Regulating device for a timepiece movement

Abstract

The invention relates to a regulating organ (20) for a clock movement (10). The regulating organ (20) comprises an oscillator (22) having at least one first and one second balance wheel. Each balance wheel has a flywheel (24a, 24b) and a balance staff (34a, 34b). The oscillator (22) has at least one elastic element (32, 32a, 32b) for maintaining the oscillations of the oscillator. The oscillator further comprises a gear train (40) having at least two moving parts (42, 44, 45, 46, 47, 48, 49). The flywheel (24a, 24b) of each balance wheel is rotationally fixed to one moving part of the gear train (40). The gear train (40) is arranged to connect the flywheels (24a, 24b) of the first and second balance wheels by a desmodromic link so that the respective oscillations of the first and second balance wheels are in opposite phase.The regulating member (20) further comprises an escapement (15) including at least one escape wheel (16, 16a, 16b) and at least one anchor (17, 17a, 17b) for regulating said at least one escape wheel (16, 16a, 16b) and for maintaining the oscillations of the oscillator (22). The invention also relates to a method for adjusting the frequency of the oscillator (22) of the regulating member (20).

Description

Domaine technique

[0001] The present invention relates to a regulating organ for a watch movement. The invention also relates to a watch movement comprising the regulating organ and a timepiece comprising such a movement. Etat de la technique

[0002] Typically, mechanical watches feature a watch movement with a regulating organ oscillation frequency ranging from 3Hz to 5Hz. However, this oscillation frequency can go beyond 5Hz to increase the watch's accuracy. However, a low-frequency regulating organ can provide several benefits, including an increase in power reserve and a simplification of the watch movement.

[0003] Low frequency regulating organs are already known from the state of the art.

[0004] For example, CH75063 discloses an escapement having a reversing wheel arranged to impart the impulse to the balance wheel via a gear in order to reduce the number of oscillations of the balance wheel so that the latter oscillates at a frequency of 0.5 Hz.

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

[0006] Document US1232285 describes an escapement comprising two balance wheels and an escape wheel.

[0007] An aim of the present invention is therefore to propose a regulating member canceling or, at least, reducing the sensitivity to angular accelerations.

[0008] Another object of the present invention is to propose a simplified watch movement comprising a low-frequency regulating organ.

[0009] An additional object of the present invention is to provide a method for adjusting the frequency of the oscillator of the regulating member. Bref résumé de l'invention

[0010] These aims are achieved in particular by a regulating organ for a watch movement. The regulating organ comprises an oscillator comprising at least a first and a second balance wheel. Each balance wheel comprises a flywheel and a balance staff. The oscillator comprises at least one elastic member intended to maintain its oscillations. This oscillator further comprises a gear train comprising at least two wheels. The flywheel of each balance wheel is rotationally fixed to a wheel of the gear train. The gear train is arranged to connect the flywheels of the first and second balance wheels together by a desmodromic connection so that the respective oscillations of the first and second balance wheels are in phase opposition.The regulating organ further comprises an escapement comprising at least one escapement wheel and at least one anchor intended to regulate said at least one escapement wheel and to maintain the oscillations of the oscillator.

[0011] According to one embodiment, the regulating member comprises at least three balances each comprising a flywheel. The respective oscillations of two balances following one another in the kinematic chain of the at least three balances are in phase opposition.

[0012] According to one embodiment, the gear train comprises more than two mobiles.

[0013] According to one embodiment, the balance shafts of the first and second balances are coaxial.

[0014] According to one embodiment, the balance axes of the first and second balances are parallel while their respective flywheels are arranged to oscillate in two parallel planes.

[0015] According to one embodiment, the flywheels of the first and second balance wheels are substantially included in the same plane.

[0016] According to one embodiment, the balance axes of the first and second balances are contained in intersecting planes.

[0017] According to one embodiment, the flywheel of each of the first and second balance wheels comprises a plurality of disjointed rim segments, for example two, three, or even four rim segments, together forming the rim of each flywheel along respective circles. These circles respectively define a first and a second disc intersecting or intersecting each other in order to form an overlapping zone or an intersection zone.

[0018] According to one embodiment, the intersection zone has the shape of a lens. This lens is preferably a symmetrical lens.

[0019] According to one embodiment, the intersection zone is a straight line segment.

[0020] According to one embodiment, at least one of the first and second balances does not comprise said at least one elastic member.

[0021] According to one embodiment, at least one elastic member is mounted on an intermediate wheel of the gear train. The inertia of the intermediate wheel is at least five times, preferably at least ten times, or even at least twenty times less than the inertia of any of the balance wheels of the oscillator.

[0022] According to one embodiment, at least one of the first and second balances and / or an intermediate wheel of the gear train comprises an even number, preferably two, of elastic members wound in opposite directions.

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

[0024] According to one embodiment, the escapement comprises two anchors arranged to cooperate, on the one hand, with the first and second balance wheels respectively and, on the other hand, with a single escape wheel, or with a first and a second escape wheel respectively.

[0025] According to one embodiment, the escapement comprises a first and a second half-anchor arranged to cooperate with the first and second balance wheels respectively. The first and second half-anchors respectively comprise a first pallet and a second pallet arranged to cooperate with a single escapement wheel set or with a first and a second escapement wheel set respectively.

[0026] According to one embodiment, the escapement comprises an anchor arranged to cooperate with one of the first and second balances. The anchor comprises a first pallet arranged to cooperate with a first escapement wheel and a second pallet arranged to cooperate with a second escapement wheel.

[0027] According to one embodiment, the escapement comprises an anchor arranged to cooperate with an intermediate wheel of the gear train and an escape wheel.

[0028] Another aspect of the invention relates to a method for adjusting the frequency of the oscillator of the regulating member. The method consists in determining, in a first step, the inertia of the set of balances and the restoring torque of said at least one elastic member of the oscillator. This method further consists, in a second step, in replacing at least one of the mobiles of the gear train, preferably an intermediate mobile, by a mobile of different inertia so as to obtain a ratio between the inertia of the set of balances and the restoring torque of said at least one elastic member defined by the desired frequency of the oscillator.

