CH715445B1 - Regulator device for clockwork. - Google Patents

Abstract

The invention relates to a regulator device (200) for a clock movement (300), comprising: - an inertial element (11) of a resonator (10) pivoted about a first axis (A1), the element inertia 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 set (30) pivoted about a second axis (A3), the escape wheel set being inscribed in a second cylinder of diameter D3 centered on the second axis and having a second inertia 13; – an ascender comprising: o a first ascender mobile (20a) pivoted around a third axis (A2a), inscribed in a third cylinder of diameter D2a centered on the third axis and having a third inertia I2a; and o a second blocker mobile (20b) 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 being arranged so as to cooperate with each other, the regulator device being such that: D2a×I2a < 4.10 -4 ×D×I, and/or D2b×I2b < 10 -4 ×D×I, and/or D3×I3 < 7.10 -5 ×D×I.

Description

The invention relates to a regulator device for a clock movement. The invention also relates to a watch module comprising such a device. The invention also relates to a watch movement comprising such a device or module. The invention finally relates to a timepiece comprising such a device or module or movement.

[0002] The majority of mechanical movements comprise a regulator including a resonator of the balance-spring type and a Swiss lever escapement cooperating with the resonator. The balance-spring constitutes the time base of the movement. The escapement, for its part, fulfills two main functions, namely maintaining the oscillations of the resonator, and counting these oscillations.

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

[0004] In the case of conventional regulator devices, it is known that a high-performance sprung balance presents a maximized regulating power 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 needed to maintain its oscillations. On the other hand, it is admitted, as for example explained in the 1969 publication by Pierre Chopard, entitled "Influence of the geometry of the balance wheel on the chronometric performances of the watch", published in the proceedings of the International Colloquium of Chronometry , and in the book „Construction horlogère“ (PPUR, 2011) that large-diameter and low-mass balance wheels offer the best performance for a given inertia.

[0005] Furthermore, the resonator must have an acceptable size, compatible with the dimensions of a watch movement, in particular a wristwatch (for example movements having diameters which may be between 20 mm and 35 mm). Typically, a resonator of the balance-spring type comprises a balance wheel whose diameter is between 7 mm and 12 mm.

[0006] The object of the invention is to provide a regulator device for a clockwork movement making it possible to improve the devices known from the prior art. In particular, the invention proposes a regulator device whose operation is optimized in terms of reliability, chronometric precision, energy losses, as well as in terms of compactness.

According to the invention, a regulator device according to the invention is defined by claim 1.

[0008] Different embodiments of the device are defined by claims 2 to 12.

According to the invention, a watch module according to the invention is defined by claim 13.

According to the invention, a watch movement according to the invention is defined by claim 14.

According to the invention, a timepiece according to the invention is defined by claim 15.

The appended figures show, by way of example, one embodiment of a timepiece according to the invention. Figure 1 is a schematic view of the embodiment of a timepiece. FIG. 2 is a detail view of part of the regulator device according to the embodiment of the timepiece. Figure 3 is a sectional view along the plane III-III of Figure 2 of the regulator device according to the embodiment of the timepiece. Figure 4 is a schematic view of a variant embodiment of the timepiece. FIGS. 5 and 6 are partial, exploded and perspective views of an embodiment of a timepiece regulator device.

An embodiment of a timepiece 400 is described below with reference to Figures 1 to 6. The timepiece is for example a watch, in particular a wristwatch. The timepiece comprises a timepiece movement 300. The timepiece movement may be a mechanical movement, in particular an automatic movement.

[0014] The movement can include a watch module 67.

The movement 300 or the watch module 67 comprises a regulator device 200.

The regulator device 200 comprises a resonator 10 and an exhaust 100.

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 set 30 comprising an escape wheel 3 and pivoted about a second axis A3, the escape wheel set being inscribed in a second cylinder of diameter D3 centered on the second axis and having a second inertia 13; – an ascender 2 comprising: o a first ascender mobile 20a comprising a first ascender element 2a, the first ascender mobile being pivoted around a third axis A2a, inscribed in a third cylinder of diameter D2a centered on the third axis and having a third inertia I2a; and o a second mobile blocker 20b comprising a second blocker element 2b, the second mobile blocker 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 mobile blocker, 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, even D2a×I2a ≤ 3.10<-4>×D×I, even D2a×I2a ≤ 2.10<-4>×D×I; and/or D2b×I2b < 10<-4>×D×I, even D2b×I2b ≤ 9.10<-5>×D×I, even D2b×I2b ≤ 8.10<-5>×D×I; and/or D3xl3 < 7.10<-5>×D×I, even D3×I3 ≤ 6.10<-5>×D×I, even D3×I3 ≤ 5.10<-5>×D×I.

