Clock movement regulators

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 regulator for a timepiece movement. The invention also relates to a timepiece movement equipped with a regulator and to a device for indicating time equipped with such a movement. [Background technology]

[0002] Generally, mechanical watches include a watch movement that can vary the oscillator of the regulator between 3 Hz and 5 Hz. While this is common, the oscillator can be greater than 5 Hz to make the watch more accurate. Thus, a lower frequency regulator can offer several advantages, including increased power reserve and simplification of the watch movement.

[0003] Low frequency governors are known in the art.

[0004] For example, the escapement disclosed in US Pat. No. 5,399,633 has a reversing wheel arranged to impinge on the balance via a gear wheel in order to reduce the frequency of the balance so that it oscillates at a frequency of 0.5 Hz.

[0005] To maintain an acceptable quality factor for the low frequency regulator oscillator, the inertia of the balance must be increased compared to mechanical movements with higher frequency oscillators. This increase in inertia has the main disadvantage of increasing the sensitivity to angular accelerations. [Prior art documents] [Patent documents]

[0006] [Patent Document 1] Swiss Patent No. 75063 [Patent Document 2] European Patent Application Publication No. 2923242 Summary of the Invention [Problem to be solved by the invention]

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

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

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

[0010] These objects are achieved in particular by a governor for a timepiece movement. The governor comprises an oscillator with at least a first balance and a second balance. Each balance comprises an inertia gear and a balance stem. The oscillator comprises at least one elastic member for maintaining its oscillation. The oscillator further comprises a gear train with at least two moving parts. The inertia gear of each balance is rotatably fixed to a moving part of the gear train. The gear train is arranged to connect the inertia gears of the first and second balances to each other by a desmodromic connection, so that the respective oscillations of the first and second balances are in opposite phase. The governor further comprises an escapement, the escapement comprising at least one escape wheel and 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 balances with inertia gears, in a kinetic chain of at least three balances, the oscillations of each of the two balances being in phase opposition.

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

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

[0014] In one embodiment, the balance stems of the first and second balances are parallel, and the respective inertia gears are provided to oscillate in two parallel planes.

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

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

[0017] In one embodiment, each inertia gear of the first and second balances comprises a number of disconnected edge pieces, for example two, three or four edge pieces, which together define an edge of each inertia gear along a respective circle, which respectively define first and second disks that intersect or overlap to form an overlap or intersection area.

[0018] In one embodiment, the overlap area is in the shape of a lens, which is preferably a symmetric lens.

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

[0020] In an embodiment, at least one of the first balance and the second balance does not include the at least one elastic member described above.

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

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

[0023] In one embodiment, the escapement comprises only one pallet arranged to cooperate with one of the first and second balances and the escape wheel.

[0024] In one embodiment, the escapement comprises: On the one hand, to cooperate with the first balance and the second balance, On the other hand, it is adapted to cooperate with a single escape wheel or with a first escape wheel and a second escape wheel, respectively. It is equipped with two ankles.

[0025] In one embodiment, the escapement comprises: To cooperate with the first and second balances, respectively, or To cooperate with a single escape wheel or with first and second escape wheels, respectively It has two ankles.

[0026] In one embodiment, the escapement comprises a first and a second half pallet arranged to cooperate with the first and second balances, respectively. The first and the second half pallet each comprise a single escape wheel or a first and a second pallet arranged to cooperate with the first and the second escape wheels, respectively.

[0027] In one embodiment, the escapement comprises a pallet arranged to cooperate with one of the first balance and the second balance, the pallet comprising a first pallet arranged to cooperate with the first escape wheel and a second pallet arranged to cooperate with the second escape wheel.

[0028] In one embodiment, the escapement comprises an anchor arranged to cooperate with the intermediate moving part of the gear train and the escape wheel.

[0029] Another aspect of the invention relates to a method for setting the frequency of an oscillator of a speed governor, comprising first determining the inertias of all balances of the oscillator and the return torque of said at least one elastic member, the method further comprising, 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 inertias of all balances and the return torque of said at least one elastic member defined by the desired frequency of the oscillator.

[0030] Another aspect of the invention relates to a method for setting the frequency of a governor oscillator according to an alternative solution, which method comprises, firstly, determining the inertia of all the balances and the return torque of said at least one elastic member, which method also comprises, secondly, obtaining a ratio between the inertia of all the balances and the return torque of said 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, preferably an intermediate moving part, with a moving part having a pitch diameter different from the pitch diameter of the moving part replaced.

[0031] Another aspect of the invention relates to a method for setting a timepiece movement comprising a drive source, in particular a barrel, and a regulator, the method comprising first determining the torque provided by the drive source to the escape wheel, the inertia of all the balances of the oscillator and the return torque of at least one elastic member, the method further comprising, secondly, replacing at least one moving part of the gear train, preferably an intermediate moving part, with a moving part having a different inertia and / or a different pitch diameter, in order to obtain a defined ratio between the inertia of all the balances of the oscillator and the return torque of said at least one elastic member, and further comprising obtaining a defined ratio between the power maintaining the oscillation of the oscillator and the power available to the escape wheel.

