Speed ​​regulator for watch movements

Abstract

To make a speed regulator for a timepiece movement insensitive to angular acceleration or at least to reduce said sensitivity. The present invention relates to a governor (20) for a timepiece movement (10). The governor (20) comprises an oscillator (22) including at least a first balance and a second balance. Each balance comprises an inertia gear (24a, 24b) and a balance stem (34a, 34b). The oscillator (22) comprises at least one elastic member (32, 32a, 32b) intended to maintain the oscillation of the oscillator. The oscillator also comprises a gear train (40) comprising at least two moving parts (42, 44, 45, 46, 47, 48, 49). The inertia gear (24a, 24b) of each balance is rotatably fixed to a moving part of the gear train (40). The gear train (40) is provided by connecting the inertia gears (24a, 24b) of the first and second balances by a desmodromic connection so that the oscillations of the first and second balances are of opposite phases.

Description

Technical Field

[0001] The present invention relates to a speed regulator for a timepiece movement. The present invention also relates to a timepiece movement provided with a speed regulator and a time-indicating device provided with such a movement.

Background Art

[0002] Generally, a mechanical timepiece includes a timepiece movement in which the oscillator of the speed regulator can be changed between 3 Hz and 5 Hz. On the one hand, in general terms, this oscillator can be above 5 Hz in order to make the timepiece more accurate. That is, a speed regulator with a low oscillation frequency can offer several advantages including an increase in power reserve (the driving time from the wound-up state of the mainspring until the timepiece completely unwinds and stops) and a simplification of the timepiece movement.

[0003] Low-frequency speed regulators are known in the art.

[0004] As an example, the escapement disclosed in Patent Document 1 has a reversing wheel provided to impart an impact to the balance through a gear in order to reduce the oscillation frequency of the balance to oscillate at a frequency of 0.5 Hz.

[0005] In order to maintain an acceptable quality factor for the oscillator of a low-frequency speed regulator, the inertia of the balance must be increased compared to a mechanical movement with an oscillator of a higher oscillation frequency. This increase in inertia has the main disadvantage of increasing the sensitivity to angular acceleration.

Prior Art Documents

Patent Documents

[0006]

Patent Document 1

Patent Document 2

Summary of the Invention

[0007] Therefore, the object of the present invention is to provide a speed governor that is insensitive to angular acceleration, or at least has reduced sensitivity to it.

[0008] Another object of the present invention is to provide a simplified clock movement equipped with a low-frequency regulator.

[0009] An additional object of the present invention is to provide a method for adjusting the vibration frequency of a governor oscillator. [Means for solving the problem]

[0010] These objectives are achieved, in particular, by a regulator for a watch movement. The regulator comprises an oscillator having at least a first balance wheel and a second balance wheel. Each balance wheel comprises an inertia gear and a balance staff. The oscillator comprises at least one elastic member for maintaining its oscillation. The oscillator further comprises a gear train having at least two moving parts. The inertia gear of each balance wheel is rotatably fixed to the moving part of the gear train. The gear train is arranged so as to connect the inertia gears of the first and second balance wheels to each other by a desmodromic coupling, such that the oscillations of the first and second balance wheels are in opposite phases. The regulator further comprises an escapement, the escapement comprising at least one escape wheel, and the escapement comprising at least one anchor intended to control the at least one escape wheel and to maintain the oscillation of the oscillator.

[0011] In one embodiment, the governor comprises at least three balance wheels, each having an inertia gear. In the kinetic chain of the at least three balance wheels, the oscillations of each of the two balance wheels are in opposite phases.

[0012] In one embodiment, the gear train comprises more than two moving parts.

[0013] In one embodiment, the first and second balances are coaxial.

[0014] In one embodiment, the balances of the first and second balances are parallel, and each inertia gear is configured to vibrate in two parallel planes.

[0015] In one embodiment, the inertia gears of the first and second balances are substantially coplanar.

[0016] In one embodiment, the balances of the first and second balances are contained within intersecting planes.

[0017] In one embodiment, each inertia gear of the first and second balance wheels comprises a plurality of unconnected edge pieces, for example, two, three, or four edge pieces, which together form the edge of each inertia gear along their respective circles. These circles intersect or overlap to define a first and second circular disc, respectively, which form an overlapping or intersecting area.

[0018] In one embodiment, the overlapping region is in the shape of a lens. The lens is preferably a symmetrical lens.

[0019] In one embodiment, the intersection area is a straight section.

[0020] In this embodiment, at least one of the first and second ends does not include the aforementioned at least one elastic member.

[0021] In one embodiment, at least one elastic member is attached to an intermediate movable part of the gear train. The inertia of the intermediate movable part is at least 5 times, preferably at least 10 times, or at least 20 times smaller than the inertia of any of the oscillator's balance wheels.

[0022] In one embodiment, at least one of the first balance wheel, the second balance wheel, and the intermediate movable part of the gear train comprises an even number, preferably two, elastic members wound in opposite directions.

[0023] In one embodiment, the derailer includes only one crank provided to cooperate with one of the first and second planks and the gangway car.

[0024] In one embodiment, the derailer On the one hand, is provided to cooperate with the first and second planks respectively, On the other hand, it includes two cranks provided to cooperate with a single gangway car or the first and second gangway cars respectively.

[0025] In one embodiment, the derailer Is provided to cooperate with the first and second planks respectively, or With a single gangway car, or the first and second gangway cars respectively to cooperate It includes two cranks provided.

[0026] In one embodiment, the derailer includes first and second half - cranks provided to cooperate with the first and second planks respectively. The first and second half - cranks each include a first pallet and a second pallet provided to cooperate with a single gangway car or the first and second gangway cars respectively.

[0027] In one embodiment, the derailer includes a crank provided to cooperate with one of the first and second planks. The crank includes a first pallet provided to cooperate with the first gangway car and a second pallet provided to cooperate with the second gangway car.

[0028] In one embodiment, the derailer includes a crank provided to cooperate with the intermediate movable part of the gear train and the gangway car.

[0029] ​Another aspect of the present invention relates to a method for setting the frequency of a governor oscillator. This method first comprises determining the inertia of all the balance wheels of the oscillator and the return torque of the at least one elastic member. The method further second comprises, secondly, replacing at least one of the moving parts of the gear train, preferably an intermediate moving part, with a moving part having a different inertia, to obtain a ratio between the inertia of all the balance wheels and the return torque of the at least one elastic member defined by a desired frequency of the oscillator.

[0030] Another aspect of the present invention relates to a method for setting the frequency of a governor oscillator according to an alternative solution. According to this alternative, the method first comprises determining the inertia of all the balance wheels and the return torque of the at least one elastic member. The method second comprises obtaining a ratio between the inertia of all the balance wheels and the return torque of the at least one elastic member defined by the desired frequency of the oscillator by replacing at least one of the moving parts of the gear train, which is preferably an intermediate moving part, with a moving part having a different pitch diameter than the pitch diameter of the moving part being replaced.

[0031] Another aspect of the present invention relates to a method for setting a clock movement comprising a drive source, in particular a mainspring barrel, and a regulator. The method first comprises determining the torque supplied from the drive source to the escape wheel, the inertia of all the balance wheels of the oscillator, and the return torque of at least one elastic member. Furthermore, the method second comprises obtaining a defined ratio between the inertia of all the balance wheels of the oscillator and the return torque of the at least one elastic member by replacing at least one movable part of the gear train, preferably an intermediate movable part, with a movable part having both or one of different inertia and different pitch diameters, and further comprising obtaining a defined ratio between the power to maintain the oscillation of the oscillator and the power available to the escape wheel.

