REGULATOR DEVICE FOR CLOCKMOVEMENT

Description

[0001] The invention relates to a watch module including a regulator device for a watch movement. The invention also relates to a watch movement comprising such a module. The invention finally relates to a timepiece comprising such a module or movement.

[0002] Most mechanical movements include a regulator that includes a sprung balance resonator and a Swiss lever escapement that cooperates with the resonator. The sprung balance constitutes the time base of the movement. The escapement, in turn, fulfills two main functions: maintaining the oscillations of the resonator and counting these oscillations.

[0003] These organs perform essential functions and it is therefore necessary to design organs to avoid any malfunction.

[0004] In the case of conventional regulator devices, it is known that a high-performance sprung balance has a regulating power maximized so as to present a high quality factor, typically of the order of 320 in the horizontal position of the movement, while minimizing the energy required to maintain its oscillations. On the other hand, it is accepted, as explained for example in the 1969 publication by Pierre Chopard, entitled "Influence of the geometry of the balance on the chronometric performance of the watch", published in the proceedings of the International Chronometry Conference, and in the book "Construction horlogère" (PPUR, 2011) that balances with a large diameter and low mass present the best performances for a given inertia.

[0005] Furthermore, the resonator must have an acceptable size, compatible with the dimensions of a watch movement, particularly a wristwatch (for example, movements with diameters ranging from 20 mm to 35 mm). Typically, a balance-spring type resonator includes a balance with a diameter ranging from 7 mm to 12 mm.

[0006] Documents CH702313B1 and WO2017 / 109004A1 disclose timepieces whose escapement blockers have two mobiles meshing with each other.

[0007] The aim of the invention is to provide a watch module comprising a regulator device for a watch movement making it possible to improve the devices known from the prior art. In particular, the invention proposes a watch module whose operation is optimized in terms of reliability, chronometric precision, energy losses, as well as in terms of compactness.

[0008] According to the invention, a watch module according to the invention is defined by claim 1.

[0009] Different embodiments of the watch module are defined by claims 2 to 12.

[0010] According to the invention, a watch movement according to the invention is defined by claim 13.

[0011] According to the invention, a timepiece according to the invention is defined by claim 14.

[0012] The attached figures represent, by way of example, an embodiment of a timepiece according to the invention. There figure 1 is a schematic view of the embodiment of a timepiece. The figure 2 is a detailed view of a part of the regulator device according to the embodiment of the timepiece. The figure 3 is a sectional view along plane III-III of the figure 2 of the regulator device according to the embodiment of the timepiece. The figure 4 is a schematic view of a variant of the embodiment of the timepiece. The figures 5 et 6 are partial, exploded and perspective views of an embodiment of a regulator device of the timepiece.

[0013] An embodiment of a timepiece 400 is described below with reference to figures 1 à 6 . The timepiece is, for example, a watch, in particular a wristwatch. The timepiece includes a watch movement 300. The watch movement may be a mechanical movement, in particular an automatic movement.

[0014] The movement includes a 67 watch module.

[0015] The clock module 67 includes a regulator device 200.

[0016] The regulator device 200 comprises a resonator 10 and an escapement 100.

[0017] In particular, the regulator device 200 comprises: an inertial element 11 of the resonator 10 pivoted about a first axis A1, the inertial element being inscribed in a first cylinder of diameter D centered on the first axis and the resonator 10 having a first inertia I; an escape wheel 30 comprising an escape wheel 3 and pivoted about a second axis A3, the escape wheel being inscribed in a second cylinder of diameter D3 centered on the second axis and having a second inertia I3; a blocker 2 comprising: ∘ a first blocker wheel 20a comprising a first blocker element 2a, the first blocker wheel being pivoted about a third axis A2a, inscribed in a third cylinder of diameter D2a centered on the third axis and having a third inertia I2a;and ∘ a second blocker mobile 20b comprising a second blocker element 2b, the second blocker mobile being pivoted around a fourth axis A2b, inscribed in a fourth cylinder of diameter D2b centered on the fourth axis and having a fourth inertia I2b,; the first and second blocker mobiles, in particular the first and second blocker elements, being arranged so as to cooperate, in particular by gearing, with each other, the regulator device being such that: D2a×I2a < 4.10 -4< ×D×I, or even D2a×I2a ≤ 3.10 -4< ×D×I, or even D2a×I2a ≤ 2.10 -4< ×D×I; and / or D2b×I2b < 10 -4< ×D×I, or even D2b×I2b ≤ 9.10 -5< ×D×I, or even D2b×I2b ≤ 8.10 -5< ×D×I, and / or D3×I3 < 7.10 -5< ×D×I, or even D3×I3 ≤ 6.10 -5< ×D×I, or even D3×I3 ≤ 5.10 -5< ×D×I.