Advantageously, the first mobile blocker 20a, in particular the first blocker element 2a, comprises a first toothing 21a and the second mobile blocker 20b, in particular the second blocker element 2b, comprises a second toothing 21b. These two teeth are arranged to cooperate and produce the gear of the first and second mobile blocker.

[0019] The escape wheel set 30 can typically comprise a shaft 31, the escape wheel 3 and an escapement pinion 32. In this case, the escape wheel 3 and/or the escapement pinion 32 can be reported on the tree 31 or come from material of the tree 31.

The first blocker mobile 20a can typically comprise a shaft 21a on which the first blocker element 2a is attached. A sting can possibly be part of this mobile.

The second blocker mobile 20b can typically comprise a shaft 21b on which the second blocker element 2b is attached.

The first mobile blocker, 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 pin could be made on the first blocker mobile, in particular on the first blocker element, and the fork could be made on the balance. Thus, the impulse to the balance-spring is achieved through or the cooperation of the first mobile blocker and the balance, in particular by the cooperation by contact of the fork 23a and the pin 11a.

[0023] The Holder's studies show that the number of teeth of the escape wheel can be minimized so as to guarantee adequate security 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.

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 ensure a first function of transmitting torque from the escape wheel and a second function of locking the escape wheel. The first torque transmission function of 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 mobile blocker 20a cooperating with the pin 11a of the balance wheel 11. During the impulse phases, the end of a tooth 3a of the escape wheel 3 cooperates with the one or the other of the respective impulse surfaces 23a, 23b of the mobile blockers 20a, 20b, in particular of the first and second blocker elements. The second function of blocking the escape wheel intervenes 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 mobiles 20a, 20b of the blocker 2. Preferably, such a surface of blocking of the blocker is concave in order to offer safety in the event of a shock or a rebound of the escape wheel. Preferably again, such a blocking surface 22a, 22b of the blocker 2 is formed by two flanks forming an angle γ of between 120° and 170°.

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

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

[0027] The principle of operation of such an exhaust 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 mobile blockers and the escapement wheel of the escapement device in rest phase of the exhaust device 100, and this independently of stokers limiting the angular travel of the fork 23a.

Etoqueaux are therefore not necessary. Furthermore, such an escapement device has a perfectly symmetrical operation, and is not dependent on the adjustment of the penetrations, nor on the positioning of the stokers.

It is thus still possible to take advantage of such advantages by optimizing the geometry of the pin 11a and of the fork 23a so as to optimize the performance of the exhaust device. To do this, the flanks of the pin and of the fork can each comprise a portion of a cylinder whose directrix is an involute of a circle. Such a conformation makes it possible to achieve quite efficient levels of efficiency, by minimizing the influence of the angle of lift of the balance wheel on its isochronism performance.

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

Furthermore, it is also possible to provide a first mobile blocker 20a devoid of sting, due to its operating precision. It is thus still possible to reduce the inertia I2a of the first mobile blocker 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.

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

Preferably, the pitch 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.

On the basis of the definition of the mobile blocker, it is also possible to conform an escapement mobile 30 of exhaust 3 whose total diameter D3 and inertia 13 are minimized.

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' ≤ 0.9D, or even D' ≤ 0.85×D.

[0036] Preferably again, the regulator device is such that D2a < 0.4xD, even D2a ≤ 0.35×D, even D2a ≤ 0.3xD; and or D2b < 0.35xD, even D2a ≤ 0.3xD, even D2a ≤ 0.25×D; and or D3 < 0.4xD, even D3 ≤ 0.35xD, even D3 ≤ 0.3×D.

[0037] Preferably, the regulator device is such that D2b×I2b ≤ D2a×I2a.

[0038] More particularly, the regulator device is such that D2b<D2a

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

[0040] The Holder's studies show that optimizing the driving of the escape wheel leads to a multiplicative gear train between the escape wheel 30 and the first and second blocker wheels 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: D2b' < D3; and/or D2a′ <D3, 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 rests the blocking surface 22b of the second mobile blocker 20b.

