CH715211A2 - Timepiece mechanism with variable geometry with elastic hand. - Google Patents

Abstract

The invention relates to a clockwork display mechanism with variable geometry comprising an elastic hand (1) with a drive barrel (2) secured to a flexible blade (3) in one piece comprising a plurality of flexible segments (5A, 5B) contiguous at the level of vertices (6), a first of which (5A) extends between the first barrel (2) and a first vertex (6), and on the other hand a second barrel also integral with the flexible blade ( 3). The mechanism also includes first drive means (11) for pivoting the first barrel (2) around an outlet axis (D), and second stressing means (12) comprising second drive means (13) of the second barrel, to vary the position of the first vertex (6) relative to the outlet axis (D). The first drive means (11) and / or the second stressing means (12) comprise an accelerator or retarder device, which is arranged to accelerate or stabilize in speed or to slow down at least the first gun (2) and / or the second barrel (4) over at least part of its angular travel.

Description

Description Field of the Invention The invention relates to a clockwork display mechanism for variable geometry timepieces, comprising at least one elastic needle which comprises a first drive barrel secured to a flexible monobloc blade and which comprises a plurality of flexible segments joined end to end at at least one vertex, a first flexible segment of which extends between said first barrel and a first vertex, said display mechanism comprising first means for driving said first barrel around an exit axis, and second means for constraining at least said first flexible segment which are arranged to vary the position of at least said first vertex relative to said exit axis, said first vertex being at a variable distance from said first barrel as a function of the forces applied to said flexible blade by said second placing means constraint.

The invention also relates to a timepiece movement comprising at least one such display mechanism.

The invention also relates to a timepiece comprising at least one such clockwork movement, or / and comprising at least one such display mechanism.

The invention also relates to a scientific apparatus comprising at least one such clockwork movement, and / or comprising at least one such display mechanism.

The invention relates to the field of analog display mechanisms by mobile mechanical components, for timepieces or scientific apparatus.

Background of the invention [0006] The documents EP 2 863 274 and EP 3 159 751 in the name of MONTRES BREGUET SA describe different arrangements of elastic hands, allowing the adaptation of a display on a timepiece to the shape of its case or of its dial, thanks to a radial extension obtained by piloting such an elastic needle comprising distinctly driven flexible segments.

Claims (30)

Summary of the invention The invention proposes to provide a reliable and very robust solution to the problem of providing a variable radial extension indicator according to its position and its control. To this end, the invention relates to a clockwork display mechanism comprising at least one such elastic needle, which comprises a first drive shaft secured to at least one flexible blade, according to claim 1. The invention also relates to a timepiece movement comprising at least one such display mechanism. The invention also relates to a timepiece comprising at least one such clockwork movement, or / and comprising at least one such display mechanism. The invention also relates to a scientific apparatus comprising at least one such clockwork movement, and / or comprising at least one such display mechanism. Brief description of the drawings [0012] Other characteristics and advantages of the invention will appear on reading the detailed description which follows, with reference to the accompanying drawings, where: fig. 1 represents, diagrammatically and in plan view, a watch, in particular a ladies' watch of oval shape, comprising a display mechanism according to the invention, comprising an elastic needle of variable length, the distal end of which, which is formed by a vertex between two flexible blades, is arranged to travel a non-circular trajectory; this elastic needle is shown in a twelve o'clock position, in which the elastic needle has an almond shape, and where the apex is in its position furthest from an axis of exit; fig. 2 shows, similarly to FIG. 1, the same watch, in a position at six o'clock of the elastic needle which then has a shape of a heart, and where the apex is in its position closest to an axis of exit; fig. 3 shows, similarly to FIG. 1, the same watch, in the same position and in the almond shape of the elastic needle, this view shows a trajectory of the apex which, relative to the outlet axis, is elongated at an angle of 120 ° from eight hours to twelve hours, and shortening on another angle of 120 ° from twelve hours to four hours; this same trajectory is substantially circular relative to a circular eccentric axis, at an angle of approximately 240 °, CH 715 211 A2 from the eight o'clock position to the twelve o'clock position, and from the latter to the four o'clock position; fig. 4 shows, similarly to FIG. 2, the same watch, where the top of the needle is in the four o'clock position, and where the shape of this elastic needle is now a heart shape, after a change in shape which occurred before this position at four o'clock; fig. 5 shows, similarly to FIG. 4, the same watch, where the apex of the hand is in the eight o'clock position, and where its shape is always the same heart, the apex has traveled, between the representations in FIG. 4 and fig. 5, a circle here centered on the exit axis, and before a new change of shape after this position at eight o'clock, to find the almond shape of FIG. 3; fig. 6 shows, schematically and in plan view, the elastic needle of FIGS. 1 to 5, in a constrained service position, where two end barrels which it comprises, at the ends of its two flexible blades, are aligned and superposed one on the other, each driven by a different mobile; fig. 7 is a variant of FIG. 6, where the apex includes an eye arranged to allow a particular visualization on a dial; fig. 8 shows, similarly to FIG. 1, the same watch, in the same position and in an empty form, in almond shape, of the elastic needle, which is free, in an unstressed state, and fixed to a driving mobile by only one of its barrels ; fig. 9 is a view from the left of the watch in FIG. 8; fig. 10 shows, similarly to FIG. 1, the same watch, in the same position and where the elastic needle comprises a breakable element connecting its two end barrels and facilitating its assembly on the clockwork movement, as well as the manipulation of the second barrel for its positioning above the first, before the watchmaker ruptures fragile attachments connecting the breakable element to the two guns; fig. 11 is a block diagram, in exploded perspective, of a display mechanism according to the invention, where a power take-off, in the lower part of the figure, is arranged to drive two gear trains, the first to drive the first gun, and the second to drive the second gun; the arrows illustrate the transmission of movement; the gear trains have shaped cogs, which are arranged to accelerate, stabilize, or slow down the rotation of one of the guns relative to the other; the elastic needle is shown in