[0018] Advantageously, the first blocker wheel set 20a, in particular the first blocker element 2a, comprises a first toothing 21a and the second blocker wheel set 20b, in particular the second blocker element 2b, comprises a second toothing 21b. These two toothings are arranged to cooperate and produce the gearing of the first and second blocker wheels.

[0019] The escapement wheel 30 may typically comprise a shaft 31, the escapement wheel 3 and an escapement pinion 32. In this case, the escapement wheel 3 and / or the escapement pinion 32 may be attached to the shaft 31 or made from the same material as the shaft 31.

[0020] The first blocker mobile 20a may typically comprise a shaft 21a on which the first blocker element 2a is attached. A dart may optionally be part of this mobile.

[0021] The second blocker mobile 20b may typically comprise a shaft 21b on which the second blocker element 2b is attached.

[0022] The first blocker wheel set, in particular the first blocker element, comprises a fork 23a arranged to cooperate with the balance, in particular arranged to cooperate with a tooth 11a or a pin 11a made on the balance. Alternatively, the tooth or the pin could be made on the first blocker wheel set, in particular on the first blocker element, and the fork could be made on the balance. Thus, the impulse to the sprung balance is produced by means of or cooperation between the first blocker wheel set and the balance, in particular by the contact cooperation between the fork 23a and the pin 11a.

[0023] The studies of the Holder show that the number of teeth of the escape wheel can be minimized so as to guarantee adequate safety measures for the proper functioning of the escapement device 100. Thus, preferably, the number of teeth 3a of the escape wheel 3 is between 2 and 4. Preferably, the number of teeth 3a of the escape wheel 3 is equal to 3.

[0024] Furthermore, the minimum value of the diameter D3 of the escape wheel 3 can be determined geometrically. The teeth of the escape wheel are here provided to provide a first function of transmitting torque to the escape wheel and a second function of blocking the escape wheel. The first function of transmitting torque to the escape wheel occurs during impulse phases of the escapement device, namely when the escape wheel 3 transmits a torque to the blocker 2 so as to cause and maintain the oscillations of the resonator 10 by means of the fork 23a of the first blocker wheel set 20a cooperating with the pin 11a of the balance 11. During the impulse phases, the end of a tooth 3a of the escape wheel 3 cooperates with one or other of the respective impulse surfaces 23a, 23b of the blocker wheels 20a, 20b, in particular of the first and second blocker elements.The second function of blocking the escape wheel occurs during rest positions of the escapement device. In such positions, a distal end of a tooth 3a of the escape wheel bears against a blocking surface 22a, 22b of the wheel sets 20a, 20b of the blocker 2. Preferably, such a blocking surface of the blocker is concave in order to provide safety in the event of an impact or rebound of the escape wheel. Preferably again, such a blocking surface 22a, 22b of the blocker 2 is formed by two flanks making an angle γ of between 120° and 170°.

[0025] The escape wheel and the first and second blocker wheels are arranged such that the escape wheel, in particular its teeth, cooperate with the first and second blocker wheels. In particular, the escape wheel and the first and second blocker wheels are arranged such that the teeth of the escape wheel act by contact on specific surfaces 22a, 22b, 23a, 23b of the first and second blocker wheels, in particular of the first and second blocker elements.

[0026] At rest, the end of a tooth 3a of the escape wheel 3 cooperates with one or other of the respective blocking surfaces 22a, 22b of the blocking wheels 20a, 20b, in particular of the first and second blocking elements. During the impulse, the end of a tooth 3a of the escape wheel 3 cooperates with one or other of the respective impulse surfaces 23a, 23b of the blocking wheels 20a, 20b, in particular of the first and second blocking elements.

[0027] The operating principle of such an escapement device is disclosed in application WO2013182243. As taught in this document, the surfaces 22a, 22b are preferably in the form of concave surfaces, so as to optimize the precision in the positioning of the first and second blocker mobiles and of the escape wheel of the escapement device in the rest phase of the escapement device 100, and this independently of the pins limiting the angular travel of the fork 23a.

