Watch with mechanical movement comprising a rotating frame governor
By employing a rotating frame regulator and an improved locking element design in a mechanical watch, the problem of the jumping seconds mechanism's inability to achieve accurate jumping under a high-frequency oscillator has been solved, enabling the watch to achieve accurate timekeeping and an easy-to-read second hand display.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- GLASHUTTER UHRENBETRIEB GMBH
- Filing Date
- 2025-12-18
- Publication Date
- 2026-06-23
AI Technical Summary
In existing mechanical watches, the jumping seconds mechanism is difficult to achieve precise jumping and the timing of the jump is difficult to adjust, especially with high-frequency oscillators, it is difficult to achieve easily readable second and half-second hand jumps.
It employs a rotating frame governor, especially a tourbillon governor, located downstream of the escapement. Through an improved design of the lower frame and locking elements, combined with a planetary locking wheel and locking stop, it achieves the jumping seconds function. The accuracy of the jumping seconds is ensured by precisely adjusting the relative position of the planetary locking wheel and the locking elements.
It achieves precise jumping seconds display under high-frequency oscillator, simplifies the assembly and adjustment process of the jumping seconds mechanism, and improves the watch's timing accuracy and reliability.
Smart Images
Figure CN122260748A_ABST
Abstract
Description
Technical Field
[0001] The present invention relates to a mechanical watch movement comprising at least one rotating frame type 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 at least one such movement.
[0004] The present invention also relates to an adjustment method for precisely adjusting the relative position of the planetary locking wheel and the locking stop, which are unique to the present invention.
[0005] This invention relates to the field of mechanical watches, which include a tourbillon regulator, and more specifically a flying tourbillon. Background Technology
[0006] This invention relates to a watch comprising a mechanical movement with a rotating frame regulator. A "rotating frame regulator" refers to a system that allows the balance wheel to rotate about an axis; tourbillons and Bonikksen carousels fall into this category. More specifically, but not limitingly, the invention can be applied to rotating frame regulators that function as tourbillons (especially flying tourbillons), such regulators including a jumping seconds display mechanism.
[0007] The proposed mechanism can enable jumping seconds display on mechanical watches equipped with rotating frame regulators (especially flying tourbillons).
[0008] The "jumping seconds" mechanism has been known for centuries, and its design purpose is to facilitate the reading of the precise seconds displayed by the clock mechanism.
[0009] Fixed precision mechanical timekeeping devices typically employ a "seconds pendulum" with an oscillation frequency of 0.5 Hz (i.e., an oscillation period of 2 seconds, or a period of 1 second for each half oscillation / alternation). Most standard escapements used in precision pendulum clocks (such as the Graham / Riefler / Strasser escapement) apply one impact to the oscillator with each half oscillation, meaning two impacts per oscillation (equivalent to 3600 vibrations per hour). The natural result is that the second hand jumps in 1-second increments. Until the mid-20th century, clocks with seconds pendulums served as standard astronomical timepieces for determining celestial transits.
[0010] The need for portable precision timekeeping instruments in the maritime field (see the Queen Anne Longitude Act of 1714) spurred the development of marine chronometers, which operated at an oscillation frequency of 2 Hz (or 14,400 vibrations per hour). These marine chronometers, combined with an escapement mechanism, drove the second hand to jump at 0.5-second intervals. This escapement mechanism applied an impact to the balance wheel only once every two and a half oscillations, i.e., an impact was applied with each oscillation.
[0011] However, pocket watches and wristwatches, which are much smaller than marine chronometers, require higher frequency oscillators to achieve similar accuracy (Q factor; the oscillation frequency commonly used in watch movements today is between 2.5 and 5 Hz), which results in smaller intervals for the second hand (for a standard anchor escapement: 5 times per second at 2.5 Hz and 10 times per second at 5 Hz).
[0012] Therefore, it is necessary to find other methods to achieve more readable second and half-second hand transitions.
[0013] In the mid-18th century, watchmaker Jean Romilly designed the first wristwatch with a stop-seconds hand, and the balance wheel oscillation frequency was chosen to produce jumping seconds.
[0014] Around 1776, Jean Moïse Pouzait invented a seconds mechanism that could be independently started and stopped (“independent jumping seconds”). This mechanism required a secondary gear train, whose “lever” engaged with a “star wheel” on the escapement wheel axis, and was subsequently released, causing it to rotate rapidly once per second. This mechanism is described in OMEGA’s patent document CH256885A. In this watch mechanism, the seconds hand jumps in 1-second increments (equipped with a higher-frequency oscillator and a standard escapement).
[0015] Subsequent designs eliminated most of the components of the secondary gear train by introducing an intermediate spring mechanism that periodically winds the main gear train.
[0016] With the advent of modern chronograph mechanisms featuring resettable seconds hands, these mechanisms were gradually forgotten; only in the 1950s and 60s did perpetual jumping seconds mechanisms experience a brief revival, such as the Omega Cal. 372 “Synchrobeat” movement.
[0017] In recent years, high-end watch enthusiasts have rediscovered interest in jumping seconds mechanisms, with many examples integrating a "constant-force winding mechanism" to drive the jumping seconds hand at 1-second loading intervals. However, this mechanism is located in the energy transfer path between the mainspring barrel and the escapement, requiring corresponding design considerations for the dimensions of each component. Furthermore, existing mechanisms struggle (if not entirely impossible) to precisely adjust the timing of the jump. Summary of the Invention
[0018] The present invention aims to manufacture a new type of watch movement, which includes a rotating frame type regulator, especially a tourbillon regulator, specifically a jumping seconds flying tourbillon regulator, wherein the mechanism is located downstream of the escapement mechanism and the jumping position can be set in the factory.
[0019] Therefore, the present invention relates to a mechanical watch movement comprising at least one rotating frame regulator as described in 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 such movement.
[0022] The present invention also relates to an adjustment method for precisely adjusting the relative position of the planetary locking wheel and the locking element, which are unique to the present invention. Attached Figure Description
[0023] The objects, advantages, and features of the present invention will become clearer from the following detailed description with reference to the accompanying drawings, in which:
[0024] - Figure 1 The diagram shows a schematic perspective view of a rotating frame governor according to a specific, non-limiting variant of the invention, in a particular, variant of a skip-seconds flying tourbillon. The rotating frame governor includes a modified lower frame with two outwardly projecting engagement teeth supported by a generally annular body, and a locking stop supported by an arm of the lower frame. The tourbillon also includes a loading wheel associated with a loading spring, the two engagement teeth arranged to engage with the loading wheel. The loading wheel is supported by a bearing ring, which also supports a planetary locking wheel. The locking wheel includes locking teeth arranged to abut against the locking stop in a locked position.