a completely free state, with no breakable element; this view also shows a conventional hand, coaxial with the elastic hand, for the display of other information, in particular time; fig. 12 is a perspective view of a display mechanism according to a first variant of the invention, in which an input mobile, arranged to cooperate with a mobile output from the clock movement, is coaxial with a shaft of drive, and to a carriageway on which the first barrel is shown mounted, the second barrel being shown in the free state of the elastic needle before its positioning coaxial with the first barrel on the drive shaft; each form wheel has an angular marking so as to correctly ensure the form gear effect; fig. 13, similar to fig. 12, illustrates the positioning of a cutting plane, according to which the cutting of FIG. 14; fig. 14 is a partial section along the plane displayed in FIG. 13, of a clockwork movement driving a mechanism according to the invention; fig. 15 illustrates, in plan view, a gear train with two stages so as to balance the angular travel of each stage, and where each stage comprises a form train; fig. 16 is a plan view of a display mechanism according to a second variant of the invention, in which an input mobile, arranged to cooperate with a mobile output from the clock movement, is distinct from the axis output, and where each gear train comprises two stages so as to balance the angular travel of each stage, and where each stage comprises a form train; fig. 17 to 20 illustrate the construction of form cogs: CH 715 211 A2 fig. 17 illustrates the choice of a space law to vary the radial length of the needle as a function of the angular difference between its two barrels, this figure illustrates the exit angle as a function of the entry angle ; fig. 18 illustrates the calculation of the primitive profiles of the teeth, according to the spacing chosen for their realization; fig. 19 illustrates the calculation of the leading teeth, as a function of the number of teeth defined; fig. 20 illustrates the calculation of the gear teeth, which then allows the cutting of the two wheels with the profile thus defined; fig. 21, similar to fig. 17 but reversed, illustrates three successive zones of radial lengthening of the needle, stabilization of the length of the needle, and shortening of the needle; fig. 22 is a plan view of the superposition of the three states illustrated in FIGS. 3 to 5, and the arrows highlight a phase of contraction CO of the needle between the positions at twelve o'clock and four hours from its apex, a phase of stability ST with constant elongation between the positions at four and eight hours, and a DE relaxation phase between the eight o'clock and twelve o'clock positions; fig. 23 is a diagram showing on the ordinate the evolution of the torque between the flexible segments of the elastic needle, as a function of the angle covered, with a first zone for reducing the length of the elastic needle with consumption of torque, a second phase for maintaining the length of the needle at substantially constant torque, and a third phase for lengthening the needle with restitution of the torque; fig. 24 is a diagram showing on the ordinate the evolution of the torque on a barrel, as a function of the angle of rotation of a barrel; fig. 25 is a diagram showing on the ordinate the radial extension of the needle, as a function of the angle of rotation of a barrel; fig. 26 shows, in plan view, a cog in shape comprising two wheels not of revolution, and comprising marks for their relative indexing with respect to one another; fig. 27 shows such a wheel, with developing teeth, enlarged in magnifying glass; fig. 28 shows such a wheel, with sinus toothing, enlarged in magnifying glass. Detailed description of the preferred embodiments The invention relates to a display indicator for a timepiece or for a scientific device. Documents EP 2 863 274 and EP 3 159 751 in the name of MONTRES BREGUET SA describe a watch display by elastic needle, and their characteristics can be directly used for the production of a display mechanism according to the present. The invention is described here in the particular, but not limiting, case of a rotary indicator, and in particular of an elastic needle. However, the principle is applicable to an indicator with a mobility path other than circular, for example a linear cursor, or other, in particular in space. The invention is more precisely described for this application of a flexible indicator to a needle, but it is applicable to other forms of indicators, in plan or even in three dimensions. Similarly, drive means comprising cogs are described below, but the invention is equally applicable to analog display means for an electronic or electric device, a quartz watch or other. The principle of the invention is to produce a display mechanism, at least one indicator of which, in particular a hand, for example the minute hand for a watch, has a variable length, or a variable radial extension, or a variable form. The invention relates to a clockwork display mechanism 10 with variable geometry, which comprises at least one elastic needle 1. This elastic needle 1 comprises a first drive barrel 2, which is integral with at least one flexible blade 3 in one piece, and a flexible blade 3 unique in the particular and nonlimiting case of the figures. The display mechanism 10 includes an input mobile 71, which is arranged to be pivotally driven about an input axis by a movement 20, and which defines an angle of entry relative to a reference direction. CH 715 211 A2 The flexible blade 3 comprises a plurality of flexible segments 5.5A, 5B, which are joined end to end at at least one vertex 6, and preferably two successive flexible segments are joined by a such a summit. In the case of the figures, a first flexible segment 5A of the flexible blade 3 extends between the first barrel 2 and a first vertex 6. More particularly the invention is illustrated in the most common case where the needle has two flexible segments 5 joined by a single apex 6, which is used for display. The display mechanism 10 includes first drive means 11 for the first barrel 2 around an outlet axis D, and includes second means 12 for stressing at least the first flexible segment 5: these second means 12 are arranged to vary the position of at least the first vertex 6 relative to the outlet axis D. The first vertex 6 is thus at a variable distance from the first barrel 2, depending on the forces applied to the blade flexible 3 by the second means 12 for stressing. Figs. 1 to 5 show a particular case of such a mechanism, with an elastic needle 1 comprising a single apex 6, which follows on an upper part of its travel an eccentric circle with respect to the outlet axis, and on a lower part another circle centered on Exit Tax. Naturally, this is a special case, and the mechanism 10, for the same ove-shaped watch, can also be dimensioned to follow the outline of the case, or any other outline highlighting the product. According to the invention, the first drive means 11 and / or the second means 12 for stressing, and in particular the second drive means 13 which they comprise, comprise a first gear train of form 111 and / or respectively a second train of form 131, which is arranged or which are arranged to accelerate or stabilize in speed or slow down at least the first barrel 2, and / or the second barrel 4, over part of its angular travel. More