[0032] Examples of embodiments of the present invention are described in the attached diagrams. [Brief explanation of the drawing]

[0033] [Figure 1] Figure 1 is a schematic top view of a simplified clock movement according to one embodiment of the present invention. [Figure 2] Figure 2 is a perspective view of an oscillator equipped with two balance springs, driven together by a desmodromic gear train according to one embodiment of the present invention. [Figure 3] Figure 3 is a top view of Figure 2. [Figure 4] Figure 4 is a diagram similar to Figure 3, but without the hairspring. [Figure 5] Figure 5 is a side view of Figure 2. [Figure 6] Figure 6 is a perspective view showing an oscillator according to another embodiment of the present invention. [Figure 7] Figure 7 is a top view of Figure 6. [Figure 8] Figure 8 is a side view of Figure 6. [Figure 9] Figure 9 is a perspective view of a governor having two balance springs driven together by a desmodromic gear train according to another embodiment of the present invention. [Figure 10] Figure 10 is a side view of Figure 9. [Figure 11] Figure 11 is a schematic top view of a speed governor according to one embodiment. [Figure 12] Figure 12 is a schematic top view of a governor according to another embodiment. [Figure 13] Figure 13 is a schematic top view of a governor according to another embodiment. [Figure 14] Figure 14 is a schematic top view of a governor according to another embodiment. [Figure 15] Figure 15 is a schematic top view of a governor according to another embodiment. [Figure 16] Figure 16 is a schematic top view of a governor according to another embodiment. [Figure 17] Figure 17 is a schematic top view of a governor according to another embodiment. [Figure 18] Figure 18 is a schematic top view of a governor according to another embodiment. [Figure 19]Figure 19 is a schematic top view of a governor according to another embodiment. [Figure 20] Figure 20 is a schematic top view of a governor according to another embodiment. [Figure 21] Figure 21 is a schematic top view of a governor according to another embodiment. [Figure 22] Figure 22 is a schematic top view of a governor according to another embodiment. [Figure 23] Figure 23 is a schematic top view of a governor according to another embodiment. [Figure 24] Figure 24 is a schematic top view of a governor according to another embodiment. [Figure 25a] Figure 25a is a top view of the escapement of the governor shown in Figure 12, according to another embodiment. [Figure 25b] Figure 25b is a top view of the escapement of the governor shown in Figure 12, according to another embodiment. [Figure 25c] Figure 25c is a top view of the escapement of the governor shown in Figure 12, according to another embodiment. [Figure 25d] Figure 25d shows the contact point between the pallet of one of the anchors in Figure 25c and the teeth of the escape wheel. [Figure 26] Figure 26 is a top view of the governor shown in Figure 17. [Figure 27] Figure 27 is a schematic top view of an oscillator according to another embodiment. [Figure 28] Figure 28 is a schematic top view of an oscillator showing the overlapping region between two points according to another embodiment. [Figure 29] Figure 29 is a schematic top view of an oscillator showing the overlapping region between two points according to another embodiment. [Figure 30] Figure 30 is a schematic diagram of an oscillator showing two crossover regions between three points according to another embodiment. [Modes for carrying out the invention]

[0034] In this specification, “oscillator” is understood to mean an oscillator having multiple balances, and on the other hand, a gear train arranged such that the balances are interdependent and mesh with each other. In addition, in this specification, “governor” is understood to mean an assembly comprising an oscillator and a counter, in particular an escapement.

[0035] Referring to Figure 1, the watch movement 10 has a simplified structure thanks to a low-frequency regulator with two balance springs 22a and 22b, described later, configured to oscillate at a frequency of less than 1.5 Hz. Depending on the inertia of the selected balance springs, the power reserve can be significantly increased, especially when high chronometric performance is not a priority.

[0036] The simplified watch movement comprises a plate 12 with a mainspring barrel 14, an escapement 15 with an escape wheel, and a motion coupling that connects the mainspring barrel 14 to the pinion of the escape wheel. The motion coupling has fewer than three movable parts.

[0037] In an advantageous embodiment, this moving linkage comprises only one movable part 19, which engages with the ratchet of the mainspring barrel 14 on one hand and with the pinion of the escape wheel on the other. In this way, the movable part 19 replaces the middle wheel, third wheel, and second hand of a conventional movement.

[0038] In modified examples not shown, the moving linkage comprises two or more interlocking movable parts. One of the two movable parts engages with the ratchet of the mainspring barrel, and the other of the two movable parts engages with the pinion of the escape wheel.

[0039] Simplified watch movements have the advantage of offering a new structure that clearly distinguishes them from others, due to their significantly different geometric constraints, such as the center distance, compared to conventional movements. In addition, simplifying the movement reduces the number of gears, thereby increasing overall efficiency.

[0040] Under certain conditions related to the gear ratio and escapement, seconds can be directly displayed on the escapement. In this case, the gear ratio between the barrel 14, the movable part 19, and the pinion of the escape wheel 16 is selected so that the escape wheel rotates once per minute. The seconds indicator 50 may be mounted on the shaft of the escape wheel.

[0041] Similarly, under certain conditions linked to the gear ratio, the movable part 19 can directly display minutes. Therefore, the gear ratio of the mainspring barrel and the movable part 19 is selected so that the movable part 19 rotates once per hour. For example, a minute indicator 52 may be mounted on the shaft of the movable part 19.

[0042] Finally, under certain conditions related to the gear ratio, the mainspring barrel 14 may display the time. For example, a time indicator 54 may be attached to the shaft of the mainspring barrel 14.

[0043] As mentioned above, simplified watch movements can only be manufactured by using low-frequency regulators. To maintain an acceptable quality factor, the inertia of the balance wheel must be increased compared to mechanical movements with higher-frequency oscillators. This increase in inertia has the disadvantage of increasing sensitivity to angular acceleration. To counteract this sensitivity to acceleration, the regulator oscillator has at least two balance wheels coupled so that their phases are opposite in different ways. Alternatively, opposite phases can be achieved by attaching two hairsprings wound in opposite directions to one of the oscillator's balance wheels, such that when one of the two hairsprings is in the contraction phase, the other is in the expansion phase.

[0044] In one advantageous embodiment shown in Figures 2 to 5, the oscillator 22 comprises a balance wheel 22a of a first hairspring and a balance wheel 22b of a second hairspring, which are arranged in the same plane. Each balance wheel 22a, 22b of a hairspring comprises inertia gears 24a, 24b, hairsprings 32a, 32b and balance stems 34a, 34b. The inertia gears comprise edge pieces 28a, 28b and balance arm portions 26a, 26b that connect the edge pieces to the balance stem. One end of each hairspring 32a, 32b is connected to the respective balance stem by, for example, a collet 36a, 36b (Figure 5) driven by the hairspring, and the other end is connected to a hairspring mounted on a hairspring holder that is connected to a receiving portion or a fixed cock (not shown) to a plate 12 of the watch movement 10.