[0025] - Figure 2 It shows Figure 1 A schematic top view of the lower part of the tourbillon, viewed from the side visible to the user and opposite to the mainplate of the movement including the tourbillon. The upper frame, balance wheel assembly, and bridge for hooking the balance spring are not shown. The escape wheel is seen at 6 o'clock, the escape fork at 5 o'clock, and the loading wheel, loading spring, and engagement tooth at 10 o'clock. One arm of the lower frame at 4 o'clock carries the locking stop, and the locking wheel is at 3 o'clock. A locking tooth can be seen resting against the support surface of the locking element (here, not limited to the locking stop / locking jewel), which extends approximately tangentially.
[0026] - Figure 3 It shows Figure 1 A schematic exploded perspective view of all the components of the tourbillon;
[0027] - Figure 4 It shows Figure 1 A schematic top view of all the jumping seconds adjustment components of the tourbillon (with) Figure 2 (Similar): The lower frame is stacked on the tourbillon fixed wheel, the escapement is on the left, the locking element and locking wheel are located at the 6 o'clock position; the locking wheel includes a pinion that meshes with the fixed wheel; the meshing teeth can be seen at the 1 o'clock position;
[0028] - Figure 5 A partial schematic diagram of the end of the locking element in a particular configuration is shown (with...). Figure 4 (Similar); In this particular configuration, the support surface of the locking element covers a 1° central angle starting from the pivot axis of the frame; This central angle is divided into an integer number of segments, 7 segments in this example, corresponding to an equal number of potential locking positions at the distal end of the locking teeth on the locking wheel;
[0029] - Figure 6 A schematic top view showing the engagement details between the locking element and the locking teeth (and) Figure 5 (Similarly): On the left, although the relative orientation of the locking wheel with respect to the virtual line connecting its own center and the center of the tourbillon's fixed wheel remains unchanged (the locking wheel is offset by exactly one tooth clockwise), the locking teeth on the locking pinion are tilted at an angle relative to their original orientation. This angle is the difference between 360° divided by the quotients of the number of teeth on the planetary locking wheel and the number of teeth on the locking pinion. In the specific example shown, this difference is 20.5714° (between the dashed and solid lines indicating the tangent to the fixed wheel). On the right, it is shown how the locking pinion rolls along the fixed wheel (on its teeth) to restore the correct meshing between its own teeth and the teeth of the fixed wheel; for the specific gear ratio shown, a 20.5714° rotation of the locking pinion around its own axis corresponds to a 1.71429° pivot around the central axis of the tourbillon.
[0030] - Figure 7 It shows Figure 2 A detailed partial schematic diagram showing the second hand position adjustment device;
[0031] - Figure 8 It shows Figure 7 A schematic exploded perspective view showing the details;
[0032] - Figure 9 A schematic perspective view showing the adjustment of the fixed wheel's angular position relative to the stopwatch dial using an eccentric tool (with...) Figure 1 similar);
[0033] - Figure 10 It shows Figure 9 Top view;
[0034] - Figure 11 A schematic front view of a watch is shown, which includes a movement fitted with a rotating frame regulator (especially a tourbillon) according to the invention;
[0035] - Figure 12 This is a flowchart illustrating the steps of an adjustment method for precisely adjusting the relative position of a planetary locking wheel and a locking element. Detailed Implementation
[0036] The present invention relates to a mechanical watch movement 1000, which includes a mechanism that can display a jumping seconds function on a mechanical watch 2000 equipped with a rotating frame type regulator 200 (especially a flying tourbillon).
[0037] The mechanism presented and illustrated is based on the flying tourbillon with a balance wheel stop device described in document CH717982, which grants patent rights to GLASHUETTE ORIGINAL and is incorporated herein by reference.
[0038] The mechanical watch movement 1000 includes at least one rotating frame-type regulator 200, which includes a fixed wheel 1, a frame (in a particular preferred variant shown in the figures, the frame includes at least a lower frame 2 and an upper frame 11), an escapement element 5 (or more specifically, an escapement fork in the illustrated example), and an escape wheel 4; the frame carries a balance spring balance wheel mechanism including a balance wheel 60 and a mainspring 90; the escape pinion 40 in the escape wheel 4 meshes directly or indirectly with the fixed wheel 1, more specifically, in the particular preferred variant shown in the figures, with direct meshing. In other variants, an intermediate moving element is provided between the escape pinion 40 and the fixed wheel 1, for example, in a Bonniksen carousel mechanism, the escape pinion is driven by a moving wheel; or in a 5-minute tourbillon, an intermediate moving element is inserted between the escape wheel and the fixed wheel.
[0039] The frame also supports the locking element 21 and a bearing fastened to the movement plate 100, which is coaxial with the frame.
[0040] According to the present invention, the rotary frame speed controller 200 includes a locking wheel 7 with locking teeth 71, which pivots on a bearing race 3. These locking teeth 71 can be stopped by a locking element 21, and their resting position can be set at the factory. The locking wheel 7 is arranged to release or lock the movement of the race 3 and carries a locking pinion 70 that is always engaged with the fixed wheel 1. The race 3 is connected to the rotary frame speed controller 200 via an intermediate loading system that winds a loading spring 62 via the movement of the rotary frame speed controller 200, such that the loading spring 62, during release, maintains the movement of the race 3 in the same direction of rotation as the rotary frame speed controller 200.
[0041] It should be understood that the nature of the escapement element 5 depends on the type of escapement mechanism employed, as the present invention can be used with any type of escapement mechanism, such as an anchor escapement, a pawl escapement, a double-lobe escapement, a cylindrical escapement, a pallet escapement, a Graham escapement, or other types. The invention is described in a non-limiting manner using an anchor escapement as a specific example, and the escapement element 5 is more specifically an escapement fork, but is not limited thereto.
[0042] According to a specific variant of the invention shown in the accompanying drawings, the lower frame 2 carries meshing teeth 22 and locking element 21 (or a locking stop as shown in the drawings). The rotating frame type speed controller 200 also includes a loading wheel 61 and a locking wheel 7. The loading wheel 61 is attached to a loading spring 62 and pivots on a bearing race 3, which is fastened (through its inner ring) to the movement plate of the movement 1000. The locking wheel 7 has locking teeth 71, which can be stopped by the locking element 21, and its locked / reset position can be set in the factory. This assembly constitutes a first planetary gear system, in which the lower frame 2 is the sun gear, the bearing race 3 is the planet carrier, and the loading wheel 61 is the first planet gear in the planet carrier. The locking wheel 7 is arranged to release or lock the movement of the race 3 and carries a locking pinion 70 that is always meshed with the fixed wheel 1.