particularly, the first drive means 11 and the second means 12 for stressing, and in particular the second drive means 13 which they comprise, comprise at least one first gear train of form 111 and respectively at least a second gear train of form 131 which are arranged to accelerate or stabilize in speed or slow down the first gun 2, and respectively the second gun 4, over at least part of the angular travel of the first gun 2, and respectively of the second gun 4. In a particular embodiment, illustrated by FIGS. 1 to 5, the first drive means 11 and the second stressing means 12 are arranged to drive the elastic needle 1 over its entire angular travel around the outlet axis D, and give it, in projection on a display plane P or on a dial, and at different angular positions of the elastic needle 1, at least a first form where the flexible segments 5: SA, 5B, which the flexible blade 3 does not cross not outside the first barrel 2, and at least a second form where the flexible segments 5: 5A, 5B, which the flexible blade 3 comprises intersect outside the first barrel 2. In the particular and non-limiting case illustrated by the figures , this first form is a form of almond, and this second form is a form of heart. In another variant where the elastic needle 1 traverses the surface defined by an ellipse, this needle can successively occupy, on its revolution, an alternation of first shapes and second shapes, for example an almond shape on each of the two ends of the major axis of the ellipse, and a heart shape on each of the two ends of the minor axis of the ellipse. More particularly, and as taught by documents EP 2 863 274 and EP 3 159 751 the elastic needle 1 comprises a second drive barrel 4 also integral with the flexible blade 3. The second means 12 for setting under stress then comprise second drive means 13 of the second barrel 4 in a mounted state of the elastic needle 1. In this mounted state of the elastic needle, both the first barrel 2 is, advantageously but not necessarily in a prestressed operating state, driven by the first drive means 11, and the second barrel 4 is, advantageously but not necessarily in a prestressed operating state, driven by the second drive means 13. And at least one of the vertices 6 is, in an unconstrained free state of the elastic needle 1 in which both the first barrel 2 and the second barrel 4 are not subjected to any stress , distant from the first barrel 2 and the second barrel 4, which first barrel 2 and second barrel 4 are spaced apart from each other in this free state of the elastic needle 1. In the particular case of the figures where the flexible blade 3 has only a first flexible segment 5A and a second flexible segment 5B, this vertex 6 which joins them is unique. Thus, more particularly, this first flexible segment 5A carries the first barrel 2 at a first end 52, this second flexible segment 5B joined to the first flexible segment 5A carries the second barrel 4 at a second end 54. And, in the free state of the elastic needle 1, the first end 52 and the second end 54 are spaced from each other, or form a non-zero angle with each other from the apex 6 of junction of the first flexible segment 5A and the second flexible segment 5B. More particularly, the output of the second drive means 13 of the second barrel 4 is coaxial with the output of the first drive means 11 of the first barrel 2, in the mounted state of the elastic needle 1. This arrangement is however not compulsory, in particular in the case of a retrograde display, where the axes of the first gun 2 and of the second gun 4 can be distinct. CH 715 211 A2 According to the invention, the first drive means 11 and the second drive means 13 comprise an accelerator or retarder device, which is arranged to accelerate or stabilize in speed or slow down at least the first gun 2 and / or said second barrel 4 over at least part of its angular travel. In a first variant, the first barrel 2 has an advance or a delay with respect to the value of the entry angle which is symmetrical to the delay or advance of the second barrel 4 with respect to the angle of entry, so that the first vertex 6 always displays, with respect to the exit axis D and to the reference, an angle equal to the entry angle. In another variant, the first barrel 2 has an advance or a delay with respect to the value of the entry angle which is, in absolute value, different from the delay or the advance of the second barrel 4 by relative to the entry angle, so that the first vertex 6 displays, relative to the exit axis D and to the reference, a variable angle relative to the entry angle throughout its course. This particular advance and / or delay arrangement relative to the entry barrel allows the hand to point the time (or another display) just on the dial, and in particular for an irregular display, for example a square trajectory. where the time is separated into twelve equidistant segments on the square trajectory, which cannot be managed in the same way as twelve indexes separated by 30 °. In yet another variant, the needle 1 is arranged to perform a non-retrograde total stroke, and, over the total stroke, the average speed of the first barrel 2 is equal to the average speed of said second barrel 4. Many configurations can be envisaged: - if the arms of the needle are symmetrical, a symmetrical advance and delay are necessary, so that the needle points to the correct hour; - if the arms of the needle are asymmetrical, there must be an advance and a delay so that the needle points at the right time; - we assume that the hand is pointing the right time. We can also have a graduation which is not separated every 30 ° as explained above. In a particular embodiment which will be detailed below, the accelerator or retarder device comprises a first train of form 111 and / or respectively a second train of form 131. In another particular embodiment which will be detailed below, the accelerator or retarder device comprises a device with a first differential 912 on the drive train of the first gun 2 and / or a second differential 914 on the train of drive of the second barrel, and at least one cam 902, 904, constituting an input of such a differential 912, 914. In yet another embodiment, the accelerator or retarder device comprises simple cogs suitably arranged to perform the required accelerations or decelerations. More particularly, and as visible in FIGS. 11 to 20, the first drive means 11 and the second drive means 13 comprise, respectively, at least one first gear train of form 111 and at least one second gear train of form 131, which are each arranged or which are arranged for speed up or stabilize or slow down the first gun 2 and respectively the second gun 4 over part of its angular travel. By gear train here we mean that at least one wheel of the train is not of revolution; more particularly, at least two antagonistic wheels of this cog are not of revolution, and are arranged to permanently mesh with minimal play with each other at constant center distance. More particularly, the first gear train 111 and the second gear train 131 are arranged to accelerate or respectively brake the first gun 2, and to brake or respectively accelerate the second gun 4 over at least part of the angular travel of the elastic needle 1, or even only over part of the angular travel of the elastic needle 1. Stated otherwise, one of the guns takes an angular advance with respect to the entry angle, while