Clock movement

Abstract

Clock movement (1) comprising: - a main barrel (3) housing a main mainspring and comprising a main winding mechanism (5) arranged to wind said main mainspring, as well as a main winding mechanism (7) arranged to enable said main mainspring to drive a clock mechanism by means of at least one gear train (9); - an auxiliary barrel (15) housing an auxiliary mainspring and comprising an auxiliary winding mechanism (17) arranged to enable said auxiliary mainspring to be wound by means of a winding oscillating weight (23), as well as an auxiliary winding mechanism (19) arranged to enable said auxiliary mainspring to wind said main mainspring by means of said main winding mechanism (5);in which said auxiliary drive unit (19) is arranged to be selectively blocked by a control ratchet (27) which is arranged to release said auxiliary drive unit (19) in order to wind said main drive spring in a punctual manner.

Description

technical field

[0001] The present invention relates to the field of watchmaking. More particularly, it concerns a watch movement equipped with a main barrel and an auxiliary barrel. State of the art

[0002] A classic self-winding system, in which the oscillating weight directly winds the mainspring barrel, has several drawbacks. First, if the timepiece is worn by the user or stored in a device designed to move it to power the oscillating weight, the mainspring barrel is often fully wound, and measures are needed to protect the mainspring from damage. These measures typically involve a sliding flange on the outer coil of the mainspring, which slides against the inner wall of the barrel when excessive torque is present, or a ratcheting mechanism designed to limit the maximum torque the weight can deliver to the winding mechanism. While a sliding flange is a simple solution, it is subject to significant wear and tear, requiring regular maintenance.This problem is avoided by a ratcheting system, but at the cost of increased complexity.

[0003] Furthermore, the best chronometric results are obtained when the torque acting on the regulating system is as constant as possible. When a mainspring is fully wound, its output torque is at its maximum; this torque decreases fairly rapidly during the initial part of its unwinding curve, and then decreases less rapidly over most of this curve, which provides the best chronometric properties before a rapid drop at the end due to a slowing of the regulating system.

[0004] The classic solution to this problem is a constant torque system, a rocket system or an equality winder, but these systems are complex and expensive.

[0005] If one wishes to avoid the use of a constant force system or an equalization winder, while maintaining good chronometric properties, there is therefore an advantage to staying, as far as possible, in the part of the curve on which the torque decreases gently, and not to wind the mainspring to its maximum too often.

[0006] The aim of the invention is therefore to provide a watch movement in which at least one of the aforementioned defects is at least partially overcome. Disclosure of the invention

[0007] More specifically, the invention relates to a watch movement as defined by claim 1. This watch movement comprises: at least one main barrel housing at least one mainspring and comprising a main winding mechanism arranged to wind said mainspring, and a main winding mechanism arranged to enable said mainspring to drive a horological mechanism (such as a regulating system (SR) combined with a display device (A), a striking mechanism, a calendar device, a chronograph mechanism or similar) by means of at least one gear train; at least one auxiliary barrel housing at least one auxiliary mainspring and comprising an auxiliary winding mechanism arranged to enable said auxiliary mainspring to be wound by means of a winding oscillating weight, and an auxiliary winding mechanism arranged to enable said auxiliary mainspring to wind said mainspring by means of said main winding mechanism.

[0008] Said auxiliary motor unit is arranged to be selectively blocked by a control ratchet which is arranged to release said auxiliary motor unit in order to raise said main motor spring in a punctual manner.

[0009] By these means, during normal operation of the movement, there is no torque transfer between the auxiliary mainspring and the mainspring, which can unwind normally without being wound fully by the oscillating weight too frequently, and, in certain configurations, never be wound fully. Torque transfer and winding of the mainspring are achieved by activating the control pawl to release the auxiliary mainspring at a precise moment, winding it to the extent that the torque available at the auxiliary mainspring is sufficient. This release can be achieved manually and / or automatically by a movement component, and if a permanent kinematic link between the auxiliary mainspring and the mainspring is not present, such a link will be established simultaneously by appropriate means.

[0010] In a manually triggered winding variant, the watch movement includes a manual pusher arranged to be moved by a user and to cooperate with said control ratchet to release said auxiliary motor mobile when said manual pusher is in a trigger position.