[0043] The locking element 21 can take different forms and can be fastened to different parts of the mechanism in different ways; for example, a pin extending from the upper frame 11 of the oscillating system can also perform the function described below.
[0044] The loading system described above is a particularly compact variant in which a planetary gear train is provided between the meshing teeth 22 on the lower frame 2 of the tourbillon and the loading wheel 61 with a loading spring 62 in the form of a hairspring; however, a leaf spring, for example, is also suitable, with one end fastened to the frame of the tourbillon and the other end fastened to the planet carrier (ring 3).
[0045] Figures 1 to 3 Perspective view, top view and exploded view of such a rotating frame speed controller 200 according to the present invention are shown respectively.
[0046] More specifically, the rotating frame regulator 200 includes a pivoting frame comprising a lower frame 2 and an upper frame 11, which are non-limitingly connected by three supports 29. The frame carries a balance spring assembly including a balance wheel 60 and a mainspring 90 attached to an outer stud 91 on a bridge plate. The frame is fastened to the shaft of a second pinion 9, which is arranged to drive the train of hands.
[0047] The frame supports an escapement mechanism including an escape wheel 4 with N4 teeth, which is arranged to engage with an escapement element 5. In this example, the escapement element 5 is a Swiss-anchored escapement fork with two pallet forks 51 and 52, but is not limited thereto. Both the escape wheel 4 and the escapement element 5 are pivotally supported in a clamping plate 50 at the top.
[0048] The tourbillon includes a fixed wheel 1 fastened to the main plate, the fixed wheel 1 including an external gear ring with N1 teeth.
[0049] The escape wheel 4 is attached to the escape pinion 40 with N40 teeth, which meshes with the gear ring of the fixed wheel 1.
[0050] According to the present invention, the lower frame 2 of the rotary frame speed regulator 200 is improved by adding two outwardly extending meshing teeth 22 and a locking element 21 (or locking stop), which is made of ruby and is carried in the receiving groove 111 by the arm 110 of the lower frame 2.
[0051] More specifically, the tourbillon includes a loading wheel 61 supported by an upper pivot 610 on the first bridge plate 66 and associated with a loading spring 62. More specifically, the outer end 622 of the loading spring 62 is attached to the first bridge plate 66, and the inner end 621 is attached to the loading wheel 61.
[0052] Two meshing teeth 22 are arranged to mesh with the loading wheel 61.
[0053] More specifically, the tourbillon also includes a planetary locking wheel 7, which includes N7 locking teeth 71 and is supported by a support 75 and a second bridge plate 76, and is assembled to pivot between the two. A locking element 21 is arranged to engage in contact with one of the locking teeth 71 on the planetary locking wheel 7.
[0054] The loading wheel 61 and the planetary locking wheel 7 are both mounted to pivot on the outer ring 3 of the ball bearing and spaced apart from each other. The ball bearing is coaxially fastened below the lower frame 2 of the rotating frame speed controller 200.
[0055] When the ball bearing 3 is stationary, the loading spring 62 is rewinded by the moving tourbillon through the meshing of the two meshing teeth 22 of the tourbillon lower frame 2 with the loading wheel 61.
[0056] Once the outer ring 3 of the ball bearing can move freely, the tension of the loading spring 62 will cause the entire outer ring 3 to rotate in the same direction as the tourbillon: this assembly constitutes the first planetary gear system, in which the tourbillon is the sun gear, the outer ring 3 of the ball bearing is the planet carrier, and the loading wheel 61 is the planet gear.
[0057] The planetary locking wheel 7 is another planetary gear mounted on the outer ring of the bearing. The free movement of the outer ring 3 of the ball bearing is thus locked by the planetary locking wheel 7, which includes a locking pinion 70 with N70 teeth that meshes with the fixed wheel 1 of the tourbillon, while the teeth of the fixed wheel 1 abut against the locking element 21 of the lower frame 2 of the tourbillon (therefore, this is a secondary planetary gear system).
[0058] Therefore, the secondary planetary gear system, which uses the fixed wheel 1 on the rotating frame speed regulator 200 as the sun gear and the locking pinion 70 on the planetary locking wheel 7 as the planetary gear, is superimposed on the first planetary gear system for the loading wheel 61. The two systems share the same planet carrier, namely the outer ring 3 of the ball bearing.
[0059] The agency operates in the order described below.
[0060] The preload of the loading spring 62 in the loading 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 the locking element 21 pressed into the lower frame 2 of the rotating frame speed controller 200.
[0061] During the rotation of the tourbillon (more specifically, in the non-limiting variant disclosed herein and shown in the accompanying drawings, its period is 1 minute), the tip of the locking element 21 (in particular, the stop as seen in the accompanying drawings) moves to the tip of the locking tooth 71, and the two meshing teeth 22 of the tourbillon lower frame 2 continue to wind the loading wheel 61.
[0062] When the tourbillon rotates about 6° (after 1 second, or 1 / 60 of a minute, i.e., 1 / 60 of a revolution, corresponding to one revolution per minute of the tourbillon), the locking tooth 71 disengages from the locking element 21, at which point the planetary locking wheel 7 and the external ball bearing assembly can rotate freely around their respective axes.
[0063] The rotation is driven by the planetary loading wheel 61 until the next locking tooth 71 of the planetary locking wheel 7 contacts the locking element 21, at which point the rotation stops and the cycle restarts.
[0064] In the proposed non-limiting scheme of the mechanism, the balance wheel of the tourbillon oscillates at a frequency of 3 Hz (i.e., 21,600 vibrations per hour), the escape wheel 4 has 15 teeth, its escape 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.
[0065] Therefore, the tourbillon frame itself jumps forward 6 times per second (i.e., the escape wheel 4 rotates 3 teeth), and each jump rotates 1°; therefore, the escape wheel 4 rotates once around its own axis every 5 seconds (5 seconds = the escape wheel 4 rotates 15 teeth, i.e., the escape wheel rotates 3 teeth per second); the planetary locking wheel 7 has a similar operation because the transmission ratio between its locking pinion 70 and the tourbillon fixed wheel 1 is the same as the transmission ratio of the escape wheel 4.
[0066] For the planetary locking wheel 7, which includes 5 teeth, the ball bearings jump in 1-second increments.
[0067] Therefore, the second hands 10 and 101, which are fastened to the outer ring 3 of the ball bearing, indicate the jumping seconds.