the other gun takes an angular delay relative to the entry angle. Thus, in a particular embodiment of the invention, the first barrel 2 has an advance or a delay relative to the value of said entry angle which is symmetrical to the delay or in advance of the second barrel 4 with respect to this same entry angle, so that the first vertex 6 always displays, with respect to the exit axis D and to the reference direction, an angle equal to the entry angle. Thus, considering the embodiment according to FIGS. 3 to 5, with a total angular stroke CAT of 360 °, from a position in fig. 3 where the apex 6 of the hand 1 is at twelve o'clock, to move to the four o'clock position in fig. 4, by turning clockwise, the second barrel 4 of the second flexible segment 5B slowed down by 60 °, and the first barrel 2 of the first flexible segment 5A accelerated by 60 °. Indeed, none of the flexible segments 5 of the hand 1 indicates, only, the time, it is only the result of the rotation of the two barrels which determines a time indication by the top 6 of the hand 1, Between the position of fig. 4 and at the eight o'clock position of fig. 5, the barrels remain synchronous with their offset. To go from the eight o'clock position in fig. 5 to that at twelve o'clock in fig. 3, it is the opposite, the second gun 4 of the second flexible segment 5B accelerated by 60 °, and the first gun 2 of the first flexible segment 5A slowed down by 60 °. The invention is illustrated in the figures by the particular case of a continuous watch display displaying a full revolution, it is understood that the invention is applicable to any display, in particular a retrograde display. CH 715 211 A2 More particularly, the first gear train 11 and the second gear train 131 are arranged to symmetrically pilot the first barrel 2 and the second barrel 4, so that the first flexible segment 5A and the second flexible segment 5B are symmetrical with respect to a radial coming from the outlet axis D and passing through the apex 6 of junction between the first flexible segment 5A and the second flexible segment 5B, over at least part of the angular travel of the elastic needle 1. This configuration is not limiting, but it offers the advantage of subjecting the first flexible segment 5A and the second flexible segment 5B to symmetrical stresses. More particularly, the first gear train 111 and the second gear train 131 each have at least one pair of wheels arranged to cooperate in mesh with one another and whose geometric supports is that is to say the primitive curves, teeth are not of revolution. More particularly still, the first drive means 11 and / or the second drive means 13 comprise at least a first gear train 115,135, and a second gear train 116,136, which are arranged to control each part the shape transformation of the elastic needle 1 over at least part of its angular travel, with weighting by stage. This weighting makes it possible to distribute part of the deformation on each of the stages, which makes it possible, in each gear train, to keep wheels whose geometry is close to a circular geometry, so as to allow a suitable meshing of the teeth, and prevent their wear. Indeed, the cogs of shape are not circular, but must not be too deformed, that is to say that their shape must allow an engagement without bracing, and without too much sensitivity to variations in center distance and to manufacturing tolerances. We can thus avoid the interference defects that cut teeth would present if the primitive curves of the teeth moved too far from the circular shape. It is therefore a question of defining a compromise between a form which is sufficiently non-circular to actuate the needle, and a form of resistance to wear. The distribution over several stages makes it possible to fulfill these conditions: each stage participates in the deformation of the needle, but its primitive curves remain close to a circular shape, this is what is called here the weighting by stage, the overall accumulation of these stages cogs making it possible to ensure the desired deformation at the level of the needle. The figures illustrate without limitation a variant with two stages of cogs, but this number of two is not limiting, only the total thickness of the movement and the loss of efficiency due to friction limit the number of stages. More particularly, both the first gear train 115, 135, and the second gear train 116,136, respectively comprise a first gear train 111 and a second train gear 131. Figs. 11 to 20 detail certain particular arrangements of such deformed cogs. [0050] FIG. 11 schematizes the operation of such a mechanism 10, the arrows symbolize the transmission of the movement to the barrels, from a power take-off 21 at the level of a clockwork movement 20, which can be both mechanical and electronic, symbolized by lower part of the figure, and which is arranged to drive by a single input mobile 71 two gear trains: a first gear train comprises idler wheels 79 and 80 around a first axis DA and wheels 73, 78, and 81 around the main pivot axis D to drive the first gun 2, - And a second gear train comprises idler wheels 74, 75, around a second axis DB and a wheel 76 around the main pivot axis D to drive the second barrel 4. It is noted that all of the gear train is under tension, due to the play of the elastic needle due to its preload. FIG. 11 again shows a conventional needle 101, coaxial with the elastic needle 1, for the display of other information, in particular time. Figs. 12 to 14 illustrate more precisely a display mechanism 10 according to a first variant of the invention, for displaying the minutes with the elastic hand 1. In this first variant, an input mobile 71 is arranged to cooperate with an output mobile 21 of the clockwork movement 20, along an input axis DO, and is guided on a fixed tube 70. This input mobile 71, which is a roadway, is arranged to drive, directly or through a friction lantern allowing a time-setting adjustment, a driving road 72 which is coaxial with it. This driving pavement 72 is of revolution, and drives a first wheel of shape 78, which meshes with a second wheel of complementary shape 79 mounted mad (with backlash) around the first axis DA, and which is pivotally secured of a third wheel of shape 80, which meshes with a fourth idler wheel of complementary shape 81, which here pivots around the axis of exit D of the barrels, and which comprises a carriageway 82 for fixing the first barrel 2. The same driving pavement 72 drives a fifth wheel of shape 73, which meshes with a sixth wheel of complementary shape 74 mounted madly around the second axis DB, and which is pivotally attached to a seventh wheel of shape 75, which meshes with an eighth idler wheel of complementary shape 76, which here pivots around the outlet axis D of the barrels, and is integral with a shaft 77 on which the second barrel 4 is fixed. Each form wheel has an angular location so as to correctly index the form train, as detailed in fig. 26 which details a cog in form comprising two wheels 75 and 76 not of revolution, and comprising references 275 and 276 for their relative indexing relative to one another, as well as oblongs 175 and CH 715 211 A2 176 facilitating their installation, which in particular allows them to be joined and indexed by means of a pin or the like. The driving pavement 72 also drives a ninth wheel 91 which comprises a mobile pivoting about an axis of the hours DH, which comprises