Watch with mechanical movement comprising a rotating cage regulator

Abstract

The invention relates to a rotating cage regulator (200) comprising a fixed wheel (1), a cage carrying a balance wheel and hairspring, an escapement element (5) and an escape wheel (4) whose pinion (40) meshes with the fixed wheel (1), a lower cage (2) carrying teeth (22) and a locking element (21), a winding wheel (61) attached to a spring (62) and pivoting on a bearing ring (3) fixed to a plate, a locking wheel (7) with teeth capable of being stopped by the locking pallet (21), the whole constituting an epicyclic gear system, of which the cage (2) is the sun gear, the ring (3) a planet carrier, the winding wheel (61) a first planet and the locking wheel (7) a second planet, arranged to release or block the movement of the ring (3), and carrying a locking pinion (70) meshing with the fixed wheel (1).

Description

Technical field of the invention

[0001] The invention relates to a mechanical clock movement, comprising at least one rotating cage regulator.

[0002] The invention also relates to a watch comprising at least one such movement.

[0003] The invention also relates to a watch assembly comprising at least one such watch and / or such a movement.

[0004] The invention further relates to a method for precisely adjusting the relative positions of a planetary locking wheel and a locking pallet specific to the invention.

[0005] The invention relates to the field of mechanical watches featuring a tourbillon regulator, more particularly a flying tourbillon. Technological background

[0006] The invention relates to a watch comprising a mechanical movement with a rotating cage regulator. A "rotating cage regulator" is understood to mean a system that rotates a balance wheel around an axis; tourbillons and Bonikksen carousels fall into this category. More particularly, and without limitation, the invention is applicable to a rotating cage regulator that is a tourbillon, notably a flying tourbillon, comprising a jumping seconds display mechanism.

[0007] The proposed mechanism allows jumping seconds to be displayed for a mechanical watch equipped with a rotating cage regulator, including a flying tourbillon.

[0008] So-called "dead seconds" mechanisms have been known for centuries, and aim to facilitate the reading of the exact second displayed by watch mechanisms.

[0009] Stationary precision mechanical timepieces typically use a "seconds pendulum" with an oscillation frequency of 0.5 Hz (i.e., an oscillation period of 2 seconds, or one second per half-oscillation or alternation). Most standard escapements used for precision pendulum clocks (e.g., the Graham / Riefler / Strasser escapement) drive the oscillator once per half-oscillation, that is, twice per oscillation (equivalent to 3600 alternations per hour). As a result, the seconds hand naturally jumps in one-second increments. Seconds pendulum clocks were used as standard chronometers in astronomy until the mid-twentieth century to determine the transit times of celestial bodies.

[0010] The need for portable precision chronometers for navigation (see the British "Queen Anne Longitude Act" of 1714) led to the development of marine chronometers, operating with an oscillation frequency of 2 Hz (or 14,400 A / h) which, in combination with a chronometer escapement that only gives an impulse to the balance wheel every two half-oscillations, i.e. one impulse per oscillation, resulted in jumps of half a second of the seconds hand.

[0011] Pocket watches and wristwatches, which are much smaller in size than marine chronometers, would, however, require higher frequency oscillators to achieve similar accuracy (Q factor; today, oscillation frequencies between 2.5 and 5 Hz are commonly used in wristwatch movements), which would result in smaller jumps of the seconds hand (with standard anchor escapements: 5 jumps per second with 2.5 Hz, and 10 jumps per second for 5 Hz).

[0012] Therefore, other methods had to be found to obtain jumps in the seconds hand or half-seconds that were more easily readable.

[0013] In the middle of the eighteenth century, Jean Romilly was the first watchmaker to build a watch with a stoppable seconds hand with a balance wheel oscillation frequency chosen so that it resulted in the jumping seconds.

[0014] Jean Moïse Pouzait invented a seconds mechanism that could be started and stopped independently ("independent deadbeat seconds") around 1776. This mechanism required a secondary gear train with a "whip" that engaged with a "star" on the escape wheel's axle and was then released to spin rapidly once per second. Document CH256885A, issued in the name of Omega, describes such a mechanism. Such watch mechanisms had seconds hands that jumped in one-second increments (with higher-frequency oscillators and standard escapements).

[0015] Later designs eliminated much of the secondary gear train by introducing an intermediate spring mechanism periodically rewound by the primary gear train.

[0016] With the advent of modern chronograph mechanisms with resettable seconds hands, these mechanisms fell into oblivion, with a small resurgence of permanently running dead seconds mechanisms in the 1950s and 1960s, such as the Omega Cal. 372 "Synchrobeat".

[0017] Recent years have seen a resurgence of interest among fine watch enthusiasts in jumping seconds mechanisms, with many examples incorporating a constant-force escapement with a one-second rewind interval to achieve a jumping seconds hand. However, such a mechanism is in the energy flow between the mainspring barrel and the escapement, and the components must be sized accordingly. Moreover, precisely setting the jump time is difficult, if not impossible, on existing mechanisms. Summary of the invention

[0018] The invention aims to produce a new watch movement comprising a rotating cage regulator, in particular with a tourbillon, in particular with a flying tourbillon with jumping seconds, the mechanism of which is downstream of the escapement mechanism, and whose jump position is adjustable in the workshop.

[0019] The invention thus relates to a mechanical clock movement, comprising at least one rotating cage regulator, according to claim 1.

[0020] The invention also relates to a watch comprising at least one such movement.

[0021] The invention also relates to a watch assembly comprising at least one such watch and / or such a movement.

[0022] The invention further relates to a method for precisely adjusting the relative positions of a planetary locking wheel and a locking element specific to the invention. Brief description of the figures