[0011] Advantageously, said manual pusher is arranged to form a kinematic link between said auxiliary motor and said main winding mechanism when said manual pusher is in said triggering position, for example by means of a linkage carried by said manual pusher.

[0012] In a variant with automatic winding, said watch movement includes an automatic pusher arranged to be moved under the control of a rotating element of the movement, said automatic pusher being arranged to cooperate with said control ratchet to release said auxiliary motor mobile when said automatic pusher is in a triggering position.

[0013] Advantageously, said automatic pusher is arranged to form a kinematic link between said auxiliary motor and said main winding mechanism when said automatic pusher is in said triggering position, for example by means of a linkage carried by said automatic pusher.

[0014] Advantageously, the rotating element is arranged to be driven in a first direction by the main drive unit, either directly or indirectly. The winding mechanism will therefore be triggered periodically.

[0015] Advantageously, the rotating element is arranged to be driven in a second direction opposite to the first by the main winding mechanism, either directly or indirectly. This can be achieved by arranging the rotating element to be driven by an output of a differential gear, the latter having a first input arranged to be driven by the main winding mechanism and a second input arranged to be driven by the main winding mechanism, but other solutions are also possible. The periodic triggering of the winding will thus be achieved according to the residual torque threshold of the main drive spring, the properties of the drive springs being able to be chosen to maintain the output torque of the main drive spring in the most constant part of its discharge curve, i.e., to avoid fully winding the main spring.

[0016] Advantageously, said rotating element is a cam, a disc carrying at least one pin, or at least one lever.

[0017] Advantageously, friction is incorporated into the kinematic chain connecting the main winding mechanism and the rotating element. This is a particularly simple solution for preventing the automatic winding mechanism from jamming if the shapes of the rotating element and the automatic pusher create such a risk. Other solutions are, of course, possible, and it is also possible to choose the shape of the automatic pusher and the rotating element in such a way that this risk is eliminated. Brief description of the drawings

[0018] Further details of the invention will become clearer upon reading the following description, made with reference to the attached drawings in which: Figure 1is a schematic plan view of a first embodiment of a watch movement according to the invention, during the normal operation of the movement; Figure 2 is a partial isometric schematic view of the motion of the figure 1 ; Figure 3 is a partial schematic plan view of the movement of the figure 1 during a reassembly on request; Figure 4 is a view similar to that of the figure 3 the manual pusher having been removed in order to show the automatic pusher, during the normal operation of the movement; Figure 5 is a view similar to the figure 4 , when an automatic winding is triggered; Figure 6 is a partial isometric schematic view of another variant with automatic winding triggering, during normal operation of the movement. Embodiments of the invention

[0019] THE Figures 1 And 2illustrate one embodiment of a watch movement according to the invention.

[0020] This movement comprises at least one main barrel 3 housing at least one mainspring (not shown) within it and comprising a main winding mechanism 5 as well as a main winding mechanism 7 arranged to drive some clockwork mechanism. In the illustrated embodiment, this clockwork mechanism is a regulating system SR (illustrated exclusively on the figure 1) of any type (for example, a conventional balance-spring escapement system or one carried by a tourbillon or single- or multi-axis carousel cage, inclined (-s) or not) whose oscillations are maintained by the force supplied by the mainspring via a suitable gear train 9, in a known manner. The gear train 9 also drives a display system A of any type. Alternatively, the horological mechanism may be a striking mechanism, a calendar device, a chronograph mechanism, or similar, driven by said gear train 9.

[0021] In the illustrated configuration, the mainspring barrel 3 has the classic design, meaning that the main winding mechanism 5 is a ratchet wheel mounted to rotate on a barrel arbor 11, which cooperates with the inner end of the mainspring. The ratchet wheel 5 is prevented from pivoting in the direction of the mainspring's unwinding by a conventional ratchet system 13, which allows the ratchet wheel 5 to pivot in the direction of the mainspring's winding.

[0022] The driving wheel 7 is a drum tooth, which meshes with the first moving wheel 9a of the gear train 9 in order to drive it. However, the reverse configuration is also possible, that is to say, the drum tooth constitutes the winding wheel, while the moving wheel fixed in rotation to the barrel arbor 11 constitutes the driving wheel.

[0023] A manual winding system (not shown) of any known type may also be provided for winding the mainspring via the main winding mechanism 5.