a pinion 92 driving the wheel 93 of an hours pavement 94 receiving the hour hand 100 . Figs. 15 and 16 illustrate a second variant of the invention, in which an input mobile, arranged to cooperate with an output mobile from the clockwork movement, pivots about an input axis DO which is here distinct from the exit axis D, and where each gear train comprises two stages so as to balance the angular travel of each stage, and where each stage comprises a form train: - A first gear train comprises a first stage with a first wheel of form 101 pivoting around the entry tax DO, which meshes with a second wheel of complementary shape 102, mounted madly around a first secondary axis D1. This second wheel of complementary shape 102 is pivotally attached to a third deformed wheel 103, which meshes with a fourth wheel of complementary shape 104, pivotally mounted on the output axis D, and designed for fixing one of the two guns; - a second gear train, isolated in fig. 16, comprises a first stage with a first wheel of form 201 pivoting around Entrance tax D0, which meshes with a second wheel of complementary form 202, mounted idly around a second secondary axis D2. This second wheel of complementary shape 202 is pivotally attached to a third wheel of shape 203, which meshes with a fourth wheel of complementary shape 204, pivotally mounted on the output axis D, and designed for fixing the other gun. The case of a construction with radial symmetry of movement between the two flexible segments of the same such needle 1 uses two similar sets of cogs of identical shape, one mounted at the place, the other at the towards. Figs. 17 to 20 illustrate the construction of the cogs of form, which begins with the choice of a law of space to vary the radial length of the needle according to the angular distance between its two barrels, fig. 17 illustrates the exit angle as a function of the entry angle for one of the two needle barrels. This law of space allows the calculation of the primitive profiles of the teeth, according to the spacing chosen for their realization, as visible in fig. 18. The calculation of the leading teeth is then carried out according to the number of teeth defined, and the type of profile chosen, in particular involute or sinus type, according to FIG. 19, then the calculation of the teeth carried out, according to FIG. 20, then allows the taiilage of the two wheels to the profile thus defined. Figs. 17 and 20 illustrate the law of space, with three successive zones of radial extension of the needle, stabilization of the length of the needle where the ratio between the exit angle of one of the two guns and the angle d Entry into the mechanism is substantially constant, and shortening the needle. [0062] FIG. 22 shows the superposition of the three states illustrated by FIGS. 3 to 5, and the arrows highlight a phase of contraction CO of the needle 1 between the positions at twelve o'clock and four hours from its apex 6, a phase of stability ST with constant elongation between the positions at four o'clock and at eight o'clock, and a DE relaxation phase between the eight o'clock and twelve o'clock positions. This weighting is made possible by the use of form cogs, and in particular of the multi-stage cog mechanisms, which make it possible to impose sufficient angular deflections on the barrels, to allow significant changes in shape, and in particular for ability to cross flexible segments as in heart shape. These cogs in shape allow you to safely slow down one cannon in relation to the other. The wheel of FIG. 27 is an example of optimization of the case of this fig. 22; to correct the trajectories on angles of 140 ° -80 ° -140 ° as illustrated, instead of 120 ° -120 ° -120 ° which would be more balanced, it is necessary, without weighting by particular stage, i.e. -to say if the upper stage and the lower stage each carry out half of the angular transformation, to design wheels with very strong deformations, and very inclined teeth, difficult to machine, and fragile. Another weighting, for example 20% of the deformation on the lower floor and 80% on the upper floor, makes it possible to have wheels closer to a round shape, easier to machine, and with teeth close to the standard. , therefore with better kinematic and tribological parameters, and less wear. FIG. 23 shows the evolution of the torque between the flexible segments of the elastic needle, as a function of the angle covered, with a first zone for reducing the length of the elastic needle with torque consumption, a second phase of maintaining the length of the needle at substantially constant torque, and a third phase of lengthening of the needle with restitution of the torque, FIG. 24 illustrates the evolution of the torque on a barrel, as a function of the angle of rotation of a barrel, and FIG. 25 shows the radial extension of the needle, as a function of the angle of rotation of a barrel. The elastic needle 1 can be produced in different ways. In a first variant, in the free state, the elastic needle 1 extends over a single plane level comprising the first barrel 2 and the second barrel 4, and the elastic needle 1 is then arranged to be mounted twisted in a constrained service position in which the first barrel 2 and the second barrel 4 are superposed on each other. CH 715 211 A2 In a second variant, in the free state, the elastic needle 1 extends over a first plane level comprising the first barrel 2 and over a second plane level comprising the second barrel 4, and comprises a connection zone between the first plane level and the second plane level at a vertex 6 between a first flexible segment 5A carrying the first barrel 2 and a second flexible segment 5B joined to the first flexible segment 5A and carrying the second barrel 4 , and the elastic needle 1 is arranged to be mounted without twisting in a service position under stress in which the first barrel 2 and the second barrel 4 are superimposed on each other. In another particular variant, when the elastic needle 1 comprises more than two flexible segments 5, in the free state, the elastic needle 1 extends over at most as many parallel levels as flexible segments 5, and is designed to be mounted without twisting in a service position under stress in which the first barrel 2 and the second barrel 4 are superimposed on each other. In a particular variant intended to facilitate assembly, visible in FIG. 10, in the free state, the elastic needle 1 comprises a breakable element 24 joining the first barrel 2 and the second barrel 4, to facilitate the mounting of the elastic needle 1 on a mobile for driving the first barrel 2 or the second barrel 4, this breakable element 24 being arranged to be broken and allow the passage of the elastic needle 1 into a service position under stress in which the first barrel 2 and the second barrel 4 are superposed on each other. [0069] FIG. 7 illustrates a particular variant where the elastic needle 1 comprises at least one eye 60, which is arranged to constitute a window for reading an indication appearing on a dial 61 which comprises the mechanism 10, and in front of which extends the elastic needle 1, or that includes a clockwork movement 20, on which the mechanism 10 is arranged to be attached. For example, this eye allows you to view a city in a GMT application, or to distinguish the morning time from 0 to 12 from the afternoon time from 13 to 24, in a particular application where training of the