[0068] Given that each of the pinions, namely the escape pinion 40 on the escape wheel 4 and the locking pinion 70 on the planetary locking wheel 7, meshes with the same fixed wheel 1 on the tourbillon, and the position of the locking element 21 remains fixed relative to the axis of the escape wheel 4, the angular orientation of the teeth of these wheels and pinions determines the locking depth of the teeth of the planetary locking wheel 7 on the locking element 21.
[0069] Considering the unavoidable tolerances, the required ease of assembly, and after-sales limitations, neither setting the position of the stop block 21 in the lower frame of the tourbillon nor adjusting the orientation of the individual wheels and pinions on the escape wheel 4 and the planetary locking wheel 7 to achieve a locking depth of approximately 5.5° after the second jump seems very practical.
[0070] Accordingly, the present invention proposes the following method steps for precisely adjusting the relative position of the planetary locking wheel 7 and the locking element 21 on the lower frame 2 of the tourbillon, that is, adjusting the locking depth of the locking teeth 71 of the planetary locking wheel 7 on the locking element 21.
[0071] In the first step A, the escape wheel 4 and the planetary locking wheel 7 are randomly riveted to their respective pinions (escape pinion 40 and locking pinion 70), regardless of their angular orientation; the position of the locking element 21 is set within ±1° of its theoretically correct position (using tools such as an optical comparator or gauge), and the locking element 21 or the locking stop is fastened to the lower frame 2 of the tourbillon.
[0072] In step B, the mechanism is assembled (without installing the balance wheel 60 or the tourbillon upper frame 11), the escape wheel 4 of the jumping seconds mechanism and the planetary locking wheel 7 are randomly positioned, and the mainspring of the movement is wound.
[0073] By manually moving the escapement element 5 back and forth, the tourbillon frame is advanced (in 1° increments) until the locking tooth 71 on the planetary locking wheel 7 reaches the distal end of the locking element 21, as... Figure 4 As shown, at this point, locking tooth 71 is about to disengage and thus release the skipping second mechanism.
[0074] In step C, the position of the tip of the locking tooth 71 on the planetary locking wheel 7 is checked to determine whether it is located at one of the multiple positions marked on the locking stop, especially Figure 5 One of the positions numbered "1" to "7" is used; among them, seven relative positions of the locking tooth 71 relative to the locking element 21 are divided within an angular interval of 1°, and these positions are identified. Advantageously, the relative position between the locking tooth 71 and the locking element 21 can be adjusted through adaptation.
[0075] Step four, D, focuses on this adjustment operation. When the movement of the outer ring of the ball bearing is temporarily locked (e.g., by wedging a piece of paper between the movement plate and the ball bearing), the planetary locking wheel 7 can be disengaged and repositioned. This repositioning is achieved by manually moving the escapement element 5 back and forth the required number of steps according to the instruction table or list shown below, so that the rotating frame regulator 200 rotates accordingly. For example, if the locking depth is "5": disengage the planetary locking wheel 7, rotate the tourbillon through 5 additional escapement steps, and reinstall the planetary locking wheel 7, which has now rotated clockwise through the angle corresponding to three teeth of the planetary locking wheel 7, positioning it at the first angle on the tourbillon's locking element 21.
[0076] Based on the calculation method described below, the above list is provided herein. This list is non-limiting and corresponds to the mechanisms shown in the accompanying drawings, wherein each moving part has a specific number of teeth, a specific oscillation frequency f0 and a jump frequency fj, and corresponds to the configuration of its escapement and locking wheel:
[0077] Section -1, lock depth "1": 9 escapement steps, planetary lock wheel 7 revolutions 0 teeth;
[0078] -Section 2, lock depth "2": 2 escapement steps, planetary locking wheel 7 turns 1 tooth;
[0079] Section -3, lock depth "3": 7 escapement steps, planetary lock wheel rotates 7 times through 4 teeth;
[0080] -Section 4, lock depth "4": 0 escapement steps, planetary lock wheel 7 turns 0 teeth;
[0081] -Section 5, lock depth "5": 5 escapement steps, planetary lock wheel 7 turns 3 teeth;
[0082] -Section 6, lock depth "6": 10 escapement steps, planetary lock wheel rotates 7 times to 1 tooth;
[0083] Section -7, lock depth "7": 3 escapement steps, planetary lock wheel rotates 7 times.
[0084] Step E is used to check whether the locking teeth 71 of the planetary locking wheel 7 have the desired or even ideal locking depth (segment 4) on the tourbillon locking element 21. If not, repeat steps C and D until the desired locking depth is achieved.
[0085] Step F involves setting the preload of the loading spring 62 on the loading wheel 61 to the minimum level required to achieve a net jump. In fact, excessive preload will reduce the amplitude of the balance wheel 60. Therefore, the loading wheel 61 can be reinstalled so that its other pair of teeth engages with the meshing teeth 22 on the lower frame 2 of the tourbillon, which is unique to this invention.
[0086] This method of fine-tuning the locking depth is based on the principle of vernier calipers: with the tourbillon position fixed and one tooth of the planetary locking wheel 7 in contact with the locking element 21, the planetary locking wheel 7 is rotated clockwise around its own axis by one tooth. The rotation angle is the quotient of 360° divided by the number of teeth N7 of the locking wheel 7 (5 teeth in this example), that is, 360° / 5=72°.
[0087] The locking pinion 70 on the planetary locking wheel 7 has N70 = 7 teeth.
[0088] Although the relative orientation of locking wheel 7 with respect to the imaginary line connecting its own center and the center of the fixed wheel 1 of the tourbillon remains unchanged (locking wheel 7 is offset by exactly one tooth clockwise), the locking tooth 71 on the locking pinion 70 of locking wheel 7 is tilted at a certain angle relative to its initial orientation. This angle is the difference between 360° divided by the quotients obtained by the number of teeth N7 of planetary locking wheel 7 (5 teeth in this example) and the number of teeth N70 of locking pinion 70 of locking wheel 7 (7 teeth in this example). This difference is (360° / 5 - 360° / 7), i.e., (72° - 51.4286°) = 144 / 7° = 20.5714° (see...). Figure 6 (Left side)
[0089] Therefore, the locking pinion 70 of the planetary locking wheel 7 must move along the tourbillon fixed wheel 1 in order to restore the correct meshing between the teeth of the locking pinion 70 and the teeth of the fixed wheel (see...). Figure 6 (Right side)
[0090] With a transmission ratio of 7 / 84=1 / 12 between the fixed wheel 1 of the tourbillon (including N1=84 teeth) and the locking pinion 70 of the planetary locking wheel 7 (including N70=7 teeth), the 20.5714° rotation of the locking pinion 70 around its own axis corresponds to a pivoting rotation around the central axis of the tourbillon of (20.5714°*1 / 12)=144 / 7°*1 / 12=12 / 7°=1.71429°. Figure 6 As shown on the right.
