A watch with a mechanical movement equipped with a rotating cage regulator.

Abstract

We manufacture new watch movements equipped with a governor located downstream of the rotary cage governor, whose jump position can be set at the factory. [Solution] A rotary cage governor 200 comprises a cage that supports a fixed wheel 1, an escapement wheel 4 having a spring-type balance wheel, an escapement element 5, and a pinion 40 that meshes with the fixed wheel, a lower cage 2 that supports teeth 22 and a locking element 21, a winding wheel 61 that is attached to a spring 62 and rotates on a bearing ring 3 fixed to a plate, and a lock wheel 7 having teeth that can be stopped by a locking pallet 21, the assembly consists of a planetary gear system, the cage 2 is a sun gear train, the ring 3 is a planetary carrier, the winding wheel is a first planetary gear, and the lock wheel is a second planetary gear, configured to release or lock the movement of the ring 3 and supporting a locking pinion 70 that meshes with the fixed wheel.

Description

Technical Field

[0001] The present invention relates to a mechanical watch movement comprising at least one rotating cage speed regulator.

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

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

[0004] The present invention also relates to a method for precisely adjusting the relative position between a planetary locking wheel and a locking pawl stone specific to the present invention.

[0005] The present invention relates to the field of mechanical watches comprising a tourbillon speed regulator, more specifically a flying tourbillon.

Background Art

[0006] The present invention relates to a watch having a mechanical movement equipped with a rotating cage speed regulator. A "rotating cage speed regulator" means a system that rotates a template around an axis, and tourbillons and Breguet's carousel belong to this category. More specifically, but not limited thereto, the present invention can be applied to a rotating cage speed regulator which is a tourbillon, particularly a flying tourbillon, equipped with a jumping second display mechanism.

[0007] The proposed mechanism enables the display of jumping seconds in a mechanical watch equipped with a rotating cage speed regulator, particularly a flying tourbillon.

[0008] The "deadbeat second" mechanism has been known for centuries and is designed to make it easier to read the exact seconds displayed by a timepiece mechanism.

[0009] Stationary high-precision mechanical clocks generally use a "seconds pendulum" with an oscillation frequency of 0.5 Hz (i.e., an oscillation period of 2 seconds or 1 second per half-oscillation or alternating oscillation). Most standard escapements used in high-precision pendulum clocks (such as the Graham / Liefler / Strasser escapement) impulse the oscillator once per half-oscillation, i.e., twice per oscillation (corresponding to 3,600 oscillations per hour), and as a natural result, the seconds hand jumps in one-second increments. Clocks with seconds pendulums were used as standard astronomical chronometers for measuring the time of celestial transits until the mid-20th century.

[0010] The need for a portable, high-precision chronometer for navigation (see Queen Anne's Act of Longitude, 1714, England) led to the development of the marine chronometer. The marine chronometer operated at an oscillation frequency of 2 Hz (i.e., 14,400 A / h) and, combined with a chronometer escapement that impulsed the balance wheel every two half-oscillations (i.e., one impulse per oscillation), drove the seconds hand in 0.5-second increments.

[0011] However, pocket watches and wristwatches, which are much smaller than marine chronometers, require higher frequency oscillators to achieve comparable accuracy (Q value) (today, wristwatch movements commonly use oscillation frequencies from 2.5Hz to 5Hz), resulting in smaller jumps in the second hand (for a standard lever escapement: 5 jumps per second at 2.5Hz, 10 jumps per second at 5Hz).

[0012] Therefore, it was necessary to find another way to achieve easy-to-read jumps for the second and half-second hands.

[0013] In the mid-18th century, Jean Romilly was the first watchmaker to design a clock with a stopable seconds hand and a balance wheel oscillation frequency chosen to produce a jumping seconds hand.

[0014] Around 1776, Jean-Moïse Pouzet invented a second hand mechanism that could be started and stopped independently ("independent deadbeat second"). This mechanism required a secondary gear train having a "whip" that engaged with a "star" on the axis of the escapement wheel and then released, causing it to rotate rapidly once per second. Such a mechanism is described in Swiss Patent Application Publication No. 256885, granted to Omega. Such a watch mechanism had a second hand that jumped in one-second increments (when using a higher-frequency oscillator and a standard escapement).

[0015] Subsequent designs introduced an intermediate spring mechanism periodically wound up by the main gear train, eliminating most of the secondary gear train.

[0016] With the advent of modern chronograph mechanisms featuring resettable seconds hands, these mechanisms gradually faded into obscurity, and in the 1950s and 1960s, permanently functioning deadbeat seconds hands made a brief comeback, such as the Omega Caliber 372's "Synchrobeat" caliber. In recent years, interest in jumping seconds mechanisms has been rekindled among enthusiasts of luxury watches, with many incorporating a "remontoir dégalité" (constant force device) that provides a one-second winding interval for the jumping seconds. However, such mechanisms involve the energy flow between the mainspring barrel and the escapement, and the components must be dimensionally designed accordingly. Furthermore, precisely setting the timing of the jump in existing mechanisms is difficult, if not impossible. [Prior art documents] [Patent Documents]

[0017] [Patent Document 1] Swiss Patent Application Publication No. 256885 [Patent Document 2] Swiss Patent Application Publication No. 717982 [Overview of the project] [Problems that the invention aims to solve]

[0018] The present invention aims to manufacture a new watch movement comprising a rotating cage speed regulator, particularly a tourbillon speed regulator, especially one in which the mechanism is downstream of the escapement mechanism and the jumping second flying tourbillon speed regulator whose jump position can be set at the factory.

Means for Solving the Problem

[0019] Therefore, the present invention relates to a mechanical watch movement comprising at least one rotating cage speed regulator according to claim 1.

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

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

[0022] The present invention also relates to a method for precisely adjusting the relative position between a planetary locking wheel and a locking element specific to the present invention.