[0029] Another aspect of the invention relates to a method for adjusting the frequency of the oscillator of the regulating member according to an alternative solution. According to this alternative, the method consists in determining, in a first step, the inertia of the set of balances and the return torque of said at least one elastic member. This method further consists, in a second step, in replacing at least some of the mobiles of the gear train, preferably an intermediate mobile, with a mobile with a primitive diameter different from the replaced mobile so as to obtain a ratio between the inertia of the set of 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 adjusting a watch movement comprising a driving source, in particular a barrel, and the regulating member. The method consists in determining, in a first step, the torque supplied by the driving source to the escape wheel, the inertia of all the balance wheels of the oscillator and the return torque of said at least one balance spring. This method further consists in replacing, in a second step, at least one wheel of the gear train, preferably an intermediate wheel, with a wheel of different inertia and / or different primitive diameter so as to obtain a defined ratio between the inertia of all the balance wheels of the oscillator and the return torque of said at least one elastic member as well as a defined ratio between the power for maintaining the oscillations of the oscillator and the power available to the escape wheel. Brève description des figures

[0031] Examples of implementation of the invention are described in the description illustrated by the appended figures in which: there figure 1 is a schematic top view of a simplified watch movement according to one embodiment of the invention; the figure 2 illustrates a perspective view of an oscillator comprising two sprung balances driven together by a desmodromic gear train according to one embodiment of the invention; figure 3 illustrates a top view of the figure 2 ; there figure 4 illustrates a view similar to the figure 3 without the representation of the spirals; the figure 5 illustrates a side view of the figure 2 , there figure 6 illustrates a perspective view of an oscillator according to another embodiment of the invention; the figure 7 illustrates a top view of the figure 6 ; there figure 8 illustrates a side view of the figure 6 ; there figure 9 illustrates a perspective view of the regulating organ comprising two sprung balances driven together by a desmodromic gear train according to another embodiment of the invention, the figure 10 illustrates a side view of the figure 9 , there figure 11 is a schematic top view of a regulating member according to one embodiment, the figure 12 is a schematic top view of a regulating member according to another embodiment, the figure 13 is a schematic top view of a regulating member according to another embodiment, the figure 14 is a schematic top view of a regulating member according to another embodiment, the figure 15 is a schematic top view of a regulating member according to another embodiment, the figure 16 is a schematic top view of a regulating member according to another embodiment, the figure 17 is a schematic top view of a regulating member according to another embodiment, the figure 18 is a schematic top view of a regulating member according to another embodiment, the figure 19 is a schematic top view of a regulating member according to another embodiment, the figure 20 is a schematic top view of a regulating member according to another embodiment, the figure 21 is a schematic top view of a regulating member according to another embodiment, the figure 22 is a schematic top view of a regulating member according to another embodiment, the figure 23 is a schematic top view of a regulating member according to another embodiment, the figure 24 is a schematic top view of a regulating member according to another embodiment, the figure 25a illustrates a top view of an escapement of the regulating organ of the figure 12 , there figure 25b illustrates a top view of an escapement, according to another embodiment, of the regulating organ of the figure 12 , there figure 25c illustrates a top view of an escapement, according to another embodiment, of the regulating organ of the figure 12 , there figure 25d illustrates a view at the point of contact between a pallet of one of the anchors of the figure 25c and a tooth of the escape wheel, the figure 26 illustrates a top view of an escapement of the regulating organ of the figure 17 , there figure 27 is a schematic top view of the oscillator according to another embodiment, the figure 28 is a schematic top view of the oscillator illustrating an area of ​​intersection between two balance wheels according to another embodiment, the figure 29 is a schematic top view of the oscillator illustrating an area of ​​intersection between two balance wheels according to another embodiment, and the figure 30 is a schematic view of the oscillator illustrating two zones of intersection between three balances according to another embodiment. Exemples de mode de réalisation de l'invention

[0032] In the present application, the term "oscillator" means a resonator comprising, on the one hand, several balance wheels and, on the other hand, a gear train arranged to be engaged with the balance wheels so as to make the latter dependent on each other. Furthermore, in the present application the term "regulating organ" means an assembly comprising the oscillator and a counting organ, in particular an escapement.

[0033] In reference to the figure 1 , the watch movement 10 has a simplified construction thanks to a low-frequency regulating organ with double-balance-spring 22a, 22b, which will be described later, configured to oscillate at a frequency lower than 1.5 Hz. Depending on the inertia of the balances selected, the power reserve can be considerably increased, in particular if achieving high chronometric performance is not a priority.

[0034] The simplified watch movement comprises a plate 12 on which are mounted a barrel 14, an escapement 15 comprising an escape wheel and a kinematic link 19 connecting the barrel 14 to the pinion of the escape wheel. The kinematic link 19 comprises fewer than three mobiles.

[0035] According to an advantageous embodiment, this kinematic connection comprises only a mobile 19 engaged on the one hand with the ratchet of the barrel 14 and, on the other hand, with the pinion of the escape wheel. The mobile 19 therefore replaces the center wheel, the middle wheel and the second wheel of a traditional movement.

[0036] According to a variant execution not illustrated, the kinematic connection comprises no fewer and no more than two mobiles meshing together. One of the two mobiles is engaged with the ratchet of the barrel while the other of the two mobiles is engaged with the pinion of the escape wheel.

[0037] The simplified watch movement has the advantage of providing a new architecture with possibilities for identifying the unique product due to the fact that the geometric constraints, for example the center distances, are very different from traditional movements. Furthermore, the simplification of the movement makes it possible to increase the overall efficiency by reducing the number of gears.

[0038] Under certain conditions related to the gear ratios and the escapement, it is possible to display the second directly on the escape wheel. In this case, the gear ratios between the barrel 14, the wheel set 19 and the pinion of the escape wheel 16 are chosen so that the latter can make one complete rotation per minute. A seconds indicator member 50 can be mounted on the escape wheel axle.

[0039] Similarly, under certain conditions related to the gear ratios, the wheel 19 can directly display the minutes. The gear ratio between the barrel and the wheel 19 is therefore chosen so that the latter can make one complete rotation per hour. A minute indicator member 52 can for example be mounted on the axis of the wheel 19.

