circular paths 244 and 246, whose radius values ​​are different from each other and they are not concentric.

[0119] It goes without saying that the invention is not limited to the embodiments just described, and those skilled in the art can conceive of various modifications and simple variations without departing from the scope of the invention as defined by the appended claims. In particular, it can be understood that when the flexible pointer performs two successive full rotations, the paths traced by the tip of the flexible pointer driven by the actuation mechanism according to the invention are different from each other and can obviously deviate from a circular shape.

[0120] List of reference numerals

[0121] 1. Flexible pointer

[0122] 2. Tip

[0123] 4. Arm

[0124] 4A. Flexible components

[0125] 4B. Rigid Part

[0126] 4C. Pipe fittings

[0127] 6. Arm

[0128] 6A. Flexible components

[0129] 6B. Rigid Part

[0130] 6C. Pipe fittings

[0131] 7. Additional panels

[0132] 8. Actuation mechanism

[0133] 10. First-shape gear system

[0134] 12. Second-shape gear system

[0135] 14. Movement and transmission components

[0136] 16. Watch movement

[0137] DA. First axis

[0138] D. Main pivot axis

[0139] DB. Second Axis

[0140] 32. Fixed tube

[0141] 34. Input wheel pair

[0142] 38. Drive gear shaft

[0143] 40. First Shape Wheel

[0144] 42. Second Shape Wheel

[0145] 44. Third Shape Wheel

[0146] 46. ​​Fourth Shape Wheel

[0147] 48. Split gear shaft

[0148] 50. Fifth Shape Wheel

[0149] 52. The Sixth Shape Wheel

[0150] 54. The Seventh Shape Wheel

[0151] 56. The Eighth Shape Wheel

[0152] 58. Gear shaft

[0153] 60. Guide Marker

[0154] 62. Guide Marker

[0155] 64. Elongated hole

[0156] 66. Elongated hole

[0157] L. Length

[0158] 68. Actuation mechanism

[0159] 70. Flexible pointer

[0160] 72. Tip

[0161] 74. Arm

[0162] 76. Arm

[0163] 78. First dividing gear shaft

[0164] 80. Second dividing gear shaft

[0165] D'. Output axis

[0166] 82. First driving device

[0167] 84. Second drive unit

[0168] 86. First differential device

[0169] 88. First Cam

[0170] 90. Second differential device

[0171] 92. Second Cam

[0172] 94. Planetary gear retainer frame

[0173] 96. First Planetary Wheel

[0174] 98. Second Planetary Wheel

[0175] 100. Cam follower finger

[0176] 102. Cam follower finger

[0177] 104. Outline

[0178] 106. Outline

[0179] 108. Top Pivot

[0180] 110. Second tooth

[0181] 112. Countersunk hole

[0182] 114. Bottom Pivot

[0183] 116. First tooth

[0184] 118. Drive gear shaft

[0185] D''. Line

[0186] 120. Actuation mechanism

[0187] 122. Flexible pointer

[0188] 124. Tip

[0189] 126. First Arm

[0190] 128. Second Arm

[0191] 130. First fitting

[0192] 132. Second fitting

[0193] D'''. Output axis

[0194] 134. Planetary gear retainer frame

[0195] 136. First Pivot

[0196] 138. Planetary Wheel

[0197] 140. Cam follower finger

[0198] 142. Outline

[0199] 144. Cam

[0200] 146. Fixed tube

[0201] 148. First drive gear shaft

[0202] 150. Second drive gear shaft

[0203] 152. First Sun Gear

[0204] 154. The Second Sun Gear

[0205] 156. Intermediate wheel

[0206] 158. Second Pivot

[0207] 160. Actuation mechanism

[0208] 162. Flexible pointer

[0209] 164. Tip

[0210] 166. Flexible arm

[0211] 166A. Pipe fittings

[0212] 166B. Pipe fittings

[0213] 168. First dividing gear shaft

[0214] 170. Second dividing gear shaft

[0215] 172. Planetary gear retainer frame

[0216] 174. Wheel

[0217] 176. First Sun Gear

[0218] 178. The Second Sun Gear

[0219] 180. First Sun Wheel

[0220] 182. The Second Sun Wheel

[0221] 184. Planetary Wheel

[0222] 186. Cam follower finger

[0223] 188. Outline

[0224] 189. Intermediate wheel

[0225] 190. Fixed Cam

[0226] 191. Actuating mechanism

[0227] 192. First planetary gear retaining frame

[0228] 194. Second planetary gear retaining frame

[0229] 196. First dividing gear shaft

[0230] 198. Second dividing gear shaft

[0231] 200. First Sun Gear

[0232] 202. First Planetary Wheel

[0233] 204. Second Planetary Gear

[0234] 206. Second Sun Gear

[0235] 208. The Sun Gear

[0236] 210. Sun Chakra

[0237] 212. The Third Planetary Wheel