Brief Description of the Drawings

[0023] The objects, advantages and features of the present invention will become apparent from the following detailed description with reference to the accompanying drawings. [Figure 1]A schematic perspective view of a rotating cage governor according to a particular variant of the present invention is shown, which is a specific and non-limiting case of a jumping second flying tourbillon, the tourbillon comprising a lower cage, the lower cage being modified by the addition of two outwardly projecting gear teeth carried by a substantially annular body and the addition of a locking pawl stone carried by an arm of the lower cage. The tourbillon also comprises a winding wheel cooperating with a winding spring, the two gear teeth being configured to mesh with the winding wheel. The winding wheel is carried by a bearing ring, which also carries a planetary locking wheel. The locking wheel comprises locking teeth configured to abut against the locking pawl stone in a locked position. [Figure 2] A schematic top view of the lower part of the tourbillon of FIG. 1, seen from the side visible to the user and from the opposite side of the plate of the movement comprising the tourbillon, the upper cage, the hairspring assembly and the cock fixing the hairspring are not shown. The escape wheel is visible at the 6 o'clock position, the anchor at the 5 o'clock position, the wheel and hairspring at the 10 o'clock position and the gear teeth are visible. One arm of the lower cage at the 4 o'clock position carries the locking pawl stone, the locking wheel is at the 3 o'clock position and it can be seen that the locking teeth are in a stationary abutment against the support surface of a locking element (here non-limitingly the locking pawl stone) extending substantially tangentially. [Figure 3] A schematic exploded perspective view of all the components of the tourbillon of FIG. 1 is shown. [Figure 4] A schematic top view similar to FIG. 2 of all the components for setting the second hand jump of the tourbillon of FIG. 1, the lower cage superimposed on the fixed tourbillon wheel, the escapement mechanism on the left, the locking element at the 6 o'clock position and the locking wheel is shown. The locking wheel comprises a pinion meshing with the fixed wheel. The gear teeth are visible at the 1 o'clock position. [Figure 5]Figure 4 shows a schematic sub-diagram of the end of a locking element similar to that shown in this particular configuration, where the support surface of the locking tooth covers a central angle of 1° from the pivot axis of the cage. This angle is divided into an integer number of sectors (seven in this case) corresponding to the number of potential locking positions of the distal end of the locking tooth on the locking wheel. [Figure 6] Figure 5 shows a schematic enlarged top view of the engagement between the locking element and the locking teeth, similar to Figure 5. On the left, the relative orientation of the locking wheel with respect to the imaginary line between the center of the locking wheel and the center of the fixed tourbillon wheel remains the same (except that it is shifted exactly by one tooth clockwise), but the locking teeth on the locking pinion are tilted by the difference between 360° divided by the number of teeth, on the one hand by the number of teeth of the planetary locking wheel, and on the other hand by the number of teeth of the locking pinion. In the particular example shown, this difference has an angular value of 20.5714° relative to the original orientation (between the dashed and solid lines tangent to the fixed wheel). On the right side of the figure, the locking pinion rolls along the fixed wheel and over the teeth of the fixed wheel, restoring proper engagement between the teeth of the locking pinion itself and the teeth of the fixed wheel. In the specific gear ratio shown in the illustrated example, a 20.5714° rotation of the lock pinion around its axis corresponds to a 1.71429° rotation around the tourbillon's central axis. [Figure 7] Figure 2 shows a partially schematic diagram of an enlarged view, illustrating the means for adjusting the position of the second hand. [Figure 8] Figure 7 shows a schematic exploded perspective view of the enlarged image shown. [Figure 9] A schematic perspective view similar to Figure 1 is shown, illustrating the use of an eccentric tool to set the angular position of the fixed wheel relative to the seconds hand dial. [Figure 10] Figure 9 shows a top view. [Figure 11] A schematic front view of a watch equipped with a rotating cage regulator according to the present invention, particularly a movement incorporating a tourbillon, is shown. [Figure 12] This flowchart shows the steps for precisely adjusting the relative position between the planetary locking wheel and the locking element. [Modes for carrying out the invention]

[0024] The present invention relates to a mechanical watch movement 1000 that includes a mechanism for displaying deadbeat seconds in a mechanical watch 2000 equipped with a rotating cage governor 200, and more particularly in a mechanical watch 2000 equipped with a flying tourbillon.

[0025] The proposed and illustrated mechanism is based on the flying tourbillon with balance stop device described in Swiss Patent Application Publication No. 717982 granted to the Glashütte Original, which is incorporated herein by reference.

[0026] The mechanical watch movement 1000 comprises at least one rotary cage regulator 200, which comprises a fixed wheel 1, a cage supporting a spring balance wheel having a balance 60 and a main hairspring 90 (in certain preferred modifications shown in the figure, comprising at least a lower cage 2 and an upper cage 11), an escapement element 5 (more specifically an anchor in the illustrated example), and an escapement wheel 4, the escapement pinion 40 of the escapement wheel 4 engaging directly or indirectly with the fixed wheel 1, more specifically directly in certain preferred modifications shown in the figure. In other modifications, for example, an intermediate movable body is present between the escapement pinion 40 and the fixed wheel 1, similar to a Bonixen carousel mechanism in which the escapement pinion is positioned by a movable wheel, or a five-minute tourbillon in which an intermediate movable body is inserted between the escapement wheel and the fixed wheel.

[0027] The cage also supports a locking element 21 and a bearing fixed coaxially to the cage on the movement plate 100.

[0028] According to the present invention, the rotary cage governor 200 comprises a lock wheel 7 having lock teeth 71 that pivot on a bearing ring 3. These lock teeth 71 can be stopped by the lock element 21 at a factory-settable locked position. The lock wheel 7 is configured to release or lock the movement of the ring 3 and carries a lock pinion 70 that permanently engages with the fixed wheel 1. The ring 3 is connected to the rotary cage governor 200 by an intermediate winding system, which winds a winding spring 62 in response to the movement of the rotary cage governor 200, and maintains the movement of the ring 3 in the same rotational direction as the rotary cage governor 200 when the winding spring 62 is released.

[0029] Since the present invention can be used in all types of escapement mechanisms, regardless of whether they are anchor escapements, detent escapements, duplex escapements, cylinder escapements, gathering anchor escapements, Graham escapements, etc., it should be understood that the properties of the escapement element 5 will differ depending on the type of escapement used. The present invention is shown non-limitingly in specific examples of anchor escapement mechanisms, and the escapement element 5 is more specifically, but not limited to, an anchor.