[0024] The watch movement 1 also includes an auxiliary barrel 15 housing an auxiliary mainspring, and an auxiliary winding wheel 17 as well as an auxiliary power wheel 19, for which the same considerations as those mentioned in connection with the main winding wheel 5 and the power wheel 7 also apply. An auxiliary ratchet system 21 performs the same function in relation to the auxiliary barrel 15 as the ratchet system 13 does for the main barrel 3.

[0025] A winding oscillating weight 23 is arranged to wind the auxiliary mainspring via a suitable winding train 25, in a known manner. Details of the type of oscillating weight 23 and the winding train 25 are not important for the present invention and may take any known form.

[0026] To prevent the auxiliary barrel 15 from unwinding due to the auxiliary drive 19, a control ratchet 27 is provided. This ratchet has a beak 27a held in contact with the teeth of the output shaft 19 of the auxiliary barrel 15 by means of a specially designed elastic return element (not shown). The control ratchet 27 also has an actuating member 27b, shown here as a lever formed with the ratchet 27. However, other solutions (pins, beaks, notches, etc., formed with or without the ratchet 27) are possible for selectively lifting the beak 27a.

[0027] The solution proposed by the present invention is to store the kinetic energy collected by the oscillating mass 23 in the auxiliary driving spring of the auxiliary barrel 15, and to supply it punctually to the main barrel, that is to say at precise moments and not continuously.

[0028] During normal operation of the movement 1, the auxiliary barrel 15 is independent of the main barrel 3; that is, there is no drive between the two. The main barrel 3 unwinds normally, and the auxiliary barrel 15 receives torque, generated by the oscillating weight 23, to wind the auxiliary mainspring.

[0029] The auxiliary barrel 15 selectively drives the main barrel 3 on an ad hoc basis, at the request of the user or automatically under the control of the movement itself.

[0030] In the embodiment illustrated on the Figures 1 And 2Both possibilities are provided for, but it is possible to provide for only one or the other.

[0031] In order to allow a user to manually control a torque transfer from the auxiliary barrel, a manual pusher 29 is provided and is movable by the user via an operating member (button, bolt or similar) provided in the case of the timepiece in which the movement 1 is integrated.

[0032] In the illustrated embodiment, the manual pusher 29 takes the form of a bar that can be moved axially against an ad hoc elastic return element, but other solutions such as a pivotally mounted lever are possible.

[0033] The manual pusher 29 carries, on the one hand, an actuator 29a arranged to cooperate with an actuating member 27b of the control pawl 27 in order to rotate the latter and thereby move its beak 27a away from the teeth of the auxiliary drive 19 of the auxiliary barrel 15, thus releasing it; and on the other hand, this pusher carries a linkage 31 arranged to kinematically connect the auxiliary drive 19 of the auxiliary barrel 15 to the main winding mechanism 5 of the main barrel 3 when the manual pusher 29 is in a trigger position corresponding to its active position. Alternatively, a linkage that meshes directly or indirectly with the auxiliary drive 19 and the main winding mechanism 5 is possible, this linkage being associated with a unidirectional rotation system if it is desired to also be able to wind the mainspring manually by a conventional winding system.

[0034] In this way, when the manual pusher 29 has been pressed, so that the linkage 31 is engaged with the auxiliary drive 19 of the auxiliary barrel 15 and the main winding drive 5 of the main barrel 3, the actuator 29a rotates the control pawl 27 to release the auxiliary drive 19 from the auxiliary barrel 15, as illustrated in the figure 3 .

[0035] Insofar as there is sufficient torque in the auxiliary barrel 15, this kinematic link and the release of the auxiliary driving wheel 19 from the auxiliary barrel 15 will cause a driving spring housed in the main barrel 3 to rise until the torque on the wheels 19 and 5 is in equilibrium.

[0036] In the case of insufficient torque available at the mobile 19, nothing happens, given that the ratchet 13 prevents the main winding mobile 5 of the main barrel from unwinding.

[0037] The method of implementation of figures 1 to 3 is also adapted to provide a kinematic link between the auxiliary drive wheel 19 of the auxiliary barrel 15 and the main winding wheel 5 of the main barrel 3 automatically, depending on the power reserve of the latter. For this purpose, a control cam 37 is mounted for rotation on a frame element, its rotations being controlled in this embodiment by a power reserve mechanism 39. The control cam 37 constitutes a rotating element of the movement arranged to be driven in rotation, but other embodiments are possible, such as a disc carrying one or more pins, one or more levers, an intermittent gear train, or the like.