Preferably, the regulator device is such that 7 mm≤D≤11 mm. Such a condition advantageously makes it possible to minimize the bulk in the plane of the first and second blocking wheels and of the escapement wheel 30 by confining them under the balance-spring (seen along the axis of the balance). This condition is advantageous for movements whose total diameter D* may be between 18 mm and 35 mm, and particularly advantageous for "ladies'" size movements whose total diameter D* may be between 18 mm and 22 mm.

Preferably, the tooth 11a or the pin 11a, the first and second blocker elements 2a, 2b and the escape wheel 3 are arranged on the same level or on the same plane P, as shown in Figure 3 Thus, the elements 11a, 2a, 2b, 3 can cooperate on one and the same plane P, that is to say there is a plane P perpendicular or substantially perpendicular to the axes A1, A2a, A2b, A3 and passing through the contact zones between: the peg and fork; the first blocker mobile, in particular the first blocker element, and the second blocker mobile, in particular the second blocker element; the first blocker mobile, in particular the first blocker element, and the escape wheel; the second blocker mobile, 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 movement. It makes it possible in particular to free up space so as to pivot an intermediate mobile 40 forming an interface between a going train 50 of the movement 300, in particular between a motor member 5, and the escapement device 100, as represented in the figure 4. Advantageously, this intermediate mobile 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 exhaust device, the first force being substantially greater than the second force of the blocker 2. The axis of rotation A4 of the mobile 40 is contained or not within the cylinder C of diameter D′.

[0045] Advantageously, the module 67 comprises a first blank 6, in particular a bridge 6, and a second blank 7, in particular a bridge 7. Advantageously again, the first and second mobile blocker and the mobile escapement are pivoted between the first blank 6 and a second blank 7. The second blank 7 can, for example, be planar. These first and second blanks can of course include pivoting means such as bearings, in particular pivoting stones.

Thus, in the embodiment of Figure 4, the three wheels 20a, 20b, and 30 are pivoted by two blanks 6, 7, and the wheel 40 is pivoted by a gear bridge 8 pivoting at least partially the movement finishing gear.

Preferably, the first and second blanks 6, 7, and at least the mobiles 20a, 20b, 30 constitute a module 67 which can be attached to a plate 9 of the movement 300 as shown in FIGS. 5 and 6. Thus, at the less 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 provided 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 in Figure 4.

Alternatively, the watch movement 300 comprises a plate on which the first and second blocker wheels and the escapement wheel are pivoted directly. In particular, these various mobiles can be pivoted between the plate and a bridge.

In the different embodiments, the resonator can 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 can be the diameter of the external circumference 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 pendulum with the same resonator inertia I and with the same rim section, but without the protuberances on the serge and which generates the same aerodynamic friction.

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 resonator pivoting device. In this case, the diameter D relates to the external diameter of the inertial element. If this inertial element has protrusions at its outer periphery, such as adjustment means for example, the diameter D to be considered will be an equivalent outer 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 outer periphery and which generates the same aerodynamic friction.

[0051] In the various variant embodiments, the escapement may be of indirect impulse, in particular of double indirect impulse, and/or of tangential drive.

[0052] In an advantageous variant, the escapement device, or even the regulator device, can be made on a module 67 which can be attached directly to a movement or to a frame to constitute a movement.

[0053] The solutions described above are advantageous because they implement efficient escapement devices having a high level of efficiency, while minimizing their impact on the isochronism of the resonator. They make it possible to achieve safe and faultless operation under all conditions of use, in particular during shocks. To meet these objectives, the tangential drive escapement device is advantageous because it requires little energy, friction being minimized, as much as possible, between the escape wheel and the blocker thanks to transmissions of the gear. As taught in patent application WO2017109004, the intensity of the release force of such an escapement device can be substantially 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 an ascender comprising two ascender wheels kinematically linked to each other such that if an angular impact acts in one direction on a first wheel, the latter is limited in its movement by the second wheel . By virtue of its conformation, such an exhaust device thus exhibits safe and flawless operation under all conditions of use, in particular during impacts. 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 to minimize its influence on the isochronism of a high-performance balance-spring.

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

[0055] Throughout this document, the term “mobile” preferably means an assembly pivoted around an axis. The assembly can be one-piece or made up of several parts fixed to each other or interlocking.

