CH714862A2 - Return spring, gear train mechanism, timepiece movement, and mechanical timepiece. - Google Patents

Abstract

The invention relates to a return spring (33) for exerting a compressive force on a rocker wheel (32), arranged to be able to swing between a first position (P1) and a second position (P2), in accordance with a tilting direction (L) extending from a first position to a second position, the return spring having a fixed armature 70; and a resiliently bendable resilient spring main body (71) having a proximal end thereof forming a connecting end (72) connected to the fixed armature and having a distal end configured as a free end (73) able to come into contact with the rocker wheel, the free end being able to come into contact with the rocker wheel when it compresses the rocker wheel to its second position; and, moving from the free end to the connecting end, the spring main body is configured in a curved shape having at least two stepped series of mutually facing portions (75, 76, 77) and (78) , adjacent to each other and spaced in the radial direction passing through the central axis O5 of the rocker wheel when it is seen in the axial direction of the rocker wheel. The invention relates to the field of watchmaking.

Description

The present invention relates to a return spring, a gear train mechanism, a timepiece movement, and a mechanical timepiece.

2. Description of the Prior Art As regards the movements of timepieces, it is known that, under the action of the tilting of a rocking wheel arranged between a first wheel and a second wheel, it is possible to switch between a mode in which the transmission of energy (rotational drive torque) between the first wheel and the second wheel is permitted, and a mode in which the power transmission between the first wheel and the second wheel is interrupted.

In this case, the rocker wheel, for example, is arranged so as to be able to switch between a meshing position in which it is engaged with the second wheel, while it is in parallel engagement with the first wheel, and a release position, in which there is no more gear take-up with the second wheel, which is released. In the case where the rocker wheel is located in the engagement position, it is possible to transmit the energy transmitted to the first wheel also to the second wheel via the rocker wheel. On the other hand, in the case where the rocker wheel is located in the release position, it is possible to prevent the energy transmitted to the first wheel from being transmitted to the second wheel via the rocker wheel.

In connection with the use of a rocker wheel of this type, a technique is known according to which the rocker wheel is kept in compression using a spring disposed laterally in a direction included in the plane movement, and which goes from the release position to the engagement position - see, for example, document JP-A-2016-114 509 (Patent document 1). Examples of side springs include flat springs, U-shaped springs, and wire springs.

[0005] A technique is also known according to which the rocking wheel is held between two tilting positions formed by the engagement position and the release position using a rocker and according to which the rocking wheel is brought into position in the mesh position - see, for example, document JP-A-2014-41 124 (patent document 2) and document JP-A-2015-219 236 (patent document 3).

Furthermore, there is also known a technique according to which the rocking wheel is held in the direction of the thickness of the movement by using a holding spring or flat spring such as a washer, thanks to which the rocking wheel is positioning in the engagement position so that it can be toggled between the engagement position and the release position.

In the case of a conventional lateral spring, when the restoring force (compression force) via which the rocker wheel is compressed is large, the rocker wheel can come to bear strongly against the second wheel, such so that a large load can be applied to the rocker wheel. For example, the gear part is subject to high abrasion or the like. Furthermore, it becomes difficult for the rocker wheel to tilt from the engagement position to the release position, so that a suitable rocking movement for the rocker wheel is likely to be prevented.

In view of the above, in the case of a lateral spring, it is desirable that the return force of the spring with which the rocker wheel is compressed is reduced. In this case, however, it is necessary to make the lateral spring take an elongated shape to guarantee a large size. It is necessary to free up a large space in the plane to install the side spring. In the movement, where a large number of components are densely arranged, it is however difficult to guarantee that there is enough space to install the side spring, which means that there is still room for improvements .

On the contrary, in the case of conventional scales, the space required in the plane can be reduced compared to the case of the lateral spring. The rocker, however, is not kept in compression towards the engagement position, so that, after switching from the engagement position to the release position, it is impossible to automatically return the rocker to the mesh position, which means that in this case also there are possibilities for improvement.

For example, in the case where the second wheel is a röchet wheel capable of winding up the main spring housed in the barrel of the movement and where the rocking wheel is an oscillating transmission wheel transmitting the rotational driving torque from the winding rod to the röchet wheel, when the oscillating transmission wheel is left in the state in which it is in the release position by the rocker, a state is reached in which the gear take-off between the wheel to röchet and the oscillating transmission wheel is released. In this state, if the engagement of the pawl with the röchet wheel is released in order, for example, to allow the main barrel spring to feed the movement

CH 714 862 A2 in energy by relaxing, one might fear that this main barrel spring will relax vigorously. Thus, in such a configuration also there are possibilities for improvement, as mentioned above.