[0038] Various types of power reserve mechanisms are known to those skilled in the art, whether based on worm gears, differentials, etc. The latter type is implemented in the illustrated embodiment, and the details of its construction are not important, insofar as there is a first input 41 driven directly or indirectly by the main driving wheel 7 (for example via the gear train 9), a second input 43 driven directly or indirectly by the main winding wheel 5, and an output 45 which drives the control cam 37 directly or indirectly, such that when the main barrel 3 unwinds, the control cam 37 pivots in a first direction (counter-clockwise in this case), and when the main barrel 3 is wound, the control cam 37 pivots in a second direction opposite to the first (clockwise in this case).

[0039] In the illustrated construction, a linkage 47 is provided in the kinematic linkage between the winding mechanism 5 of the main barrel 3, and another linkage 49 is provided between the output 45 and a toothed wheel 37a which is rotationally fixed to the control cam 37, but other solutions are of course possible.

[0040] The control cam 37 cooperates with a cam follower 33a carried by an automatic pusher 33, which is mounted to move in translation under the effect of a return element (not shown) arranged to keep the follower 33a in contact with the periphery of the control cam 37.

[0041] The automatic pusher 33 also carries a linkage 35, analogous to the linkage 31, and also arranged to mesh with both the driving wheel 19 of the auxiliary barrel 15 and with the main winding wheel 5 of the main barrel 3. Since the linkage 35 is not at the same height in the movement as the linkage 31, the thicknesses of the teeth of the driving wheel 19 of the auxiliary barrel 15 as well as with the main winding wheel 5 of the main barrel 3 are chosen accordingly, the main winding wheel 5 being illustrated as a double wheel in the illustrated construction.

[0042] Similar to the manual pusher 29, the automatic pusher 33 is movable in translation, but can alternatively be movable in rotation. The latter also carries an actuator 33b, which cooperates with the control ratchet 27 when it is in its trigger position in the same way as the actuator 29a when the linkage 35 is engaged with the moving parts 19 and 5, and this under the control of the control cam 37.

[0043] THE figures 4 And 5 illustrate this principle. In the figure 4 The power reserve of the main barrel 3 remains sufficient, and the cam follower 33a simply follows the circumference of the control cam 37, which is pivoting counterclockwise (according to the orientation of the figures). On the other hand, on the figure 5The cam follower 33a passed the top of the control cam 37 and fell towards its small radius portion under the effect of the return element (not shown). In doing so, the linkage 35 engaged with the teeth of the auxiliary drive wheel 19 of the auxiliary barrel 15 and the winding wheel 5 of the main barrel 3, and the actuator 33b actuated the control pawl 27 in the same manner as described above in relation to the actuator 29a.

[0044] In doing so, the auxiliary winding mechanism 19 of the auxiliary barrel 15 drives the main winding mechanism 5 of the main barrel, insofar as sufficient torque is stored there to drive the latter.

[0045] The control cam 37 is thus driven clockwise. A friction point, positioned at a suitable location in the kinematic chain between the main winding mechanism 5 and the control cam 37, prevents the latter from pivoting during automatic winding, its flank being in contact with the cam follower 33a. Preferably, this friction point is located between the toothed wheel 37a and the control cam 37. After automatic winding, the control cam 37 will begin to pivot counterclockwise again, causing the automatic pusher 33 to retract due to the shape of the cam 37. Alternatively, a suitable system allowing the cam follower 33a to retract during automatic winding can be provided if it is desired for the control cam 37 to pivot in the opposite direction (i.e., clockwise according to the illustrated construction and the orientation of the figures).Alternatively, it is also possible to choose the shape of the automatic pusher 33 (in particular at the level of the cam follower 33a) as well as the rotating element 37 in such a way that this risk does not exist.

[0046] In this embodiment, the maximum torque available at the auxiliary barrel 15 can be chosen so that the main barrel cannot be fully wound, but this is not mandatory.

[0047] There figure 6 schematically illustrates another variant for obtaining an automatic winding trigger, which differs from that of the figures 1 to 5in that the power reserve device 39 has been omitted, and the control cam 37 is simply driven by the main drive wheel 7, via the gear train 9. Consequently, the latter is always driven in the same direction (i.e., counterclockwise according to the orientation of the figures) and periodically triggers a winding in the manner described in connection with the figures 4 And 5 The winding frequency can be chosen at will, such as every 24 hours, 36 hours, or similar.