[0045] The oscillator may include elastic members other than the conventional flat hairspring, such as a cylindrical hairspring, a hemispherical or spherical hairspring, or a conical hairspring. Alternatively, the helix may have multiple turns. The oscillator may also include non-hairspring-like elastic members to satisfy the balance wheel's return function.

[0046] The balance wheels 22a of the first hairspring and 22b of the second hairspring of the oscillator 22 are connected by a gear train 40 to drive these balance wheels by desmodromic coupling, so that one inertia gear 24a of the two balance wheels 22a and 22b vibrates in opposite phases to the other inertia gear 24b of the two balance wheels 22a and 22b. In other words, one hairspring 32a of the two balance wheels 22a and 22b is in the expansion phase, and the other hairspring 32b of the two balance wheels 22a and 22b is in the contraction phase, which has the effect of driving the respective inertia gears 24a and 24b in opposite directions. This particular arrangement of the two hairsprings 32a and 32b can cancel out, or at least reduce, the sensitivity of the oscillator 22 to angular acceleration.

[0047] In particular, as can be seen in Figures 4 and 5, the gear train 40 that guarantees the desmodromic connection between the balance wheels 22a and 22b of the two hairsprings comprises a first movable part 42 connected to the balance staff 34a of one of the balance wheels 22a and 22b of the two hairsprings, a second movable part 44 connected to the balance staff 34b of the other balance wheel 22a and 22b of the two hairsprings, and an intermediate movable part 46 that meshes with the first movable part 42 and an intermediate movable part 48 that meshes with the second movable part 44. The ratio and number of gears are determined so that the first inertia gear 24a and the second inertia gear 24b of the balance wheels 22a and 22b of each hairspring vibrate in opposite phases.

[0048] Referring particularly to Figure 2, the inertia gears 24a and 24b of the balance springs 22a and 22b, respectively, are each equipped with four arms 26a and 26b that are spaced 90° apart from one another. Each arm 26a and 26b extends radially from the balance staff 34a and 34b of the respective balance spring to the distal portions 28a and 28b. Furthermore, the thickness of each arm 26a and 26b increases from the balance staff to the corresponding distal portion.

[0049] The distal portions of the first inertia gear 24a and the second inertia teeth 24b each form four discontinuous edges 28a, 28b along the first circle 25a and the second circle 25b, respectively, as shown in Figure 4. Each of the four discontinuous edges 28a, 28b of each tip 22a, 22b extends along an arc between 20° and 50°, and preferably along an arc between 30° and 40°.

[0050] In other variations, the inertia gear of each hairspring's balance wheel may have only two or three arms. In this case, the rim piece with each arm becomes larger, and the inertia of each balance wheel remains constant. For example, each discontinuous rim piece of the inertia gear may extend along an arc greater than 45° if each hairspring's balance wheel has three arms, or along an arc greater than 60° if each hairspring has only two arms.

[0051] Screw-shaped weights 30a and 30b are screwed into the respective edge pieces 28a and 28b, for example, radially, so that the inertia of the inertia gears 24a and 24b can be changed in order to adjust the oscillation frequency of the balance springs 24a and 24b of each hairspring.

[0052] The center distance between the balances 34a, 34b of the two balances 22a of the first hairspring and 22b of the second hairspring is made small to limit the variation in the effect of acceleration between the first inertia gear 24a and the second inertia gear 24b. In this configuration, the first circle 25a and the second circle 25b, each having discontinuous edges 28a, 28b, are arranged to intersect. This configuration also has the advantage of reducing the overall dimensions of the balance (surface). In one embodiment, the dimensions of the two inertia gears are substantially identical. These two inertia gears define two discs with an overlapping region 29a resembling a symmetrical lens, as shown in Figure 28. In another embodiment shown in Figure 29, the diameter D1 of one of the inertia gears 24a, 24b is smaller than the diameter D2 of the other inertia gear. For example, the first diameter D1 is less than 80% of the second diameter D2. In this case, the overlapping region 29a resembles an asymmetric lens.

[0053] When the governor 20 is operating, the oscillators of the inertia gears 24a and 24b of the balance wheels 22a and 22b are synchronized in opposite phases so that the edge piece 28a of one of the balance wheels 22a and 22b of the two balance wheels does not come into contact with the edge piece 28b of the other balance wheel 24b of the two balance wheels 22a and 22b.

[0054] In another embodiment shown in Figures 6 to 8, the oscillator 22 comprises a first hairspring balance 22a and a second hairspring balance 22b, which are mounted coaxially. The first and second hairspring balances 22a and 22b are connected to each other by a gear train 40 such that the inertia gear 24a of one of the two hairspring balances 22a and 22b vibrates in opposite phases to the inertia gear 24b of the other hairspring balance, thereby canceling out or at least reducing the sensitivity of the oscillator 22 to angular acceleration. In another embodiment not shown, the first and second hairspring balances are arranged so that their respective inertia gears use balances parallel to each other and vibrate in two parallel planes.

[0055] In Figure 8, the gear train 40 comprises a first movable part 42 connected to the balance staff 34a of the first balance wheel 22a of the hairspring, a second movable part 44 connected to the balance staff 34b of the second balance wheel 22b of the second hairspring, and an intermediate gear train. The intermediate gear comprises a third movable part 45 that meshes with the first movable part 42, a fourth movable part 46 that meshes with the second movable part 44, a fifth movable part 47 that meshes with the fourth movable part 45, and a lower movable part 48 and an upper movable part 49 that are mounted coaxially to mesh with the third movable part 45, respectively.

[0056] Similar to the first embodiment, the inertia gears 24a and 24b of the balance wheels 22a and 22b of each hairspring are spaced 90° apart from each other and have four arms 26a and four arms 26b, respectively, having the same characteristics as the arms of the balance wheels (two) of the speed governor hairspring shown in Figure 2. The number of arms may be other than four. Each inertia gear 24a and 24b may have only two or three arms, for example, as described above.

[0057] In another embodiment shown in Figures 9 and 10, the oscillator 22 comprises a first hairspring balance 22a and a second hairspring balance 22b, mounted such that the balances of the respective hairspring balances move simultaneously. For example, in Figure 10, the first and second balances of the hairspring balances are at an angle substantially equal to 45° between them, but this angle may be substantially different in some alternative embodiments, for example, between 30° and 60°. According to one embodiment shown in Figure 30, the oscillator comprises three balances, each comprising inertia gears 24a, 24b, and 24c defining a disc. The balances are arranged such that the first and second discs intersect with the third disc along linear first and second intersection regions 29b.

[0058] The advantage of this embodiment is that, in particular, the gear train is a simplified gear train that allows the inertia gears 24a and 24b of the first balance wheel 22a and second balance wheel 22b of the hairspring to vibrate in opposite phases, since the gear train has only two movable parts 42 and 44, for example, two conical teeth, that mesh directly with each other.

[0059] Similar to the first and second embodiments, the inertia gears 24a, 24b of each hairspring balance wheel have four arms 26a, 26b spaced at 90° angles from each other, having the same characteristics as the arms of the two hairspring balance wheels of the governor shown in Figure 2. Each hairspring balance wheel 24a, 24b (balance wheel 22a, 22b, inertia gears 24a, 24b) may alternatively have only two or three arms, as previously described.