[0032] Examples of embodiments of the invention are illustrated in the accompanying drawings and described in the description. [Brief description of the drawings]

[0033] [Figure 1] FIG. 1 is a schematic top view of a simplified watch movement according to one embodiment of the present invention. [Diagram 2] FIG. 2 is a perspective view of an oscillator with two hairspring balances, both driven by a desmodromic gear train according to an embodiment of the present invention. [Diagram 3] FIG. 3 is a top view of FIG. [Figure 4] FIG. 4 is a view similar to FIG. 3, but without the hairspring. [Diagram 5] FIG. 5 is a side view of FIG. [Figure 6] FIG. 6 is a perspective view showing a vibrator according to another embodiment of the present invention. [Figure 7] FIG. 7 is a top view of FIG. [Figure 8] FIG. 8 is a side view of FIG. [Figure 9] FIG. 9 is a perspective view of a governor with two hairspring balances driven together by a desmodromic gear train according to another embodiment of the invention. [Figure 10] FIG. 10 is a side view of FIG. [Figure 11] FIG. 11 is a schematic top view of a governor according to one embodiment. [Figure 12] FIG. 12 is a schematic top view of a governor according to another embodiment. [Figure 13] FIG. 13 is a schematic top view of a governor according to another embodiment. [Figure 14] FIG. 14 is a schematic top view of a governor according to another embodiment. [Figure 15] FIG. 15 is a schematic top view of a governor according to another embodiment. [Figure 16] FIG. 16 is a schematic top view of a governor according to another embodiment. [Figure 17] FIG. 17 is a schematic top view of a governor according to another embodiment. [Figure 18] FIG. 18 is a schematic top view of a governor according to another embodiment. [Figure 19]FIG. 19 is a schematic top view of a governor according to another embodiment. [Figure 20] FIG. 20 is a schematic top view of a governor according to another embodiment. [Figure 21] FIG. 21 is a schematic top view of a governor according to another embodiment. [Figure 22] FIG. 22 is a schematic top view of a governor according to another embodiment. [Diagram 23] FIG. 23 is a schematic top view of a governor according to another embodiment. [Figure 24] FIG. 24 is a schematic top view of a governor according to another embodiment. [Figure 25a] FIG. 25a is a top view of the escapement of the governor of FIG. 12 according to another embodiment. [Figure 25b] FIG. 25b is a top view of the escapement of the governor of FIG. 12 according to another embodiment. [Figure 25c] FIG. 25c is a top view of the escapement of the governor of FIG. 12 according to another embodiment. [Figure 25d] FIG. 25d shows the contact points between the pallets of one of the pallets in FIG. 25c and the escape wheel teeth. [Figure 26] FIG. 26 is a top view of the governor of FIG. [Figure 27] FIG. 27 is a schematic top view of a transducer according to another embodiment. [Figure 28] FIG. 28 is a schematic top view of an oscillator showing the overlap area between the two balances according to another embodiment. [Figure 29] FIG. 29 is a schematic top view of an oscillator showing the overlap area between the two balances according to another embodiment. [Diagram 30] FIG. 30 is a schematic diagram of an oscillator showing two crossing areas between the three balances according to another embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0034] In the present application, "oscillator" is to be understood to mean an oscillator comprising, on the one hand, a number of balances and, on the other hand, a gear train in which the balances are arranged to mesh with one another interdependently. In addition, in the present application, "governing mechanism" is to be understood to mean an assembly comprising an oscillator and a counter, in particular an escapement.

[0035] 1, the watch movement 10 has a simplified structure thanks to a low-frequency regulator with two hairspring balances 22a, 22b, described below, arranged to oscillate at a frequency below 1.5 Hz. Depending on the inertia of the balance chosen, 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 barrel 14, an escapement 15 with an escape wheel, and a kinematic linkage connecting the barrel 14 to the escape wheel pinion. The kinematic linkage comprises fewer than three moving parts.

[0037] In an advantageous embodiment, this kinematic linkage comprises only one moving part 19 which, on the one hand, meshes with the ratchet of the barrel 14 and, on the other hand, with the pinion of the escape wheel. As such, moving part 19 replaces the center wheel, the third wheel and the seconds hand of a conventional movement.

[0038] In a variant not shown, the kinematic connection comprises two or more intermeshing moving parts, one of which engages with a ratchet of the barrel and the other of which engages with a pinion of the escape wheel.

[0039] Simplified watch movements have the advantage that geometric constraints, such as center distance, are significantly different from traditional movements, providing a new design that will likely prove to be a unique product. Additionally, simplifying the movement allows for a reduction in the number of gears, improving overall efficiency.

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

[0041] Similarly, under certain conditions in conjunction with the gear ratio, the moving part 19 may directly display the minutes. To that end, the gear ratio of the barrel and the moving part 19 is selected such that the moving part 19 completes one rotation per hour. For example, a minute indicator 52 may be attached to the axis of the moving part 19.

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

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

[0044] In an advantageous embodiment shown in Figures 2 to 5, the oscillator 22 comprises a first balance spring 22a and a second balance spring 22b arranged in the same plane. Each balance spring 22a, 22b comprises an inertia gear 24a, 24b, a balance spring 32a, 32b and a balance stem 34a, 34b. The inertia gear comprises a rim 28a, 28b and a balance arm 26a, 26b connecting the rim to the balance stem. One end of each balance spring 32a, 32b is connected to the respective balance stem, for example by a collet 36a, 36b (Figure 5) driven by the balance spring, and the other end is connected to a balance attached to a bristles which are connected to a receiver or fixed cock (not shown) for the plate 12 of the watch movement 10.

[0045] The oscillator may comprise an elastic member other than a conventional flat hairspring, for example a cylindrical hairspring, a hemispherical or spherical hairspring, a conical hairspring. Alternatively, the spiral may comprise several turns. The oscillator may also comprise a non-hairspring-like elastic member in fulfilling the return function of the balance.