[0091] In summary, by removing the planetary locking wheel 7, rotating it clockwise by one tooth, and then reinstalling it, the tip of the locking tooth 71 of the locking wheel 7 will be aligned with the locking element 21. Figure 4 , 5 The contact point between the two (represented by the ruby stop in section 6) moves clockwise by an angle of 1.71429° = (360° / 5 - 360° / 7) * 7 / 84 (thus falling deeper onto the locking element 21). If the planetary locking wheel 7 is rotated two teeth instead of one before installation, the corresponding tooth on the locking wheel will fall onto the locking element 21 at an angle of 2 * 1.71429° = 3.42857°. Accordingly, the locking depth Δ / the angle of rotation of the locking wheel around the fixed second wheel will theoretically change according to the number of teeth X rotated by the planetary locking wheel 7 before reinsertion, where Δ = X * 1.71429° = X * 12 / 7°:
[0092] X=1, Δ=1.71429°=12 / 7°;
[0093] X=2, Δ=3.42857°;
[0094] X=3, Δ=5.14286°;
[0095] X=4, Δ=6.85714°;
[0096] X=5, Δ=8.57143°;
[0097] X=6, Δ=10.28571°;
[0098] X=7, Δ=12°.
[0099] However, when the escapement is released once, the locking element 21 will then move 360° / (84 / 7*15*2)=1° clockwise (because the fixed wheel 1 or second wheel of the tourbillon has 84 teeth, the escape pinion 40 of the escape wheel 4 has 7 teeth, and the escape wheel 4 has 15 teeth; due to the use of the Swiss anchor escapement 5, the escape wheel 4 will rotate half a tooth each time the escapement is released, in which each complete oscillation applies 2 impacts), so the coefficient is 2.
[0100] As a result, for each step of the escapement mechanism, the locking depth Δ of the locking tooth 71 of the planetary locking wheel 7 on the stop 21 of the tourbillon frame 2 can be reduced by 1°.
[0101] To modify the lock depth by only a fraction of a degree, the escapement can be released 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 after modification with the corresponding number of N additional escapement steps:
[0102] X=1, Δ=1.71429°; N=1, ΔM=1.71429° mod1°=0.71429°=5 / 7°;
[0103] X=2, Δ=3.42857°; N=3, ΔM=3.42857° mod1°=0.342857°=3 / 7°;
[0104] X=3, Δ=5.14286°; N=5, ΔM=5.14286° mod1°=0.14286°=1 / 7°;
[0105] X=4, Δ=6.85714°; N=6, ΔM=6.85714° mod1°=0.85714°=6 / 7°;
[0106] X=5, Δ=8.57143°; N=8, ΔM=8.57143° mod1°=0.57143°=4 / 7°;
[0107] X=6, Δ=10.28571°; N=10, ΔM=10.28571° mod1°=0.285714°=2 / 7°;
[0108] X=7, Δ=12°; N=12, ΔM=12°mod1°=0°=0 / 7°.
[0109] Or N=1=1.71429°div1°, N=3=3.42857°div1°, and so on.
[0110] It can also be expressed as:
[0111] N=1=12 / 7°div1°
[0112] N=3=24 / 7°div1°
[0113] N=5=36 / 7°div1°
[0114] N=6=48 / 7°div1°
[0115] N=8=60 / 7°div1°
[0116] N=10=72 / 7°div1°
[0117] N=12=84 / 7°div1°
[0118] Or the following general formula:
[0119] Δ=X*12 / 7°
[0120] N=Δdiv1°
[0121] ΔM = Δmod1°
[0122] Therefore, by appropriately combining "rotating the planetary locking wheel 7 before repositioning" with "releasing an appropriate number of escapement steps," the locking depth can be modified in 1 / 7° steps. This is because the release of the jumping seconds mechanism occurs within one escapement step, and the tourbillon frame and the locking element 21 fastened thereto rotate 1° accordingly. Thus, during the last half of the oscillation before the jumping seconds release, the locking teeth 71 of the planetary locking wheel 7 can be in the position... Figure 5 One of the seven positions shown.
[0123] The middle position "4" is preferred because it provides sufficient safety margin to prevent premature or late release in the event of concentricity deviation, gear ring accuracy error, or any geometric defects.
[0124] However, depending on the random orientation of the components during assembly, the watchmaker may encounter other positions (1-3 or 5-7). By removing the planetary locking wheel 7 again, advancing the escapement a specified number of steps, and re-inserting the planetary locking wheel 7, which has already rotated the specified number of teeth, it should be possible to reach position "4". For example, starting from position "5", this can be achieved by generating a 1 / 7° rotation, which can be achieved by repositioning N=5 supplementary escapement steps and the planetary locking wheel 7, which has already rotated X=3 teeth (as shown in the list above).
[0125] This leads to the following correspondence between segments 1-7 and the list above, where the last value Y represents the correspondence with the reference segment (i.e., Figure 5(The required location in the text):
[0126] X=1, Δ=1.71429°; N=1, ΔM=1.71429° mod1°=0.71429°=5 / 7°; Y=2*;
[0127] X=2, Δ=3.42857°; N=3, ΔM=3.42857° mod1°=0.342857°=3 / 7°; Y=7;
[0128] X=3, Δ=5.14286°; N=5, ΔM=5.14286° mod1°=0.14286°=1 / 7°; Y=5;
[0129] X=4, Δ=6.85714°; N=6, ΔM=6.85714° mod1°=0.85714°=6 / 7°; Y=3*;
[0130] X=5, Δ=8.57143°; N=8, ΔM=8.57143° mod1°=0.57143°=4 / 7°; Y=1*;
[0131] X=6, Δ=10.28571°; N=10, ΔM=10.28571° mod1°=0.285714°=2 / 7°; Y=6;
[0132] X=7, Δ=12°; N=12, ΔM=12°mod1°=0°=0 / 7°; Y=(4).
[0133] However, for the Y=1-3 segment (marked with *: 1*, 2*, 3*), following the above list would result in a jump trigger delay of two escapement stages, so an additional escapement stage must be considered here. Furthermore, the planetary locking wheel 7 only has N7=5 teeth; therefore, rotating 5 teeth corresponds to the starting position, thus omitting the actual rotation (similarly, rotating 6 teeth corresponds to rotating 1 tooth, rotating 7 teeth corresponds to rotating 2 teeth, so the result of Xmod5 is the same as rotating X teeth).