[0060] Similar to the first embodiment, when the oscillator 22 is operating, the vibration of one inertia gear 24a of the balance wheels 22a and 22b of the two hairsprings is synchronized in opposite phases with the vibration of the other inertia gear 24b of the balance wheels 22a and 22b of the two hairsprings, so that the edges 28a and 28b of the respective inertia gears 24a and 24b never come into contact.

[0061] The governor 20 according to the present invention can be implemented in different configurations of the oscillator and escapement shown in schematic Figures 11 to 24, preferably via a single movable part 19 in the schematic diagram of Figure 1, to transmit the oscillation frequency of the governor 20 to a motion coupling that connects the mainspring barrel 14 to the pinion of the escape wheel 16. The escapement may include one or more anchors, such as Swiss anchors. Alternatively, the escapement may include other devices acting between the oscillator and the escape wheel, such as a detent escapement or a coaxial escapement. Therefore, in this specification, the term “anchor” is used in a broad sense to mean any member intended to cooperate between the governor and the escapement.

[0062] According to the embodiment shown in Figure 11, the governor 20 includes an oscillator 22 having two balance springs 22a and 22b, for example, the oscillator 22 shown in Figure 2. The first inertia gear 24a and the second inertia gear 24b are arranged to vibrate in opposite phases. The escapement has a single escapement lever 17, for example, a Swiss lever.

[0063] The anchor 17 includes a pawl 170 and a pawl 172, which are arranged to cooperate with the escape wheel 16 in a conventional manner to transmit the vibration of the inertia gear 24a of the balance wheel 22a of the governor 20 to the escape wheel 16 so that the rotation of the escape wheel 16 occurs at the speed of the vibration of the inertia gear 24a. For this purpose, the anchor 17 includes a fork 179, which is arranged to cooperate with the balance staff's impact pin.

[0064] One inertia gear 24a of the balance wheel of the hairspring is connected to the other inertia gear 24b of the balance wheel of the hairspring by a gear train having even-numbered gears 42, 44, 46, and 48, so as to reverse the direction of rotation of the balance wheel(s).

[0065] The balance springs 22a and 22b of the hairspring are equipped with hairsprings 32a and 32b wound in the same direction such that while the movement is running, one hairspring is in the contraction phase and the other hairspring is in the expansion phase, i.e., they are in opposite phases.

[0066] Referring to the embodiment shown in Figure 12, and the different embodiments shown in Figures 25a to 25d, the governor 20 has a structure similar to that in Figure 11, but the difference is that the first balance wheel 22a and the second balance wheel 22b of the hairspring cooperate with the first anchor 17a and the second anchor 17a, respectively, which cooperate with the same escape wheel 16.

[0067] Referring particularly to Figure 25a, the first escapement anchor 17a includes an inward claw 170a and an outward claw 172a provided to cooperate with the teeth of the escape wheel 16, while the second escapement anchor 17b includes an inward claw 170b and an outward claw 172b provided to cooperate with the teeth of the escape wheel 16 alternately with the first escapement anchor 17a. The inward claws and outward claws of each anchor are provided to cooperate with different teeth.

[0068] In this configuration, the entry jaw 170a of the first escapement anchor 17a and the exit jaw 172b of the second escapement anchor 17b are spaced apart to cooperate with the teeth of the escape wheel 16, which are separated by an angle of less than 180° as they pass through the center of the escape wheel 16, while the exit jaw 172a of the first escapement anchor 17a is positioned facing the entry jaw 170b of the second escapement anchor 17b. Thus, the escape wheel 16 has at least 20 teeth, and the forks 179a, 179b of each anchor are positioned to cooperate with the impact pins 35a of the balance wheel rollers 35 of the corresponding balance springs 22a, 22b. Under certain conditions, escape wheels with fewer than 20 teeth, for example, 15 teeth, may also be used.

[0069] Due to the opposite rotation of the inertia gears 24a and 24b (Figure 12) described earlier, the anchors 17a and 17b operate symmetrically. Figure 25a shows one tooth of the escape wheel 16 on the mounting surface 176 of the entry jaw 170a of the first anchor 17a, and one tooth of the escape wheel 16 on the mounting surface 176 of the exit jaw 172b of the second anchor 17b. The angle between the respective mounting surfaces 176 of the entry jaw 170a and exit jaw 172b of the first anchor 17a and the second anchor 17b, the respective mounting surfaces 176 of the entry jaw 170a and exit jaw 172b having the first and second teeth of the escape wheel 16, and the center of the escape wheel 16 is less than 180°, preferably between 130° and 160°. The operating principle of the escapement 15 in Figure 25a requires that the operation stages of the anchors occur simultaneously.

[0070] In the embodiment shown in Figure 25b, the impact surfaces of the protruding jaws 172a of the first anchor 17a and the protruding jaws 172b of the second anchor 17b are eliminated, so that the distal portions of the protruding jaws 172a of the first anchor 17a and the protruding jaws 172b of the second anchor 17b form an angle of approximately 90° with the pallet mounting surface 176.

[0071] This particular shape of the distal portion of the aforementioned pallet (outing claw) has the advantage of avoiding the constraints imposed by the operating stages of the first and second anchors, which must be performed simultaneously according to the embodiment shown in Figure 25a. This simplifies the setup of the escapement 15. Nevertheless, the pallet is sized so that the pulling function is satisfied.

[0072] The dimensions of the pallet are designed so that the escapement gear teeth make firm contact with the remaining flat surface of the notched pallet, preventing the anchor from moving in the conventional manner, and so that the release phase of this pallet is not longer than the notched pallet of the other anchor, in order to avoid energy loss during impulse. This structure has the advantage of facilitating the automatic activation of the escapement 15.

[0073] In the embodiment shown in Figure 25c, the escapement employs the operating principle described in Patent Document 2, which is incorporated into this application by reference. This avoids the excessive restraint of the escapement 15 shown in Figure 25a and the residual sensitivity of the escapement adjustment shown in Figure 25b. In this embodiment, in order for the escapement to operate normally, the support of the teeth on the pawl of the escapement's anchor must be positioned very precisely with respect to the edges of the resting surfaces of the pawl and pawl. This ensures that each stage of the escapement's release and impulse operates normally.

[0074] Considering manufacturing tolerances, conventional escapements with an anchor generally require final adjustment of the entry and exit jaw positions. This adjustment is typically lengthy and delicate because it significantly impacts the efficiency of the escapement.

[0075] The escapement 15 in Figure 25c is similar to the escapement in Figure 25a in the arrangement of the first and second anchors 17a and 17b, which are provided to function with the escape wheel 16. The escape wheel, however, differs in the shape of its teeth.

[0076] In this case (Figure 25d), each tooth of the escape wheel 16 has a drive surface 182 (Figure 25d), and through the drive surface 182, the contact between the escape wheel and the in-jaws 170a, 170b and out-jaws 172a, 172b of each anchor 17a, 17b generates a torque that acts to reduce the angle between the anchor and the reference axes V1, V2, which connect the axes of each anchor 17a, 17b and the balances for the first anchor 17a and the second anchor 17b. In other words, in this embodiment, a drive surface is provided that generates a torque that moves the anchor toward the equilibrium position, so that the anchor is provided with a drive surface that allows the anchor to naturally reach the equilibrium position.

[0077] In one embodiment not shown, the drive surface is located on one of the pallets of the first and second anchors, and the escape wheel has conventional teeth.