[0046] The first and second balance springs 22a, 22b of the oscillator 22 are connected by a gear train 40 in order to drive these balance springs by desmodromic coupling, such that the inertia gear 24a of one of the two balance springs 22a, 22b can oscillate in opposite phase with respect to the inertia gear 24b of the other of the two balance springs 22a, 22b. In other words, the balance spring 32a of one of the two balance springs 22a, 22b is in an expansion phase and the balance spring 32b of the other of the two balance springs 22a, 22b is in a contraction phase, which has the effect of driving the respective inertia gears 24a, 24b in opposite directions. This particular arrangement of the two hairsprings 32a, 32b makes it possible to cancel or at least reduce the sensitivity of the oscillator 22 to angular acceleration.

[0047] As can be seen particularly in Figures 4 and 5, the gear train 40 ensuring the desmodromic coupling between the two hairspring balances 22a, 22b comprises a first movable part 42 connected to the balance stem 34a of one of the two hairspring balances 22a, 22b, a second movable part 44 connected to the balance stem 34b of the other of the two hairspring balances 22a, 22b, and an intermediate movable part 46 meshing with the first movable part 42 and an intermediate movable part 48 meshing with the second movable part 44. The ratio and number of gears are determined so that the first inertia gears 24a and the second inertia gears 24b of each hairspring balance 22a, 22b can oscillate in opposite phases.

[0048] 2, the inertia gear 24a, 24b of each hairspring balance 22a, 22b includes four arms 26a, 26b spaced apart from one another by an angle of 90°. Each arm 26a, 26b extends radially from a respective balance arbor 34a, 34b to a distal portion 28a, 28b. Furthermore, the thickness of each arm 26a, 26b increases from the balance arbor to the corresponding distal portion.

[0049] The distal portions of the first inertia gear 24a and the second inertia tooth 24b respectively form four discontinuous edge pieces 28a, 28b along the first circle 25a and the second circle 25b as shown in Fig. 4. Each of the four discontinuous edge pieces 28a, 28b of each balance 22a, 22b extends along an arc between 20° and 50°, for example, and preferably between 30° and 40°.

[0050] In other variants, the inertia gear of each balance spring may have only two or three arms, in which case the edge pieces with each arm are larger and the inertia of each balance remains constant. For example, each discrete edge piece of the inertia gear may extend along an arc of more than 45° if each balance spring has three arms, or may extend along an arc of more than 60° if each balance spring has only two arms.

[0051] Weights 30a, 30b in the form of a screw are screwed, for example radially, into each of the edge pieces 28a, 28b so that the inertia of the inertia wheels 24a, 24b can be modified to adjust the frequency of the balance 24a, 24b of each hairspring.

[0052] The center distance between the balance arbores 34a, 34b of the two balances of the first and second balance springs 22a, 22b, respectively, is small to limit the variation of the effects of acceleration between the first and second inertia gears 24a, 24b. In this configuration, the first and second circles 25a, 25b with the discontinuous edge pieces 28a, 28b of the first and second inertia gears 24a, 24b, respectively, 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. The two inertia gears define two disks with an overlap area 29a resembling a symmetrical lens, as shown in FIG. 28. In another embodiment, shown in FIG. 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 overlap area 29a resembles an asymmetric lens.

[0053] When the governor 20 is in operation, the oscillators of the inertia gears 24a, 24b of the hairspring balances 22a, 22b are synchronized in opposite phase so that the edge piece 28a of the inertia gear 24a of one of the two hairspring balances 22a, 22b does not come into contact with the edge piece 28b of the inertia gear 24b of the other of the two hairspring balances 22a, 22b.

[0054] In another embodiment shown by Figures 6 to 8, the oscillator 22 comprises a first balance spring 22a and a second balance spring 22b mounted coaxially. The first and second balance springs 22a, 22b are connected to each other by a gear train 40 in such a way that the inertia gear 24a of one of the two balance springs 22a, 22b oscillates in opposite phase with respect to the inertia gear 24b of the other of the two balance springs 22a, 22b, thus cancelling or at least reducing the sensitivity of the oscillator 22 to angular accelerations. In another embodiment not shown, the first balance spring and the second balance spring are arranged such that the respective inertia gears oscillate in two parallel planes using balance arbors parallel to each other.

[0055] 8, the gear train 40 includes a first movable part 42 connected to the balance stem 34a of the first balance 22a of the hair spring, a second movable part 44 connected to the balance stem 34b of the second balance 22b of the second hair spring, and an intermediate gear train. The intermediate gear includes a third movable part 45 meshing with the first movable part 42, a fourth movable part 46 meshing with the second movable part 44, a fifth movable part 47 meshing with the fourth movable part 45, a lower movable part 48 and an upper movable part 49 attached coaxially to mesh with the fifth movable part 47 and the third movable part 45, respectively.

[0056] As in the first embodiment, the inertia gear 24a, 24b of each balance 22a, 22b comprises four arms 26a and four arms 26b spaced apart from one another by an angle of 90° and having the same characteristics as the arms of the balance of the governor spring illustrated in particular in Fig. 2. The number of arms may be other than four. Each inertia gear 24a, 24b may, for example, comprise only two or three arms, as described above.

[0057] In another embodiment shown by Fig. 9 and Fig. 10, the oscillator 22 comprises a first balance spring 22a and a second balance spring 22b mounted so that the balance stems of the respective balance springs move simultaneously. For example, the first and second balance stems of the balance springs form an angle between them substantially equal to 45° in Fig. 10, but this angle may be substantially different in alternative embodiments, for example between 30° and 60°. According to an embodiment shown in Fig. 30, the oscillator comprises three balances, each of which comprises an inertia gear 24a, 24b and 24c defining a disk. The balances are arranged such that the first and second disks intersect with the third disk along linear first and second intersection areas 29b.