[0028] Therefore, no pins are required. Furthermore, such an escapement system operates perfectly symmetrically and is not dependent on the adjustment of the penetrations or the positioning of the pins.

[0029] It is thus still possible to take advantage of such benefits by optimizing the geometry of the pin 11a and the fork 23a so as to optimize the efficiency of the escapement device. To do this, the sides of the pin and the fork can each comprise a portion of cylinder whose directrix is ​​an involute of a circle. Such a conformation makes it possible to achieve very high levels of efficiency, by minimizing the influence of the balance lift angle on its isochronism performance.

[0030] The good performance of the escapement device can thus allow an increase in the balance wheel lift angle. It is thus still possible to reduce the center distance between the axis A1 of the sprung balance and the axis A2a of the first blocker wheel 2a, and therefore the total diameter D2a of the first blocker wheel 2a.

[0031] Furthermore, it is also possible to propose a first blocker mobile 20a without a stinger, due to its operating precision. It is thus still possible to reduce the inertia I2a of the first blocker mobile 20a. This inertia can in particular be minimized by the judicious choice of a low-density material, such as silicon for example, to produce the first mobile or the first blocker element, as well as by one or more cutouts 24a made on the board of the first blocker element 2a.

[0032] It is also possible to minimize the total diameter D2b and the inertia I2b of the second blocker wheel set 20b. Advantageously, the total diameter D2b may be substantially equal to the head diameter D2b' of the toothing 21b, with a blocking surface 22b arranged substantially at the level of the diameter D2b'. Additionally, the inertia I2b of the second blocker wheel set 20b may in particular be minimized by the judicious choice of a low-density material, such as silicon for example, to produce the second wheel set or the second blocker element, as well as by one or more cutouts, not shown in the figures, made on the board of the second blocker element 2b.

[0033] Preferably, the primitive diameters D2a*, D2b* of the teeth 21a, 21b of the first and second mobiles 20a, 20b are equal in order to minimize the differences in inertia between these two mobiles.

[0034] Based on the definition of the blocker mobiles, it is also possible to conform an escapement mobile 30 of escapement 3 whose total diameter D3 and inertia I3 are minimized.

[0035] Preferably, the axes A3, A2a, A2b of the escape wheel and of the first and second blocker wheels are contained in a cylinder centered on the first axis A1 and of diameter D', with D' < D, or even D' ≤ 0.9×D, or even D' ≤ 0.85×D.

[0036] More preferably, the regulator device is such that D 2 a < 0 , 4 × D , voire D 2 a ≤ 0 , 35 × D , voire D 2 a ≤ 0 , 3 × D ; and / or D 2 b < 0 , 35 × D , voire D 2 a ≤ 0 , 3 × D , voire D 2 a ≤ 0 , 25 × D ; and / or D 3 < 0 , 4 × D , voire D 3 ≤ 0 , 35 × D , voire D 3 ≤ 0 , 3 × D .

[0037] Preferably, the regulator device is such that D 2 b × I 2 b ≤ D 2 a × I 2 a .

[0038] More particularly, the regulator device is such that D 2 b < D 2 a

[0039] Preferably, the regulator device is such that D 5< ×f / l > 20.10 -2< m 3< kg -1< s -1< with f the frequency of the resonator, the frequency preferably being greater than or equal to 4 Hz.

[0040] Studies by the Holder show that an optimization of the escape wheel drive leads to a multiplicative gear train between the escape wheel 30 and the first and second blocking wheel sets 20a, 20b. Thus, knowing that the blocking surfaces 22a, 22b provided to cooperate with the distal ends of the teeth 3a can advantageously be arranged substantially at the level of the diameters D2a', D2b' opposite the respective axes A2a, A2b, the following conditions are preferably observed: D 2 b ′ < D 3 ; and / or D 2 a ′ < D 3 , with : D2a' a diameter, relative to the axis A2a, of a cylinder on which the blocking surface 22a of the first blocker mobile 20a rests, and D2b' a diameter, relative to the axis A2b, of a cylinder on which the blocking surface 22b of the second blocker mobile 20b rests.