[0078] The governor 20 according to the embodiment in Figure 13 has a structure similar to that of Figure 12, but differs in that one of the balance wheels lacks a hairspring. This balance wheel has an inertia gear 24 connected to a first movable part 42. The latter meshes with a gear train comprising two intermediate movable parts 46, 48 and a second movable part 44 connected to the balance wheel 22b of the hairspring. The inertia gear 24a is thus driven by a desmodromic mechanism and vibrates in sync with the vibration of the balance wheel 22b of the hairspring, but in the opposite direction. The balance wheel 22b of the hairspring may comprise a single hairspring, or, in a modified example similar to that in Figure 14 (not shown), may comprise a pair of hairsprings wound in opposite directions to obtain opposite phases.

[0079] In the embodiment shown in Figure 14, only one of the balance wheels of the oscillator 22 is configured to cooperate with the escape wheel 16. This balance wheel does not have a hairspring, and its inertia gear 24a is connected to a first movable part 42. Similar to the governor in Figure 13, the first movable part 42 meshes with a gear train comprising two intermediate movable parts 46, 48 and a second movable part 44 connected to the balance wheel 22b of the hairspring. The inertia gear 24a vibrates at the same speed as the vibration of the balance wheel 22b of the hairspring, but in the opposite direction, by desmodromic coupling. The balance wheel 22b of the hairspring comprises, as part, a single hairspring, or preferably two hairsprings 32a, 32b mounted coaxially with opposite phases and wound in opposite directions.

[0080] In the embodiment shown in Figure 15, the oscillator 22 of the governor 20 comprises two balance wheels 22a and 22b with hairsprings and one balance wheel without a hairspring. The latter has an inertia gear 24c connected to a movable part 43 of the gear train and is configured to cooperate with the escape wheel 16 via an anchor 17. The two balance wheels 22a and 22b are located on either side of the balance wheel without a hairspring at the ends of the desmodromic linked kinetic chain CC of the oscillator 22. In the illustrated example, the inertia gears 24a and 24b rotate in the same direction thanks to the odd number of movable parts 43, 46, 47, 48, and 49 of the gear train connecting the two balance wheels 24a and 24b. Therefore, the hairspring 32a of the balance wheel 22a is wound in the opposite direction to the hairspring 32b of the balance wheel 22b, resulting in opposite phases. Generally, in the kinetic chain CC of a governor having at least three balance wheels, the oscillations of two consecutive balance wheels are in opposite phases.

[0081] In the embodiment shown in Figure 16, the oscillator 22 of the governor 20 also has three balance wheels: a central balance wheel 22c of the hairspring, which is provided to cooperate with the escape wheel 16, and two balance wheels without hairsprings, one on each side of the central balance wheel. The latter consists of two hairsprings 32a and 34 that are mounted coaxially and wound in opposite directions to obtain a phase difference. In modified examples not shown, the central balance wheel of the hairspring may have only one hairspring. The vibrations of the inertia gears 24a and 24b located on either side of the central balance wheel 22c of the hairspring are generated by the gear train at the vibration speed of the central balance wheel of the hairspring.

[0082] Referring to the embodiment in Figure 17 and Figure 26, the first balance wheel 22a and the second balance wheel 22b of the speed governor 20 cooperate with the first half-anchor 18a and the second half-anchor 18b of the escapement, respectively, which cooperate with the same escape wheel 16. In this case, the first anchor 18a is equipped with an in-pawl 180a, and the second anchor 18b is equipped with an out-pawl 180b. By creating two half-anchors in this way, the operation of the anchor 15 is separated, and each is coupled with the shock pin of the balance staff. In this case, the shock is distributed between the balance wheels 22a and 22b of the first and second hairsprings of the oscillator 22. The hairsprings 32a and 32b of the hairsprings 22a and 22b, respectively, are wound in the same direction to obtain opposite phases. In a modified example not shown, one balance wheel lacks a hairspring, while the other balance wheel has a pair of hairsprings mounted in opposite phases.

[0083] According to the embodiments shown in Figures 18 and 19, the governor 20 has a structure similar to that of Figure 17, in which the first balance wheel 22a and the second balance wheel 22b of the hairspring are connected via the first anchor 17a and the second anchor 17b. According to the governor 20 in Figure 18, via the first anchor 17a and the second anchor 17b, or According to the governor in Figure 19, via the first and second half anchors 18a and 18b, The first balance wheel 22a and the second balance wheel 22b of the hairspring differ in that they cooperate with the first escape wheel 16a and the second escape wheel 16b, respectively. To obtain opposite phases, the hairsprings 32a and 32b of the balance wheel are also wound in the same direction. In a modified example not shown, one balance wheel has no hairspring, while the other balance wheel has a pair of hairsprings attached in opposite phases.

[0084] In the embodiment shown in Figure 20, the oscillator 22 of the governor 20 comprises a balance wheel 22a with a hairspring and a balance wheel without a hairspring. The governor comprises an escapement comprising, on the one hand, a first escape wheel 16a and a second escape wheel 16b arranged to rotate in opposite directions to each other, and on the other hand, an anchor 17 arranged to cooperate with, for example, the balance wheel without a hairspring, and the two escape wheels. The balance wheel 22a with a hairspring preferably comprises two hairsprings mounted in opposite phases. In a modified example not shown, each balance wheel comprises a hairspring.

[0085] Two other embodiments of the governor are shown in Figures 21 and 22. The first and second balance wheels of the oscillator 22 are mounted in opposite phases and do not have hairsprings. Therefore, these balance wheels consist only of inertia gears 24a and 24b. The hairspring 32 is mounted on the movable part 48 of the gear train of the oscillator 22. Placing this hairspring at the center of the gear train has the advantage of reducing the return effect compared to a hairspring at one end of the oscillator chain. For this reason, the inertia gears 24a and 24b preferably do not have hairsprings. According to this embodiment, the inertia of the movable part 48 is at least 5 times, preferably at least 10 times, or at least 20 times smaller than the inertia of either balance wheel.

[0086] Referring to Figure 22, there is a gear train provided to give reciprocating motion to the movable part 48, and the gear train cooperates with the anchor 17 by, for example, a pin (not shown) connected to the movable part 48.

[0087] The movable part 48 can be larger or smaller than the movable parts 42 and 44 connected to the first balance wheel 22a and the second balance wheel 22a, respectively. This expands the dimensional range of the balance wheel coupling and amplitude of the hairspring (the amplitude of the hairspring can be adapted to the ideal operation of the escapement, while the amplitude of the balance wheel can be adapted to their inertia). In the governor of Figure 22, the pitch diameter of the movable part 48 is larger than the pitch diameters of the movable parts 42 and 44 of the first and second balance wheels 22a and 22b, respectively.

[0088] Another example of a governor is schematically shown in Figure 23. This governor is similar to the governor in Figure 22, but differs in that the hairspring 32 is attached to a movable part 48 of a gear train having a pitch diameter smaller than the pitch diameters of the movable parts 42 and 44 of the first and second balance wheels 24a and 24b, respectively.

[0089] In another embodiment schematically shown in Figure 24, the movable part 48 of the gear train is configured to cooperate with the anchor 17 by, for example, a pin (not shown) connected to the movable part 48, while the governor comprises two balance springs 22a, 22b arranged in opposite phases. The pin is moved by a reciprocating motion when the governor is operated to regulate the rotation of the escape wheel 16 and maintain the oscillation of the first and second balance springs.