[0058] The advantage of this embodiment lies in, in particular, the simplified gear train, since it comprises only two movable parts 42, 44 with suitable teeth, for example of conical shape, in direct meshing, so that the inertia gears 24a, 24b of the first and second balances 22a, 22b of the hairspring, respectively, can oscillate in opposite phases.

[0059] As in the first and second embodiments, the inertia gear 24a, 24b of each hairspring balance has four arms 26a, 26b spaced apart by an angle of 90° from each other, with the same characteristics as the arms of the two hairspring balance of the governor illustrated in particular in Figure 2. Each hairspring balance 24a, 24b (balance 22a, 22b, inertia gear 24a, 24b) may alternatively have only two or three arms, as already mentioned.

[0060] As in the first embodiment, when the oscillator 22 is operating, the vibrations of the inertia gear 24a of one of the two hair spring balances 22a, 22b are synchronized in opposite phase with respect to the vibrations of the other inertia gear 24b of the two hair spring balances 22a, 22b, so that the edge pieces 28a, 28b of the respective inertia gears 24a, 24b never come into contact with each other.

[0061] The governor 20 according to the invention can be implemented with different configurations of oscillator and escapement in the schematic diagrams 11 to 24 in order to transmit the frequency of the governor 20, preferably via a single moving part 19, to the kinematic linkage connecting the barrel 14 to the pinion of the escape wheel 16, in the schematic diagram of FIG. 1. The escapement may comprise one or more anchors, for example of the Swiss anchor type. Alternatively, the escapement may comprise other devices acting between the oscillator and the escapement, for example a detent escapement or a coaxial escapement. The term "anchor" is therefore used in the broad sense in this specification to mean any member intended to cooperate between the governor and the escapement.

[0062] According to the embodiment shown in Fig. 11, the governor 20 comprises an oscillator 22 with two hairspring balances 22a, 22b, for example the oscillator 22 shown in Fig. 2. The first inertia gear 24a and the second inertia gear 24b are arranged to oscillate in antiphase. The escapement has a single escapement pallet 17, for example a Swiss pallet.

[0063] The pallet fork 17 comprises an inlet pawl 170 and an outlet pawl 172 arranged to cooperate with the escape wheel 16 in a conventional manner in order to transmit the oscillations of the inertia gear 24a of the single hairspring balance 22a of the governor 20 to the escape wheel 16 so that the rotation of the escape wheel 16 occurs at the speed of oscillation of the inertia gear 24a. For this purpose, the pallet fork 17 comprises a fork 179 arranged to cooperate with an impulse pin of the balance.

[0064] One inertia gear 24a of the hairspring balance is connected to the other inertia gear 24b of the hairspring balance by a gear train having an even number of gears 42, 44, 46, 48 so as to reverse the direction of rotation of the balances.

[0065] The hairspring balances 22a, 22b are provided with hairsprings 32a, 32b wound in the same direction such that, during the operation of the movement, one of the hairsprings is in a contraction phase while the other of the hairsprings is in an expansion phase, i.e. in opposite phases.

[0066] With reference to the embodiment of FIG. 12 and to the different embodiments illustrated in FIGS. 25a to 25d, the governor 20 has a structure equivalent to that of FIG. 11, with the difference that the first and second balances 22a, 22b of the hairspring cooperate respectively with first and second pallet forks 17a, 17a which cooperate with the same escape wheel 16.

[0067] 25a in particular, the first escapement pallet fork 17a has an inset pawl 170a and an exit pawl 172a arranged to cooperate with the teeth of the escape wheel 16, while the second escapement pallet fork 17b has an inset pawl 170b and an exit pawl 172b arranged to cooperate with the teeth of the escape wheel 16 alternately with the first escapement pallet fork 17a. The first escapement pallet fork 17a and the second escapement pallet fork 17b are arranged so that the inset pawl and the exit pawl of each pallet can cooperate with different teeth.

[0068] In this arrangement, the recessed pawl 170a of the first escapement pallet 17a and the exit pawl 172b of the second escapement pallet 17b are spaced apart so as to cooperate with teeth of the escape wheel 16 that are separated by an angle of less than 180° when passing through the center of the escape wheel 16, while the exit pawl 172a of the first escapement pallet 17a faces the recessed pawl 170b of the second escapement pallet 17b. Thus, the escape wheel 16 has at least 20 teeth, and each pallet fork 179a, 179b is arranged to cooperate with an impulse pin 35a of the roller 35 of the balance of the corresponding hairspring balance 22a, 22b. Under certain conditions, escape wheels with fewer than 20 teeth, for example 15 teeth, may also be used.

[0069] The counter rotation of the inertia gears 24a, 24b (FIG. 12) described above causes the pallets 17a, 17b to operate symmetrically. FIG. 25a shows one tooth of the escape wheel 16 on the mounting surface 176 of the inset pallet 170a of the first pallet 17a and one tooth of the escape wheel 16 on the mounting surface 176 of the outset pallet 172b of the second pallet 17b. The angle between the mounting surface 176 of the inset pallet 170a and the outset pallet 172b of the first pallet 17a and the second pallet 17b, the mounting surface 176 of the inset pallet 170a and the outset pallet 172b with the first and second teeth of the escape wheel 16, and the center of the escape wheel 16 is less than 180°, and preferably between 130° and 160°. The operating principle of the escapement 15 of FIG. 25a must be set so that the operating steps of the pallets occur simultaneously.