[0023] The aims, advantages and features of the invention will become clearer upon reading the detailed description that follows, with reference to the attached drawings, where: there figure 1illustrates, schematically and in perspective, a rotating cage regulator according to a particular embodiment of the invention, in the specific and non-limiting case of a jumping seconds flying tourbillon, which comprises a lower cage modified by the addition of two externally projecting gear teeth carried by a substantially annular body, and a locking pallet carried by an arm of this lower cage; the tourbillon further comprises a winding wheel associated with a winding spring, these two gear teeth being arranged to mesh with this winding wheel; the winding wheel is carried by a bearing ring, which further carries a planetary locking wheel; this locking wheel comprises locking teeth arranged to bear against the locking pallet in a rest position; the figure 2illustrates, schematically in a top view, from the side visible to the user and opposite the movement plate containing the tourbillon, the lower part of the tourbillon of the figure 1 The upper cage, the balance wheel and hairspring assembly, and the balance cock are not shown; the escape wheel is visible at six o'clock, the pallet fork at five o'clock, the locking wheel and hairspring at ten o'clock, as well as the gear teeth; an arm of the lower cage, at four o'clock, carries the locking pallet; the locking wheel is at three o'clock; a locking tooth can be seen resting on the bearing surface of the locking element, here but not limited to a locking pallet, which extends substantially tangentially; the figure 3 illustrates, schematically in exploded perspective, all the components of the vortex of the figure 1 ; there figure 4illustrates, schematically and from a top view, in a manner similar to the figure 2 , the set of components allowing adjustment of the tourbillon's seconds jump figure 1 : the lower cage surmounting the tourbillon's fixed wheel, the escapement mechanism on the left, the locking element, and the locking wheel at six o'clock; the locking wheel has a pinion that meshes with the fixed wheel; the gear teeth are visible at one o'clock; the figure 5 illustrates, in a schematic, partial way, in a manner analogous to the figure 4 , the end of the locking element, in a particular configuration where the bearing surface of the locking teeth covers a central angle of 1° from the pivot axis of the cage; this angle is divided into a whole number of sectors, here seven sectors, corresponding to as many possible rest positions of the distal end of the locking tooth of the locking wheel; the figure 6illustrated, schematically, and from above like the figure 5, the detail of the cooperation between the locking element and a locking tooth: on the left side, while the relative orientation of the locking wheel with respect to the imaginary line between its own center and the center of the fixed tourbillon wheel remains identical (except that it is offset by exactly one tooth in the direction of the hands of a clock), the locking teeth of the locking pinion are inclined by the difference between the values ​​of the quotients of 360° by the number of teeth, on the one hand the number of teeth of the planetary locking wheel, and on the other hand the number of teeth of the locking pinion, this difference having, in the particular case illustrated, an angular value of 20.5714° (between the tangent lines with the fixed wheel in dashed line and in solid line), with respect to their original orientation.On the right side of the figure, we see the locking pinion rolling along the fixed wheel, rolling on its teeth, in order to restore correct meshing between its own teeth and the teeth of the fixed wheel; with the particular gear ratio of the illustrated case, the 20.5714° rotation of the locking pinion around its axis corresponds to a 1.71429° pivot around the central axis of the tourbillon; the . figure 7 illustrates, in a schematic, partial, and top-down manner, a detail of the figure 2 illustrating methods of adjusting the position of the seconds hand; the figure 8 illustrates, in a schematic and exploded perspective manner, the detail illustrated in figure 7 ; there figure 9 illustrates, in a schematic way and with a perspective similar to the figure 1 , an adjustment using an eccentric tool to determine the angular position of the fixed wheel relative to the seconds dial; the Figure 10 is the top-view representation of the figure 9 ; there figure 11 represents, schematically and in front view, a watch comprising a movement equipped with a rotating cage regulator, in particular a tourbillon, according to the invention; figure 12 is a block diagram representing the steps of a precision adjustment process for the relative positions of the planetary locking wheel and the locking element. Detailed description of the invention

[0024] The invention relates to a 1000 mechanical watch movement, comprising a mechanism which allows the dead second to be displayed on a 2000 mechanical watch equipped with a 200 rotating cage regulator, in particular a flying tourbillon.

[0025] The proposed and illustrated mechanism is based on the flying tourbillon with balance stop device described in document CH717982 in the name of GLASHUETTE ORIGINAL, incorporated here by reference.

[0026] This mechanical horological movement 1000 comprises at least one rotating cage regulator 200 having a fixed wheel 1, a cage (comprising, in the preferred variant illustrated in the figures, at least one lower cage 2 and one upper cage 11) carrying a balance wheel and hairspring comprising a balance wheel 60 and a mainspring 90, an escapement element 5 (or more particularly an anchor in the illustrated case), and an escape wheel 4 whose escape pinion 40 meshes directly or indirectly with the fixed wheel 1, and in particular directly in the preferred variant illustrated in the figures. In other variants, there is an intermediate moving part between this escape pinion 40 and the fixed wheel 1, as for example in a Bonniksen carousel mechanism where the escape pinion is arranged by a moving wheel, or, in a five-minute tourbillon, an intermediate moving part is interposed between the escape wheel and the fixed wheel.

[0027] The cage also carries a locking element 21, as well as a bearing fixed to a movement plate 100 coaxially with the cage.

[0028] According to the invention, the rotating cage regulator 200 comprises a locking wheel 7 with locking teeth 71, pivoting on a bearing ring 3. These locking teeth 71 are able to be stopped by this locking element 21 with a rest position adjustable in the workshop. The locking wheel 7 is arranged to release or lock the movement of the ring 3, and carries a locking pinion 70 that permanently meshes with said fixed wheel 1. The ring 3 is connected to the rotating cage regulator 200 by an intermediate winding system, which winds a winding spring 62 by the movement of the rotating cage regulator 200 such that the winding spring 62 maintains the movement of the ring 3 in the same direction of rotation as the rotating cage regulator 200 by releasing its tension.

[0029] It is understood that the nature of the escapement element 5 depends on the type of escapement used, since the invention is applicable to any type of escapement mechanism, whether lever, detent, duplex, cylinder, comma, Graham, or other. The invention is illustrated, without limitation, in the specific case of a lever escapement mechanism, and the escapement element 5 is more particularly, but not exclusively, a lever.

[0030] According to the particular embodiment of the invention illustrated in the figures, the lower cage 2 carries gear teeth 22 and a locking element 21 or, as illustrated in the figures, a locking pallet. The rotating cage regulator 200 further comprises a winding wheel 61 attached to a winding winding spring 62 and pivoting on a ring 3 of a bearing fixed to a movement plate 1000 (by its inner ring), and a locking wheel 7 with locking teeth 71 capable of being stopped by the locking element 21 with a rest position adjustable in the workshop. The assembly constitutes a first epicyclic gear system, of which the lower cage 2 is the sun gear, the bearing ring 3 a planet carrier, and the winding wheel 61 a first planet gear. The locking wheel 7 is arranged to release or lock the movement of the ring 3 and carries a locking pinion 70 that permanently meshes with the fixed wheel 1.

[0031] The locking element 21 can take different forms, and be fixed in different ways to different components of the mechanism; for example, a pin protruding from the upper cage 11 of the oscillating system would also function in the manner described below.

[0032] The charging system described above with the epicyclic gear between the teeth 22 of the lower cage 2 of the tourbillon and the charging wheel 61 with its charging spring 62 in the form of a spiral spring is a particularly compact variant; but for example a leaf spring fixed by one end to the tourbillon cage, and by a second end to the satellite carrier (the ring 3) is also suitable.