[0040] Finally, under certain conditions related to the gear ratios, barrel 14 can display the time. For example, an hour indicator organ 54 can be mounted on the shaft of barrel 14.

[0041] As mentioned above, the realization of a simplified watch movement is only possible by the implementation of a low-frequency regulating organ. In order to maintain an acceptable quality factor, the inertia of the balance must be increased compared to a mechanical movement equipped with a higher-frequency oscillator. This increase in inertia has the main disadvantage of increasing the sensitivity to angular accelerations. In order to counter this sensitivity to accelerations, the oscillator of the regulating organ comprises at least two balances coupled in phase opposition according to different embodiments, that is to say that a balance spring is associated with each of the two balances so that one of the balance springs is in a contraction phase while the other of the balance springs is in an expansion phase.According to a variant, the phase opposition can be achieved by mounting on one of the oscillator's balances two hairsprings wound in the opposite direction so that one of the two hairsprings is in a contraction phase when the other of the two hairsprings is in an expansion phase.

[0042] According to an advantageous embodiment, illustrated by the figures 2 à 5 , the oscillator 22 comprises a first and a second sprung balance 22a, 22b arranged in the same plane. Each sprung balance 22a, 22b comprises a flywheel 24a, 24b, a balance spring 32a, 32b and a balance staff 34a, 34b. The flywheel comprises rim segments 28a, 28b and balance arms 26a, 26b connecting the rim segments to the balance staff. One end of each balance spring 32a, 32b is connected to the respective balance staff by means of, for example, a collet 36a, 36b ( figure 5 ) driven onto the axis while the other end is connected for example to a stud mounted on a stud holder itself secured to a bridge or fixed cock (not shown) relative to the plate 12 of the watch movement 10.

[0043] The oscillator may include an elastic member other than a conventional flat spiral spring, for example a cylindrical spiral, a hemispherical or spherical spiral, or a conical spiral. The spiral may also include several turns according to a variant. The oscillator may also include an elastic member not similar to a spiral to fulfill the function of returning the balance wheel.

[0044] 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 a desmodromic connection so that the flywheel 24a of one of the two balance springs 22a, 22b can oscillate in phase opposition with respect to the flywheel 24b of the other of the two balance springs. In other words, the balance spring 32a of one of the two balance springs 22a, 22b is in an expansion phase while the balance spring 32b of the other of the two balance springs 22a, 22b is in a contraction phase, which has the consequence of driving the respective flywheels 24a, 24b in an opposite direction. This particular arrangement of the two spirals 32a, 32b makes it possible to cancel or, at least, reduce the sensitivity of the oscillator 22 to angular accelerations.

[0045] As can be seen in particular in the figure 4 And 5, the gear train 40, ensuring the desmodromic connection between the two balance springs 22a, 22b, comprises a first wheel set 42 secured to the balance staff 34a of the balance of one of the two balance springs 22a, 22b, a second wheel set 44 secured to the balance staff 34b of the balance of the other of the two balance springs 22a, 22b and two intermediate wheel sets 46, 48 meshing with the first and second wheel sets 42, 44 respectively. The ratios and the number of gears have been determined so that the first and second flywheels 24a, 24b of the respective balance springs 22a, 22b can oscillate in phase opposition.

[0046] With particular reference to the figure 2 , the flywheel 24a, 24b of each sprung balance 22a, 22b comprises four arms 26a, 26b separated by an angle of 90° from each other. Each arm 26a, 26b extends from the respective balance staff 34a, 34b, in a radial direction, to a distal portion 28a, 28b. Furthermore, the thickness of each arm 26a, 26b increases from the balance staff to the corresponding distal portion.

[0047] The distal portions of the first and second flywheels 24a, 24b each form four disjointed rim segments 28a, 28b along a first and second circle 25a, 25b respectively as shown in figure 4 . Each of the four separate rim segments 28a, 28b of each balance 24a, 24b extends along an arc of a circle of, for example, between 20° and 50° and preferably along an arc of a circle of between 30° and 40°.

[0048] According to other variants of execution, the flywheel of each sprung balance may have only two or three arms. In this case, the rim segment associated with each arm will be of larger dimension so that the inertia of each balance remains constant. For example, each discontinuous rim segment of the flywheel may extend along an arc of a circle greater than 45° in the case where each balance has three arms, or even greater than 60° in the case where each balance has only two arms.

[0049] A weight 30a, 30b in the form of screws are screwed into each rim segment 28a, 28b, for example in a radial direction, in order to be able to modify the inertia of the flywheel 24a, 24b of each sprung balance to adjust their oscillation frequency.

[0050] The center distance between the two balance shafts 34a, 34b respectively of the first and second sprung balances 22a, 22b is reduced so as to limit the differences in influence of the acceleration between the first and second flywheels 24a, 24b. According to this configuration, the first and second circles 25a, 25b, along which the disjoint rim segments 28a, 28b respectively of the first and second balances 24a, 24b are arranged, intersect. This configuration also has the advantage of reducing the size of the balances (surface). According to one embodiment, the dimensions of the two flywheels are substantially identical. These two flywheels define two discs with an overlapping zone 29a resembling a symmetrical lens as illustrated in figure 28 . According to another embodiment illustrated in the figure 29 , the diameter D1 of one of the flywheels 24a, 24b is less than the diameter D2 of the other of the flywheels. The first diameter D1 represents for example less than 80% of the second diameter D2. The intersection zone 29b is similar in this case to an asymmetrical lens.

[0051] When the regulating member 20 is in operation, the oscillations of the flywheels 24a, 24b of the balance springs 22a, 22b are synchronized in phase opposition so that the rim segments 28a of the flywheel 24a of one of the two balance springs 22a, 22b never come into contact with the rim segments 28b of the flywheel 24b of the other of the two balance springs 22a, 22b.

[0052] According to another embodiment illustrated by the figures 6 à 8 , the oscillator 22 comprises a first and a second sprung balance 22a, 22b mounted coaxially. The first and second sprung balances 22a, 22b are connected to each other by a gear train 40 so that the flywheel 24a of one of the two sprung balances 22a, 22b can oscillate in phase opposition with respect to the flywheel 24b of the other of the two sprung balances to cancel or, at least, reduce the sensitivity of the oscillator 22 to angular accelerations. According to another embodiment not illustrated, the first and second sprung balances are arranged so that their respective flywheel oscillates in two parallel planes with their respective axis parallel to each other.