[0070] In the embodiment shown in FIG. 25b, the collision surfaces of the protruding claws 172a of the first ankle 17a and the protruding claws 172b of the second ankle 17b are eliminated, and the distal portions of the protruding claws 172a of the first ankle 17a and the protruding claws 172b of the second ankle 17b form an angle of approximately 90° with the mounting surface 176 of the pallet.

[0071] This particular shape of the distal part of the aforementioned pallet has the advantage of avoiding the constraints imposed by the first and second pallet operating steps, which must be carried out simultaneously according to the embodiment shown in Fig. 25a, thus simplifying the setting of the escapement 15. The pallet is nevertheless sized so that the pulling function is fulfilled.

[0072] The dimensions of the pallet are designed so that the escapement teeth rest firmly on the remaining flat surface of the notched pallet, preventing the pallet from moving in a conventional manner, and the release phase of this pallet is not longer than that of the other pallet without a notch, in order to avoid energy losses during impulse. This construction has the advantage that it facilitates automatic start-up of the escapement 15.

[0073] In the embodiment shown in Fig. 25c, the escapement adopts the operating principle described in the patent application WO 2005 / 023363, the contents of which are incorporated herein by reference. This avoids the over-rest of the escapement 15 according to Fig. 25a and the residual sensitivity of the adjustment of the escapement according to Fig. 25b. In this form, in order for the escapement to work properly, the support of the teeth on the inset or outset of the escapement anchor must be positioned very accurately with respect to the edge of the rest surface of the inset and outset of the escapement. This ensures that the release and impulse stages of the escapement work properly.

[0074] Considering manufacturing tolerances, escapements with conventional anchors generally require final adjustment of the position of the inset and outset lugs, which is generally long and delicate, since it has a large effect on the efficiency of the escapement.

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

[0076] In this case (FIG. 25d), each tooth of the escape wheel 16 has a drive surface 182 (FIG. 25d), and through the drive surface 182, a torque is generated by contact between the recessed tines 170a, 170b and the projecting tines 172a, 172b of each pallet fork 17a, 17b and the escape wheel, which acts to reduce the angle between the pallet and the reference axes V1, V2 connecting the axis of each pallet fork 17a, 17b and the balance for the first pallet fork 17a and the second pallet fork 17b, via the drive surface 182. In other words, in this embodiment, a drive surface is provided that generates a torque that moves the pallet toward the equilibrium position, and therefore a drive surface that allows the pallet to naturally reach the equilibrium position is provided.

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

[0078] The governor 20 according to the embodiment of FIG. 13 has a structure similar to that of FIG. 12, but differs in that one of the balance wheels is devoid of 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 hairspring balance 22b. The inertia gear 24a is thus driven by a desmodromic mechanism and oscillates in synchronism with the oscillations of the hairspring balance 22b, but in the opposite direction. The hairspring balance 22b may be equipped with a single hairspring or, in a variant not shown but similar to FIG. 14, with a pair of hairsprings wound in opposite directions to obtain the opposite phases.

[0079] In the embodiment of FIG. 14, only one of the balances of the oscillator 22 is arranged to cooperate with the escape wheel 16. This balance does not have a hairspring and its inertia gear 24a is connected to a first movable part 42. As in the governor of FIG. 13, the first movable part 42 is meshed with a gear train comprising two intermediate movable parts 46, 48 and a second movable part 44 connected to the hairspring balance 22b. The inertia gear 24a oscillates at the speed of oscillation of the hairspring balance 22b, but in the opposite direction, by means of a desmodromic connection. The hairspring balance 22b comprises, for its part, a single hairspring or preferably two hairsprings 32a, 32b, mounted coaxially and wound in opposite directions so as to be in phase with each other.

[0080] In the embodiment of FIG. 15, the oscillator 22 of the governor 20 comprises, namely, two hairspring balances 22a, 22b and one hairspringless balance. The latter has an inertia gear 24c connected to a moving part 43 of the gear train and is arranged to cooperate with the escape wheel 16 via the pallet fork 17. The two hairspring balances 22a, 22b are arranged on either side of the hairspringless balance, at the ends of the kinetic chain CC of the desmodromic coupling of the oscillator 22. In the example shown, the inertia gears 24a, 24b rotate in the same direction, thanks to the odd number of moving parts 43, 46, 47, 48, 49 of the gear train connecting the two hairspring balances 24a, 24b. The balance spring 32a of the balance spring 22a is therefore wound in the opposite direction to the balance spring 32b of the balance spring 22b, resulting in opposite phases. Generally, in a kinetic chain CC of a governor with at least three balances, the oscillations of two successive balances are of opposite phases.

[0081] In the embodiment of FIG. 16, the oscillator 22 of the governor 20 also comprises three balances, namely a central balance 22c arranged to cooperate with the escape wheel 16 and two balances without a hairspring, one on each side of the central balance. The latter comprises two hairsprings 32a, 34 mounted on the same axis and wound in opposite directions to obtain the phase difference. In a variant not shown, the central balance may have only one hairspring. The oscillations of the inertia gears 24a, 24b located on either side of the central balance 22c are generated at the oscillation speed of the central balance by means of a gear train.