[0033] THE figures 1 to 3 illustrate, in perspective, in top view, and in exploded perspective, such a rotating cage regulator 200 according to the invention.

[0034] More specifically, this rotating cage regulator 200 comprises a pivoted cage, including a lower cage 2 and an upper cage 11, here connected, but not limited to, three pillars 29. The cage carries a balance wheel and hairspring assembly comprising a balance wheel 60 and a mainspring 90 attached to a stud 91 of a bridge. This cage is fixed to the axis of the seconds pinion 9, which is arranged to drive the minute hand.

[0035] The cage carries the escapement mechanism, which includes an escape wheel 4, with a number of teeth N4, which is arranged to cooperate with an escapement element 5, here not limited to a Swiss lever with two pallets 51 and 52. The escape wheel 4 and the escapement element 5 are both pivoted superiorly in a bridge 50.

[0036] The tourbillon includes a fixed wheel 1, fixed to the plate, which has external teeth with a number of teeth N1.

[0037] The exhaust wheel 4 is integral with an exhaust pinion 40, with a number of teeth N40, which meshes with the teeth of the fixed wheel 1.

[0038] Compared to this known mechanism, according to the invention the lower cage 2 of the rotating cage regulator 200 is modified by the addition of two externally projecting gear teeth 22 and a locking element 21 (or a locking pallet), in particular made of ruby, carried by an arm 110 of the lower cage 2 in a housing 111.

[0039] More specifically, the tourbillon also includes a charging wheel 61, carried by an upper pivot 610 on a first cock 66, and associated with a charging spring 62. More specifically, this charging spring 62 is attached at its ends, outer 622 to the first cock 66, and inner 621 to the charging wheel 61.

[0040] The two teeth 22 are arranged to mesh with this charging wheel 61.

[0041] More specifically, the tourbillon also includes a planetary locking wheel 7, having N7 locking teeth 71, which is supported by a bracket 75 and a second cock 76 between which it is pivotally mounted. The locking element 21 is arranged to cooperate in contact with a locking tooth 71 of this planetary locking wheel 7.

[0042] The charging wheel 61 and the planetary locking wheel 7 are both pivotally mounted, at a distance from each other, on the outer ring 3 of a ball bearing which is fixed coaxially under the lower cage 2 of the rotating cage governor 200.

[0043] While the ball bearing 3 is stationary, the winding spring 62 is therefore wound up by the moving tourbillon via the meshing between the two teeth 22 of the lower cage of the tourbillon 2 and the winding wheel 61.

[0044] The tension of the winding spring 62 will allow the entire outer ring 3 of the ball bearing to rotate in the same direction as the tourbillon once it is free to move: the whole constitutes a first epicyclic gear system, of which the tourbillon is the sun gear, and of which the outer ring 3 of the ball bearing is a satellite carrier, and of which the winding wheel 61 is a planetary wheel.

[0045] The planetary locking wheel 7 is another planetary wheel pivotally mounted on the outer ring of the bearing. The free movement of the outer ring 3 of the ball bearing is thus blocked by the planetary locking wheel 7, which has a locking pinion 70, having N70 teeth, which meshes with the fixed tourbillon wheel 1, while the teeth of the wheel bear against the locking element 21 of the lower cage 2 of the tourbillon (it is therefore a secondary epicyclic gear).

[0046] Thus, a secondary epicyclic gear system with the fixed wheel 1 of the rotating cage regulator 200 as the sun gear, and with the locking pinion 70 of the planetary locking wheel 7 as the planetary wheel, is superimposed on the first epicyclic gear system for the charging wheel 61, the two systems sharing a common planet carrier, i.e. the outer ring of the ball bearing 3.

[0047] The mechanism operates according to the sequence described below.

[0048] The preload of the winding spring 62 of the winding wheel 61 causes the ball bearing to rotate in the same direction as the tourbillon. This movement is blocked by a locking tooth 71 of the planetary locking wheel 7, which rests on the locking element 21 embedded in the lower cage 2 of the rotating cage regulator 200.

[0049] While the tourbillon (more particularly with a one-minute cycle in the non-limiting variant shown here and illustrated by the figures) rotates around its axis, the tip of the locking element 21, in particular a paddle as seen in the figures, goes to the tip of this locking tooth 71, and the two teeth 22 of the lower cage 2 of the tourbillon continue to raise the charging wheel 61.

[0050] When the tourbillon has rotated by about 6° (after one second, i.e. 1 / 60 of a minute, therefore 1 / 60 of a turn, for one rotation of the tourbillon per minute), the locking tooth 71 detaches from the locking element 21, and both the planetary locking wheel 7 and the entire outer ball bearing assembly are then free to rotate around their respective axes.

[0051] This rotation is driven by the planetary charging wheel 61, and stops when the next locking tooth 71 of the planetary locking wheel 7 touches the locking element 21, and the cycle begins again.

[0052] In the proposed and non-limiting version of the mechanism, the tourbillon balance wheel oscillates at a frequency of 3Hz (i.e. 21600 alternations per hour), the escape wheel 4 has 15 teeth and its escape pinion 40 has 7 teeth; the planetary locking wheel 7 has 5 teeth and its locking pinion 70 has 7 teeth, while the fixed seconds wheel has 84 teeth.

[0053] Thus, the tourbillon cage itself progresses by 6 jumps per second (i.e., 3 teeth of the escape wheel 4) with 1° of rotation per jump; consequently, the escape wheel 4 completes a rotation around its axis in 5 seconds (5 seconds = 15 teeth of the escape wheel 4, i.e., 3 teeth of the escape wheel per second); the same applies to the planetary locking wheel 7, because the gear ratio between its locking pinion 70 and the fixed wheel 1 of the tourbillon is the same as that of the escape wheel 4.

[0054] With a planetary locking wheel 7 having 5 teeth, the ball bearing jumps in increments of one second.

[0055] A seconds hand 10, 101, fixed on the outer ring of the ball bearing 3, therefore indicates the jumping seconds (or dead seconds).

[0056] Since the pinions, respectively escape pinion 40 of the escape wheel 4 and locking pinion 70 of the planetary locking wheel 7, mesh with the same fixed tourbillon wheel 1, and the position of the locking element 21 is fixed relative to the axis of the escape wheel 4, the respective angular orientation of their wheel and pinion teeth defines the locking depth of the teeth of the planetary locking wheel 7 on the locking element 21.