[0053] According to the figure 8 , the gear train 40 comprises a first wheel set 42 secured to the balance staff 34a of the first sprung balance 22a, a second wheel set 44 secured to the balance staff 34b of the second sprung balance 22b and an intermediate gear train. The intermediate gear train comprises a third wheel set 45 engaged with the first wheel set 42, a fourth wheel set 46 engaged with the second wheel set 44, a fifth wheel set 47 engaged with the fourth wheel set 45 and a lower wheel set 48 and an upper wheel set 49 mounted coaxially so that the lower and upper wheel sets 48, 49 are engaged respectively with the fifth wheel set 47 and the third wheel set 45.

[0054] Just like the first embodiment, the flywheel 24a, 24b of each sprung balance 22a, 22b comprises four arms 26a, 26b separated by an angle of 90° from each other and comprising the same characteristics of the arms of the two sprung balances of the regulating organ illustrated in particular in figure 2 The number of arms may be other than four. Each flywheel 24a, 24b may, for example, have only two or three arms as mentioned above.

[0055] According to another embodiment illustrated by the figures 9 et 10 , the oscillator 22 comprises a first and a second sprung balance 22a, 22b mounted so that their respective balance axes are concurrent. For example, the first and second axes form an angle between them substantially equal to 45° according to the figure 10 although this angle may vary significantly depending on the execution variants, for example between 30° and 60°. According to an embodiment variant, illustrated by the figure 30 , the oscillator comprises three balances each comprising a flywheel 24a, 24b, 24c, each defining a disc. The balances are arranged so that a first and a second disc a third disc according to a first and a second intersection zone 29a which are rectilinear.

[0056] The advantage of this embodiment lies in particular in the simplified gear train so that the flywheels 24a, 24b respectively of the first and second sprung balances 22a, 22b can oscillate in phase opposition since this gear train only comprises two mobiles 42, 44 with appropriate teeth, conical for example, in direct engagement.

[0057] Just like the first and second embodiments, the flywheel 24a, 24b of each sprung balance comprises four arms 26a, 26b separated by an angle of 90° from each other and having the same characteristics of the arms of the two sprung balances of the regulating organ illustrated in particular in figure 2 Each balance 24a, 24b may comprise only two or three arms according to an execution variant as already specified previously.

[0058] As with the first embodiment, when the oscillator 22 is running, the oscillations of the flywheel 24a of one of the two balance springs 22a, 22b are synchronized in phase opposition with respect to the oscillations of the flywheel 24b of the other of the two balance springs 22a, 22b so that the rim segments 28a, 28b of the respective flywheels 24a, 24b never come into contact.

[0059] The regulating member 20 according to the invention can be implemented according to different configurations of the oscillator and the escapement according to the schematic figures 11 to 24 in order to transmit the oscillation frequency of the regulating member 20 to the kinematic link 19 connecting the barrel 14 to the pinion of the escape wheel 16, preferably by means of a single mobile 19 according to the schematic representation of the figure 1 The escapement may comprise one or more anchors, for example of the Swiss anchor type. The escapement may alternatively comprise any other device acting between the oscillator and an escape wheel, for example a detent or coaxial escapement. The term "anchor" is therefore to be taken in the present application in the broad sense, designating any organ intended to cooperate between the regulating organ and the escape wheel(s).

[0060] Depending on the embodiment of the figure 11 , the regulating organ 20 comprises an oscillator 22 comprising two sprung balances 22a, 22b, for example the oscillator 22 illustrated in figure 2 . The first and second flywheels 24a, 24b are arranged to oscillate in phase opposition. The escapement comprises a single escapement anchor 17, for example a Swiss anchor.

[0061] The anchor 17 comprises an input pallet 170 and an output pallet 172 arranged to cooperate with the escape wheel 16 in a conventional manner in order to transmit the oscillations of the flywheel 24a of a single sprung balance 22a of the regulating member 20 to the escape wheel 16 so that the rotation of the escape wheel 16 is carried out at the whim of the oscillations of the flywheel 24a. For this purpose, the anchor 17 comprises a fork 179 arranged to cooperate with a roller pin of the balance staff.

[0062] The flywheel 24a of one of the sprung balances is connected to the flywheel 24b of the other of the sprung balances by a gear train with an even number of return wheels 42, 44, 46, 48 so as to reverse the direction of rotation of the balances.

[0063] Each balance spring 22a, 22b comprises a balance spring 32a, 32b wound in the same direction so that during the operation of the movement, the balance spring of one of the balance springs is in a contraction phase while the balance spring of the other of the balance springs is in an expansion phase, that is to say in phase opposition.

[0064] According to the figure 12 and with reference to the different embodiments illustrated by the figures 25a-25d , the regulating organ 20 has an architecture comparable to that of the figure 11 , with the difference that the first and second sprung balances 22a, 22b cooperate respectively with a first and a second anchor 17a, 17b, which cooperate with the same escape wheel 16.

[0065] In particular, with particular reference to the figure 25a , the first anchor 17a comprises an input pallet 170a, and an output pallet 172a arranged to cooperate with the teeth of the escape wheel 16 while the second escape anchor 17b comprises an input pallet 170b and an output pallet 172b arranged to cooperate with the teeth of the escape wheel 16 alternately with the first escape anchor 17a. The first and second escape anchors 17a, 17b are arranged so that the input and output pallets of each anchor can cooperate with different teeth.

[0066] According to this arrangement, the output pallet 172a of the first anchor 17a is arranged opposite the input pallet 170b of the second anchor 17b while the input pallet 170a of the first anchor and the output pallet 172b of the second anchor 17b are spaced apart from each other in order to cooperate with teeth of the escape wheel 16 which are separated by an angle of less than 180° passing through the center of the wheel 16. The escape wheel 16 has for this purpose at least 20 teeth while a fork 179a, 179b of each anchor is arranged to cooperate with the roller pin 35a of the roller 35 of the corresponding balance-spring staff 22a, 22b. The escape wheel with less than 20 teeth, for example 15 teeth, can also be used under certain conditions.