[0090] According to the embodiments shown in Figures 12, 13 and 21, in particular, to optimize both or either compensation for play and / or contact with the pallet(s), the escape wheel 16 may be replaced by two coaxial escape wheels that are connected to each other or movable relative to each other.

[0091] According to another embodiment schematically shown in Figure 27, the governor oscillator comprises four inertia gears 24a, 24b, 24c, and 24d. Each inertia gear 24a, 24b, 24c, and 24d is similar to the governor inertia gears in the embodiments shown in particular in Figures 2 to 4. The distal portion of each inertia gear forms a plurality of discontinuous rims, for example, consisting of three or four pieces, along a first circle, a second circle, a third circle, and a fourth circle. The distance between the centers of the four balances is made small such that each circle intersects with another of the four circles. The four inertia gears 24a, 24b, 24c, and 24d are interconnected by a gear train (not shown) adapted such that two inertia gears 24a and 24c vibrate in the same phase, and two inertia gears 24a and 24c are in the opposite phase to the other two inertia gears 24b and 24d. The four inertia gears 24a, 24b, 24c, and 24d are preferably arranged to vibrate on the same plane.

[0092] The governor according to the present invention enables the involvement of multiple movable parts of the gear train between the balance wheel, hairspring, and escape wheel, which were directly connected in conventional governors. The dimensions of each movable part determine their connection. These dimensions enable the implementation of a new adjustment method between the items described below. - While keeping the power required for the oscillator's vibration constant, the return torque of at least one hairspring and the inertia of the balance wheel, - Power required for controlling the oscillator and power transmitted from at least one escape wheel.

[0093] These adjustment methods have the advantage of being able to compensate for the following: - Variations in the mass production of parts (variations in the torque of the hairspring or the inertia of the balance wheel in a production batch), - The torque fluctuations supplied from the drive mechanism of a movement with such a speed regulator, - Variations resulting from the use of additional functions in the mechanism of a movement with such a regulator (the same basic movement can power several calibers that are expected to use the same regulator, although the additional functions differ. The power is optimized depending on how these additional functions are used).

[0094] These adjustments may complement other conventional adjustments, particularly those using screws or eccentrics attached to the balance wheel, or adjustments using a graduated assembly.

[0095] By changing the geometric characteristics (either pitch diameter or inertia) of at least one of the movable parts of the gear train, particularly the movable parts 42, 43, 44, 45, 46, 47, 48, and 49 of gear train 40, it is possible to change the combination between the return torque of at least one hairspring and the inertia of the balance wheel while keeping the power required to maintain the oscillation of the oscillator constant.

[0096] Therefore, this method comprises the following steps. - Determines the inertia of all the oscillator's balances, - Determine the return torque of the elastic member of the oscillator. - Whether or not the moving parts have high or low inertia, or high or low nominal diameter, compare the above values ​​with theoretical values ​​to indicate the target performance, and determine the modifications that should be made to achieve the target performance. - Replace the initial movable part with the movable part determined in the previous step. - Selectively measure the performance of the governor. - If further improvement or refinement of the combination is required, the method is run again from the beginning.

[0097] Although the inertia of the moving parts of the gear train is much smaller than that of the balance wheel (the moving parts do not have enough inertia to maintain oscillation, i.e., they cannot be treated the same as the balance wheel), this change in inertia still slightly alters the relationship between the balance wheel's inertia and the balance spring's return torque, changing the oscillation period and thus altering the operation of the movement of a watch equipped with such a regulator.

[0098] The inertia of the moving parts of the gear train can be changed in various ways, especially, 1) Changing materials to achieve different densities and therefore different inertia while maintaining the same dimensions. 2) Changing the thickness to achieve different inertia with the same pitch diameter (or profile), or 3) Use a perforated movable part to change the effective mass while maintaining the same external dimensions. It can be changed by [this method].

[0099] By changing the pitch diameter of one of the moving parts, particularly the one containing the hairspring, the ratio between the hairspring's moment of inertia and return torque is altered. Changing the pitch diameter of a gear generally involves changing the number of teeth with the same module. However, there are other fine-tuning methods, such as offset (fine-tuning consisting of changing the pitch diameter with the same number of teeth, thereby changing the relationship between the meshing moving parts).

[0100] Since the energy available to the escape wheel can vary upstream (particularly due to the torque generated by the mainspring in the barrel, which can fluctuate during production, but can also fluctuate in more specific cases, such as the addition of openings to the moving parts (framework), and can also fluctuate when driving additional modules with different (energy) consumption levels), it is possible to change these combinations to adapt the governor's characteristics to the amount of energy available to the escape wheel.

[0101] This includes the following steps: - Determines the torque supplied from the drive source to one or more escape wheels. - Determines the effective inertia of a balance wheel equipped with a governor. - Determine the return torque of the elastic member equipped with a speed governor. - Compare these values ​​with theoretical values ​​to determine the target performance and decide on the necessary adjustments to achieve the target (adjustments to the gear inertia can be made along with adjustments to the nominal diameter of the same moving part or another moving part of the gear train, which is necessary to maintain the balance of the hairspring's balance wheel). - Replace the initially configured movable part with the movable part determined in the previous step. - Selectively measure the performance of the governor. - If further improvement or refinement of the combination is required, the method is run again from the beginning.

[0102] To optimize the above adjustment process, it is useful to divide the combined moving parts into classes and determine the size of these classes (gaps) according to the aforementioned needs, either by statistical determination (if the problem is only about compensating for continuous distribution) or by necessity determination (if the problem is about compensating for variations in the (energy) consumption of additional functions).

[0103] Finally, when using movable parts with different pitch diameters, it is clear that the positioning of the support parts (escape wheel holders, cock plates, etc.) and guide means (bearings, ball bearings, etc.) of these movable parts must be configured to adapt to the change in center distance resulting from the combination of their relative spacing. These means for adjusting the center distance are well known in the prior art, for example, as disclosed in Patent Document 1.