[0134] For example, this allows watchmakers to follow these simple instructions when adjusting the mechanism: section number Y, number of teeth X that the planetary locking wheel 7 needs to rotate clockwise, and number of supplementary escapement steps N:
[0135] Y=1, X=0, N=9;
[0136] Y=2, X=1, N=2;
[0137] Y=3, X=4, N=7;
[0138] Y=4, X=0, N=0;
[0139] Y=5, X=3, N=5;
[0140] Y=6, X=1, N=10;
[0141] Y=7, X=2, N=3.
[0142] Therefore, by rotating the planetary locking wheel 7 by X teeth, it will be rotated relative to its initial position (clockwise around the tourbillon axis) to a new position (X*1.71429°). Furthermore, the tangential displacement of the tip of the locking tooth 71 of the planetary locking wheel 7 along the stop 21 substantially corresponds to this value.
[0143] Since manually moving the escapement element 5 from one end to the other causes the entire tourbillon to jump in increments of 1° (a 1-minute tourbillon jumps 6 times per second, 60 seconds per minute = 360 jumps, each time 1°), the position of the far end of the locking tooth 71 of the planetary locking wheel 7 relative to the locking element 21 can be adjusted according to (X*1.71429°) mod 1°, that is, in increments of 1 / 7°, thus deriving the rule mentioned above for defining the adjustment list.
[0144] To adjust the relative position of the second hand and the lower frame 2 of the tourbillon, the support 10 can be slid along a constant radius before screwing the support 10 of the second hand 101 onto the outer ring 3 of the ball bearing. This ensures that when the seconds jump occurs, the support 10 is perfectly aligned with the support column 29 on the tourbillon. Figure 7 and Figure 8 As shown. Advantageously, adjustment and fastening are achieved by the combination of shoulder screw 81 and oblong countersunk hole 82.
[0145] To ensure precise alignment of the second hand with the seconds mark on the dial, the fixed wheel 1 of the rotating frame regulator 200 can be rotated relative to the chronograph dial. This can be achieved, for example, through an elongated hole 84 around its fastening screw 83 and a slot 85, which allows for fine-tuning of the position using an eccentric tool 300. Figure 9 , Figure 10 and Figure 11 As shown.
[0146] In summary, the present invention improves upon the existing jumping seconds mechanism. The core of the improvement lies in the fact that the mechanism according to the present invention is not based on the known working principle of a constant force winding mechanism, but operates outside the energy transfer path between the mainspring barrel and the escapement mechanism, which significantly reduces the stress on the mechanism components.
[0147] More specifically, the tourbillon in the mechanism of this invention is a flying tourbillon.
[0148] In the current embodiment of the invention, it should be noted that the loading spring driving the proposed jumping seconds mechanism is not located on the same axis as the tourbillon, but rather on a planetary gear mounted on the ball bearings of the jumping seconds mechanism. This allows the use of the mechanism described in document CH717982, patented by GLASHUETTE ORIGINAL, Glashütter Uhrenbetrieb GmbH, to stop the balance wheel 60 of the tourbillon when adjusting the hour and minute hands. This mechanism also allows for easy adjustment of the spring preload simply by assembling the spring with another pair of gear teeth (which contact the tourbillon gears).
[0149] Furthermore, the compact layout of this invention utilizes the previously unused space beneath the tourbillon cage, and the entire mechanism is fully visible through the existing opening on the flying tourbillon dial. The modular nature of this invention allows it to be applied to existing movements with minimal adjustments.
[0150] By changing the number of teeth on the planetary locking wheel, the mechanism can be easily modified to jump at intervals of other values, such as half-second intervals (by doubling the number of teeth on the planetary locking wheel), similar to a marine chronometer.
[0151] The mechanism according to the invention can also be applied by changing specific parameters—especially the frequency f0 of the oscillator and the number of teeth of each pinion and wheel of the mechanism (always an integer): 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 tourbillon fixed wheel 1, 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, wherein the required jump frequency fj must satisfy the following two conditions.
[0152] First condition: fj = ((tpe*tb) / tpb)*f0 / (te), or use the code of its moving part to replace the number of teeth, that is:
[0153] - fj=((N40*N7) / N70)*(f0 / N4)
[0154] Second condition: The ratio f0 / (0.5*fj) is an integer.
[0155] In this manner, and without limitation, the following organizations are also applicable:
[0156] First example: fj=2Hz, f0=4Hz, te=20, tpe=10, tpb=16, tb=16; or use the code of its moving part to replace the number of teeth: N4=20, N40=10, N70=16, N7=16.
[0157] Second example: fj=4 / 3Hz, f0=4Hz, te=20, tpe=12, tpb=9, tb=5; or use the code of its moving part to replace the number of teeth: N4=20, N40=12, N70=9, N7=5; therefore, the jump interval of this configuration is 3 / 4 seconds.
[0158] Please remember that the specific variants shown in the attached diagram correspond to the following values: fj=1Hz, f0=3Hz, te=15, tpe=7, tpb=7, tb=5; or use the code of its moving part to replace the number of teeth: N4=15, N40=7, N70=7, N7=5.
[0159] If we assume that the tourbillon completes one rotation per minute (i.e., each 360° rotation corresponds to a true second display of 60 seconds), then the following additional condition must be met:
[0160] - ttf=60*(tpe*f0) / te is an integer, or the number of teeth can be replaced by the code of the moving part: ttf=N1=60*(N40*f0) / N4 is an integer.
[0161] The proposed arrangement of the planetary gears can also be used to apply other jumping seconds mechanisms to the flying tourbillon described above according to CH717982A2. Such flying tourbillons typically require a coaxially mounted hairspring to accumulate the required jumping energy, or a secondary drive system, such as the secondary anchor escapement used by Jaquet Droz.
[0162] For this type of mechanism, the tourbillon lower frame can be used as the drive wheel of the escapement fork, and the ball bearing outer ring with the planetary loading wheel can be used as the jumping seconds wheel.
[0163] The present invention also relates to a watch 2000 comprising at least one such movement 1000.
[0164] The present invention also relates to a watch assembly comprising at least one such watch 2000 and / or at least one such movement 1000. For each movement 1000 or each movement model, the watch assembly includes a list for use by watchmakers in the factory or after-sales department, which lists the number of teeth X of the planetary locking wheel 7 that needs to be rotated clockwise, and the number of supplementary escapement steps N that need to be performed on the escapement element 5 to achieve a predetermined locking position of the locking tooth 71 on the locking element 21.