[0067] Due to the opposite directions of rotation of the flywheels 24a, 24b ( figure 12 ) as previously described, the anchors 17a, 17b work symmetrically. The figure 25a has a tooth of the escape wheel 16 on the resting plane 176 of the entry pallet 170a of the first anchor 17a and another tooth of the escape wheel 16 on the resting plane 176 of the exit pallet 172b of the second anchor 17b. The angle α defined by the points of contact between the respective resting planes 176 of the entry pallet 170a and of the exit pallet 172b respectively of the first and second anchor 17a, 17b with respectively a first and a second tooth of the escape wheel 16 and by the center of the escape wheel 16 is less than 180° and is preferably located between 130° and 160°. The operating principle of the escapement 15 of the figure 25a requires that the settings be made so that the operating phases of the anchors take place simultaneously.

[0068] According to the embodiment illustrated in figure 25b , the impulse plane of the output pallet 172a of the first anchor 17a and the impulse plane of the output pallet 172b of the second anchor 17b are suppressed so that the distal portion of the output pallets 172a, 172b of the first and second anchors 17a, 17b forms an angle of approximately 90° with the rest plane 176 of the pallet.

[0069] This specific shape of the distal part of the aforementioned pallets has the advantage of avoiding the constraint imposed by the operating phases of the first and second anchors which must be carried out simultaneously according to the embodiment illustrated in figure 25a This simplifies the adjustment of the escapement 15. The pallets are however sized so that the draft function is fulfilled.

[0070] The dimensions of the pallets are such that the teeth of the escape wheel rest well on the resting planes of the truncated pallets so as to ensure locking of the anchor in a conventional manner and that the release phase on this pallet is not longer than on the non-truncated pallet of the other anchor in order to avoid a loss of energy during the impulse. This embodiment has the advantage of facilitating the self-starting of the escapement 15.

[0071] According to the embodiment illustrated in figure 25c , the exhaust uses the operating principle described in EP2923242A1, the content of which is incorporated by reference into the present application, so as to avoid hyperstaticism of the exhaust 15 according to the figure 25a and the residual sensitivity of the exhaust adjustment according to the figure 25b In this case, to obtain proper functioning of the escapement, the tooth resting on the entry or exit pallets must be positioned very precisely in relation to the end of the pallet resting plane so that the release and impulse phases of the escapement take place correctly.

[0072] Given manufacturing tolerances, a classic lever escapement generally requires a final adjustment of the positions of the entry and exit pallets. This adjustment is generally long and delicate because it can significantly influence the performance of the escapement.

[0073] The 15 exhaust according to the figure 25c is similar to the exhaust of the figure 25a by the arrangement of a first and a second anchor 17a, 17b arranged to cooperate with an escape wheel 16. The escape wheel nevertheless differs by the profile of its teeth.

[0074] In this case, each tooth of the escape wheel 16 has a driving plane 182 ( figure 25d ) oriented so that contact between the input pallet 170a, 170b and the output pallet 172a, 172b of each anchor 17a, 17b and the escape wheel via the driving plane 182 creates a torque that tends to reduce the angle between the anchor and the reference axis V 1 , V 2 connecting the axes of the anchor and the balance for each of the first and second anchors 17a, 17b. In other words, the present implementation provides a driving plane that causes the anchor to naturally arrive in an equilibrium position, because the driving plane is arranged to create a torque creating a movement towards the equilibrium position.

[0075] According to a non-illustrated variant, the driving plane can be located on one of the pallets of the first and second anchor while the escape wheel has conventional teeth.

[0076] The regulating organ 20 according to the embodiment of the figure 13 has an architecture comparable to that of the figure 12 , with the difference that one of the balances does not have a balance spring. This balance includes a flywheel 24 secured to the first wheel set 42. The latter meshes with a gear train comprising two intermediate wheels 46, 48 and the second wheel set 44 secured to the balance spring 22b. The flywheel 24a is thus driven by a desmodromic connection to oscillate according to the oscillations of the balance spring 22b but in the opposite direction. The balance spring 22b may have only one balance spring or according to a variant not illustrated but similar to the figure 14 , a pair of spirals wound in opposite directions to obtain phase opposition.

[0077] Depending on the embodiment of the figure 14 , only one of the balance wheels of the oscillator 22 is arranged to cooperate with the escape wheel 16. This balance wheel has no hairspring and its flywheel 24a is integral with the first wheel set 42. Like the adjustment member of the figure 13 , the first mobile 42 is engaged with a gear train comprising two intermediate mobiles 46, 48 and the second mobile 44 secured to the sprung balance 22b. The flywheel 24a is thus driven by a desmodromic connection to oscillate according to the oscillations of the sprung balance 22b but in the opposite direction. The sprung balance 22b comprises, for its part, a single balance spring or preferably two balance springs 32a, 32b mounted coaxially and wound in opposite directions to obtain phase opposition.

[0078] Depending on the embodiment of the figure 15 , the oscillator 22 of the regulating member 20 comprises three balances, namely two sprung balances 22a, 22b as well as a balance without a hairspring. The latter comprises a flywheel 24c secured to a wheel set 43 of the gear train and is arranged to cooperate with the escape wheel 16 via an anchor 17. The two sprung balances 22a, 22b are arranged at the end of the kinematic chain CC of the desmodromic link of the oscillator 22 on either side of the balance without a hairspring. In the example illustrated, the flywheels 24a, 24b rotate in the same direction thanks to the odd number of wheels 43, 46, 47, 48, 49 of the gear train connecting the two balance springs 24a, 24b. The balance spring 32a of the balance spring 22a is therefore wound in the opposite direction relative to the balance spring 32b of the balance spring 22b to obtain phase opposition.Generally speaking, the respective oscillations of two balances following each other in the CC kinematic chain of a regulating organ comprising at least three balances are in phase opposition.

[0079] Depending on the embodiment of the figure 16 , the oscillator 22 also comprises three balance wheels from the regulating member 20, namely a central balance wheel 22c arranged to cooperate with the escape wheel 16 and two balance wheels without a balance spring and which are arranged on either side of the central balance wheel. The latter comprises two balance springs 32a, 34 mounted coaxially and wound in opposite directions to obtain phase opposition. According to a variant not illustrated, the central balance wheel may only comprise a single balance spring. The oscillations of the flywheels 24a, 24b located on either side of the central balance wheel 22c are carried out according to the oscillations of the latter by the gear train.