[0030] According to a particular modification of the present invention shown in the figure, the lower cage 2 carries gear teeth 22 and a locking element 21 or a locking pallet stone as shown in the figure. The rotary cage governor 200 further comprises a winding wheel 61 that is attached to a winding hairspring 62 and revolves on a bearing ring 3 fixed to a plate of the movement 1000 (by its inner ring), and a locking wheel 7 having locking teeth 71 that can be stopped by the locking element 21 at a factory-settable stop position, the assembly comprising a first planetary gear set, where the lower cage 2 is a sun gear train, the bearing ring 3 is a planetary carrier, and the winding wheel 61 is a first planetary gear. The locking wheel 7 is configured to release or lock the movement of the ring 3 and carries a locking pinion 70 that permanently meshes with a fixed wheel 1.

[0031] The locking element 21 can have different shapes and can be fixed to different parts of the mechanism in different ways. For example, a pin protruding from the upper cage 11 of the vibrating system also functions as described below.

[0032] The winding system described above, which uses a planetary gear mechanism between teeth 22 on the lower cage 2 of the tourbillon and a winding wheel 61 having a winding spring 62 in the form of a hairspring, is a particularly compact modification, but a leaf spring with, for example, a first end fixed to the cage of the tourbillon and a second end fixed to the planetary carrier (ring 3) is also suitable.

[0033] Figures 1 to 3 show a perspective view, a top view, and an exploded view of such a rotary cage governor 200 according to the present invention.

[0034] More specifically, the rotary cage governor 200 comprises a volute cage having a lower cage 2 and an upper cage 11 connected by three pillars 29. The cage supports a spring balance wheel comprising a balance 60 and a main hairspring 90 mounted on a stud 91 on a bar. The cage is fixed to the axis of a seconds pinion 9 configured to drive the day's motion wheel.

[0035] The cage supports an escapement mechanism, which comprises an escapement wheel 4 having N4 teeth, and the escapement wheel 4 is configured to engage with an escapement element 5 (in this case, a Swiss lever having two pallet stones 51 and 52, but not limited to this case). Both the escapement wheel 4 and the escapement element 5 pivot at the top of the bar 50.

[0036] The tourbillon comprises a fixed wheel 1 fixed to a plate, and the fixed wheel 1 has an outer tooth portion having a number of teeth N1.

[0037] The escape wheel 4 is attached to an escape pinion 40 having N40 teeth, and the escape pinion 40 meshes with the teeth of the fixed wheel 1.

[0038] With respect to this known mechanism, according to the present invention, the lower cage 2 of the rotary cage governor 200 is modified by adding two outwardly projecting gear teeth 22 and, in particular, a ruby ​​locking element 21 (or locking pawl), the locking element 21 being supported in the bed 111 by the arm 110 of the lower cage 2.

[0039] More specifically, the tourbillon includes a winding wheel 61, which is supported by an upper pivot 610 on a first cock 66 and works in conjunction with a winding spring 62. More specifically, the winding spring 62 has its outer end 622 attached to the first cock 66 and its inner end 621 attached to the winding wheel 61.

[0040] The two teeth 22 are positioned to mesh with the winding wheel 61.

[0041] More specifically, the tourbillon also comprises a planetary locking wheel 7 having N7 locking teeth 71, the planetary locking wheel 7 being supported by a support 75 and a second cock 76 and mounted to pivot between them. A locking element 21 is configured to contact and engage with the locking teeth 71 on this planetary locking wheel 7.

[0042] Both the hoisting wheel 61 and the planetary locking wheel 7 are mounted so as to pivot away from each other on the outer ring 3 of a ball bearing that is coaxially fixed below the lower cage 2 of the rotary cage governor 200.

[0043] While the ball bearing 3 is stationary, the winding spring 62 is wound by the tourbillon, which is moving due to the meshing of two teeth 22 on the lower cage 2 of the tourbillon with the winding wheel 61.

[0044] The tension of the winding spring 62 allows the entire outer ring 3 of the ball bearing to move freely and simultaneously rotate in the same direction as the tourbillon. The assembly consists of a first planetary gear system in which the tourbillon is the sun gear train, the outer ring 3 of the ball bearing is the planetary carrier, and the winding wheel 61 is the planetary wheel.

[0045] The planetary locking wheel 7 is another planetary wheel mounted to pivot on the outer ring of the bearing. The free movement of the outer ring 3 of the ball bearing is locked by the planetary locking wheel 7. The planetary locking wheel 7 has a locking pinion 70 with N70 teeth that mesh with the fixed wheel 1 of the tourbillon, while the teeth of the wheel abut against the locking element 21 of the lower cage 2 of the tourbillon (thus this is a secondary planetary gear mechanism).

[0046] A secondary planetary gear system, having a fixed wheel 1 of a rotating cage governor 200 as a solar gear train and a lock pinion 70 of a planetary lock wheel 7 as a planetary wheel, is superimposed on a first planetary gear system for a hoisting wheel 61, and both systems share a common planetary carrier, i.e., an outer ring 3 of a ball bearing.

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

[0048] The pre-tension of the winding spring 62 within the winding wheel 61 causes the ball bearing to rotate in the same direction as the tourbillon. This movement is locked by the locking teeth 71 of the planetary locking wheel 7, which rests on a locking element 21 pressed into the lower cage 2 of the rotary cage governor 200.

[0049] While the tourbillon (more specifically, in non-limiting modifications disclosed herein and shown in the drawings, with a period of one minute) rotates on its axis, the locking element 21, in particular the tip of the pallet stone as shown in the figure, advances to the tip of the locking tooth 71, and the two teeth 22 of the lower cage 2 of the tourbillon continue to wind the winding wheel 61.

[0050] When the tourbillon rotates approximately 6° (for a tourbillon that rotates once per minute, this occurs after 1 second, or 1 / 60th of a minute, or 1 / 60th of a rotation), the locking tooth 71 disengages from the locking element 21, allowing both the planetary locking wheel 7 and the ball bearing outer ring assembly to rotate freely around their respective axes.