[0082] With reference to the embodiment of FIG. 17 and to FIG. 26, the first and second balances 22a, 22b of the balance spring of the governor 20 cooperate with the first and second half pallets 18a, 18b of the escapement, respectively, which cooperate with the same escape wheel 16. In this case, the first pallet 18a has an inset pallet 180a, and the second pallet 18b has an exit pallet 180b. By making two half pallets in this way, the movement of the pallets 15 is separated, each of which is associated with an impulse pin of the balance arbor. In this case, the impulses are distributed between the balances 22a, 22b of the first and second balance spring of the oscillator 22. The balance springs 32a, 32b of the balance springs 22a, 22b, respectively, are wound in the same direction to obtain opposite phases. In a variant not shown, one balance has no hair spring and the other has a pair of hair springs mounted in diametrically opposite phase.

[0083] According to the embodiment of Figs. 18 and 19, the speed governor 20 has a structure similar to that of Fig. 17, in which the first balance 22a and the second balance 22b of the hairspring are connected via the first pallet fork 17a and the second pallet fork 17b, but via the first anchor 17a and the second anchor 17b according to the governor 20 of FIG. 18, or According to the governor of FIG. 19, through the first and second half anchors 18a, 18b, It differs in that the first and second balances 22a and 22b of the hairspring cooperate with the first and second escape wheels 16a and 16b, respectively. To obtain the opposite phases, the hairsprings 32a, 32b of the hairspring balance are also wound in the same direction. According to a variant not shown, one balance has no hairspring and the other has a pair of hairsprings mounted in opposite phase.

[0084] In the embodiment of Fig. 20, the oscillator 22 of the governor 20 comprises a balance with a hairspring 22a and a balance without a hairspring. The governor comprises an escapement including, on the one hand, a first escape wheel 16a and a second escape wheel 16b arranged to be driven in rotation in opposite directions, and, on the other hand, an anchor 17 arranged to cooperate with the balance without a hairspring and the two escape wheels. The balance with a hairspring 22a preferably comprises two hairsprings mounted in diametrically opposed phases. In a variant not shown, each balance comprises a hairspring.

[0085] Two other embodiments of the governor are depicted in Figs. 21 and 22. The first and second balances of the oscillator 22 are mounted in diametrically opposite phase and have no hairspring. They therefore only comprise inertia gears 24a, 24b. The hairspring 32 is mounted in the moving part 48 of the gear train of the oscillator 22. The arrangement of this hairspring in the centre of the gear train has the advantage of reducing the return effect compared to a hairspring at one end of the oscillator chain. The inertia gears 24a, 24b therefore preferably have no hairspring. According to this embodiment, the inertia of the moving part 48 is at least 5 times, preferably at least 10 times or at least 20 times smaller than the inertia of either balance.

[0086] With reference to FIG. 22, there is a gear train arranged to impart reciprocating motion to the movable part 48, which cooperates with the anchor 17, for example by means of a pin (not shown) connected to the movable part 48.

[0087] The moving part 48 can be larger or smaller than the moving parts 42, 44 connected to the first and second balances 22a, 22b, respectively, which allows a larger dimensional range of the balance coupling and amplitude of the hairspring (the latter can be adapted to the ideal operation of the escapement, while the latter to their inertia). In the governor of Fig. 22, the pitch diameter of the moving part 48 is larger than the pitch diameter of the moving parts 42, 44 of the first and second balances 22a, 22b, respectively.

[0088] Another example of a governor is diagrammatically depicted in Figure 23. This governor is similar to the one in Figure 22, with the difference that the hairspring 32 is attached to a moving part 48 of the gear train having a pitch diameter smaller than the pitch diameters of the moving parts 42, 44 of the first and second balances 24a, 24b, respectively.

[0089] In another embodiment, depicted diagrammatically in Figure 24, a movable part 48 of the gear train is arranged to cooperate with the pallet 17, for example by means of a pin (not shown) connected to the movable part 48, while the governor comprises two hairspring balances 22a, 22b arranged in diametrically opposed phases. The pin is moved by a reciprocating motion when the governor operates to regulate the rotation of the escape wheel 16 and thus maintain the oscillations of the first and second balances.

[0090] According to the embodiments depicted in Figures 12, 13 and 21, in particular to optimise the compensation of play and / or the contact with the pallets, the escape wheel 16 can be replaced by two coaxial escape wheels connected to each other or movable relative to each other.

[0091] According to another embodiment, which is shown diagrammatically in Fig. 27, the oscillator of the speed governor comprises four inertia gears 24a, 24b, 24c, 24d. Each inertia gear 24a, 24b, 24c, 24d is similar to the inertia gear of the speed governor according to the embodiment shown in particular in Figs. 2 to 4. The distal part of each inertia gear forms a plurality of discontinuous edge pieces, for example consisting of three or four pieces, along the first, second, third and fourth circles, respectively. The distance between the centers of the four balance shafts is made small so that each circle intersects another circle of the four circles. The four inertia gears 24a, 24b, 24c, 24d are interconnected by a gear train (not shown) adapted so that the two inertia gears 24a, 24c oscillate in the same phase and in opposite phase with respect to the other two inertia gears 24b, 24d. The four inertia gears 24a, 24b, 24c, 24d are preferably arranged to oscillate in the same plane.

[0092] The governor according to the invention allows the involvement of several moving parts of the gear train between the balance, the hairspring and the escape wheel, which in conventional governors are directly connected. The dimensions of each moving part determine their coupling. These dimensions make it possible to implement new methods of adjustment between the items described below. - the return torque of at least one hairspring and the inertia of the balance, while keeping constant the power required for the oscillation of the oscillator, - the power required to control the oscillator and the power transmitted by at least one escape wheel.