display mechanism is made on two revolutions, the first with a certain extension of the elastic hand 1 for the display of the morning hours, and the second with a different extension for the display of the afternoon hours ; of course this variant can also accommodate a display by the tops of the needle 1, the presence of such an eye 60 provides reading comfort to the user. Fig. 7 also illustrates two indexes, inside and outside, on either side of this eye 60, which also allow specific readings, depending on the dial configuration adopted. One of the great advantages of the invention is to allow great freedom of design of the dial, and the postponement of certain display areas outside of unavailable areas, for example due to the presence of a vortex, or else another complication. Advantageously, the needle 1 is made of micro-machinable material according to a "LIGA" process, in particular nickel-phosphorus NIP ₁₂ or the like. Such a needle can be golden, or receive another coloring, the adhesion being satisfactory on such a material. The needle 1 can be colored by different processes: PVD, CVD, ALD, galvano, paint, lacquer, or other coating or ionization. The needle 1 may include a gem setting or the like, and / or a decoration by guilloche, engraving, chamfering, or even enamelling, the latter being reserved for areas with low deformation such as the turn of the barrels, a turn of eye, tip, or the like. More particularly, the mechanism 10 constitutes an additional module, which is arranged to be attached to a clockwork movement 20, and the first drive means 11 and the second means 12 for stressing have a common input 71 , which is arranged to be driven by a single outlet 21 which comprises the movement 20, such as the road which turns in one hour, or the mobile minutes. In a variant, in addition to or instead of the cogs of form, the mechanism 10 comprises, on the one hand between the input mobile 71 arranged to be driven by the movement 20, and on the other hand the first barrel 2 and / or the second barrel 4, at at least one stage, a cam 902, 904. This cam is arranged to drive a differential 912,914, a first input of which is constituted by the input mobile 71, including a second input is a mobile, in particular a rake 922,924, controlled by this cam 902, 904, and the output of which meshes with the gear train for transmitting the movement to the first gun 2 or respectively to the second gun 4. In a first application of this variant, the mechanism 10 comprises, between the input mobile 71 and the first barrel 2 at at least one stage, a single cam 902 arranged to drive a first differential 912, one of which first input is constituted by the input mobile 71, a second input of which is a first mobile or a first rake 922 controlled by the cam 902, and the output of which meshes with the gear train for transmitting movement to the first barrel 2, and between the input mobile 71 and the second barrel 4, the same single cam 902 arranged to drive a second differential 914, a first input of which is constituted by the input mobile 71, of which a second input is a second mobile or a second rake 924 controlled by cam 902, and the output of which meshes with the gear train for transmitting movement to the second barrel 4. In a second application of this variant, the mechanism 10 comprises, between the input mobile 71 and the first barrel 2 at at least one stage, a first cam 902 arranged to drive a first differential 912, one of which first input is constituted by the input mobile 71, a second input of which is a first mobile or first rake 922 controlled by the first cam 902, and the output of which meshes with the gear train for transmitting movement to the first barrel 2; and, between the input mobile 71 and the second barrel 4, a second cam 904 driven by the input mobile and arranged to drive a second differential 914 of which a first input is constituted by CH 715 211 A2 the input mobile 71, a second input of which is a second rake 924 controlled by the second cam 904, and the output of which meshes with the gear train for transmitting the movement to the second barrel 4. The use of a cam allows highly non-circular trajectories, and also with jumps of the needle. The use of a single cam for the two differentials allows a simultaneous jump of the two guns, for example at midnight; the first differential adds information from the cam for the first barrel, and the second differential subtracts the information for the second barrel. In another particular variant, at least one wheel that includes the gear mechanism arranged between on the one hand the input mobile 71 arranged to be driven by a movement 20, and on the other hand the first barrel 2 and / or the second barrel 4, at at least one stage, has an incomplete toothing, each missing tooth authorizing a relaxation of the elastic needle 1 f by rotation of only one of the barrels 2, 4, during the passage of the space corresponding to a missing tooth, or to the missing teeth, so as to command a retraction of the apex 6 of the elastic needle 1. In particular, it is then possible to use a gear train comprising one or more, or even all, of the circular wheels, of which at least one circular wheel is devoid of one or more teeth to allow the needle to relax, and to perform a jump at the end of the so-called display spiral course performed by the apex 6 of the needle 1. If for example the first barrel rotates faster than the second barrel, and if the driving surface 72 is locally devoid of teeth, the needle tends to contract, for example over two turns, and, when the missing teeth release the first barrel, the needle tightens but the second barrel does not move, the top of the needle retreats. The advantage of such a variant is that it allows conventional machining of the wheels. FIG. 24 shows the very low level of torque consumption for the deformation of such a needle 1 in LIGA, when it is shortened, which has only a very small influence on the progress of the movement. Due to the proximity of the exhaust it is nevertheless advantageous to reduce this disturbance as much as possible, which can be obtained with very thin flexible segments 5, typically less than 100 micrometers in width and 200 micrometers in height for a LIGA construction. We understand in fig. 24, where we see that the torque curve as a function of the angle is U-shaped with a very flat cup, that it is advantageous, during design, to choose an angular range of deformation corresponding to the most bottom of the torque curve, so as to minimize the parasitic torque induced, and therefore to minimize the disturbance of the running of the watch. A tiered design with particular weighting helps to choose the optimal angular domains. The correct choice of this angular range also makes it possible to thicken the segments 5 of the needle 1 to make it more visible, without significantly increasing its disturbing torque. By way of comparison, the disturbance induced on the march is less than that caused by a change of date at midnight for a date mechanism. The invention is illustrated in the figures with a simple form, but it can be declined with very different forms of needles. For example an asymmetric needle, composed of two ves nested one in the other and of the same directions, each arm of each vee being integral with one of the cannons, and the extreme end of the other arm being linked to the 'similar end of the other vé. Or a needle with double