[0048] In this embodiment, the maximum torque available at the auxiliary barrel 15 can be chosen to fully wind the main barrel according to the interval between automatic windings, or not.

[0049] Finally, we reiterate that movement 1 can be configured for automatic, manual, or both on-demand winding.

[0050] Regarding usable materials, the entire range of materials used in contemporary watchmaking can be considered (metals, non-metals such as silicon, silicon compounds, synthetic diamond, sapphire, structureable glasses, ceramics, glass-ceramics, metallic glasses, polymers, composites, materials suitable for additive manufacturing, etc.). Furthermore, flexible pivots can be used for components where this makes technical sense.

[0051] Although the invention has been described in connection with particular embodiments, other variants are possible without departing from the scope of the annexed claims.

Claims

1. A watch movement (1) comprising: - at least one main barrel (3) housing at least one main mainspring and comprising a main winding wheel set (5) arranged to wind said main mainspring, as well as a main motor wheel set (7) arranged to allow said main mainspring to drive a watch mechanism via at least one gear train (9); - at least one auxiliary barrel (15) housing at least one auxiliary mainspring and comprising an auxiliary winding wheel set (17) arranged to allow the winding of said auxiliary mainspring by a winding oscillating weight (23), as well as an auxiliary motor wheel set (19) arranged to allow said auxiliary mainspring to wind said main mainspring via said main winding wheel set (5);wherein said auxiliary motor wheel (19) is arranged to be selectively blocked by a control pawl (27) which is arranged to release said auxiliary motor wheel (19) in order to wind said main motor spring punctually.; 2. Watch movement (1) according to the preceding claim, comprising a manual pusher (29) arranged to be moved by a user, said manual pusher (29) being arranged to cooperate with said control pawl (27) to release said auxiliary motor wheel set (19) when said manual pusher (29) is in a trigger position.

3. Watch movement (1) according to the preceding claim, wherein said manual pusher (29) is arranged to form a kinematic link between said auxiliary motor wheel set (19) and said main winding wheel set (5) when said manual pusher (29) is in said trigger position.

4. Watch movement (1) according to one of claims 2 and 3 in which said kinematic connection is at least partially obtained by means of a return (31) carried by said manual pusher (29).

5. Watch movement (1) according to one of the preceding claims, comprising an automatic pusher (33) arranged to be moved under the control of a rotary element (37) of the movement (1), said automatic pusher (33) being arranged to cooperate with said control pawl (27) to release said auxiliary motor wheel set (19) when said automatic pusher (33) is in a trigger position.

6. Watch movement (1) according to the preceding claim, wherein said automatic pusher (33) is arranged to form a kinematic link between said auxiliary motor wheel set (19) and said main winding wheel set (5) when said automatic pusher (33) is in said trigger position.

7. Watch movement (1) according to the preceding claim, in which said kinematic connection is at least partially obtained by means of a return (35) carried by said automatic pusher (33).

8. Clock movement (1) according to one of claims 5 to 7, wherein said rotary element (37) is arranged to be driven in a first direction by said main drive wheel set (7).

9. Watch movement (1) according to the preceding claim, wherein said rotating element (37) is arranged to be further driven in a second direction opposite to said first direction by said main winding wheel set (5).

10. Clock movement (1) according to the preceding claim, wherein said rotary element (37) is arranged to be driven by an output (45) of a differential gear (39), the latter further comprising a first input (41) arranged to be driven by said main drive wheel set (7) as well as a second input (43) arranged to be driven by said main winding wheel set (5).

11. Watch movement (1) according to one of claims 5 to 10, wherein said rotating element (37) is a cam, a disc carrying at least one pin, or at least one lever.

12. Watch movement according to one of claims 5 to 11, in which friction is provided in the kinematic chain connecting said main winding wheel set (5) and said rotating element (37).

13. Watch movement according to one of the preceding claims, in which said watch mechanism is chosen from: - a regulating system (SR) associated with a display device (A); - a striking mechanism; - a calendar device; - a chronograph mechanism.

14. Timepiece comprising a watch movement (1) according to one of claims 1 to 13.

Images