[0057] Neither adjusting the position of the pallet 21 in the lower tourbillon cage, nor orienting the wheels and pinions of the escape wheel 4 and the planetary locking wheel 7, to obtain a locking depth of about 5.5° after the seconds jump, seems very practical, given the inevitable tolerances and the necessary ease of assembly, as well as after-sales constraints.

[0058] Therefore, the invention proposes the following procedure for precisely adjusting the relative positions of the planetary locking wheel 7 and the locking element 21 of the lower cage 2 of the tourbillon, i.e. for adjusting the locking depth of the locking teeth 71 of the planetary locking wheel 7 on the locking element 21.

[0059] In a first step A, a random riveting of the escape wheel 4 on the one hand, and of the planetary locking wheel 7 on the other hand, is carried out on their respective pinions, escape pinion 40 and locking pinion 70, without regard to their angular orientation; a positioning adjustment of the locking element 21 is carried out to ± 1° of its theoretical correct position (using an optical comparator or a gauge, or similar) and this locking element 21 or this locking pallet is fixed to the lower cage 2 of the tourbillon.

[0060] In a second stage B, the assembly of the mechanism is carried out (without the balance wheel 60 or the upper cage 11 of the tourbillon), the random positioning of the escape wheel 4 and the planetary locking wheel 7 of the seconds jump mechanism, and the winding of the mainspring of the movement.

[0061] The tourbillon cage is advanced (in 1° increments) by manually moving the escapement element 5 back and forth until the locking tooth 71 of the planetary locking wheel 7 reaches the distal end of the locking element 21 as seen in figure 4 , just before it falls and thus releases the seconds jump mechanism.

[0062] In a third step C, it is verified that, at this stage, the tip of the locking tooth 71 of the planetary locking wheel 7 is in one of the positions marked on the locking pallet, in particular one of the positions numbered "1" to "7" of the figure 5on which an angular deviation of 1° is divided into seven relative positions of the locking tooth 71 with respect to the locking element 21, and this position is identified. It is advantageous to be able to adjust, by a suitable adjustment, the relative position between the locking tooth 71 and the locking element 21.

[0063] A fourth step D is devoted to this adjustment setting. When the movement of the outer ring of the ball bearing is temporarily blocked (for example by wedging a piece of paper between the movement plate and the ball bearing), it is possible to disengage the planetary locking wheel 7, and reposition it in accordance with a nomogram or instruction table such as can be read below, after rotating the rotating cage regulator 200 accordingly by manually moving the escapement element 5 back and forth for the required number of steps.For example, with a blocking depth of "5": disengage the planetary locking wheel 7, rotate the tourbillon five additional escapement steps and reinstall the planetary locking wheel 7 rotated at an angle corresponding to three planetary locking wheel teeth clockwise, positioned in the first angular degree on the tourbillon locking element 21.

[0064] Such a table, which is not exhaustive and corresponds to the mechanism illustrated by the figures, with particular numbers of teeth on the different moving parts, and very specific oscillation frequencies f0 and jump frequencies fj, and corresponding to the configuration of its escapement mechanism and that of its locking wheel, is presented here, according to a calculation method explained below: sector no. 1, locking depth of "1": 9 escape steps, no teeth of the planetary locking wheel 7; sector no. 2, locking depth of "2": 2 escape steps, 1 tooth of the planetary locking wheel 7; sector no. 3, locking depth of "3": 7 escape steps, 4 teeth of the planetary locking wheel 7; sector no. 4, locking depth of "4": no escape steps, no teeth of the planetary locking wheel 7; sector no. 5, locking depth of "5": 5 escape steps, 3 teeth of the planetary locking wheel 7; sector no. 6, locking depth of "6": 10 escape steps, 1 tooth of the planetary locking wheel 7; sector no. 7, locking depth of "7": 3 escape steps, 2 teeth of the planetary locking wheel 7.

[0065] A fifth step E verifies that the locking tooth 71 of the planetary locking wheel 7 now has the desired, or even ideal (sector 4), locking depth on the tourbillon locking element 21. If this is not the case, steps three C and four D must be repeated until the desired locking depth is achieved.

[0066] A sixth step F consists of adjusting the preload of the winding spring 62 of the winding wheel 61 to the lowest level necessary to obtain a clean seconds jump. Indeed, any excessive preload will reduce the amplitude of the balance wheel 60. To do this, the winding wheel 61 can be reinstalled with another pair of teeth in contact with the teeth 22 of the lower cage of the tourbillon 2, specific to the invention.

[0067] This method of fine-tuning the locking depth is based on the principle of the Vernier scale: with the position of the tourbillon fixed and one tooth of the planetary locking wheel 7 in contact with the locking element 21, the planetary locking wheel 7 is rotated one tooth clockwise around its axis, by the value of the quotient of 360° by the number of teeth N7 of the locking wheel 7, here 5 teeth, i.e. 360° / 5 = 72°.

[0068] The locking pinion 70 of the planetary locking wheel 7 here has N70 = 7 teeth.

[0069] While the relative orientation of the locking wheel 7 with respect to the imaginary line between its own center and the center of the fixed tourbillon wheel 1 remains identical (except that it is offset by exactly one tooth clockwise), the locking teeth 71 of the locking pinion 70 of the locking wheel 7 are inclined by the difference between the values ​​of the quotients of 360° by the number of teeth, on the one hand the number of teeth N7 of the planetary locking wheel 7, here 5 teeth, and on the other hand the number of teeth N70 of the locking pinion 70 of the locking wheel 7, here 7 teeth. This difference has the value (360° / 5 - 360° / 7), or (72° - 51.4286°) = 144 / 7° = 20.5714° with respect to their original orientation (see figure 6 (on the left).

[0070] The locking pinion 70 of the planetary locking wheel 7 must therefore be moved along the fixed wheel 1 of the tourbillon, in order to restore correct meshing between its own teeth and the teeth of the fixed wheel (see figure 6 (on the right).

[0071] With a gear ratio of 7 / 84 = 1 / 12 between the fixed tourbillon wheel 1 (which has N1 = 84 teeth) and the locking pinion 70 (which has N70 = 7 teeth) of the planetary locking wheel 7, this 20.5714° rotation of the locking pinion 70 around its axis corresponds to a pivot of (20.5714° * 1 / 12) = 144 / 7° * 1 / 12 = 12 / 7° = 1.71429° around the central axis of the tourbillon, as seen on the figure 6 , on the right.