[0080] Depending on the embodiment of the figure 17 and with reference to the figure 26 , the first and second sprung balances 22a, 22a of the regulating member 20 cooperate respectively with a first and a second escapement half-anchor 18a, 18b which cooperate with the same escape wheel 16. In this case, the first half-anchor 18a comprises an input pallet 180a while the second half-anchor 18b comprises an output pallet 180b. The operation of the escapement 15 is thus decoupled by producing two half-anchors each working with the roller pin of a balance staff. In this case, the impulses are distributed between the first and second sprung balances 22a, 22b of the oscillator 22. The balance springs 32a, 32b of the respective sprung balances 22a, 22a are wound in the same direction in order to obtain phase opposition. According to a non-illustrated variant, one of the balance wheels is without the balance spring while the other balance wheel has a pair of balance springs mounted in phase opposition.

[0081] According to the embodiments of the figures 18 And 19 , the regulating organ 20 has an architecture comparable to that of the figure 17 with the difference that the first and second sprung balances 22a, 22b cooperate respectively with a first and a second escape wheel 16a, 16b by means of a first and a second anchor 17a, 17b according to the regulating organ 20 of the figure 18 or by means of a first and a second half-anchor 18a, 18b depending on the organ of the figure 19 . The balance springs 32a, 32b of the respective balance springs 22a, 22a are also wound in the same direction in order to obtain phase opposition. According to a variant not illustrated, one of the balances is without the balance spring while the other balance has a pair of balance springs mounted in phase opposition.

[0082] Depending on the embodiment of the figure 20 , the oscillator 22 of the regulating member 20 comprises a sprung balance 22a and a balance without a hairspring. The regulating member comprises an escapement comprising, on the one hand, a first and a second escape wheel 16a, 16b arranged to be driven in opposite directions to each other, and on the other hand, an anchor 17 arranged to cooperate with one of the balances, for example the one without a hairspring, and with the two escape wheels. The sprung balance 22a preferably comprises two hairsprings mounted in phase opposition. In a variant not illustrated, each balance comprises a hairspring.

[0083] Two other embodiments of the regulating organ are illustrated by the figures 21 et 22 The first and second balance wheels of the oscillator 22 are mounted in phase opposition and are without a balance spring. These balance wheels therefore comprise only a flywheel 24a, 24b. The balance spring 32 is mounted on a wheel set 48 of the gear train of the oscillator 22. The centering of the balance spring in the gear train has the advantage of reducing the return effects compared to a balance spring at one of the ends of the oscillator chain. The flywheels 24a, 24b are then preferably without a balance spring. According to this embodiment, the inertia of the wheel set 48 is at least five times, preferably at least ten times, or even at least twenty times lower than the inertia of any of the balance wheels.

[0084] In reference to the figure 22 , the gear train is arranged to impart a back-and-forth movement to the mobile 48, which cooperates with the anchor 17 by means, for example, of a pin (not illustrated) secured to the mobile 48.

[0085] The wheel set 48 may be larger or smaller than the wheel sets 42, 44 secured respectively to the first and second balances 24a, 24b, so as to increase the dimensioning range of the balance-spring couplings and the amplitudes (the amplitude of the wheel set may be adapted to the ideal operation of the escapement while the amplitude of the balances may be adapted to their inertia). Depending on the regulating organ of the figure 22 , the primitive diameter of the mobile 48 is greater than the primitive diameter of the respective mobiles 42, 44 of the first and second balances 24a, 24b.

[0086] Another example of a regulating organ is schematically illustrated by the figure 23 . This regulating organ is similar to the regulating organ of the figure 22 with the difference that the balance spring 32 is mounted on a wheel 48 of the gear train whose primitive diameter is less than the primitive diameter of the respective wheels 42, 44 of the first and second balances 24a, 24b.

[0087] According to another embodiment schematically illustrated by the figure 24 , the regulating organ comprises two sprung balances 22a, 22b mounted in phase opposition while the wheel set 48 of the gear train is arranged to cooperate with the anchor 17 by means, for example, of a pin (not illustrated) secured to the wheel set 48. The latter is driven in a back-and-forth movement during the operation of the regulating organ in order to regulate the rotation of the escape wheel 16 and to maintain the oscillations of the first and second sprung balances.

[0088] According to the embodiments illustrated by the figures 12 , 13 And 21 , the escape wheel 16 can be replaced by two coaxial escape wheels which can be fixed or movable between them, in particular to take up play and / or to optimize the contacts with the pallets.

[0089] According to another embodiment schematically illustrated in the figure 27 , the oscillator of the regulating organ comprises four flywheels 24a, 24b, 24c, 24d. Each flywheel 24a, 24b, 24c, 24d is similar to the flywheels of the regulating organ according to the embodiment illustrated in particular in figures 2 to 4. The distal portions of each flywheel together form several disjointed serge segments, for example three or four segments, along respectively a first, a second, a third and a fourth circle. The center distance between the four balance shafts is reduced so that each circle intersects another circle among the four circles. The four flywheels 24a, 24b 24c, 24d are interconnected by a gear train (not shown) adapted so that two flywheels 24a, 24c oscillate in the same phase and in phase opposition with respect to the other two oscillators 24b, 24d. The four flywheels 24a, 24b, 24c, 24d are preferably arranged to oscillate in the same plane.

[0090] The regulating organ according to the invention allows several mobiles of a gear train to be used between the balance, the balance spring and the escape wheel, which are directly linked together in a conventional regulating organ. The dimensioning of each mobile determines their respective couplings. This dimensioning allows the implementation of new adjustment methods between: the return torque of the at least one balance spring and the inertia of the balances while maintaining unchanged the power necessary to maintain the oscillations of the oscillator, the power necessary to maintain the oscillator and the power delivered by the at least one escapement wheel.