[0051] This rotation is driven by the planetary winding wheel 61, and stops when the next locking tooth 71 of the planetary locking wheel 7 contacts the locking element 21, at which point the cycle restarts.

[0052] In the proposed non-restrictive form of the mechanism, the tourbillon balance oscillates at a frequency of 3 Hz (i.e., 21,600 vibrations per hour), the escapement wheel 4 has 15 teeth, and its escapement pinion 40 has 7 teeth. The planetary locking wheel 7 has 5 teeth, its locking pinion 70 has 7 teeth, and the fixed seconds wheel has 84 teeth.

[0053] Therefore, the tourbillon cage itself moves forward with a rotation of 1° for each jump, which is 6 times per second (i.e., 3 teeth of the escapement wheel 4). Consequently, the escapement wheel 4 rotates once around its axis in 5 seconds (5 seconds = 15 teeth of the escapement wheel 4, i.e., 3 teeth of the escapement wheel per second). The same applies to the planetary lock wheel 7, since the gear ratio between its lock pinion 70 and the fixed tourbillon wheel 1 is the same as the gear ratio of the escapement wheel 4.

[0054] The five-tooth planetary locking wheel 7 allows the ball bearings to jump in one-second increments.

[0055] Therefore, the second hands 10 and 101, fixed to the outer ring 3 of the ball bearing, indicate a jumping second (or deadbeat second).

[0056] Considering that the escapement pinion 40 on the escapement wheel 4 and the lock pinion 70 on the planetary lock wheel 7 mesh with the same fixed wheel 1 of the tourbillon, and that the position of the lock element 21 is fixed with respect to the axis of the escapement wheel 4, the locking depth of the teeth of the planetary lock wheel 7 with respect to the lock element 21 is defined by the respective angular directions of the teeth of the wheel and pinion.

[0057] Setting the position of the pallet stone 21 in the lower cage of the tourbillon, or aligning the wheels and pinions of the escapement wheel 4 and planetary lock wheel 7, in order to obtain a lock depth of approximately 5.5° after a jump of seconds, does not seem very practical, considering the unavoidable tolerances, the required ease of assembly, and the constraints of after-sales service.

[0058] Therefore, the present invention proposes the following procedure for precisely adjusting the relative position between the planetary locking wheel 7 and the locking element 21 of the lower cage 2 of the tourbillon, that is, for adjusting the locking depth of the locking teeth 71 of the planetary locking wheel 7 to the locking element 21.

[0059] In the first step A, random riveting is performed on the escapement wheel 4 on one side and the planetary lock wheel 7 on the other side, with respect to their respective pinions (escapement pinion 40 and lock pinion 70), without regard to angular direction. The position of the lock element 21 is set within ±1° of its exact theoretical position (using an optical comparator or gauge, etc.), and this lock element 21 or this locking pallet is fixed to the lower cage 2 of the tourbillon.

[0060] In the second step B, the mechanism is assembled (without the balance wheel 60 or the upper tourbillon cage 11), the escapement wheel 4 and planetary lock wheel 7 of the jumping seconds mechanism are randomly positioned, and the mainspring of the movement is wound.

[0061] The tourbillon carriage can be advanced (1° at a time) by manually moving the escapement element 5 back and forth until the locking teeth 71 on the planetary locking wheel 7 reach the distal end of the locking element 21, just before the locking teeth 71 disengage and release the jumping seconds mechanism, as shown in Figure 4.

[0062] In the third step C, it is confirmed that the tip of the locking tooth 71 of the planetary lock wheel 7 is at one of the positions marked on the locking pallet, particularly the positions numbered "1" through "7" in Figure 5. In Figure 5, a 1° angular interval is divided into seven relative positions of the locking tooth 71 with respect to the locking element 21, and these positions are identified. It is advantageous that the relative position between the locking tooth 71 and the locking element 21 can be adjusted using a preferred setting.

[0063] The fourth step D is dedicated to this adjustment setting. Once the movement of the outer ring of the ball bearing is temporarily locked (for example, by inserting a piece of paper between the movement plate and the ball bearing), the planetary lock wheel 7 can be removed, and the rotary cage governor 200 can be rotated appropriately by manually moving the escapement element 5 back and forth for the required number of steps, after which it can be reinstalled according to an instruction sheet or table such as the one shown below. For example, if the lock depth is "5": Remove the planetary lock wheel 7, rotate the tourbillon for 5 additional escapement steps, and reinstall the planetary lock wheel 7 rotated clockwise by an angle equivalent to 3 teeth of the planetary lock wheel 7, positioning it at the first angle of the lock element 21 on the tourbillon.

[0064] Such tables are non-limiting and correspond to the mechanisms shown in the figures, having various movable bodies with specific numbers of teeth, very specific vibration frequencies f0 and jump frequencies fj, corresponding to the configuration of the escapement mechanism and the configuration of the lock wheel, and are provided herein according to the calculation method described below. • Sector number 1, lock depth "1": 9 escapement steps, no teeth on planetary lock wheel 7 • Sector number 2, lock depth "2": 2 escapement steps, planetary lock wheel 7 teeth 1 • Sector number 3, lock depth "3": 7 escapement steps, planetary lock wheel 7 teeth 4 • Sector number 4, lock depth "4": 0 escapement steps, no teeth on planetary lock wheel 7 • Sector number 5, lock depth "5": 5 escapement steps, planetary lock wheel 7 with 3 teeth • Sector number 6, lock depth "6": 10 escapement steps, planetary lock wheel 7 teeth 1 • Sector number 7, lock depth "7": 3 escapement steps, planetary lock wheel 7 has 2 teeth.

[0065] The fifth step E is used to verify that the locking teeth 71 on the planetary locking wheel 7 now have the desired or ideal locking depth (sector number 4) relative to the locking element 21 on the tourbillon. If not, steps C and D are repeated until the desired locking depth is reached.

[0066] The sixth step F consists of setting the pre-tension of the winding spring 62 on the winding wheel 61 to the minimum level required to obtain a net jump of 1 second. Excessive pre-tension actually reduces the amplitude of the balance wheel 60. To do so, the winding wheel 61 can be repositioned so that another pair of teeth contacts the teeth 22 of the lower cage 2 of the tourbillon, which is unique to this invention.