[0041] Preferably, the regulator device is such that 7 mm ≤ D ≤ 11 mm. Such a condition advantageously makes it possible to minimize the space requirement in the plane of the first and second blocking wheels and of the escapement wheel 30 by confining them under the sprung balance (seen along the balance axis). This condition is advantageous for movements whose total diameter D* can be between 18 mm and 35 mm, and particularly advantageous for “lady” size movements whose total diameter D* can be between 18 mm and 22 mm.

[0042] Preferably, the tooth 11a or the pin 11a, the first and second blocking elements 2a, 2b and the escape wheel 3 are arranged on the same level or on the same plane P, as shown in the figure 3 . Thus, the elements 11a, 2a, 2b, 3 can cooperate on a single plane P, that is to say that there exists a plane P perpendicular or substantially perpendicular to the axes A1, A2a, A2b, A3 and passing through the contact zones between: the pin and the fork; the first blocker wheel, in particular the first blocker element, and the second blocker wheel, in particular the second blocker element; the first blocker wheel, in particular the first blocker element, and the escape wheel; the second blocker wheel, in particular the second blocker element, and the escape wheel.

[0043] Such a conformation makes it possible to minimize the thickness of the regulator device, in particular to minimize the thickness of the exhaust device, while implementing parts 11a, 2a, 2b, 2c which are flat and whose manufacture is facilitated.

[0044] Such a conformation thus makes it possible to free up space in the plane of the movement. In particular, it makes it possible to free up space so as to pivot an intermediate wheel set 40 forming an interface between a finishing train 50 of the movement 300, in particular between a driving member 5, and the escapement device 100, as shown in the figure 4 Advantageously, this intermediate wheel 40 comprises a wheel 4 which can be shaped to transmit a first force during the impulse phases of the escapement device and a second force during the release phases of the escapement device, the first force being substantially greater than the second force of the blocker 2. The axis of rotation A4 of the wheel 40 is contained or not within the cylinder C of diameter D'.

[0045] According to the invention, the module 67 comprises a first bridge 6 and a second bridge 7, and the first and second blocking wheels and the escapement wheel are pivoted between the first bridge 6 and the second bridge 7. The second bridge 7 may, for example, be flat. These first and second bridges may of course comprise pivoting means such as bearings, in particular pivoting stones.

[0046] Thus, in the embodiment of the figure 4 , the three mobiles 20a, 20b, and 30 are pivoted by two bridges 6, 7, and the mobile 40 is pivoted by a gear train bridge 8 pivoting at least partially the finishing gear train of the movement.

[0047] The first and second bridges 6, 7, and at least the mobiles 20a, 20b, 30 constitute the module 67 which can be attached to a plate 9 of the movement 300 as shown in the figures 5 et 6 . Thus, at least the mobiles 20a, 20b, 30 can be assembled independently of the other parts of the movement. Such a solution is particularly advantageous in the case where the mobiles 20a, 20b, 30 are intended to implement, at least partially, an escapement device intended to equip different movements. Thus, the module 67 can be assembled, checked, lubricated upstream of the final assembly of the components of the movement. Such a solution is particularly advantageous when the elements 2a, 2b, 3 are made of a fragile material such as silicon. figure 4 illustrates such a module integrating the mobiles 20a, 20b, 30, the mobile 40 being pivoted by the gear bridge 8 shown schematically on the figure 4 .

[0048] In the various embodiments, the resonator may be of the balance-spring type, i.e. comprising a balance 11 and a balance spring 12. In the case where the inertial element is a balance, the diameter D may be the diameter of the external periphery of the balance rim. If this rim has protuberances, such as adjustment means for example, the diameter D to be considered will be an equivalent external diameter, obtained by considering a virtual balance with the same resonator inertia I and with the same rim section, but without the protuberances on the rim and which generates the same aerodynamic friction.

[0049] In the various embodiments, the resonator may alternatively comprise a monolithic structure comprising an inertial element whose oscillations are maintained by flexible blades which can act as a pivoting device for the resonator. In this case, the diameter D relates to the external diameter of the inertial element. If this inertial element has protuberances at its external periphery, such as adjustment means for example, the diameter D to be considered will be an equivalent external diameter, obtained by considering a virtual inertial element with the same resonator inertia I and with a geometry of the inertial element similar to that of the reference inertial element (obtained by homothety), but without the protuberances on the external periphery and which generates the same aerodynamic friction.

[0050] In the various embodiments, the escapement may be indirect impulse, in particular double indirect impulse, and / or tangentially driven.

[0051] The regulating device is made on module 67 which can be directly attached to a movement or to a frame to constitute a movement.