[0104] In particular, the guiding means may be attached to an intermediate support that enables this adjustment, but other means are also conceivable without departing from the scope of the present invention. This application offers, for example, the following perspectives. [Perspective 1] An oscillator (22) comprising the first and second balances, wherein each of the first and second balances is equipped with an inertia gear (24a, 24b) and a balance staff (34a, 34b), The vibrator (22) comprises at least one elastic member (32, 32a, 32b) for maintaining its vibration, and the vibrator (22) further comprises a gear train (40) having at least two movable parts (42, 44, 45, 46, 47, 48, 49), The inertia gears (24a, 24b) of each balance are rotatably fixed to the movable parts (42, 44) of the gear train (40), A speed regulator (20) for a clock movement (10) is provided, wherein the gear train (40) is arranged so as to connect the inertia gears (24a, 24b) of the first balance wheel and the second balance wheel to each other by desmodromic coupling, so that the vibrations of the first balance wheel and the second balance wheel are in opposite phases, An escapement (15) comprising at least one escape wheel (16, 16a, 16b), wherein the escapement (15) further comprises at least one anchor (17, 17a, 17b) intended to control at least one escape wheel (16, 16a, 16b) and to maintain the vibration of the oscillator (22), the governor (20) further comprises the escapement (15), A speed regulator (20) for a clock movement (10). [Perspective 2] A governor (20) according to viewpoint 1, comprising at least three balance wheels, each balance wheel comprising an inertia gear (24a, 24b, 24c), wherein the phases of the vibrations of two balance wheels that follow each other in the kinetic chain (CC) of the at least three balance wheels are in opposite directions. [Perspective 3] The governor (20) according to viewpoint 1 or 2, wherein the gear train (40) has two or more movable parts (42, 44, 45, 46, 47, 48, 49). [Perspective 4] A speed governor (20) according to any one of viewpoints 1 to 3, wherein the balances (34a, 34b) of the first and second balances are coaxial. [Perspective 5] A governor (20) according to any one of viewpoints 1 to 3, wherein the balance axes (34a, 34b) of the first balance and the second balance are parallel, and the respective inertia gears (24a, 24b) are arranged to vibrate in two parallel planes. [Perspective 6] A governor (20) according to any one of viewpoints 1 to 3, wherein the inertia gears (24a, 24b) of the first and second balance wheels are substantially on the same plane. [perspective 7] A governor (20) according to any one of viewpoints 1 to 3, wherein the balances (34a, 34b) of the first and second balances are contained within an intersecting plane. [Perspective 8] The governor (20) according to view 6 or 7, wherein the inertia gears (24a, 24b) of the first and second balance wheels each comprise a plurality of unconnected edge pieces (28a, 28b), for example two, three, or four edge pieces, and these edge pieces together form the edges of each inertia gear (24a, 24b) along their respective circles (25a, 25b), and the circles each intersect or overlap to define a first disc and a second disc (27a, 27b) that form an overlapping area (29a) or an intersection area (29b). [Perspective 9] The governor (20) according to viewpoint 8, wherein the overlapping area is shaped like a lens (29a), and the lens is preferably a symmetrical lens. [Perspective 10] The governor (20) described in Viewpoint 8, wherein the aforementioned intersection area is a straight line segment (29b). [Viewpoint 11] A speed governor (20) according to any one of viewpoints 1 to 10, wherein at least one of the first and second speed governors does not have the at least one elastic member. [Perspective 12] A speed governor (20) according to any one of views 1 to 11, wherein at least one elastic member (32) is attached to an intermediate movable part (45, 46, 47, 48, 49) of the gear train (40), and the inertia of the intermediate movable part (45, 46, 47, 48, 49) is at least 5 times, preferably at least 10 times, or at least 20 times smaller than the inertia of any of the aforementioned balances. [Perspective 13] A governor (20) according to any one of views 1 to 12, wherein one or both of the first balance wheel and the second balance wheel and the intermediate movable parts (45, 46, 47, 48, 49) of the gear train (40) are provided with an even number, preferably two, elastic members wound in opposite directions. [Perspective 14] A governor (20) according to any one of viewpoints 1 to 13, wherein the escapement (15) comprises only one anchor (17) provided to cooperate with one of the first balance wheel, the second balance wheel, and the escape wheel (16). [Perspective 15] The escapement (15) On the one hand, in cooperation with the first and second temps, On the other hand, a single escape wheel (16) or a first escape wheel and a second escape wheel (16a, 16b) can cooperate with each other. A governor (20) provided with two anchors (17a, 17b), as described in any one of viewpoints 1 to 13. [Perspective 16] The escapement (15) A governor (20) according to any one of views 1 to 13, comprising a first half anchor and a second half anchor (18a, 18b) provided to cooperate with the first and second balance wheels, respectively, wherein the first and second half anchors (18a, 18b) each comprise a single escape wheel (16) or a first pallet (180a) and a second pallet (180b) provided to cooperate with a first and second escape wheel (16a, 16b), respectively. [Perspective 17] A governor (20) according to any one of views 1 to 13, wherein the escapement (15) comprises an anchor (17) provided to cooperate with one of the first balance wheel and the second balance wheel, and the anchor comprises a first pallet provided to cooperate with a first escape wheel (16a) and a second pallet provided to cooperate with a second escape wheel (16b). [Perspective 18] A governor (20) according to any one of viewpoints 1 to 13, wherein the escapement (15) comprises an anchor (17) provided to cooperate with the intermediate movable parts (45, 46, 47, 48, 49) of the gear train (40) and the escape wheel (16). [Perspective 19] A method for adjusting the vibration frequency of the oscillator (22) of a speed governor (20) as described in any one of viewpoints 1 to 18, The inertia of all the balances (24a, 24b, 34a, 34b) of the vibrator (22) and the return torque of at least one of the elastic members (32, 32a, 32b) of the vibrator are determined. Then, at least one of the movable parts (42, 44, 45, 46, 47, 48, 49) of the gear train (40), preferably an intermediate movable part (45, 46, 47, 48, 49), is replaced with a movable part of a different inertia to obtain a ratio between the inertia of all the balances and the return torque of the at least one elastic member defined by the desired frequency of the oscillator (22). A method for adjusting the vibration frequency of the oscillator (22) of the speed governor (20). [perspective 20] A method for adjusting the vibration frequency of the oscillator (22) of a speed governor (20) as described in any one of viewpoints 1 to 18, The inertia of all the balances (24a, 24b, 34a, 34b) of the vibrator (22) and the return torque of at least one of the elastic members (32, 32a, 32b) are determined. Then, by replacing at least one of the movable parts (42, 44, 45, 46, 47, 48, 49) of the gear train (40), preferably an intermediate movable part (45, 46, 47, 48, 49), with a movable part having a different pitch diameter from the movable part being replaced, a ratio between the inertia of all the balances of the oscillator and the return torque of the at least one elastic member, defined by the desired frequency of the oscillator, A method for adjusting the vibration frequency of the oscillator (22) of the speed governor (20). [Perspective 21] A method for setting a watch movement (10) comprising a drive source (14), in particular a mainspring barrel, and a regulating mechanism (20) described in any one of viewpoints 1 to 17, The torque supplied from the drive source (14) to the escape wheels (16, 16a, 16b), the inertia of all the balances (24a, 24b, 34a, 34b), and the return torque of at least one elastic member (32, 32a, 32b) are determined. Then, by replacing at least one of the movable parts (42, 44, 45, 46, 47, 48, 49) of the gear train (40), preferably an intermediate movable part (45, 46, 47, 48, 49), with a movable part having either or both different inertia and different pitch diameters, A ratio defined between the inertia of all the aforementioned balances and the return torque of the at least one elastic member, The ratio defined between the power required to maintain the vibration of the vibrator (22) and the power available to the escape wheel is To obtain How to set the clock movement (10). [Explanation of Symbols]

[0105] 10 Watch movements 12 boards 14. Incense box 15 Escapement 16 Elevator wheels, 16a, 16b First escape car, second escape car Transmission device 17a, 17b Escapement anchor 170, 172 Pallets (In-jaw, Out-jaw) 170a, 172a In-claw 170b, 172b Dezume 174 Collision surface 176 Mounting surface 178 Distal part 182 Drive surface 179 Fork 18a First half ankle 180a Inlet nail 18b Second half ankle 180b Dezume 20 Governor 22 transducers 22a, 22b Tempura of the hairspring 24a, 24b, 24c, 24d Inertia gears 25a, 25b: 1st yen and 2nd yen 26a, 26b Tempura arm 28a, 28b edge pieces 29a, 29b Intersection Area 30a, 30b weights 32, 32a, 32b Hairspring 34a, 34b Tenshin 35 rollers 35a Impact pin 36a, 36b Colette 40 gear train 42 1st moving part 44 Second moving part 45, 46, 47, 48, 49 Intermediate moving part CC kinetic chain 50 seconds indicator 52 minute indicator 54 hour indicator