[0072] In summary, removing the planetary locking wheel 71 and replacing it by rotating it one tooth clockwise results in the point of contact between the tip of the locking tooth 71 of the locking wheel 7 and the locking element 21 (represented by a ruby ​​pallet on the figures 4 , 5 and 6), moves by an angular value of 1.71429° = (360° / 5 - 360° / 7) * 7 / 84 clockwise (and therefore falls deeper onto the locking element 21). If the planetary locking wheel 7 is rotated not by one, but by two teeth before being put in place, the corresponding tooth of the locking wheel then falls by an angle of 2 * 1.71429° = 3.42857° lower onto the locking element 21. Consequently, depending on the number X of teeth by which the planetary locking wheel 7 is rotated before being reinserted, the following theoretical modifications of the rest depth Δ / rotation of the locking wheel around the fixed seconds wheel are obtained, with Δ = X * 1.71429° = X * 12 / 7°: X = 1, Δ = 1.71429°= 12 / 7; X = 2, Δ = 3.42857°; X = 3, Δ = 5.14286°; X = 4, Δ = 6.85714°; X = 5, Δ = 8.57143°; X = 6, Δ = 10.28571°; X = 7, Δ =12°.

[0073] Now, when the escapement is triggered once, the blocking element 21 moves in turn by the value of 360° / (84 / 7*15*2) = 1°, in the direction of a clockwise direction (because the fixed wheel 1 of the tourbillon or seconds wheel has 84 teeth, the escape pinion 40 of the escape wheel 4 has 7 teeth, and the escape wheel 4 has 15 teeth; at each triggering of the escapement, the escape wheel 4 turns by half a tooth due to the Swiss lever escapement 5 used, with 2 impulses per complete oscillation), hence the factor 2.

[0074] As a result, the rest depth Δ of the locking tooth 71 of the planetary locking wheel 7 on the rest pallet 21 of the tourbillon cage 2 can be reduced by 1° per escapement step.

[0075] To modify the rest depth by only a few fractions of a degree, one can trigger the escapement by a corresponding number of steps, as follows, where Δ is the rest depth without additional escapement steps, where N is the number of additional escapement steps, and where ΔM is the rest depth modified with this corresponding number N of additional escapement steps: X = 1, Δ = 1.71429°; N = 1, ΔM = 1.71429° mod 1° = 0.71429° = 5 / 7°; X = 2, Δ = 3.42857°; N = 3, ΔM = 3.42857° mod 1° = 0.342857° = 3 / 7°; X = 3, Δ = 5.14286°; N = 5, ΔM = 5.14286° mod 1° = 0.14286° = 1 / 7°; X = 4, Δ = 6.85714°; N = 6, ΔM = 6.85714° mod 1° = 0.85714° = 6 / 7°; X = 5, Δ = 8.57143°; N = 8, ΔM = 8.57143° mod 1 = 0.57143° = 4 / 7°; X = 6, Δ = 10.28571°; N = 10, ΔM = 10.28571° mod 1° = 0.285714 = 2 / 7°; X = 7, Δ = 12°; N = 12, ΔM = 12° mod 1° = 0° = 0 / 7°.

[0076] Or N = 1 = 1.71429° div 1°, N = 3 = 3.42857° div 1°, and so on. In other words,

[0077] N = 1 = 12 / 7 ° div 1 ° N = 3 = 24 / 7 ° div 1 ° N = 5 = 36 / 7 ° div 1 ° N = 6 = 48 / 7 ° div 1 ° N = 8 = 60 / 7 ° div 1 ° N = 10 = 72 / 7 ° div 1 ° N = 12 = 84 / 7 ° div 1 ° or, as a general rule: Δ = X * 12 / 7 ° N = Δ div 1 ° Δ M = Δ mod 1 °

[0078] Consequently, a suitable combination of rotating the planetary locking wheel 7 before returning to position, and further triggering an appropriate number of escapement steps, allows for adjustments to the depth of rest in 1 / 7° increments. This is because, as the jump mechanism is triggered within an escapement step and the associated 1° rotation of the tourbillon cage and the locking element 21 attached to it, the locking tooth 71 of the planetary locking wheel 7 can now be in one of the seven positions illustrated in the figure 5 , during the last half-oscillation before the jump is triggered.

[0079] The middle position "4" is preferred, as it offers sufficient security against triggering too early or too late in case of concentricity deviation / imprecision of the teeth / or any geometric defect.

[0080] Depending on the random orientation of the components during assembly, the watchmaker may find another position (1-3 or 5-7). By disassembling the planetary locking wheel 7 again, advancing the escapement by a defined number of steps, and reinstalling the planetary locking wheel 7 rotated by a defined number of teeth, one should now reach the state "4". This can be achieved from the state "5", for example by causing a rotation of 1 / 7°, which can be obtained (as can be seen in the table above) by N = 5 additional escapement steps and reinstalling the planetary locking wheel 7 rotated by X = 3 teeth.

[0081] This gives us the following correspondence between sectors 1 to 7 and the table above, the last Y value indicating the correspondence to the referenced sector, that is to say the required position on the figure 5 : X = 1, Δ = 1.71429°; N = 1, ΔM = 1.71429° mod 1° = 0.71429° = 5 / 7°; Y = 2*; X = 2, Δ = 3.42857°; N = 3, ΔM = 3.42857° mod 1° = 0.342857° = 3 / 7°; Y = 7; X = 3, Δ = 5.14286°; N = 5, ΔM = 5.14286° mod 1° = 0.14286° = 1 / 7°; Y = 5; X = 4, Δ = 6.85714°; N = 6, ΔM = 6.85714° mod 1° = 0.85714° = 6 / 7°; Y = 3*; X = 5, Δ = 8.57143°; N = 8, ΔM = 8.57143° mod 1° = 0.57143° = 4 / 7°; Y = 1*; X = 6, Δ = 10.28571°; N = 10, ΔM = 10.28571° mod 1° = 0.285714 = 2 / 7°; Y = 6; X = 7, Δ = 12°; N = 12, ΔM = 12° mod 1° = 0° = 0 / 7°; Y = (4).

[0082] However, for sectors Y = 1 to 3 (marked with an *: 1*, 2*, 3*), a procedure according to the table above would result in the jump occurring only two escapement steps later; therefore, an additional escapement step must be taken into account here. Furthermore, the planetary locking wheel 7 has only N7 = 5 teeth; a rotation of 5 teeth thus corresponds to the starting position, so it is possible to disregard the actual rotation (analogously, the rotation of 6 teeth corresponds to that of 1 tooth, that of 7 teeth to that of 2 teeth, therefore X modulo 5 leads to the same result as the rotation of X).