[0052] According to another aspect not forming part of the invention, an embodiment of a regulator device comprises: an inertial element 11 of a resonator 10 pivoted about a first axis A1, the inertial element being inscribed in a first cylinder of diameter D centered on the first axis and the resonator 10 having a first inertia I; an escape wheel 30 comprising an escape wheel 3 and pivoted about a second axis A3, the escape wheel being inscribed in a second cylinder of diameter D3 centered on the second axis and having a second inertia I3; a blocker 2 comprising: ∘ a first blocker wheel 20a comprising a first blocker element 2a, the first blocker wheel being pivoted about a third axis A2a, inscribed in a third cylinder of diameter D2a centered on the third axis and having a third inertia I2a;and ∘ a second blocker mobile 20b comprising a second blocker element 2b, the second blocker mobile being pivoted around a fourth axis A2b, inscribed in a fourth cylinder of diameter D2b centered on the fourth axis and having a fourth inertia I2b,; the first and second blocking wheels being arranged so as to cooperate, in particular by gearing, with each other, the axes A3, A2a, A2b of the escapement wheel and of the first and second blocking wheels are contained in a cylinder C centered on the first axis A1 and of diameter D', with D' < D, or even D' ≤ 0.9×D, or even D' ≤ 0.85×D.

[0053] The solutions described above are advantageous because they implement high-performance escapement devices with a high level of efficiency, while minimizing their impact on the isochronism of the resonator. They make it possible to achieve safe and fault-free operation under all operating conditions, particularly during impacts. To meet these objectives, the tangential drive escapement device is advantageous because it requires little energy, with friction being minimized, as much as possible, between the escape wheel and the blocker thanks to gear-type transmissions. As taught in patent application WO2017109004, the intensity of the disengagement force of such an escapement device can be significantly lower than the intensity of the impulse force of this same escapement device, which has the advantage of greatly minimizing its impact on the isochronism of the resonator.Furthermore, such an escapement device comprises a blocker comprising two blocker mobiles kinematically linked together so that if an angular shock acts in one direction on a first mobile, the latter is limited in its movement by the second mobile. By virtue of its conformation, such an escapement device thus has a safe and faultless operation under all conditions of use, in particular during shocks. It is thus still possible to minimize the inertia of the elements taking part in such an escapement device so as to optimize its efficiency and minimize its influence on the isochronism of a high-performance sprung balance.

[0054] Throughout this document, the term "inertia of the resonator" means the inertia of all the moving elements of the resonator. In the case of a balance-spring type resonator, the set of moving elements includes in particular the balance 11, the balance spring 12 and the moving pivoting means, such as, for example, a balance shaft.

[0055] Of course, throughout this document, by "inertia of an element" is meant the inertia of the element around its axis of rotation in operation. The first inertia I is the inertia of the inertial element 11 around the first axis A1. The second inertia I3 is the inertia of the escape wheel 30 around the second axis A3. The third inertia I2a is the inertia of the first blocking wheel 20a around the third axis A2a. The fourth inertia I2b is the inertia of the second blocking wheel 20b around the fourth axis A2b.

[0056] Throughout this document, the term "mobile" preferably means an assembly pivoted around an axis. The assembly may be a single piece or made up of several parts fixed to each other or in a built-in connection.

[0057] Of course, throughout this document, by "an element inscribed in a cylinder having a diameter D centered on an axis" is meant that the diameter D is the smallest diameter centered on the axis such that the element is included in the cylinder.