Claims (15)

1. Regulator device (200) for a clock movement (300), comprising: – an inertial element (11) of a resonator (10) pivoted around 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 set (30) comprising an escape wheel (3) and pivoted about a second axis (A3), the escape wheel set being inscribed in a second cylinder of diameter D3 centered on the second axis and having a second inertia I3; including a first – a blocker (2) comprising: o a first blocker mobile (20a) comprising a first blocker element (2a), the first blocker mobile being pivoted around a third axis (A2a), inscribed in a third cylinder of diameter D2a centered on the third axis and having a third inertia I2a; and o a second mobile blocker (20b) comprising a second mobile blocker (2b), the second mobile blocker 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 mobile blockers 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, even D2a×I2a ≤ 3.10<-4>×D×I, even D2a×I2a ≤ 2.10<-4>×D×I; and or D2b×I2b < 10<-4>×D×I, even D2b×I2b ≤ 9.10<-5>×D×I, even D2b×I2b ≤ 8.10<-5>×D×I; and or D3×I3 < 7.10<-5>×D×I, even D3×I3 ≤ 6.10<-5>×D×I, even D3×I3 ≤ 5.10<-5>×D×I. 2. Device according to claim 1, characterized in that 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, even D' ≤ 0.9×D, even D' ≤ 0.85×D. 3. Device according to claim 1 or 2, characterized in that the regulator device is such that D2a < 0.4×D, even D2a ≤ 0.35×D, even D2a ≤ 0.3×D; and or D2b < 0.35×D, even D2a ≤ 0.3×D, even D2a ≤ 0.25×D; and or D3 < 0.4×D, even D3 ≤ 0.35×D, even D3 ≤ 0.3×D. 4. Device according to one of the preceding claims, characterized in that the regulator device is such that D2b×I2b ≤ D2a×I2a. 5. Device according to one of the preceding claims, characterized in that the regulator device is such that D<5>×f/l > 20.10<-2>m<3>kg<-1>s<-1> with f being the frequency of the resonator, the frequency preferably being greater than or equal to 4 Hz. 6. Device according to one of the preceding claims, characterized in that the regulator device is such that D2b < D2a; and or D2b' < D3; and or D2a' < D3, with : D2a' being a diameter of a cylinder on which rests a blocking surface (22a) of the first blocker mobile (20a), and D2b' being a diameter of a cylinder on which rests a blocking surface (22b) of the second mobile blocker (20b). 7. Device according to one of the preceding claims, characterized in that the regulator device is such that 7mm≤D≤11mm. 8. Device according to one of the preceding claims, characterized in that the device comprises: – on the inertial element, respectively on the first mobile blocker, a tooth (11a) or a pin (11a) whose sides comprise a cylinder portion with an involute profile of a circle, and – on the first mobile blocker, respectively on the inertial element, a fork (23a) whose sides comprise a cylinder portion with an involute profile of a circle. 9. Device according to one of the preceding claims, characterized in that the first blocker mobile (20a), in particular the first blocker element (2a) is made of silicon and/or comprises cutouts (24a) on its board and / or in that the second blocker mobile (20b), in particular the second blocker element (2b) is made of silicon and/or comprises cutouts on its board. 10. Device according to one of the preceding claims, characterized in that the escape wheel comprises two or three or four teeth and/or in that the device comprises a resonator of the balance-spring type, the inertial element being a pendulum. 11. Device according to one of the preceding claims, characterized in that the tooth (11a) or the pin (11a), the first and second blocker elements and the escapement wheel are arranged on the same level or on the same plane (P). 12. Device according to one of the preceding claims, characterized in that it comprises an intermediate wheel set (40) arranged between a going train (50) of the movement (300) and the escapement wheel set, the intermediate wheel set (40 ) comprising a wheel (4) shaped to transmit to the blocker a first force during the exhaust impulse phases and to transmit to the blocker a second force during the exhaust release phases, the first force being greater than the second force. 13. Watchmaker module (67) comprising a device according to one of claims 1 to 12, characterized in that the first and second blocker wheels and the escapement wheel are pivoted between a first blank (6), in particular a bridge (6), and a second blank (7), in particular a bridge (7). 14. Watch movement (300) comprising a watch module according to claim 13 and/or a device according to one of claims 1 to 12. 15. Timepiece (400), in particular a wristwatch, comprising a timepiece movement (300) according to claim 14 and/or a timepiece module (67) according to claim 13 and/or a device according to one of claims 1 at 12.