[0067] This method of fine-tuning the locking depth is based on the principle of the vernier scale. With the tourbillon in a fixed position and one tooth of the planetary locking wheel 7 in contact with the locking element 21, the planetary locking wheel 7 is rotated clockwise by one tooth around its axis, that is, by 360° divided by the number of teeth N7 on the locking wheel 7 (5 teeth in this example), or in other words, by 360° / 5 = 72°.

[0068] The lock pinion 70 on the planetary lock wheel 7 has N70 = 7 teeth.

[0069] The relative orientation of the lock wheel 7 with respect to the imaginary line between the center of the lock wheel 7 itself and the center of the fixed wheel 1 of the tourbillon remains the same (except that it is shifted by exactly 11 teeth clockwise), but the lock teeth 71 on the lock pinion 70 on the lock wheel 7 are tilted relative to their original orientation by a difference of 360° divided by the number of teeth. The number of teeth is, on the one hand, the number of teeth N7 of the planetary lock wheel 7 (5 teeth in this example), and on the other hand, the number of teeth N70 of the lock pinion 70 on the lock wheel 7 (7 teeth in this example), and the difference is (360° / 5 - 360° / 7), i.e., (72° - 51.4286°) = 144 / 7° = 20.5714° (see left side of Figure 6).

[0070] Therefore, the lock pinion 70 on the planetary lock wheel 7 needs to move along the fixed wheel 1 on the tourbillon in order to restore proper engagement between the teeth of the lock pinion 70 itself and the teeth of the fixed wheel (see the right side of Figure 6).

[0071] In the case of a gear ratio of 7 / 84 = 1 / 12 between the fixed wheel 1 of the tourbillon (N1 = 84 teeth) and the lock pinion 70 of the planetary lock wheel 7 (N70 = 7 teeth), a rotation of 20.5714° around the axis of the lock pinion 70 corresponds to a rotation of (20.5714° * 1 / 12) = 144 / 7° * 1 / 12 = 12 / 7° = 1.71429° around the central axis of the tourbillon, as can be seen on the right side of Figure 6.

[0072] In summary, when the planetary lock wheel 71 is removed, rotated clockwise by 11 teeth, and reinstalled, the contact point between the tip of the locking teeth 71 of the lock wheel 7 and the locking element 21 (represented by the ruby ​​pallet in Figures 4, 5, and 6) moves clockwise by an angle of 1.71429° = (360° / 5 - 360° / 7) * 7 / 84 (and therefore lowers further on the locking element 21). If the planetary lock wheel 7 is rotated by 2 teeth instead of 1 tooth before reinstallation, the corresponding teeth of the lock wheel will lower further on the locking element 21 by an angle of 2 * 1.71429° = 3.42857°. Therefore, depending on the number of teeth X rotated before reinserting the planetary lock wheel 7, the following theoretical changes are obtained in the lock depth Δ / rotation of the lock wheel around the fixed second wheel. Here, 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] However, once the escapement is released, the locking element 21 moves 360° / (84 / 7*15*2)=1° clockwise (this is because the fixed tourbillon wheel 1, i.e., the seconds wheel, has 84 teeth, the escapement pinion 40 of the escapement wheel 4 has 7 teeth, and the escapement wheel 4 has 15 teeth. Each time the escapement is released, the escapement wheel 4 rotates by half a tooth due to the Swiss lever escapement 5 used, which has two impulses per complete oscillation). Therefore, the coefficient is 2.

[0074] As a result, the locking depth Δ of the locking teeth 71 of the planetary lock wheel 7 to the pallet stone 21 on the tourbillon cage 2 can be reduced by 1° for each escapement step.

[0075] To change the lock depth by a fraction of a second, the escapement can be released by a corresponding number of steps, as follows: where Δ is the lock depth without additional escapement steps, N is the number of additional escapement steps, and ΔM is the lock depth changed by this corresponding number of N 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] That is, when N = 1, it is 1.71429° div 1°, when N = 3, it is 3.42857° div 1°, and so on.

[0077] To put it another way, 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 generally, Δ = X * 12 / 7° N = Δ div 1° ΔM = Δ mod 1°

[0078] As a result, the lock depth can be changed in 1 / 7° increments by the appropriate combination of the rotation of the planetary lock wheel 7 before repositioning and the release of an appropriate number of escapement steps. This is because, when the jump mechanism is released in one escapement step and the corresponding 1° rotation of the tourbillon cage and the lock element 21 fixed to the tourbillon cage, the lock teeth 71 on the planetary lock wheel 7 can be positioned in any of the seven positions shown in Figure 5 during the last half-oscillation before the jump is released.

[0079] The central position of "4" is preferable because it provides a sufficient safety margin against premature or delayed release in the event of concentricity deviation, poor gear cutting accuracy, or any other shape defects.

[0080] However, depending on the random orientation of the parts during assembly, the watchmaker may find other positions (1-3 or 5-7). By removing the planetary lock wheel 7 again, advancing the escapement by a predetermined number of steps, and reinserting the planetary lock wheel 7 rotated by a predetermined number of teeth, state "4" should be reached. This can be achieved from state "5" by, for example, causing a rotation of 1 / 7°, which can be achieved by N=5 additional escapement steps (as seen in the table above) and repositioning the planetary lock wheel 7 rotated by X=3 teeth.

[0081] This yields the following correspondence between sectors 1 through 7 and the table above. The last Y value indicates the correspondence with the referenced sector, i.e., the required position in 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 (indicated by *1*, 2*, and 3*), following the procedure in the table above means that the jump only occurs after two escapement steps, so in this case, an additional escapement step must be considered. Furthermore, the planetary lock wheel 7 has only N7=5 teeth, and therefore the rotation of 5 teeth corresponds to the starting position, so the actual rotation can be omitted (similarly, the rotation of 6 teeth corresponds to the rotation of 1 tooth, and the rotation of 7 teeth corresponds to the rotation of 2 teeth, and therefore the remainder when X is divided by 5 yields the same result as the rotation of X).