arms, with two segments joining a first vertex and fixed to the two barrels, and two other segments joining a second vertex distant from the first, and fixed to the same barrels. Or a needle with thickened zones on a central zone of the flexible segments, for better visualization of the needle. The invention also relates to a timepiece movement 20 comprising at least one such display mechanism 10. The invention also relates to a timepiece 30 comprising at least one timepiece movement 20, and / or comprising at least one such display mechanism 10. More particularly, 21 this timepiece 30 is a watch. The invention also relates to a scientific apparatus comprising at least one clockwork movement 20, and / or comprising at least one such display mechanism 10. claims 1. Clockwork display mechanism (10) with variable geometry, comprising at least one elastic needle (1) which comprises on the one hand a first drive barrel (2) integral with at least one flexible blade (3 ) integral and which comprises a plurality of flexible segments (5; 5A; 5B) joined end to end at at least one vertex, of which a first flexible segment (5A) extends between said first barrel (2) and a first vertex (6), and on the other hand a second drive barrel (4) also integral with said flexible blade (3), said display mechanism (10) comprising an input mobile (71) arranged to be driven in pivoting about an entry axis by a movement (20) and defining an entry angle with a reference, and comprising first drive means (11) of said first barrel (2) around an axis output (D) parallel or coincident with said input axis, and second means s (12) for stressing at least said first flexible segment (5) which are arranged to vary the position of at least said first vertex (6) relative to said exit axis (D), said first vertex (6) being at a variable distance from said first barrel (2) as a function of the forces applied to said flexible blade (3) by said second stressing means (12), where said second stressing means (12) comprise second drive means (13) of said second barrel (4) in a mounted state of said elastic needle CH 715 211 A2 (1) wherein both said first barrel (2) is driven by said first drive means (11), and said second barrel (4) is driven by said second drive means (13) , and where at least one of said vertices (6) is, in an unconstrained free state of said elastic needle (1) in which both said first barrel (2) and said second barrel (4) are not subjected to any stress , distant from said first barrel (2) and said second barrel (4), which first barrel (2) and second barrel (4) are spaced from each other in said free state of said elastic needle (1), characterized in that said first drive means (11) and / or said second stressing means (12) comprise an accelerator or retarder device which is arranged to accelerate or stabilize in speed or at least slow down said first gun (2) and / or said second barrel (4) on at least one part ie of its angular course. 2. Mechanism (10) according to claim 1, characterized in that said first cannon (2) has an advance or a delay with respect to the value of said entry angle which is symmetrical to the delay or advance of said second cannon (4) relative to said entry angle, so that said first vertex (6) always displays, relative to said exit axis (D) and to said reference, an angle equal to said entry angle. 3. Mechanism (10) according to claim 1, characterized in that said first barrel (2) has an advance or a delay with respect to the value of said entry angle which is, in absolute value, different from the delay or l advancement of said second barrel (4) relative to said entry angle, so that said first vertex (6) displays, relative to said exit axis (D) and to said reference, a variable angle relative to said angle of entry throughout its course. 4. Mechanism (10) according to one of claims 1 to 3, characterized in that said needle (1) is arranged to perform a total non-retrograde stroke, and that, on said total stroke, the average speed of said first barrel ( 2) is equal to the average speed of said second barrel (4). 5. Mechanism (10) according to one of claims 1 to 4, characterized in that said accelerator or retarder device comprises a first gear train (111) and / or respectively a second gear train (131). 6. Mechanism (10) according to one of claims 1 to 5, characterized in that said accelerator or retarder device comprises a device with a first differential (912) on the drive train of said first barrel (2) and / or a second differential (914) on the drive train of said second barrel, and at least one cam (902,904) constituting an input of a said differential (912, 914). 7. Mechanism (10) according to one of claims 1 to 6, characterized in that said first drive means (11) and / or said second drive means (13) comprise at least a first gear train ( 115; 135) and a second gear stage (116; 136) each arranged to control part of the shape transformation of said elastic needle (1) over part of its angular travel, with weighting per stage. 8. Mechanism (10) according to one of claims 1 to 7, characterized in that said first drive means (11) and said second drive means (13) respectively comprise at least one first gear train (111 ) and / or at least one second gear train (131), each arranged to accelerate or stabilize in speed or slow down said first gun (2), and respectively said second gun (4), over at least part of the angular travel of said first barrel (2), and respectively of said second barrel (4), 9. Mechanism (10) according to one of claims 1 to 8, characterized in that said first drive means (11) and said second means (12) for stressing are arranged to drive said elastic needle (1) over its entire angular travel around said output axis (D), and give it, at projection on a display plane P or on a dial, and at different angular positions of said elastic needle (1), at least one first form where said flexible segments (5; 5A; 5B) which comprises said flexible blade (3) do not intersect outside of said first barrel (2), and at least a second form where said flexible segments (5; 5A; 5B ) that comprises said flexible blade (3) intersect outside said first barrel (2). 10. Mechanism (10) according to claim 9, characterized in that said first form is a form of almond, and said second form is a form of heart. 11. Mechanism (10) according to one of claims 1 to 10, characterized in that said first flexible segment (5Â) carries said first barrel (2) at a first end (52), a second flexible segment (5B) joined to said first flexible segment (5A) carries said second barrel (4) at a second end (54), and in that, in said free state of said elastic needle (1), said first end (52) and said second end (54 ) are distant from each other or form a non-zero angle with each other from said apex (6) of junction of said first flexible segment (5A) and said second flexible segment (5B). 12. Mechanism (10) according to one of claims 1 to 11, characterized in that the outlet of said second drive means (13) of said second barrel (4) is coaxial with the outlet of said first drive means (11 ) of said first barrel (2). 