[0238] 214. Cam follower finger

[0239] 216. Outline

[0240] 218. Fixed Cam

[0241] 220. Actuation mechanism

[0242] 222. Intermediate reduction gear pair

[0243] 224. Intermediate reduction pinion

[0244] 226. Intermediate reduction gear

[0245] 228. Planetary gear retainer frame

[0246] 230. First dividing gear shaft

[0247] 232. Second dividing gear shaft

[0248] 234. First Planetary Wheel

[0249] 236. Second Planetary Gear

[0250] 238. Cam follower finger

[0251] 240. Outline

[0252] 242. Rotary Cam

[0253] 243. Roller

[0254] 244. Circular Path

[0255] 246. Circular Path

Claims

1. An actuation mechanism (160; 191; 220) for a flexible pointer (162), wherein a gear train of a watch movement applies a first angular rotation θ1 to the actuation mechanism, the flexible pointer (162) comprising a first tube (166A) and a second tube (166B) connected via a flexible arm (166) to the tip (164) of the flexible pointer (162), wherein when the flexible pointer (162) is in a stress-free free state, the first tube (166A) and the second tube (166B) are far apart from each other, wherein the operating position of the flexible pointer (162) having a defined shape and length is a stressed position, wherein in the stressed position, the first tube (166A) and the second tube (166B) are coaxial about an output axis (D0), the first tube (166A) being defined by a first... The prestressed angle assembly, and the second tube (166B) is assembled at a second defined prestressed angle with a direction opposite to that of the first tube (166A), the actuation mechanism (160; 191; 220) is arranged to actuate the flexible pointer (162) to change the angular position of the second tube (166B) relative to the first tube (166A) by pivoting about the output axis (D0), thereby changing the shape and length of the flexible pointer (162) in a desired manner, each flexible arm (166) of the flexible pointer (162) performing an angular rotation θ1 applied by the wheel assembly of the watch movement to the actuation mechanism (160; 191; 220), the angular rotation θ1 applied by the wheel assembly of the watch movement being further angularly rotated by the actuation mechanism (160; 191; 220) by an additional angle. Modulation is performed on the additional angles applied in opposite directions to the two flexible arms (166A, 166B) of the flexible pointer (162). The shape and length changes of the flexible pointer (162) in two closely successive rotations were determined such that the tip (164) of the flexible pointer (162) traces two distinct paths, and the shape and length changes ΔL(φ) are performed for a rotation of angle 2xθ1 applied to the input of the actuation mechanism by the gear train of the watch movement. in, The actuation mechanism includes cam follower fingers (186; 214; 238) that sense the profile (188; 216; 240) of a cam (190; 218; 242), the profile (188; 216; 240) determining changes in the shape and length of the flexible pointer (162), while the cam follower fingers (186; 214; 238) travel along the entire profile of the cam on the profile (188; 216; 240) of the cam (190; 218; 242), the flexible pointer (162) performs two distinct successive rotations; and The actuation mechanism (160; 191; 220) includes at least one rotating planetary gear retaining frame (172; 192, 194; 228), which is driven by the gear train of the watch movement and carries the cam follower finger (186; 214; 238). While the gear train of the watch movement applies an angular rotation θ1 to the planetary gear retaining frame (172), the planetary gear retaining frame (172) performs an angular rotation. .

2. The actuation mechanism (160; 191; 220) according to claim 1, characterized in that, The watch movement's wheel assembly, which applies an angular rotation θ1 to the actuation mechanism (160; 191; 220), must perform two complete rotations so that the cam-driven fingers (186; 214; 238) travel along the entire profile (188; 216; 240) of the cam (190; 218; 242), and the tip (164) of the flexible pointer (162) traces a path (244, 246) corresponding to the two different complete rotations.