[0093] These adjustment methods can have the advantage, inter alia, that they allow compensation for: - variations in the mass production of components (variations in the torque of the hairspring or the inertia of the balance within a production batch), - variations in the torque delivered by the drive mechanism of a movement equipped with such a regulator, - Variations due to the use of additional functions of the mechanism of such a regulator (the same basic movement can power several calibres with different additional functions but assuming the same regulator; its power is optimized depending on the use of these additional functions).

[0094] Adjustment by these methods may be complementary to other conventional adjustments, in particular adjustments using screws or eccentrics attached to the balance, or adjustments using graduated assemblies.

[0095] By varying the geometric characteristics (pitch diameter and / or inertia) of at least one of the moving parts of the gear train, in particular the moving parts 42, 43, 44, 45, 46, 47, 48, 49 of gear train 40, it is possible to vary the combination between the return torque of at least one hairspring and the inertia of the balance, while keeping unchanged the power required to maintain the oscillation of the oscillator.

[0096] To this end, the method comprises the following steps: - determining the inertia of all the balances of the oscillator, - Determine the return torque of the vibrator's elastic member, - whether it involves moving parts with large or small inertia, or large or small nominal diameter, compare said values ​​with the theoretical values ​​to indicate the target performance and determine the corrections that should be made to achieve the target performance; - Replace the default moving parts with the moving parts determined in the previous step, - optionally, measuring governor performance; - Optionally, if further refinement or improvement of the combination is required, the method is carried out again from the beginning.

[0097] Although the inertia of the moving parts of the gear train is much smaller than that of the balance (the moving parts do not have sufficient inertia to maintain oscillations, i.e. they cannot be treated as equivalent to the balance), a change in this inertia nevertheless slightly alters the relationship between the inertia of the balance and the return torque of the hairspring, altering the period of oscillation and therefore the behavior of a watch movement equipped with such a regulator.

[0098] The inertia of the moving parts of the gear train can be modified in various ways, in particular 1) Changing materials to achieve different densities and therefore inertias for the same dimensions; 2) Varying thickness to achieve different inertias with the same pitch diameter (or profile), or 3) Using a perforated moving part to change the effective mass while keeping the same overall dimensions can be changed by

[0099] By changing the pitch diameter of one of the moving parts, especially the one with the hairspring, the ratio between the moment of inertia of the hairspring and the return torque is changed. Changing the pitch diameter of a gear generally involves changing the number of teeth with the same module. However, there are other means of fine adjustment, such as offset fine adjustment, which consists in changing the pitch diameter with the same number of teeth and thus changing the relationship between the meshing moving parts.

[0100] Since the energy available to the escape wheel can change upstream (notably due to the torque generated by the barrel spring, which can vary during production, but also in more specific cases, such as additional openings in the moving part (skeleton), or when driving additional modules with different (energy) consumption levels), a modification of these combinations is also possible in order to adapt the characteristics of the governor to the amount of energy available to the escape wheel.

[0101] This involves the following steps: - determining the torque supplied by a drive source to one or more escape wheels, - Determines the effective inertia of the governor-equipped balance, - Determining the return torque of an elastic member equipped with a governor; - comparing these values ​​with theoretical values ​​to indicate the target performance and to determine the corrections required to achieve the target (corrections to the inertia of a gear can be made together with corrections to the nominal diameter of the same moving part or of another moving part of the gear train, in order to maintain the equilibrium of the hairspring balance); - Replace the default moving parts with the moving parts determined in the previous step, - optionally, measuring governor performance; - Optionally, if further refinement or improvement of the combination is required, the method is carried out again from the beginning.

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

[0103] Finally, when using moving parts with different pitch diameters, it is clear that the positioning of the supports (escape wheel holders, cock plates or other) and guide means (bearings, ball bearings, etc.) of those moving parts must be configured so that their relative spacing can accommodate the change in center distance caused by the combination. These means of adjusting the center distance are well known in the prior art, for example as disclosed in Patent Document 1.

[0104] In particular, guide means may be attached to the intermediate support which allow this adjustment, although other means are conceivable without departing from the scope of the invention. [Explanation of symbols]

[0105] 10. Clock Movement 12 boards 14 Incense box 15 Escapement 16 Escape wheel, 16a, 16b First escape wheel, second escape wheel Transmission device 17a, 17b Escapement anchor 170, 172 Palette (with protruding claws, with protruding claws) 170a, 172a In-claw 170b, 172b Dezume 174 Collision surface 176 Placement surface 178 Distal 182 Drive surface 179 Fork 18a 1st half ankle 180a Inlet nail 18b 2nd half ankle 180b Dezume 20 Governor 22 Transducer 22a, 22b Hairspring balance 24a, 24b, 24c, 24d Inertia gear 25a, 25b 1st and 2nd Circles 26a, 26b Balance arm 28a, 28b edge piece 29a, 29b Intersection Area 30a, 30b weight 32, 32a, 32b Hairspring 34a, 34b Tenshin 35 Roller 35a Impact pin 36a, 36b Collet 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) including at least a first balance and a second balance, each of which includes an inertia gear (24a, 24b) and a balance stem (34a, 34b), The oscillator (22) comprises at least one elastic member (32, 32a, 32b) for maintaining its oscillation, and the oscillator (22) further comprises a gear train (40) having 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 movable part (42, 44) of the gear train (40), A governor (20) for a timepiece movement (10) including the oscillator (22), in which the gear train (40) is provided to connect the inertia gears (24a, 24b) of the first balance and the second balance to each other by a desmodromic connection, so that the oscillations of the first balance and the second balance are in opposite phases, the governor (20) further comprises an escapement (15) with at least one escape wheel (16, 16a, 16b), the escapement (15) comprising at least one anchor (17, 17a, 17b) intended to control the at least one escape wheel (16, 16a, 16b) and to maintain the oscillation of the oscillator (22); A regulator (20) for a clock movement (10).