Claims

1. A watch module (67) comprising a regulator device (200) for a watch movement (300), the regulator device (200) comprising: - an inertial element (11) of a resonator (10) pivoted about a first axis (A1), the inertial element being inscribed within a first cylinder having a diameter D centered on the first axis and the resonator (10) having a first inertia I; - an escapement mobile (30) comprising an escape wheel (3) and pivoted about a second axis (A3), the escapement mobile being inscribed within a second cylinder having a diameter D3 centered on the second axis and having a second inertia I3; - a blocking member (2) comprising: o a first blocking lever mobile (20a) comprising a first blocking lever element (2a), the first blocking lever mobile being pivoted about a third axis (A2a), inscribed within a third cylinder having a diameter D2a centered on the third axis and having a third inertia I2a; and ∘ a second blocking lever mobile (20b) comprising a second blocking lever element (2b), the second blocking lever mobile being pivoted about a fourth axis (A2b), inscribed within a fourth cylinder having a diameter D2b centered on the fourth axis and having a fourth inertia I2b, the first and second blocking lever mobiles being arranged in such a way as to cooperate, especially by gearing, with each other, the regulator device being such that: D 2 a × I 2 a < 4.10 − 4 × D × I , or D 2 a × I 2 a ≤ 3.10 − 4 × D × I , or D 2 a × I 2 a ≤ 2.10 − 4 × D × I ; and / or D 2 b × I 2 b < 10 − 4 × D × I , or D 2 b × I 2 b ≤ 9.10 − 5 × D × I , or D 2 b × I 2 b ≤ 8.10 − 5 × D × I ; and / or D 3 × I 3 < 7.10 − 5 × D × I , or D 3 × I 3 ≤ 6.10 − 5 × D × I , or D 3 × I 3 ≤ 5.10 − 5 × D × I , wherein the first and second blocking lever mobiles and the escapement mobile are pivoted between a first bridge (6) and a second bridge (7).

2. The module according to claim 1, wherein the axes (A3, A2a, A2b) of the escapement mobile and of the first and second blocking lever mobiles are contained within a cylinder centered on the first axis (A1) and having a diameter D', where D' < D, or D' ≤ 0.9 × D, or D' ≤ 0.85 × D.

3. The module according to claim 1 or 2, wherein the regulator device is such that D 2 a < 0.4 × D , or D 2 a ≤ 0.35 × D , or D 2 a ≤ 0.3 × D ; and / or D 2 b < 0.35 × D , or D 2 a ≤ 0.3 × D , or D 2 a ≤ 0.25 × D ; and / or D 3 < 0.4 × D , or D 3 ≤ 0.35 × D , or D 3 ≤ 0.3 × D .

4. The module according to one of the preceding claims, wherein the regulator device is such that D 2 b × I 2 b ≤ D 2 a × I 2 a .

5. The module according to one of the preceding claims, wherein the regulator device is such that D5 × f / l > 20.10-2 m3kg-1s-1, where f is the frequency of the resonator, the frequency preferably being greater than or equal to 4 Hz.

6. The module according to one of the preceding claims, wherein the regulator device is such that D 2 b < D 2 a ; and / or D 2 b ′ < D 3 ; and / or D 2 a ′ < D 3 , where: D2a' is a diameter of a cylinder on which a blocking surface (22a) of the first blocking lever mobile (20a) rests, and D2b' is a diameter of a cylinder on which a blocking surface (22b) of the second blocking lever mobile (20b) rests.

7. The module according to one of the preceding claims, wherein the regulator device is such that 7 mm ≤ D ≤ 11 mm .

8. The module according to one of the preceding claims, wherein the device comprises: - on the inertial element, respectively on the first blocking lever mobile, a tooth (11a) or a pin (11a) of which the flanks comprise a portion of cylinder having a profile of an involute of a circle, and - on the first blocking lever mobile, respectively on the inertial element, a fork (23a) of which the flanks comprise a portion of cylinder having a profile of an involute of a circle.

9. The module according to one of the preceding claims, wherein the first blocking lever mobile, in particular the first blocking lever element, is made of silicon and / or comprises cutouts (24a) on its plate, and / or wherein the second blocking lever mobile, in particular the second blocking lever element, is made of silicon and / or comprises cutouts on its plate.

10. The module according to one of the preceding claims, wherein the escape wheel comprises two or three or four teeth and / or wherein it comprises a resonator of the balance wheel and hairspring type, the inertial element being a balance wheel.

11. The module according to one of the preceding claims, wherein the tooth (11a) or the pin (11a), the first and second blocking lever elements and the escape wheel are arranged on the same level or in the same plane (P).

12. The module according to one of the preceding claims, wherein it comprises an intermediate mobile (40) arranged between a going train (50) of the movement (300) and the escapement mobile, the intermediate mobile (40) comprising a wheel (4) configured to transmit to the blocking member a first effort during the pulse phases of the escapement and to transmit to the blocking member a second effort during the phases of disengagement of the escapement, the first effort being greater than the second effort.

13. A watch movement (300) comprising a watch module according to one of claims 1 to 12.

14. A timepiece (400), especially a wristwatch, comprising a watch movement (300) according to the preceding claim and / or a watch module (67) according to one of claims 1 to 12.