[0091] These adjustment methods can in particular have the advantage of making it possible to overcome: variations in the production of series components (distribution of balance spring torques or balance wheel inertias in production batches), variations in torque supplied by the driving organ of a movement equipped with such a regulating organ, variations caused by the consumption of additional mechanism functions in a movement equipped with such a regulating organ (the same basic movement being able to power several calibers whose additional functions vary, but for which the same regulating organ would be used, its power being adapted according to the consumption of these additional functions).

[0092] Adjustment by these methods can be complementary to various other conventional adjustments, including adjustment by screws or by eccentrics mounted on balance wheels or adjustment by the index.

[0093] It is possible, by modifying the geometric properties (primitive diameter and / or inertia) of the mobiles of the gear train, in particular of at least one of the mobiles 42, 43, 44, 45, 46, 47, 48, 49 of the gear train 40, to modify the pairing between the return torque of the at least one spiral spring and the inertia of the balances while maintaining unchanged the power necessary to maintain the oscillations of the oscillator.

[0094] The process therefore includes the following steps: determine the inertia of all the oscillator balance wheels, determine the restoring torque of the elastic organ of the oscillator, compare these values ​​with the theoretical values ​​giving the targeted performances and determine the modification to be made to achieve this, whether it is a mobile of greater / lower inertia or a mobile of larger / smaller nominal diameter, replace the initial mobile(s) with mobiles determined in the previous step optionally, measure the chronometric performances of the regulating organ, and optionally start again if the pairing still needs to be improved / refined.

[0095] Although the inertia of the wheel sets is much lower than that of the balance wheels (the wheel sets do not have sufficient inertia to allow them to maintain oscillations, i.e. they cannot be considered as balance wheels), a variation in this inertia can, however, modulate in small proportions the relationship between the inertia of the balance-spring and the restoring torque of the balance spring and modify the period of the oscillations, and therefore the rate of the watch movement equipped with such a regulating organ.

[0096] The modification of the inertia of a gear train mobile can be carried out in different ways, in particular by 1) a change of material to aim for different densities and therefore different inertias with equal dimensions, by 2) a change of thickness, therefore different inertias with equal primitive diameter (or contour profile), or by 3) a change of effective mass with equal external dimensions, using openwork mobiles.

[0097] By modifying the pitch diameter of one of the mobiles, in particular a mobile bearing a balance spring, the relationship between the inertia and the restoring torque of the balance spring is modified. Modifying the pitch diameter in gearing generally involves, for an equal module, a change in the number of teeth. However, there are other means of fine modulation such as offsets, which consist of modifying the pitch diameter and thus the relationship between mobiles meshing together for an equal number of teeth.

[0098] Since the energy available to the escape wheel can vary upstream (in particular due to the moment developed by the barrel spring which can vary in production, but also in more specific cases such as additional openings on skeleton mobiles, or in the case of driving additional modules with different consumptions), it is also possible to modify these pairings to adapt the characteristics of the regulating organ to the quantity of energy available to the escape wheel.

[0099] This involves the following steps: determine the torque supplied by the driving source to one or more escapement mobiles, determine the effective inertia of the balances equipping the regulating organ, determine the return torque of the elastic organ equipping the regulating organ, compare these values ​​with the theoretical values ​​giving the targeted performances and determine the modification to be made to achieve this, a modification of inertia of a mobile being able to be accompanied by a modification of the nominal diameter of the same mobile or of another mobile of the gear train, this in order to maintain the balance-spring balance, replace the initial mobile(s) with mobiles determined in the previous step optionally measure the chronometric performances of the regulating organ, and optionally start again if the pairing still needs to be improved / refined.

[0100] In order to optimize the adjustment process described above, it may be useful to carry out statistical determinations (if it is only a question of overcoming serial distributions) or determinations of needs (if it is a question of overcoming variations in consumption of additional functions) in order to distribute the pairing mobiles by classes, and to size these classes (deviations) according to the aforementioned needs.

[0101] Finally, if it is a question of involving mobiles of different primitive diameters, it is obvious that the positions of the mobiles in their support (escapement holder, plate-cock or other), guiding means (bearing, ball bearings, etc.) will have to be configured so that their relative spacing can be adapted to the variations in center distance resulting from the pairing. These means for adjusting the center distances are well known in the state of the art, as disclosed for example in CH131854.

[0102] The guide means can in particular be mounted on intermediate supports allowing this adjustment, but other means are also conceivable without going beyond the scope of the invention. Reference list

[0103] Watch movement10 Plate 12 Barrel 14 Escapement 15 Escapement wheel 16, 16a, 16b Transmission organ Escapement anchor 17; 17a, 17b Input and output pallets 170, 172; 170a, 172a; 170b, 172b Impulse plane 174 Rest plane 176 Distal portion 178 Driving plane 182 Fork 179 First escapement half-anchor 18a Entry pallet 180a Second escapement half-anchor 18b Exit pallet 180b Kinematic connection 19 between the barrel and the escape wheel Less than three mobiles Single mobile Regulating organ 20 Oscillator 22 Sprung balance 22a, 22b Flywheel 24a, 24b, 24c, 24d First and second circles 25a, 25b Balance arms 26a, 26b Rim segments 28a, 28b Intersection zone 29a, 29b Inertia-blocks 30a, 30b Balance spring 32, 32a, 32b Balance shaft 34a, 34b Single chainring 35 Chainring pin 35a Ferrule 36a,36b Gear train 40 connecting the first and second oscillators First wheel set 42 (attached to one of the balance shafts) Second wheel set 44 (attached to the other of the balance shafts) Intermediate wheel sets 45, 46, 47, 48, 49 CC kinematic chain Seconds indicator 50 Minutes indicator 52 Hours indicator 54,

Claims

1. Regulating member (20) for a watch movement (10), comprising an oscillator (22) including at least a first and a second balance each comprising an inertia wheel (24a, 24b) and a balance staff (34a, 34b), the oscillator (22) comprising at least one elastic member (32, 32a, 32b) intended to maintain the oscillations of the oscillator, said oscillator (22) further comprising a gear train (40) comprising at least two mobiles (42, 44, 45, 46, 47, 48, 49), the inertia wheel (24a, 24b) of each balance being fixed in rotation to a mobile (42, 44) of the gear train (40), said gear train (40) being arranged to connect together the inertia wheels (24a, 24b) of the first and second balances by a desmodromic link so that the respective oscillations of the first and second balances are in phase opposition, the regulating member (20) further comprising an escapement (15) comprising at least one escapement wheel (16, 16a, 16b) and at least one anchor (17, 17a, 17b) intended to regulate said at least one escapement wheel (16, 16a, 16b) and to maintain the oscillations of said oscillator (22).