Claims

1. An oscillator (22) comprising the first and second balances, wherein each of the first and second balances is equipped with an inertia gear (24a, 24b) and a balance staff (34a, 34b), The vibrator (22) comprises at least one elastic member (32, 32a, 32b) for maintaining its vibration, and the vibrator (22) further comprises a gear train (40) having at least two movable parts (42, 44, 45, 46, 47, 48, 49), wherein the movable parts of the gear train are separate components from the inertia gears (24a, 24b) of the first balance wheel and the second balance wheel, respectively. The inertia gears (24a, 24b) of each balance are rotatably fixed to the movable parts (42, 44) of the gear train (40), A speed regulator (20) for a clock movement (10) is provided, wherein the gear train (40) is arranged so as to connect the inertia gears (24a, 24b) of the first balance wheel and the second balance wheel to each other by desmodromic coupling, so that the vibrations of the first balance wheel and the second balance wheel are in opposite phases, An escapement (15) comprising at least one escape wheel (16, 16a, 16b), wherein the escapement (15) further comprises at least one anchor (17, 17a, 17b) intended to control at least one escape wheel (16, 16a, 16b) and to maintain the vibration of the oscillator (22), the governor (20) further comprises the escapement (15), A speed regulator (20) for a clock movement (10).

2. A governor (20) according to claim 1, comprising at least three balance wheels, each balance wheel comprising an inertia gear (24a, 24b, 24c), wherein the phases of vibration of two balance wheels that follow each other in a kinetic chain (CC) of the at least three balance wheels are in opposite directions.

3. The governor (20) according to claim 1, wherein the gear train (40) comprises two or more movable parts (42, 44, 45, 46, 47, 48, 49).

4. The governor (20) according to claim 1, wherein the balance axes (34a, 34b) of the first balance and the second balance are coaxial.

5. The governor (20) according to claim 1, wherein the balance axes (34a, 34b) of the first balance and the second balance are parallel, and the respective inertia gears (24a, 24b) are arranged to vibrate in two parallel planes.

6. The governor (20) according to claim 1, wherein the inertia gears (24a, 24b) of the first and second balances are on the same plane.

7. The governor (20) according to claim 1, wherein the balance shafts (34a, 34b) of the first and second balances are contained within an intersecting plane.

8. The governor (20) according to claim 6, wherein the inertia gears (24a, 24b) of the first and second balances are provided with a plurality of unconnected edge pieces (28a, 28b), and these edge pieces are joined together to form the edges of each inertia gear (24a, 24b) along their respective circles (25a, 25b), and the circles intersect or overlap to define first and second circular discs (27a, 27b) that form overlapping area (29a) or intersection area (29b).

9. The speed governor (20) according to claim 8, wherein the overlapping area is in the shape of a lens (29a).

10. The governor (20) according to claim 8, wherein the intersection area is a straight line segment (29b).

11. The governor (20) according to claim 1, wherein at least one of the first and second valves does not have the at least one elastic member.

12. The governor (20) according to claim 1, wherein at least one elastic member (32) is attached to an intermediate movable part (45, 46, 47, 48, 49) of the gear train (40), and the inertia of the intermediate movable part (45, 46, 47, 48, 49) is at least five times smaller than the inertia of any of the aforementioned balances.

13. The governor (20) according to claim 1, wherein at least one of the first balance wheel and the second balance wheel, and one or both of the intermediate movable parts (45, 46, 47, 48, 49) of the gear train (40), are provided with an even number of elastic members wound in opposite directions.

14. The governor (20) according to claim 1, wherein the escapement (15) comprises only one anchor (17) provided to cooperate with one of the first balance wheel, the second balance wheel, and the escape wheel (16).

15. The escapement mechanism (15) On the one hand, in cooperation with the first tempo and the second tempo, On the other hand, a single escape wheel (16) or a first escape wheel and a second escape wheel (16a, 16b) cooperate in the same manner. The governor (20) according to claim 1, comprising two anchors (17a, 17b).

16. The escapement mechanism (15) A first half anchor (18a) is provided to cooperate with the first temp and is equipped with a first pallet (180a), A second half-anchor (18b) is provided to cooperate with the second temp, and is equipped with a second pallet (180b) Equipped with, The first half-anchor and the second half-anchor are arranged to cooperate with a single escape wheel (16), or The first half-anchor is provided to cooperate with the first escape wheel (16a), and the second half-anchor is provided to cooperate with the second escape wheel (16b). The governor (20) according to claim 1.

17. The governor (20) according to claim 1, wherein the escapement (15) comprises an anchor (17) provided to cooperate with one of the first balance wheel and the second balance wheel, and the anchor comprises a first pallet provided to cooperate with a first escape wheel (16a) and a second pallet provided to cooperate with a second escape wheel (16b).

18. The governor (20) according to claim 1, wherein the escapement (15) comprises an anchor (17) provided to cooperate with the intermediate movable parts (45, 46, 47, 48, 49) of the gear train (40) and the escape wheel (16).

19. A method for adjusting the vibration frequency of the oscillator (22) of the speed governor (20) according to claim 1, The inertia of all the balances (24a, 24b, 34a, 34b) of the vibrator (22) and the return torque of at least one of the elastic members (32, 32a, 32b) of the vibrator are determined. Then, at least one of the movable parts (42, 44, 45, 46, 47, 48, 49) of the gear train (40) is replaced with a movable part of a different inertia to obtain a ratio between the inertia of all the balances and the return torque of the at least one elastic member defined by the desired frequency of the vibrator (22). A method for adjusting the vibration frequency of the oscillator (22) of the speed governor (20).

20. A method for adjusting the vibration frequency of an oscillator (22) of a speed governor (20) according to claim 1, wherein the inertia of all the balances (24a, 24b, 34a, 34b) of the oscillator (22) and the return torque of at least one elastic member are determined. Then, by replacing at least one of the movable parts (42, 44, 45, 46, 47, 48, 49) of the gear train (40) with a movable part having a different pitch diameter from the movable part to be replaced, a ratio is obtained between the inertia of all the balances of the vibrator and the return torque of the at least one elastic member (32, 32a, 32b) defined by the desired frequency of the vibrator. A method for adjusting the vibration frequency of the oscillator (22) of the speed governor (20).

21. A method for setting a clock movement (10) comprising a drive source (14) and a speed regulator (20) as described in claim 1, The torque supplied from the drive source (14) to the escape wheels (16, 16a, 16b), the inertia of all the balances (24a, 24b, 34a, 34b), and the return torque of at least one elastic member (32, 32a, 32b) are determined. Then, by replacing at least one of the movable parts (42, 44, 45, 46, 47, 48, 49) of the gear train (40) with a movable part having either or both different inertia and different pitch diameters, A ratio defined between the inertia of all the aforementioned balances and the return torque of the at least one elastic member, The ratio defined between the power required to maintain the vibration of the vibrator (22) and the power available to the escape wheel is To obtain How to set the clock movement (10).

Images