[0165] Specifically, for the particular example described in this specification, where: fj=1Hz, f0=3Hz, te=15, tpe=7, tpb=7, tb=5; or the number of teeth is replaced by the code of its moving part: N4=15, N40=7, N70=7, N7=5, the parameters of the number of teeth X of the planetary locking wheel 7 that needs to rotate clockwise, and the parameters of the number of supplementary escapement steps N that need to be performed on the escapement element 5 are as follows: the 1° center angle of the locking element 21 or the locking stop is divided into 7 locking positions of the locking teeth 71, called sections 1 to 7, where: section 1, the locking depth is "1", 9 Section 1, with a lock depth of "2", has 2 escapement stages and planetary locking wheel 7 rotates 0 teeth; Section 2, with a lock depth of "2", has 2 escapement stages and planetary locking wheel 7 rotates 1 tooth; Section 3, with a lock depth of "3", has 7 escapement stages and planetary locking wheel 7 rotates 4 teeth; Section 4, with a lock depth of "4", has 0 escapement stages and planetary locking wheel 7 rotates 0 teeth; Section 5, with a lock depth of "5", has 5 escapement stages and planetary locking wheel 7 rotates 3 teeth; Section 6, with a lock depth of "6", has 10 escapement stages and planetary locking wheel 7 rotates 1 tooth; Section 7, with a lock depth of "7", has 3 escapement stages and planetary locking wheel 7 rotates 2 teeth.
Claims
1. A movement (1000) for a mechanical timepiece, comprising: At least one rotating frame regulator (200), the rotating frame regulator (200) comprising a fixed wheel (1), a frame supporting a balance wheel mechanism, an escapement element (5), an escape wheel (4), a locking element (21), and a bearing coaxially fastened to the plate of the movement (1000) with the frame, characterized in that the rotating frame regulator (200) includes a locking wheel (7) with locking teeth (71), the locking wheel (7) pivoting on a ring (3) of the bearing, and the locking teeth (71) being deactivated by the locking element (21), wherein the locked position is capable of... It can be adjusted in the factory; the locking wheel (7) is arranged to release or lock the movement of the collar (3) and carries the locking pinion (70) that is always engaged with the fixed wheel (1); and the collar (3) is connected to the rotating frame speed regulator (200) through an intermediate loading system, the intermediate loading system being wound by the movement of the rotating frame speed regulator (200) to load the loading spring (62) so that when the loading spring (62) is gradually released, the loading spring (62) can keep the collar (3) moving in the same direction of rotation as the rotating frame speed regulator (200).
2. The movement (1000) according to claim 1, characterized in that, The escapement pinion (40) meshes with the fixed wheel (1); the intermediate loading system includes a lower frame (2) and a loading wheel (61), the lower frame (2) being contained within the frame and carrying a meshing tooth (22), the loading wheel (61) being attached to the loading spring (62) and pivoting on the collar (3), and meshing with the meshing tooth (22) of the lower frame (2); the assembly consisting of the lower frame (2), the loading wheel (61), the loading spring (62), the collar (3), the locking wheel (7) and the locking element (21) constitutes a first planetary gear system, wherein the lower frame (2) is a sun gear, the collar (3) is a planet carrier, in which the loading wheel (61) is a first planetary gear, and the locking wheel (7) is a second planetary gear.
3. The movement (1000) according to claim 2, characterized in that, The loading spring (62) on the loading wheel (61) is wound in such a way that, when the bearing is stationary, the winding is achieved by the movement of the lower frame (2) and the engagement between the meshing teeth (22) of the lower frame (2) and the loading wheel (61); when the lower frame (2) pivots about its own pivot axis (DP), the tip of the locking element (21) can move all the way to the tip of the locking tooth (71), wherein the locking tooth (71) abuts against the locking element (21).
4. The movement (1000) according to any one of claims 1 to 3, characterized in that, The fixed wheel (1) is fastened to the plate of the movement (1000) and includes an external gear ring; the meshing teeth (22) extend outward; the loading wheel (61) pivots in the first bridge plate (66) and is associated with the loading spring (62), the two ends of which are respectively attached to the first bridge plate (66) and the loading wheel (61); the planetary locking wheel (7) pivots in the second bridge plate (76); the loading wheel (61) and the planetary locking wheel (7) are assembled to pivot on the collar (3) and spaced apart from each other. The outer ring (3) serves as the outer ring of the ball bearing. When the outer ring (3) is stationary, the loading spring (62) is wound up by the movement of the rotating frame speed regulator (200) and by the meshing between the meshing teeth (22) and the loading wheel (61). Once the outer ring (3) is released, the tension of the loading spring (62) causes the outer ring (3) to rotate in the same direction as the rotating frame speed regulator (200). The locking teeth (71) are arranged to abut against the locking element (21) or the locking stop.
5. The movement (1000) according to claim 2 and any one of claims 1 to 4, characterized in that, The rotary frame speed regulator (200) includes a secondary planetary gear system in which the fixed gear (1) is a sun gear, the outer ring (3) is a planet carrier, and the locking pinion (70) is a planet gear. By adding the planet carrier composed of the outer ring (3), the secondary planetary gear system is superimposed on the first planetary gear system.
6. The movement (1000) according to any one of claims 1 to 5, characterized in that, The rotating frame speed regulator (200) is a jumping second flying tourbillon, and its jumping 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 locking wheel (7), N70 is the number of teeth of the locking pinion (70), f0 is the frequency of the oscillator including the balance wheel mechanism, and N4 is the number of teeth of the escapement wheel (4); and the ratio f0 / (0.5*fj) is an integer.
7. The movement (1000) according to any one of claims 1 to 6, characterized in that, The locking element (21) or the locking stop includes a support surface capable of engaging each of the locking teeth (71). The support surface extends in a substantially tangential direction relative to the receiving groove (111) in a plane perpendicular to the pivot axis of the lower frame (2). The locking element (21) is inserted into and secured within the receiving groove (111). The jump time can be set by adjusting the relative tangential position between the locking element (21) and each of the locking teeth (71), wherein the relative tangential position corresponds to the locking position of the locking teeth (71).
8. The movement (1000) according to claim 7, characterized in that, In the stationary position of the collar (3), the locking position can be adjusted by moving the escapement element (5) by a predetermined number N escapement steps and rotating the planetary locking wheel (7) by an angle corresponding to a predetermined number of teeth X of the planetary locking wheel (7).
9. The movement (1000) according to claim 8, characterized in that, Each of the locking teeth (71) is arranged to occupy an integer number of discrete locking positions in an incremental manner over the depth range of the locking element (21), wherein each locking position is identified by a segment number Y and is accessible according to a list indicating the number of teeth X that the planetary locking wheel (7) needs to rotate clockwise, and the number of supplementary escapement steps N that the escapement element (5) or escapement fork needs to perform.