[0083] This results, for example, in the following easy-to-follow instructions for the watchmaker who regulates the mechanism: sector number Y, number X of teeth on the planetary locking wheel 7 satellite to be turned clockwise, number N of additional escapement steps: Y = 1, X = 0, N = 9; Y = 2, X = 1, N = 2; Y = 3, X = 4, N = 7; Y = 4, X = 0, N = 0; Y = 5, X = 3, N = 5; Y = 6, X = 1, N = 10; Y = 7, X = 2, N = 3.

[0084] The rotation of the planetary locking wheel 7 by several teeth X will therefore result in a new position of the planetary locking wheel 7 of (X * 1.71429°) relative to the original position (clockwise around the tourbillon axis). And the tangential displacement of the tip of the locking tooth 71 of the planetary locking wheel 7 along the pallet 21 corresponds approximately to this value.

[0085] And since the manual movement of the escapement element 5 from one edge to the other causes the entire tourbillon to jump in increments of 1° (one-minute tourbillon, 6 jumps per second, 60 seconds per minute = 360 jumps of 1°), the position of the distal end of the 71 tooth of the planetary locking wheel 7 relative to the locking element 21 can be adjusted to (X * 1.71429°) modulo 1°, i.e. in increments of 1 / 7°, which leads to the rules described above for defining the adjustment table.

[0086] To adjust the relative position of the seconds hand and the lower cage 2 of the tourbillon, the seconds hand support 10 101 can be adjusted by sliding it along a constant radius before screwing it onto the outer ring 3 of the ball bearing, so as to coincide exactly with the tourbillon pillar 29 at the moment of the seconds jump, as seen on the figures 7 and 8The adjustment and fixing are advantageously achieved by the combination of a screw with a bearing surface 81 and an oblong countersink 82.

[0087] To ensure that the seconds hand aligns precisely with the seconds markers on the dial, the fixed wheel 1 of the rotating cage regulator 200 is adjustable in rotation relative to the seconds dial, for example, as provided by oblong holes 84 around its fixing screws 83 and a cutout 85 allowing the use of an eccentric tool 300 to finely adjust the position, as seen on the figures 9, 10 And 11 .

[0088] In summary, the invention brings an improvement to the jumping seconds mechanisms of the prior art, in particular in that, instead of operating on the known principle of the constant-force escapement, the mechanism according to the invention operates outside the flow of energy between the barrel and the escapement, which considerably reduces the stresses induced on its parts.

[0089] More specifically, the vortex of the mechanism of the invention is a flying vortex.

[0090] In the present embodiment of the invention, it is noted that the winding spring that drives the proposed seconds-jumping mechanism is not located on the same axis as the tourbillon, but on a planetary wheel mounted on the ball bearing of the jump-jumping mechanism. This allows the mechanism described in document CH717982, issued on behalf of GLASHUETTE ORIGINAL, Glashütter Uhrenbetrieb GmbH, to be used to stop the tourbillon balance wheel 60 during the setting of the hour and minute hands. This mechanism also allows for easy adjustment of the spring preload by simply assembling it with another pair of teeth in contact with the tourbillon gear.

[0091] Furthermore, the invention's compact design utilizes the otherwise unused space beneath the tourbillon cage, and the entire mechanism is also fully visible through the existing opening in the flying tourbillon dial. The modular nature of the invention allows it to be applied to existing movements with minimal adjustments.

[0092] By varying the number of teeth on the planetary locking wheel, the mechanism can also be very easily modified to jump at intervals of other values, for example at half-second intervals (by doubling the number of teeth on the planetary locking wheel), in a manner similar to a marine chronometer.

[0093] The mechanism according to the invention can also be implemented by varying certain parameters, in particular the frequency f 0 of the oscillator, and the number of teeth (always an integer) of the different pinions and wheels of the mechanism: the number of teeth te or N4 of the escape wheel 4, the number of teeth tpe or N40 of the escape pinion 40 of the escape wheel 4, the number of teeth ttf or N1 of the fixed wheel 1 of the tourbillon, the number of teeth tpb or N70 of the locking pinion 70 of the locking wheel 7, and the number of teeth tb or N7 of the locking wheel 7, given that the desired jump frequency fj must satisfy the following two conditions.

[0094] First condition: fj = ((tpe*tb) / tpb) * f0 / (te), or, with the number of teeth referred to the references of their moving parts, fj = N 40 * N7 / N70 * f0 / N4

[0095] Second condition: the ratio f0 / (0.5*fj) is an integer.

[0096] Thus, and without limitation, the following mechanisms would also work: First example: fj = 2 Hz, f0 = 4 Hz, te = 20, tpe = 10, tpb = 16, tb = 16, or, with the number of teeth referred to the references of their moving parts, N4 = 20, N40 = 10, N70 = 16, N7 = 16. Second example: fj = 4 / 3 Hz, f0 = 4 Hz, te = 20, tpe = 12, tpb = 9, tb = 5, or, with the number of teeth referred to the references of their moving parts, N4 = 20, N40 = 12, N70 = 9, N7 = 5, a configuration which therefore provides a jump of ¾ of a second.

[0097] Let us recall that the particular variant illustrated by the figures corresponds to the values: fj = 1 Hz, f0 = 3 Hz, te = 15, tpe = 7, tpb = 7, tb = 5, or, with the number of teeth referred to the references of their mobiles, N4 = 15, N40 = 7, N70 = 7, N7 = 5.

[0098] If the tourbillon is intended to complete one revolution in one minute (i.e., display 60 true seconds per 360° revolution), the following additional condition must apply: ttf = 60*(tpe*f0) / te is an integer, or, with the number of teeth referred to the references of the mobiles, ttf = N1 = 60*(N40*f0) / N4, is an integer.

[0099] The proposed arrangement of a charging planetary wheel is also usable to apply other deadbeat seconds mechanisms to the aforementioned flying tourbillon according to document CH717982A2, which would usually require a coaxially mounted balance spring to accumulate the necessary jump energy or a secondary kinematic chain, for example secondary lever escapement mechanisms, such as those used by Jaquet Droz, or others.

[0100] For this class of mechanisms, the lower cage of the tourbillon can be used as the anchor drive wheel, and the outer ring of the ball bearing with the planetary charging wheel as the seconds jump wheel.

[0101] The invention also relates to a 2000 watch comprising at least one such 1000 movement.

[0102] The invention further relates to a watch assembly comprising at least one such watch 2000 and / or one such movement 1000. This watch assembly comprises, for each type of movement 1000 or caliber, a table for the factory or after-sales watchmaker, said table detailing the number X of teeth of the planetary locking wheel 7 to be turned clockwise, and the number N of additional escapement steps to be made at the level of the escapement element 5, to obtain a predetermined rest position of the locking tooth 71 on the locking element 21.