[0083] This provides, for example, the following easy-to-understand instructions for a watchmaker setting up the mechanism: sector number Y, number of teeth X on the planetary lock wheel 7 to be rotated clockwise, and 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] Therefore, by rotating the planetary lock wheel 7 by a number of teeth X, the planetary lock wheel 7 moves to a new position (X * 1.71429°) relative to its original position (clockwise around the axis of the tourbillon). The tangential displacement of the tip of the lock tooth 71 on the planetary lock wheel 7 along the pallet stone 21 substantially coincides with this value.

[0085] Furthermore, by manually moving the escapement element 5 from one edge to the other, the entire tourbillon jumps by 1° (tourbillon per minute, 6 jumps per second, 60 seconds per minute = 360 1° jumps). This allows the position of the distal end of the teeth 71 on the planetary lock wheel 7 relative to the lock element 21 to be adjusted in increments of 1 / 7°, i.e., by the remainder of (X * 1.71429°) divided by 1°, thus providing a rule for defining the above adjustment table.

[0086] To adjust the relative position of the seconds hand with respect to the lower cage 2 of the tourbillon, the support 10 of the seconds hand 101 can be adjusted by sliding it along a certain radius before screwing it to the outer ring 3 of the ball bearing, so that it can precisely align with the pillar 29 of the tourbillon when a seconds jump occurs, as can be seen in Figures 7 and 8. The adjustment and fixing can be advantageously achieved by a combination of a shouldered screw 81 and an oval counterbore 82.

[0087] To ensure that the second hand is precisely aligned with the second scale on the dial, the rotation of the fixed wheel 1 on the rotary cage governor 200 can be set relative to the second dial, as suggested by the oval hole 84 around its fixing screw 83 and the blank 85 which allows for fine adjustment of the position using an eccentric tool 300, as seen, for example, in Figures 9, 10, and 11.

[0088] In summary, the present invention improves upon the conventional jumping second mechanism, particularly in that, instead of functioning on the principle of a known constant-force device (remontoir dégalité), the mechanism according to the present invention operates outside the energy flow between the barrel and the escapement, thereby significantly reducing the stress induced in its components.

[0089] More specifically, the tourbillon in the mechanism of the present invention is a flying tourbillon.

[0090] In this embodiment of the present invention, it should be noted that the winding spring driving the proposed seconds jump mechanism is located on a planetary wheel positioned on the ball bearing of the jump mechanism, rather than on the same axis as the tourbillon. This makes it possible to use the mechanism described in Swiss Patent Application Publication No. 717982 granted to Glashütte Original, Glashütte Uhlenbetlieb GmbH, to stop the balance wheel 60 on the tourbillon when setting the hour and minute hands. This mechanism also facilitates adjustment of the spring pre-tension by simply incorporating the mechanism such that another pair of teeth contacts the tourbillon gear.

[0091] Furthermore, the compact layout of the present invention utilizes the otherwise empty space below the tourbillon cage, and the entire mechanism is fully visible through the existing opening in the flying tourbillon dial. The modularity of the present invention allows it to be applied to existing movements with minimal adjustments.

[0092] By changing the number of teeth on the planetary locking wheel, the mechanism can also be easily modified to jump at intervals of other values, for example, at 0.5-second intervals (by doubling the number of teeth on the planetary locking wheel), similar to a marine chronometer.

[0093] The mechanism according to the present invention can also be used by changing certain parameters, in particular the oscillator frequency f0, and the number of teeth (always integers) of various pinions and wheels of the mechanism, namely, the number of teeth of the escapement wheel 4 te or N4, the number of teeth of the escapement pinion 40 on the escapement wheel 4 tpe or N40, the number of teeth of the fixed tourbillon wheel 1 ttf or N1, the number of teeth of the lock pinion 70 on the lock wheel 7 tpb or N70, and the number of teeth of the lock wheel 7 tb or N7. However, the desired jump frequency fj must satisfy the following two conditions.

[0094] First condition: fj = ((tpe*tb) / tpb)*f0 / (te), or replace the number of teeth with the sign of their movable parts, fj=((N40*N7) / N70)*(f0 / N4)

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

[0096] In this way, the following mechanisms also function without limitation.

[0097] First example: fj=2Hz, f0=4Hz, te=20, tpe=10, tpb=16, tb=16, or replace the number of teeth with the sign of their movable parts, N4=20, N40=10, N70=16, N7=16.

[0098] Second example: fj=4 / 3Hz, f0=4Hz, te=20, tpe=12, tpb=9, tb=5, or replace the number of teeth with the sign of their moving parts, N4=20, N40=12, N70=9, N7=5, so this configuration results in a 3 / 4 second jump.

[0099] Please note that the specific modifications shown in the figure correspond to values ​​N4=15, N40=7, N70=7, and N7=5, by substituting the signs of the teeth for fj=1Hz, f0=3Hz, te=15, tpe=7, tpb=7, tb=5, or the number of teeth for the signs of the movable parts.

[0100] If the tourbillon is designed to rotate once per minute (i.e., to display 60 seconds accurately for every 360° rotation), the following additional conditions must apply: ttf = 60 * (tpe * f0) / te is an integer, or by replacing the number of teeth with the movable body reference code, ttf = N1 = 60 * (N40 * f0) / N4 is an integer.

[0101] The proposed configuration of the winding planetary wheel can also be used to apply other deadbeat second mechanisms to the flying tourbillon described in Swiss Patent Application Publication No. 717982, which typically requires a coaxially mounted hairspring or a secondary kinetic chain such as a secondary escapement mechanism, as used by Jaquet Droz, to store the necessary jump energy.

[0102] In this type of mechanism, the lower cage of the tourbillon can be used as the drive wheel for the anchor, and the outer ring of a ball bearing with a planetary winding wheel can be used as the jumping seconds wheel.

[0103] The present invention also relates to a clock 2000 comprising at least one movement 1000.

[0104] The present invention also relates to a watch assembly comprising at least one watch 2000 and / or one movement 1000. The watch assembly includes, for each type of movement 1000 or caliber, a table for use by a watchmaker in the factory or after-sales service department, the number of teeth X of a planetary lock wheel 7 to be rotated clockwise to obtain a predetermined locked position of the lock teeth 71 on the lock element 21, and the number of additional escapement steps N to be performed with respect to the escapement element 5.