13. Mechanism (10) according to one of claims 1 to 12, characterized in that said first form train (111) and said second form train (131) are arranged to accelerate or respectively brake said first gun (2), and for braking or respectively accelerating said second barrel (4), over only part of the angular travel of said elastic needle (1). CH 715 211 A2 14. Mechanism (10) according to one of claims 1 to 13, characterized in that said first form train (111) and said second form train (131) are arranged to pilot symmetrically said first barrel (2) and said second barrel (4) so that said first flexible segment (5A) and said second flexible segment (5B) are symmetrical with respect to a radial coming from said outlet axis (D) and passing through said junction top (6) between said first flexible segment (5A) and said second flexible segment (5B), over at least part of the angular travel of said elastic needle (1). 15. Mechanism (10) according to one of claims 1 to 14, characterized in that said first gear train (111) and / or said second gear train (131) each comprise at least one pair of wheels arranged to cooperate in meshing with one another and whose primitive curves of the teeth are not of revolution. 16. Mechanism (10) according to claim 7 and one of claims 1 to 15, characterized in that said first gear stage (115; 135) and said second gear stage (116; 136) respectively comprise a said first gear train (111) and a said second gear train (131). 17. Mechanism (10) according to one of claims 1 to 16, characterized in that, in the free state, said elastic needle (1) extends over a first plane level comprising said first barrel (2) and on a second planar level comprising said second barrel (4), and comprises a connection zone between said first planar level and said second planar level at a said vertex (6) between a first flexible segment (5A) carrying said first barrel (2) and a second flexible segment (5B) joined to said first flexible segment (5A) and carrying said second barrel (4), and in that said elastic needle (1) is arranged to be mounted without twisting in a service position under stress in which said first barrel (2) and said second barrel (4) are superimposed on each other. 18. Mechanism (10) according to one of claims 1 to 16, characterized in that, in the free state, said elastic needle (1) extends over as many parallel levels as said flexible segments (5), is designed to be mounted without twisting in a service position under stress in which said first barrel (2) and said second barrel (4) are superimposed on each other. 19. Mechanism (10) according to one of claims 1 to 16, characterized in that, in the free state, said elastic needle (1) extends over a single plane level comprising said first barrel (2) and said second barrel (4), and in that said elastic needle (1) is arranged to be mounted twisted in a service position under stress in which said first barrel (2) and said second barrel (4) are superposed one on the other the other. 20. Mechanism (10) according to one of claims 1 to 19, characterized in that, in the free state, said elastic needle (1) comprises a breakable element (24) joining said first barrel (2) and said second barrel (4), to facilitate the mounting of said elastic needle (1) on a mobile for driving said first barrel (2) or said second barrel (4), said breakable element (24) being arranged to be broken and allow the passage of said elastic needle (1) in a service position under stress in which said first barrel (2) and said second barrel (4) are superimposed on each other. 21. Mechanism (10) according to one of claims 1 to 20, characterized in that said elastic needle (1) comprises at least one eye (60) arranged to constitute a window for reading an indication appearing on a dial ( 61) that comprises said mechanism (10) and in front of which extends said elastic needle (1), or that comprises a clockwork movement (20) on which said mechanism (10) is arranged to be attached. 22. Mechanism (10) according to one of claims 1 to 21, characterized in that said mechanism (10) constitutes an additional module arranged to be attached to a clockwork movement (20), and in that said first means drive (11) and said second means (12) for stressing have a common input (71) arranged to be driven by a single output (21) that includes said movement (20). 23. Mechanism (10) according to one of claims 1 to 22, characterized in that said mechanism (10) comprises, between on the one hand an input mobile (71) arranged to be driven by a movement (20) , and secondly said first barrel (2) and / or said second barrel (4), at at least one said stage, a cam (902, 904) arranged to drive a differential (912, 914) of which a first input is formed by said input mobile (71), a second input of which is a rake (922, 924) controlled by said cam (902, 904), and the output of which meshes with the gear train for transmitting said movement first barrel (2) or second barrel (4) respectively. 24. Mechanism (10) according to claim 23, characterized in that said mechanism (10) comprises, between said input mobile (71) and said first barrel (2) at at least one said stage, a cam (902) unique arranged to drive a first differential (912), a first input of which is constituted by said input mobile (71), a second input of which is a first rake (922) controlled by said cam (902), and whose the output meshes with the gear train for transmitting movement to said first barrel (2), and between said input mobile (71) and said second barrel (4), the same single cam (902) arranged to drive a second differential ( 914), a first input of which is constituted by said input mobile (71), a second input of which is a second rake (924) controlled by said cam (902), and the output of which meshes with the gear train for transmitting said movement second barrel (4). 25. Mechanism (10) according to claim 23, characterized in that said mechanism (10) comprises, between said input mobile (71) and said first barrel (2) at at least one said stage, a first cam (902) arranged to drive a first differential (912), a first input of which is constituted by said input mobile (-71), one of which CH 715 211 A2 second input is a first rake (922) controlled by said first cam (902), and the output of which meshes with the gear train for transmitting movement to said first barrel (2), and between said input mobile (71 ) and said second barrel (4), a second cam (904) driven by the input mobile and arranged to drive a second differential (914), a first input of which is constituted by said input mobile (71), one of which second input is a second rake (924) controlled by said second cam (904), and the output of which meshes with the gear train for transmitting movement to said second barrel (4). 26. Mechanism (10) according to one of claims 1 to 25, characterized in that at least one wheel that comprises the gear mechanism arranged between on the one hand an input mobile (71) arranged to be driven by a movement (20), and on the other hand said first barrel (2) and / or said second barrel (4), at at least one said stage, has an incomplete toothing, each missing tooth authorizing an expansion of said elastic needle (1), by rotation of only one of said barrels (2; 4) during the passage of the space corresponding to a missing tooth, so as to control a retraction of the apex (6) of said elastic needle (1) . 27. Clock movement (20) comprising at least one display mechanism (10) according to one of claims 1 to 26. 28. Timepiece (30) comprising at least one timepiece movement (20) according to claim 27. 29. Timepiece (30) according to claim 28, characterized in that said timepiece (30) is a watch. 30. Scientific apparatus comprising at least one clockwork movement (20) according to claim 27. CH 715 211 A2

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