[0103] In particular, for the specific case detailed in this description, with: fj = 1 Hz, f0 = 3 Hz, te = 15, tpe = 7, tpb = 7, tb = 5, or, with the number of teeth referred to the references of their moving parts, N4 = 15, N40 = 7, N70 = 7, N7 = 5, the parameters of the number X of teeth of said planetary locking wheel 7 satellite to be rotated clockwise, and of the number N of additional escape steps to be made at the level of the escapement element 5, are as follows: for a division of a central angle of 1° on said locking element (21) or said locking pallet into seven rest positions of said locking tooth (71) designated sector No. 1 to sector No. 7, with sector No. 1, locking depth of "1", 9 escape steps, no tooth of the planetary locking wheel 7, with sector No. 2, locking depth of "2", 2 escapement steps, 1 tooth of the planetary locking wheel 7, with sector no. 3, locking depth of "3", 7 escapement steps,4 teeth of the planetary locking wheel 7, with sector no. 4, locking depth of "4", no escapement, no teeth of the planetary locking wheel 7, with sector no. 5, locking depth of "5", 5 escapement, 3 teeth of the planetary locking wheel 7, with sector no. 6, locking depth of "6", 10 escapement, 1 tooth of the planetary locking wheel 7, and with sector no. 7, locking depth of "7", 3 escapement, 2 teeth of the planetary locking wheel 7.

Claims

1. Mechanical clock movement (1000) comprising at least one rotating cage regulator (200) having a fixed wheel (1), a cage carrying a balance wheel and hairspring, an escapement element (5), an escape wheel (4) and a locking element (21), as well as a bearing fixed to a plate of said movement (100) coaxially with the cage, characterized in that The rotating cage regulator (200) includes a locking wheel (7) with locking teeth (71) pivoting on a ring (3) of said bearing and said locking teeth (71) being able to be stopped by said locking element (21) with a rest position adjustable in the workshop, in that said locking wheel (7) is arranged to release or lock the movement of said ring (3) and carries a locking pinion (70) permanently meshing with said fixed wheel (1), and in thatsaid ring (3) is connected to the rotating cage regulator (200) by an intermediate charging system, which winds a charging spring (62) by the movement of said rotating cage regulator (200) in such a way that said charging spring (62) maintains the movement of said ring (3) in the same direction of rotation as the rotating cage regulator (200) by relaxing.

2. Movement (1000) according to claim 1, characterized in that the exhaust pinion (40) meshes with said fixed wheel (1), and in that said intermediate charging system consists of a lower cage (2) which includes said cage and which carries gear teeth (22) and a charging wheel (61) attached to said charging spring (62) and pivoting on said ring (3) and meshing with said gear teeth (22) of said lower cage (2), and in thatthe assembly consisting of said lower cage (2), said charging wheel (61) and its said charging spring (62), said ring (3), said locking wheel (7) and said locking element (21), constitutes a first epicyclic gear system, of which said lower cage (2) is the sun gear, said ring (3) a satellite carrier, of which said charging wheel (61) is a first planetary gear, and of which said locking wheel (7) is a second planetary gear.

3. Movement (1000) according to claim 2, characterized in that the rewinding of said winding spring (62) of said winding wheel (61) is effected by the movement of said cage (2), said bearing being stationary, via the meshing between said teeth (22) of said lower cage (2) and said winding wheel (61), and in that, during the pivoting of said lower cage (2) around its pivot axis (DP), the tip of said locking element (21) is mobile up to the tip of a said locking tooth (71) which is in contact with said locking element (21).

4. Movement (1000) according to one of claims 1 to 3, characterized in that said fixed wheel (1) is fixed to a plate of said movement (1000) and comprises external teeth, in that said gear teeth (22) are externally projecting, in that said charging wheel (61) is pivoted in a first cock (66) and is associated with said charging spring (62) attached at its ends to said first cock (66) and to said charging wheel (61), and in that said planetary locking wheel (7) is pivoted in a second cock (76), in thatsaid charging wheel (61) and said planetary locking wheel (7) are pivotally mounted at a distance from each other on said ring (3), which is an outer ring of said ball bearing, said charging spring (62) being, when said outer ring (3) is stationary, wound up by the movement of said rotating cage governor (200) via the meshing between said teeth (22) and said charging wheel (61), and the tension of said charging spring (62) allowing said outer ring (3), once released, to rotate in the same direction as said rotating cage governor (200), and in that said locking teeth (71) are arranged to bear against said locking element (21) or said locking pallet.

5. Movement (1000) according to claim 2 and one of claims 1 to 4, characterized in thatsaid rotating cage regulator (200) includes a second secondary epicyclic gear system of which said fixed wheel (1) is the sun gear, said outer ring (3) a planet carrier, and said locking pinion (70) a planet wheel, said second secondary epicyclic gear system being superimposed on the first epicyclic gear system by the sharing of the planet carrier constituted by said outer ring (3).

6. Movement (1000) according to one of claims 1 to 5, characterized in thatsaid rotating cage regulator (200) is a jumping seconds flying tourbillon, the jump frequency of which fj is determined by the formula fj = ((N40*N7) / N70)*(f0 / N4), where N40 is the number of teeth of said escape pinion (40), N7 is the number of teeth of said locking wheel (7), N70 is the number of teeth of said locking pinion (70), f0 is the frequency of the oscillator constituted by said balance wheel and hairspring, and N4 is the number of teeth of said escape wheel (4), and further characterized in that the ratio f0 / (0.5*fj) is an integer.

7. Movement (1000) according to one of claims 1 to 6, characterized in thatsaid locking element (21) or said locking pallet comprises a bearing surface, suitable for cooperating with each said locking tooth (71), and which extends, in a plane perpendicular to the pivot axis of said cage (2), in a direction substantially tangential to a housing (111) in which said locking element (21) is inserted and fixed, and in that the jump instant is adjustable by adjusting the relative tangential position between said locking element (21) and each said locking tooth (71), corresponding to a rest position of said locking tooth (71).

8. Movement (1000) according to claim 7, characterized in thatsaid rest position is adjustable in a locked position of said ring (3) by moving said escapement element (5) by a predetermined number N of escapement steps, and by rotating said planetary locking wheel (7) by an angle corresponding to a predetermined number X of teeth of said planetary locking wheel (7).