3. The actuation mechanism (160; 191; 220) according to claim 1 or 2, characterized in that, By means of the mechanical tension caused by the stress assembly of the flexible pointer (162), the cam follower fingers (186; 214; 238) are held against the profile (188; 216; 240) of the cam (190; 218; 242).

4. The actuation mechanism (160; 191; 220) according to claim 1, characterized in that, The cams (190; 218) are fixed.

5. The actuation mechanism (160; 191; 220) according to claim 4, characterized in that, The planetary gear retainer (172) carries a first sun gear pair and a second sun gear pair arranged coaxially with each other. The first sun gear pair consists of a first sun pinion (176) and a first sun gear (180), and the second sun gear pair consists of a second sun pinion (178) and a second sun gear (182). The first sun pinion (176) meshes with a planet gear (184) carried by the planetary gear retainer (172), and the planet gear (184) carries the cam follower finger (186). The planetary gear (184) meshes with the intermediate gear (189), the intermediate gear (189) itself meshes with the second sun pinion (178), the actuation mechanism (160) further includes a first gear shaft (168) and a second gear shaft (170) arranged coaxially with each other, the first tube (166A) of the flexible pointer (162) is fastened to the first gear shaft (168), and the second tube (166B) of the flexible pointer (162) is fastened to the second gear shaft (170).

6. The actuation mechanism (160; 191; 220) according to claim 5, characterized in that, The second sun gear (182) meshes with the first indexing shaft (168) at a multiplication factor of 2, the first indexing shaft (168) at an angle The first sun gear (180) rotates, and the first sun gear (180) meshes with the second indexing gear (170) at a multiplication factor of 2, the second indexing gear (170) at an angle Rotate.

7. The actuation mechanism (160; 191; 220) according to claim 4, characterized in that, The actuation mechanism (191) includes a first planetary gear retaining frame (192), the first planetary gear retaining frame (192) being... The gear reduction ratio meshes with a second planetary gear retainer (194), the first planetary gear retainer (192) carrying concentric first and second index gear shafts (196 and 198), each flexible arm (166A, 166B) of the flexible pointer (162) being press-fitted onto one of the index gear shafts (196, 198), the first and second index gear shafts (196, 198) being kinematically associated with each other such that the first and second index gear shafts (196, 198) rotate relative to the first planetary gear retainer (192) in opposite directions. The second planetary gear retainer (194) carries the sun gear pair that engages with the second indexing shaft (198). The second planetary gear retainer (194) also carries planet gears (212) that engage with the sun gear pair. The planet gears (212) are equipped with cam follower fingers (214) arranged to travel along the profile (216) of the cam (218). The cam follower fingers (214) sense the fixed profile (216) of the cam, and the planet gears (212) rotate at an angle. To modulate the angular rotation (θ1) applied by the gear pair of the watch movement to the sun gear pair, the sun gear pair then drives the second minute gear shaft (198) at an angle with a multiplication factor of 2. Rotation, the second gear shaft (198) drives the first gear shaft (196) at an angle Rotate.

8. The actuation mechanism (160; 191; 220) according to claim 1, characterized in that, The cam (242) is movable.

9. The actuation mechanism (160; 191; 220) according to claim 8, characterized in that, The actuation mechanism (220) includes a planetary gear retaining frame (228) driven by a wheel of the watch movement at an angle θ1. The planetary gear retaining frame (228) further drives an intermediate reduction gear pair (222). The planetary gear retaining frame (228) carries a first gear shaft (230) and a second gear shaft (232) concentric with the first gear shaft (230). The planetary gear retaining frame (228) also carries a first planetary gear (234), which meshes with the first gear shaft (230) on one hand and with the second planetary gear (222) on the other hand. 36) Engagement: The second planetary gear (236), which engages with the second indexing shaft (232), is equipped with a cam follower finger (238) arranged to travel along the profile (240) of a rotating cam (242), the cam follower finger (238) being elastically held against the profile (240), the rotating cam (242) engaging with the intermediate reduction gear pair (222) such that when the planetary gear retaining frame (228) rotates through angle θ1, the rotating cam (242) rotates through angle θ1. The second planetary gear (236) thus rotates by an angle θ1 together with the planetary gear retaining frame (228) about the output axis (D0), while rotating by the following rotation angle: that is, the rotation angle is determined as an angle The rotation of the two flexible arms (166a, 166b) of the flexible pointer (162) is modulated so that the flexible pointer (162) changes its length and shape in a desired manner.

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