[0105] In particular, in the specific example described herein, namely fj=1Hz, f0=3Hz, te=15, tpe=7, tpb=7, tb=5, or by replacing the number of teeth with the symbols of those movable bodies, N4=15, N40=7, N70=7, N7=5, the parameters for the number of teeth X of the planetary lock wheel 7 to be rotated clockwise and the number of additional escapement steps N to be performed on the escapement element 5 are as follows: When the central angle of 1° in the lock element (21) or the locking pallet is divided into seven locking positions of the locking teeth (71) referred to as sector number 1 to sector number 7, sector number 1 and locking depth "1" have 9 escapement steps and no teeth on the planetary locking wheel 7; sector number 2 and locking depth "2" have 2 escapement steps and 1 tooth on the planetary locking wheel 7; sector number 3 and locking depth "3" have 7 escapement steps and 4 teeth on the planetary locking wheel 7; sector number 4 and locking depth "4" have no escapement steps and no teeth on the planetary locking wheel 7; sector number 5 and locking depth "5" have 5 escapement steps and 3 teeth on the planetary locking wheel 7; sector number 6 and locking depth "6" have 10 escapement steps and 1 tooth on the planetary locking wheel 7; sector number 7 and locking depth "7" have 3 escapement steps and 2 teeth on the planetary locking wheel 7.

Claims

1. A mechanical watch movement (1000) comprising at least one rotary cage governor (200), wherein the rotary cage governor (200) comprises a cage supporting a fixed wheel (1), a spring balance wheel, an escapement element (5), an escapement wheel (4), and a locking element (21), and a bearing fixed coaxially to the cage on a plate (100) of the movement, wherein the rotary cage governor (200) comprises a locking wheel (7) having locking teeth (71) that pivot on a ring (3) of the bearing, and the locking teeth (71) can be stopped by the locking element (21) at a factory-settable locked position. A mechanical watch movement (1000) characterized in that the lock wheel (7) is configured to release or lock the movement of the ring (3) and carries a lock pinion (70) that permanently engages with the fixed wheel (1), the ring (3) is connected to the rotary cage governor (200) by an intermediate winding system, the intermediate winding system enables a winding spring (62) to be actuated by the movement of the rotary cage governor (200), and when the winding spring (62) is released, the ring (3) moves in the same rotational direction as the rotary cage governor (200).

2. The escapement pinion (40) meshes with the fixed wheel (1), and the intermediate winding system is a lower cage (2) included in the cage, comprising a lower cage (2) that supports gear teeth (22), and a winding wheel (61) attached to the winding spring (62), which revolves on the ring (3) and meshes with the gear teeth (22) on the lower cage (2), and the assembly comprising the lower cage (2), the winding wheel (61) and its winding spring (62), the ring (3), the lock wheel (7), and the lock element (21) constitutes a first planetary gear device in which the lower cage (2) is a sun gear train, the ring (3) is a planetary carrier, the winding wheel (61) is a first planetary gear, and the lock wheel (7) is a second planetary gear, as described in claim 1 (1000).

3. The movement (1000) according to claim 2, characterized in that the winding spring (62) on the winding wheel (61) is wound up by the movement of the cage (2) due to the meshing of the teeth (22) on the lower cage (2) and the winding wheel (61) while the bearing is stationary, and when the lower cage (2) rotates about its pivot axis (DP), the tip of the locking element (21) is movable to the tip of the locking tooth (71) that abuts against the locking element (21).

4. The fixed wheel (1) is fixed to the plate of the movement (1000) and has an outer tooth portion, the gear teeth (22) protruding outward, the winding wheel (61) pivots within the first cock (66) and both ends thereof are in conjunction with the winding spring (62) attached to the first cock (66) and the winding wheel (61), the planetary locking wheel (7) pivots within the second cock (76), and the winding wheel (61) and the planetary locking wheel (7) are separated from each other on the ring (3), which is the outer ring of the ball bearing. The movement (1000) according to claim 1, characterized in that it is mounted to rotate, the winding spring (62) is wound up by the movement of the rotary cage governor (200) by the meshing of the teeth (22) and the winding wheel (61) when the outer ring (3) is stationary, the tension of the winding spring (62) allows the outer ring (3) to rotate in the same direction as the rotary cage governor (200) when released, and the locking teeth (71) are configured to contact the locking element (21) or the locking pawl stone.

5. The movement (1000) according to claims 2 and 1, wherein the rotary cage governor (200) comprises a second auxiliary planetary gear set in which the fixed wheel (1) is a solar ring train, the outer ring (3) is a planetary carrier, and the lock pinion (70) is a planetary gear, and the second auxiliary planetary gear set is superimposed on the first planetary gear set by adding the planetary carrier consisting of the outer ring (3).

6. The movement (1000) according to claim 1, characterized in that the rotary cage governor (200) is a jumping second flying tourbillon, and its jump frequency fj is determined by the formula fj = ((N40 * N7) / N70) * (f0 / N4), where N40 is the number of teeth of the escapement pinion (40), N7 is the number of teeth of the lock wheel (7), N70 is the number of teeth of the lock pinion (70), f0 is the frequency of the oscillator consisting of the spring balance wheel, N4 is the number of teeth of the escapement wheel (4), and furthermore the ratio f0 / (0.5 * fj) is an integer.

7. The movement (1000) according to claim 1, characterized in that the locking element (21) or the locking pallet stone has a support surface which can engage with each of the locking teeth (71) and extends substantially tangentially with respect to the bed (111) into which the locking element (21) is inserted and fixed in a plane perpendicular to the pivot axis of the cage (2), and the moment of jumping can be set by setting a relative tangential position between the locking element (21) and each of the locking teeth (71) that corresponds to the locked position of the locking teeth (71).

8. The movement (1000) according to claim 7, characterized in that the lock position can be set to the lock position of the ring (3) by moving the escapement element (5) a predetermined number of escapement steps N and rotating the planetary lock wheel (7) by an angle corresponding to a predetermined number of teeth X of the planetary lock wheel (7).