9. Movement (1000) according to claim 8, characterized in that each said locking tooth (71) is arranged to take, in increments, an integer number of discrete rest positions on the depth of said locking element (21), each referenced by a sector number Y, and reachable according to a table indicating said number X of teeth of said planetary locking wheel (7) satellite to be rotated clockwise, and said number N of additional escape steps to be made at the level of said escape element (5) or said anchor.

10. Movement (1000) according to one of demands 7 to 9, characterized in thateach said locking tooth (71) is arranged to occupy, with respect to said locking element (21), rest positions within a predetermined angular interval, with respect to said pivot axis of said cage (2), corresponding to an integer number of degrees.

11. Movement (1000) according to one of claims 7 to 10, characterized in that said exhaust pinion (40) and said locking pinion (70) mesh with the same said fixed wheel (1), in that the position of said locking element (21) is fixed relative to the pivot axis of said escape wheel (4), and in that the locking depth of the teeth of said planetary locking wheel (7) on said locking element (21) is defined by the respective angular orientation of the teeth of said escape pinion (40) and of said locking pinion (70).

12. Movement (1000) according to one of claims 7 to 11, characterized in thatthe frequency f0 of the oscillator, and the whole number of teeth of the different pinions and wheels of the mechanism, namely the number of teeth N4 of said escape wheel (4), the number of teeth N40 of said escape pinion (40), the number of teeth N1 of said fixed wheel (1), the number of teeth N70 of said locking pinion (70), and the number of teeth N7 of said locking wheel (7) are such that the desired jump frequency fj satisfies a first condition according to which fj = ((N40*N7) / N70)*(f0 / N4), and a second condition according to which the ratio f0 / (0.5*fj) is a whole number.

13. Movement (1000) according to claim 12, characterized in that fj = 1 Hz, f0 = 3 Hz, N4 = 15, N40 = 7, N70 = 7, N7 = 5, for one jump per second.

14. Movement (1000) according to claim 12, characterized in that fj = 2 Hz, f0 = 4 Hz, N4 = 20, N40 = 10, N70 = 16, N7 = 16, for a jump per half-second.

15. Watch (2000) comprising at least one movement (1000) according to any one of claims 1 to 14.

16. A watch assembly comprising at least one watch according to claim 15 and / or a movement (1000) according to any one of claims 1 to 14, characterized in that said watch assembly includes, for each type of said movement (1000) or caliber, a table for the factory or after-sales watchmaker, said table detailing the number X of teeth of said planetary locking wheel (7) satellite to be turned clockwise, and the number N of additional escapement steps to be made at the level of said escapement element (5), to obtain a predetermined rest position of said locking tooth (71) on said locking element (21).

17. A timepiece assembly according to claim 16 comprising a movement (1000) according to claim 13, comprising, as parameters of said number X of teeth of said planetary locking wheel (7) to rotate clockwise, and of said number N of additional escapement steps to be made at the level of said escapement element (5), for a division of a central angle of 1° on said locking element (21) into seven rest positions of said locking tooth (71) designated sector No. 1 to sector No. 7, with sector No. 1, locking depth of "1", 9 escapement steps, no teeth of the planetary locking wheel 7, with sector No. 2, locking depth of "2", 2 escapement steps, 1 tooth of the planetary locking wheel 7, with sector No. 3, locking depth of "3", 7 escapement steps, 4 teeth of the planetary locking wheel 7, with sector No. 4, locking depth of "4 "No escapement, no teeth on the planetary locking wheel 7,with sector no. 5, locking depth of "5", 5 escapement steps, 3 teeth of the planetary locking wheel 7; with sector no. 6, locking depth of "6", 10 escapement steps, 1 tooth of the planetary locking wheel 7; and with sector no. 7, locking depth of "7", 3 escapement steps, 2 teeth of the planetary locking wheel 7.

18. A method for precisely adjusting the relative positions of said planetary locking wheel (7) and said locking element (21) of a watch assembly according to claim 16 or 17, by adjusting the locking depth of the locking teeth (71) of the planetary locking wheel (7) on said locking element (21), said method comprising a first step (A) of randomly riveting said escape wheel (4) onto its said escape pinion (40) on the one hand, and of said planetary locking wheel (7) onto its said locking pinion (70), said first step (A) comprising a positioning adjustment of said locking element (21) is carried out to ± 1° from its correct theoretical position and its fixing to said cage (2), a second step (B) of assembling the mechanism without a balance wheel of said balance-hairspring or an upper cage comprising said rotating cage regulator (200),with random positioning of said escape wheel (4) and said planetary locking wheel (7) of the seconds-jumping mechanism, and winding of the mainspring of the movement, said second step (B) comprising advancing said cage (2) in increments of 1° by manually moving said escapement element (5) back and forth until said locking tooth (71) reaches the distal end of said locking element (21), just before it falls and thus releases the seconds-jumping mechanism, a third step (C) of verifying that the tip of said locking tooth (71) is in one of the positions marked on said locking element (21), on which an angular deviation of 1° is cut into an integer number of relative positions of said locking tooth (71) with respect to said locking element (21), and this position is identified, a fourth adjustment step (D) by temporarily blocking said ring (3),disengagement of said planetary locking wheel (7) and its repositioning in accordance with said instruction table after rotating said cage (2) by manually moving said escapement element (5) back and forth for the required number of steps, a fifth step (E) of checking the locking depth of said locking tooth (71), and, if the desired locking depth is not achieved, iterative repetition of said third step (C) and said fourth step (D) until the desired locking depth is achieved.

19. Adjustment method according to claim 18, comprising a sixth step (F) of adjusting the preload of said reload spring (62) of said reload wheel (61) to the lowest level necessary to obtain a net jump of seconds.

20. Adjustment method according to claim 19, said sixth step (F) comprising reinstalling said charging wheel (61) with another pair of teeth in contact with said teeth (22) of said cage (2).

21. Adjustment method according to any one of claims 18 to 20, wherein, in said third step (C), the relative position between said locking tooth (71) and said locking element (21) is adjusted by a suitable adjustment.

22. Adjustment method according to any one of claims 18 to 21, wherein, in order to adjust the relative position of a seconds hand (101) and said tourbillon cage (2), a support (10) of said seconds hand (101) is adjusted by sliding on a constant radius, before screwing it onto said ring (3), in order to coincide exactly with a pillar (29) comprising said rotating cage regulator (200) at the moment of the seconds jump.

23. Adjustment method according to any one of claims 18 to 22, wherein, to ensure alignment exactly with a seconds index of a dial, said fixed wheel (1) is adjusted in rotation relative to a seconds dial, by oblong holes around its fixing screws and a cutout allowing the passage of an eccentric tool (300) to finely adjust the position.

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