2. 2. The governor (20) according to claim 1, comprising at least three balances, each of which comprises an inertia gear (24a, 24b, 24c), and wherein the phases of oscillation of each of two balances which follow each other in a kinematic chain (CC) of the at least three balances are opposite to each other.

3. 3. The governor (20) according to claim 1 or 2, wherein the gear train (40) comprises more than two moving parts (42, 44, 45, 46, 47, 48, 49).

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

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

6. 4. The governor (20) according to claim 1, wherein the inertia gears (24a, 24b) of the first balance and the second balance are substantially coplanar.

7. 4. The speed governor (20) according to claim 1, wherein the balance stems (34a, 34b) of the first and second balances are contained within intersecting planes.

8. 8. A governor (20) according to claim 6 or 7, wherein the inertia gears (24a, 24b) of the first and second balance wheels have a plurality of unconnected edge pieces (28a, 28b), for example two, three or four edge pieces, which together define an edge of each inertia gear (24a, 24b) along a respective circle (25a, 25b) which intersect or overlap to define, respectively, first and second disks (27a, 27b) forming an overlap area (29a) or an intersection area (29b).

9. 9. The governor (20) of claim 8, wherein the overlap area is in the shape of a lens (29a), said lens being preferably a symmetrical lens.

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

11. 11. The speed governor (20) according to any one of claims 1 to 10, wherein at least one of the first balance and the second balance does not include the at least one elastic member.

12. 12. The governor (20) according to any one of claims 1 to 11, wherein the at least one elastic member (32) is attached to an intermediate moving part (45, 46, 47, 48, 49) of the gear train (40), the inertia of which is at least 5 times, preferably at least 10 times or at least 20 times smaller than the inertia of any of the balances.

13. 13. The governor (20) according to any one of claims 1 to 12, wherein at least one of the first balance and the second balance and / or the intermediate movable part (45, 46, 47, 48, 49) of the gear train (40) is provided with an even number of elastic members, preferably two, wound in opposite directions.

14. 14. The governor (20) according to any one of claims 1 to 13, wherein the escapement (15) comprises only one anchor (17) arranged to cooperate with one of the first and second balances and the escape wheel (16).

15. The escapement (15) On the one hand, to cooperate with the first balance and the second balance, On the other hand, to cooperate with a single escape wheel (16) or with a first escape wheel and a second escape wheel (16a, 16b), respectively. The speed governor (20) according to any one of claims 1 to 13, comprising two anchors (17a, 17b) provided thereon.

16. The escapement (15) 14. The speed governor (20) according to any one of claims 1 to 13, comprising a first half pallet (18a, 18b) arranged to cooperate with the first balance and the second balance, respectively, and the first half pallet (18a, 18b) each comprises a single escape wheel (16) or a first pallet (180a) and a second pallet (180b) arranged to cooperate with a first escape wheel (16a, 16b), respectively.

17. 14. The governor (20) according to any one of claims 1 to 13, wherein the escapement (15) comprises an anchor (17) arranged to cooperate with one of the first balance and the second balance, the anchor comprising a first pallet arranged to cooperate with a first escape wheel (16a) and a second pallet arranged to cooperate with a second escape wheel (16b).

18. 14. The governor (20) according to any one of claims 1 to 13, wherein the escapement (15) comprises an anchor (17) arranged to cooperate with an intermediate moving part (45, 46, 47, 48, 49) of the gear train (40) and with an escape wheel (16).

19. A method for adjusting the frequency of the oscillator (22) of a governor (20) according to any one of claims 1 to 18, comprising the steps of: determining the inertia of all balances (24a, 24b, 34a, 34b) of the oscillator (22) and the return torque of the at least one elastic member (32, 32a, 32b) of the oscillator; then replacing at least one of the moving parts (42, 44, 45, 46, 47, 48, 49) of the gear train (40), preferably the intermediate moving part (45, 46, 47, 48, 49), with a moving part of 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 frequency of the oscillator (22) of the governor (20).

20. A method for adjusting the frequency of an oscillator (22) of a governor (20) according to any one of claims 1 to 18, comprising the steps of: determining the inertia of all balances (24a, 24b, 34a, 34b) of the oscillator (22) and the return torque of the at least one elastic member (32, 32a, 32b); then replacing at least one of the moving parts (42, 44, 45, 46, 47, 48, 49) of the gear train (40), preferably the intermediate moving part (45, 46, 47, 48, 49), with a moving part having a pitch diameter different from the pitch diameter of the moving part replaced, thereby obtaining 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 frequency of the oscillator (22) of the governor (20).

21. A method for setting a timepiece movement (10) comprising a drive source (14), in particular a barrel, and a governor (20) according to any one of claims 1 to 17, comprising the steps of: determining a torque supplied from the driving source (14) to the escape wheel (16, 16a, 16b), the inertia of all the balances (24a, 24b, 34a, 34b), and a return torque of the at least one elastic member (32, 32a, 32b); Then, by replacing at least one of the moving parts (42, 44, 45, 46, 47, 48, 49) of the gear train (40), preferably the intermediate moving part (45, 46, 47, 48, 49), with a moving part having a different inertia and / or a different pitch diameter, a ratio defined between the inertia of all of the balances and the return torque of the at least one elastic member; a ratio defined between the power that maintains the oscillation of the oscillator (22) and the power available to the escape wheel; get How to set a watch movement (10).

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