9. The movement (1000) according to claim 8, wherein each of the locking teeth (71) is configured to take an integer number of discrete locking positions in steps along the depth of the locking element (21), and each of the locking positions is reachable according to a table that shows the number of teeth X of the planetary locking wheel (7) to be rotated clockwise and the number of additional escapement steps N to be performed with respect to the escapement element (5) or the anchor.

10. The movement (1000) according to claim 7, characterized in that each of the locking teeth (71) is configured to occupy a locked position with respect to the locking element (21) at a predetermined angular interval with respect to the pivot axis of the cage (2) corresponding to an integer degree.

11. The movement (1000) according to claim 7, characterized in that the escapement pinion (40) and the lock pinion (70) mesh with the same stationary wheel (1), the position of the lock element (21) is fixed with respect to the pivot axis of the escapement wheel (4), and the locking depth of the teeth of the planetary lock wheel (7) with respect to the lock element (21) is defined by the respective angular directions of the teeth of the escapement pinion (40) and the lock pinion (70).

12. The movement (1000) according to claim 7, characterized in that the frequency f0 of the oscillator and the integer number of teeth of various pinions and wheels of the mechanism, namely the number of teeth N4 of the escapement wheel (4), the number of teeth N40 of the escapement pinion (40), the number of teeth N1 of the fixed wheel (1), the number of teeth N70 of the lock pinion (70), and the number of teeth N7 of the lock wheel (7), are such that the desired jump frequency fj satisfies the first condition fj = ((N40 * N7) / N70) * (f0 / N4) and the second condition that the ratio f0 / (0.5 * fj) is an integer.

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

14. The movement (1000) according to claim 12, characterized in that fj = 2 Hz, f0 = 4 Hz, N4 = 20, N40 = 10, N70 = 16, and N7 = 16 for one jump every 0.5 seconds.

15. A clock (2000) comprising at least one movement (1000) as described in claim 1.

16. A watch assembly comprising at least one watch according to claim 15 and / or a movement (1000) according to claim 1, wherein the watch assembly comprises, for each type of movement (1000) or caliber, a table for use by a watchmaker in the factory or after-sales service department, wherein the table indicates the number of teeth X of the planetary lock wheel (7) to be rotated clockwise to reach a predetermined locked position of the lock teeth (71) on the lock element (21), and the number of additional escapement steps N to be performed with respect to the escapement element (5).

17. A clock assembly according to claim 16, comprising the movement (1000) according to claim 13, wherein the parameters for the number of teeth X of the planetary lock wheel (7) to be rotated clockwise and the number of additional escape steps N to be performed on the escape element (5) are defined as follows: when a 1° central angle on the lock element (21) is divided into seven lock positions of the lock teeth (71) referred to as sector number 1 to sector number 7, then for sector number 1, lock depth "1", there are 9 escape steps; for the number of teeth of the planetary lock wheel 7, there are no teeth; for sector number 2, lock depth " In "2", the clock assembly includes two escapement steps, one tooth on planetary lock wheel 7, sector number 3, and lock depth "3", seven escapement steps, four teeth on planetary lock wheel 7, sector number 4, and lock depth "4", no escapement steps, no teeth on planetary lock wheel 7, sector number 5, and lock depth "5", five escapement steps, three teeth on planetary lock wheel 7, sector number 6, and lock depth "6", ten escapement steps, one tooth on planetary lock wheel 7, sector number 7, and lock depth "7", three escapement steps, and two teeth on planetary lock wheel 7.

18. A method for adjusting the accuracy of the relative position between the planetary locking wheel (7) and the locking element (21) in the clock assembly according to claim 16, wherein the method is: On the other hand, a first step (A) is to randomly rivet the escapement wheel (4) to the escapement pinion (40) and randomly rivet the planetary lock wheel (7) to the lock pinion (70), wherein the position of the lock element (21) is set to within ±1° from its exact theoretical position and fixed to the cage (2), The mechanism is assembled without the balance wheel of the spring-type balance wheel or the upper cage included in the rotary cage governor (200), the escapement wheel (4) and the planetary lock wheel (7) are randomly arranged in the second jump mechanism, and the mainspring of the movement is wound, the second step (B) comprising moving the escapement element (5) back and forth by hand to advance the cage (2) in 1° increments until the locking tooth (71) reaches the distal end of the locking element (21) and the locking tooth (71) disengages, releasing the second jump mechanism, A third step (C) to confirm that the tip of the locking tooth (71) is in one of the positions marked on the locking element (21), wherein an angular deviation of 1° on the locking element (21) is divided into an integer relative position of the locking tooth (71) with respect to the locking element (21), and this position is identified. A fourth step (D) involves temporarily locking the ring (3), removing the planetary lock wheel (7), rotating the cage (2) by manually moving the escapement element (5) back and forth the required number of steps, and then setting the adjustment by repositioning the planetary lock wheel (7) according to the instruction sheet. The locking depth of the locking teeth (71) is checked, and if the desired locking depth has not been reached, the third step (C) and the fourth step (D) are repeated until the desired locking depth is reached in the fifth step (E). A method that includes this.

19. The adjustment method according to claim 18, further comprising a sixth step (F) of setting the pre-tension of the winding spring (62) on the winding wheel (61) to the minimum level required to obtain accurate second jumps.

20. The adjustment method according to claim 19, wherein the sixth step (F) includes reinstalling the winding wheel (61) such that another pair of teeth are in contact with the teeth (22) on the cage (2).

21. The adjustment method according to claim 18, wherein in the third step (C), the relative position between the locking tooth (71) and the locking element (21) is adjusted by appropriate settings.

22. The adjustment method according to claim 18, wherein, in order to adjust the relative position of the second hand (101) and the tourbillon cage (2), the support (10) of the second hand (101) is adjusted by sliding it along a certain radius before screwing it to the ring (3) so that it precisely aligns with the column (29) included in the rotating cage governor (200) when the second jump occurs.

23. The adjustment method according to claim 18, wherein, in order to ensure accurate alignment of the dial with respect to the second scale, the fixing wheel (1) is set in the rotational direction relative to the second dial by an oval hole around its fixing screw and a blank that allows for fine adjustment of its position by moving an eccentric tool (300).

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