2. Regulating member (20) for a watch movement (10), comprising at least three balances, each comprising an inertia wheel (24a, 24b, 24c), the respective oscillations of two balances following each other in the kinematic chain (CC) of said at least three balances being in phase opposition.

3. Regulating member (20) according to claim 1 or 2, wherein said gear train (40) comprises more than two mobiles (42, 44, 45, 46, 47, 48, 49).

4. Regulating member (20) according to one of the preceding claims, wherein the balance staffs (34a, 34b) of the first and second balances are coaxial.

5. Regulating member (20) according to one of claims 1 to 3, wherein the balance staffs (34a, 34b) of the first and second balances are parallel while their respective inertia wheels (24a, 24b) are arranged to oscillate in two parallel planes.

6. Regulating member (20) according to any of claims 1 to 3, wherein the inertia wheels (24a, 24b) of the first and second balances are substantially comprised in the same plane.

7. Regulating member (20) according to one of claims 1 to 3, wherein the balance staffs (34, 34b) of the first and second balances are comprised in intersecting planes.

8. Regulating member (20) according to one of claims 6 or 7, wherein the inertia wheel (24a, 24b) of each of the first and second balances comprises a plurality of disjoint rim segments (28a, 28b), for example two, three or even four rim segments, forming together the rim of each inertia wheel (24a, 24b) along respective circles (25a, 25b) defining respectively a first and a second disc (27a, 27b) intersecting or overlapping so as to form an overlapping zone (29a) or an intersecting zone (29b).

9. Regulating member (20) according to claim 8, wherein said overlapping zone has the shape of a lens (29a), said lens preferably being a symmetrical lens.

10. Regulating member (20) according to claim 8, wherein said intersecting zone is a straight-line segment (29b).

11. Regulating member (20) according to one of the preceding claims, wherein at least one of the first and second balances does not comprise said at least one elastic member.

12. Regulating member (20) according to one of the preceding claims, wherein said at least one elastic member (32) is mounted on an intermediate mobile (45, 46, 47, 48, 49) of said gear train (40), the inertia of said intermediate mobile (45, 46, 47, 48, 49) being at least five times, preferably at least ten times, or even at least twenty times less than the inertia of any of said balances.

13. Regulating member (20) according to one of the preceding claims, in which at least one of the first and second balances and / or an intermediate mobile (45, 46, 47, 48, 49) of the gear train (40) comprises an even number, preferably two, of elastic members (32a, 32b) wound in opposite directions.

14. Regulating member (20) according to one of the preceding claims, wherein the escapement (15) comprises only one anchor (17) arranged to cooperate with one of the first and second balances and the escapement wheel (16).

15. Regulating member (20) according to one of claims 1 to 13, wherein the escapement (15) comprises two anchors (17a, 17b) arranged to cooperate, on the one hand, with the first and second balances respectively and, on the other hand, with a single escapement wheel (16), or with a first and second escapement wheel (16a, 16b) respectively.

16. Regulating device (20) according to one of claims 1 to 13, wherein the escapement (15) comprises a first and a second half-anchor (18a, 18b) arranged to cooperate respectively with the first and second balances, the first and second half-anchors (18a, 18b) comprising respectively a first pallet (180a) and a second pallet (180b) arranged to cooperate with a single escapement wheel (16) or respectively with a first and a second escapement wheel (16a, 16b).

17. Regulating device (20) according to one of claims 1 to 13, wherein the escapement (15) comprises an anchor (17) arranged to cooperate with one of the first and second balances, the anchor comprising a first pallet arranged to cooperate with a first escapement wheel (16a) and a second pallet arranged to cooperate with a second escapement wheel (16b).

18. Regulating device (20) according to one of claims 1 to 13, wherein the escapement (15) comprises an anchor (17) arranged to cooperate with an intermediate mobile (45, 46, 47, 48, 49) of the gear train (40) and an escapement wheel (16).

19. Method for adjusting the frequency of the oscillator (22) of the regulating member (20) according to one of the preceding claims, wherein one determines the inertia of all the balances (24a, 24b, 34a, 34b) of the oscillator (22) and the return torque of said at least one elastic member (32, 32a, 32b) of the oscillator, then one replaces at least one of the mobiles (42, 44, 45, 46, 47, 48, 49) of said gear train (40), preferably an intermediate mobile (45, 46, 47, 48, 49), by a mobile of different inertia so as to obtain 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 (22).

20. Method of adjusting the frequency of the oscillator (22) of the regulating member (20) according to one of claims 1 to 18, wherein one determines the inertia of all the balances (24a, 24b, 34a, 34b) of the oscillator (22) and the return torque of said at least one elastic member (32, 32a, 32b), then one replaces at least one of the mobiles (42, 44, 45, 46, 47, 48, 49) of said gear train (40), preferably an intermediate mobile (45, 46, 47, 48, 49), by a mobile with a pitch diameter different from the replaced mobile so as to obtain a ratio between the inertia of all the balances of the oscillator and the return torque of said at least one elastic member defined by the desired frequency of the oscillator.

21. Method of setting a watch movement (10) comprising a driving source (14), in particular a barrel, and the regulating member (20) according to one of claims 1 to 17, wherein one determines the torque supplied by said driving source (14) to said escapement wheel (16, 16a, 16b), the inertia of all the balances (24a, 24b, 34a, 34b) and the return torque of said at least one hairspring (32, 32a, 32b), and then one replaces at least one mobile (42, 44, 45, 46, 47, 48, 49) of said gear train (40), preferably an intermediate mobile (45, 46, 47, 48, 49) by a mobile with a different inertia and / or a different pitch diameter so as to obtain a defined ratio between the inertia of all the balances and the return torque of said at least one elastic member and a defined ratio between the power for maintaining the oscillations of the oscillator (22) and the power available to the escapement wheel.

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