10. The movement (1000) according to any one of claims 7 to 9, characterized in that, Each of the locking teeth (71) is arranged to occupy a locking position within a predetermined angular interval relative to the locking element (21), wherein the predetermined angular interval is defined about the pivot axis of the lower frame (2) and corresponds to an integer number of degrees.
11. The movement (1000) according to any one of claims 7 to 10, characterized in that, The escape pinion (40) and the locking pinion (70) mesh with the same fixed wheel (1); the position of the locking element (21) is fixed relative to the pivot axis of the escape wheel (4); and the locking depth of the teeth of the planetary locking wheel (7) on the locking element (21) is defined by the angular orientation of the teeth of the escape pinion (40) and the locking pinion (70).
12. The movement (1000) according to any one of claims 7 to 11, characterized in that, The frequency f0 of the oscillator, and the integer number of teeth of each pinion and wheel of the mechanism, namely the number of teeth N4 of the escape wheel (4), the number of teeth N40 of the escape pinion (40), the number of teeth N1 of the fixed wheel (1), the number of teeth N70 of the locking pinion (70), and the number of teeth N7 of the locking wheel (7), are set such that the required jump frequency fj satisfies the first condition: fj=((N40*N7) / N70)*(f0 / N4), and satisfies the second condition: the ratio f0 / (0.5*fj) is an integer.
13. The movement (1000) according to claim 12, characterized in that, fj=1Hz, f0=3Hz, N4=15, N40=7, N70=7, N7=5, corresponding to one jump per second.
14. The movement (1000) according to claim 12, characterized in that, fj=2Hz, f0=4Hz, N4=20, N40=10, N70=16, N7=16, corresponding to a jump every half second.
15. A watch (2000), characterized in that, The watch includes 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, For each type of movement (1000) or each movement model, the watch assembly includes a list for use by watchmakers in the factory or after-sales department; the list lists the number of teeth X that the planetary locking wheel (7) needs to rotate clockwise, and the number of supplementary escapement steps N that the escapement element (5) needs to perform in order to achieve a predetermined locking position of the locking tooth (71) on the locking element (21).
17. The watch assembly according to claim 16, the watch assembly comprising the movement (1000) according to claim 13, characterized in that, The parameters of the number of teeth X that the planetary locking wheel (7) needs to rotate clockwise and the parameters of the number of supplementary escape steps N that the escapement element (5) needs to perform are as follows: The 1° center angle of the locking element (21) is divided into 7 locking positions of the locking teeth (71), referred to as section 1 to section 7, wherein: section 1, the locking depth is "1", 9 escape steps, and the planetary locking wheel 7 rotates 0 teeth; section 2, the locking depth is "2", 2 escape steps, and the planetary locking wheel 7 rotates Section 3, lock depth "3", 7 escapement steps, planetary lock wheel 7 rotates 4 teeth; Section 4, lock depth "4", 0 escapement steps, planetary lock wheel 7 rotates 0 teeth; Section 5, lock depth "5", 5 escapement steps, planetary lock wheel 7 rotates 3 teeth; Section 6, lock depth "6", 10 escapement steps, planetary lock wheel 7 rotates 1 tooth; Section 7, lock depth "7", 3 escapement steps, planetary lock wheel 7 rotates 2 teeth.
18. An adjustment method for adjusting the relative positional accuracy of the planetary locking wheel (7) and the locking element (21) in a watch assembly according to claim 16 or 17, and achieving this by adjusting the locking depth of the locking teeth (71) of the planetary locking wheel (7) on the locking element (21), the adjustment method comprising: The first step (A) involves randomly riveting the escape wheel (4) to its escape pinion (40) and randomly riveting the planetary locking wheel (7) to its locking pinion (70). The first step (A) includes setting the position of the locking element (21) within ±1° of its correct theoretical position and fastening the locking element (21) to the lower frame (2). The second step (B) involves assembling the mechanism and winding the mainspring of the movement, but without installing the balance wheel of the balance spring mechanism or the upper frame included in the rotating frame regulator (200). The escape wheel (4) and the planetary locking wheel (7) are randomly positioned in the jumping seconds mechanism. The second step (B) includes manually moving the escape element (5) back and forth to advance the lower frame (2) in 1° increments until the locking tooth (71) reaches the far end of the locking element (21). At this time, the locking tooth (71) 1) The jumping seconds mechanism is about to disengage and thus release; third step (C), wherein the tip of the locking tooth (71) is checked to determine whether the tip is located at one of the multiple positions marked on the locking element (21) and the position is identified, wherein a 1° angular offset of the locking element (21) is divided into an integer number of relative positions of the locking tooth (71) relative to the locking element (21); fourth step (D), wherein adjustment is performed by temporarily locking the collar (3) to disengage the planetary locking wheel (7), and repositioning the planetary locking wheel (7) according to the guide list after rotating the lower frame (2) by manually moving the escapement element (5) back and forth a number of steps as required; fifth step (E), wherein the locking depth of the locking tooth (71) is checked, and if the required locking depth is not reached, the third step (C) and the fourth step (D) are iteratively repeated until the required locking depth is reached.
19. The adjustment method according to claim 18, characterized in that, The adjustment method includes a sixth step (F), wherein the pretension of the loading spring (62) of the loading wheel (61) is set to the minimum level required to achieve net jump seconds.
20. The adjustment method according to claim 19, characterized in that, The sixth step (F) includes reinstalling the loading wheel (61) so that another pair of teeth contacts the meshing teeth (22) of the lower frame (2).
21. The adjustment method according to any one of claims 18 to 20, characterized in that, In the third step (C), the relative position between the locking tooth (71) and the locking element (21) is adjusted by adaptation adjustment.
22. The adjustment method according to any one of claims 18 to 21, characterized in that, In order to adjust the relative position of the second hand (101) and the lower frame (2) of the tourbillon, the support (10) is adjusted by sliding it on a constant radius before screwing the support (10) of the second hand (101) onto the ring (3) so that when the second hand jumps, the support (10) is fully aligned with the support (29) contained in the rotating frame regulator (200).
23. The adjustment method according to any one of claims 18 to 22, characterized in that, To ensure precise alignment with the seconds mark on the dial, the fixed wheel (1) is rotated relative to the stopwatch dial through an elongated hole around the fastening screw of the fixed wheel (1) and a slot, wherein the slot allows the eccentric tool (300) to move for fine-tuning of its position.