Furthermore, compared to the lateral spring, as in the case of the rocker, in the case of a conventional retaining spring or a washer, it is possible to reduce the space required in the plane. However, after the rocker wheel has switched from the engagement position to the release position, the rocker wheel cannot automatically return to the engagement position, which means that there are still possibilities here. improvement.

In addition, it is necessary to assemble the retaining spring or the washer in the direction of the thickness of the movement relative to the rocker wheel, so that, for example, when a temporary assembly is performed before the final screwing step by means of a screw or the like, the components of the timepiece are liable to come off in the direction of the thickness of the movement of their elevation or the like. This results in unsatisfactory assembly properties, which means that, there again, there are possibilities for improvement.

SUMMARY OF THE INVENTION An object of the present application is to provide a return spring, a gear train mechanism, a timepiece movement, and a mechanical timepiece which can be assembled without requiring large space in the plane, and which make it possible to compress the rocker wheel in one direction while removing the load applied to the rocker wheel.

(1) According to the present application, there is provided a return spring which exerts a compressive force on the rocking wheel, arranged so as to be able to switch between a first position and a second position, in a tilting direction s extending from a first position to a second position, the return spring including: a fixed frame; and a main body of elastically deformable spring in the form of a beam, one proximal end of which forms a connecting end connected to the fixed frame, and one distal end of which is configured as a free end which can come into contact with the rocking wheel. , the free end being capable of coming into contact with the rocking wheel when it pushes the rocking wheel towards its second position; and, going from the free end to the connecting end, the main spring body is configured in a curved shape having at least two stepped series of parts facing each other, adjacent to each other and spaced apart the radial direction passing through the central axis of the rocker wheel when the latter is seen in the axial direction of the rocker wheel.

In the return spring of the present application, when the rocker wheel moves from the second position to the first position, the main spring body undergoes elastic deformation in the radial direction in accordance with the tilting movement of the wheel. rocker. At this time, the main spring body undergoes elastic deformation so that the parts facing each other and which are adjacent to each other in a spacing in the radial direction move towards or away from each other in the tilting direction. Therefore, by using the elastic return force of the main spring body, it is possible to induce the rocker wheel to move from the first position to the second position via the free end, thus making it possible to turn the wheel swings to its second position.

In particular, from the free end to the connecting end, the main spring body has a curved shape having at least two stages of adjacent parts facing each other at a spacing in the radial direction, so that its shape occupies little space in the plane while ensuring a sufficient effective length of spring from the free end to the connecting end.

Since it is possible to guarantee a sufficient spring length for the main spring body, it is possible to reduce the compression force (the spring force using the elastic restoring force) with which the main spring body compress the rocking wheel, thus making it possible to induce the rocking wheel to move in a direction going to the second position, while removing the load applied to the rocking wheel. Furthermore, since the main spring body can take a relatively small shape according to a plan view, it is possible to mount the return spring without requiring significant space in the plane. Thus, it is possible to mount the return spring in a smaller space than in the case of a conventional spring arranged laterally.

(2) The free end may be arranged on the side of the first position of the rocker wheel and may be able to come into contact with the rocker wheel from the first position.

In this case, it is possible to encourage the rocking wheel to move towards the second position while keeping the free end with the rocking wheel on the side of the first position. Thus, it is possible to combine the return spring with the rocking wheel in a simple structure in which the free end, for example, comes to bear against the rocking wheel from the first position. Thus, the return spring can be easily mounted.

(3) The main spring body can take the form of a multi-turn spiral surrounding the rocker wheel and extending around it in the radial direction.

In this case, the main spring body is configured in the form of a spiral, so that the effective length of the spring from the free end to the connecting end of the main spring body can be made as yet bigger. Furthermore, the main spring body can be made in an even smaller shape in the plane.

CH 714 862 A2 (4) The main spring body can be made in such a way that, going in the opposite direction to that of the direction of compression from the central axis of the rocker wheel, at least one spacings formed along the tilting direction between the mutually facing and adjacent portions relative to each other is greater than the spacings formed along the tilting direction between the mutually facing and adjacent portions the relative to each other going from the central axis of the rocker wheel following the direction of compression.

In this case, the main spring body has a spiral configuration in which, for example, the spacings between the mutually adjacent and facing parts are not equivalent to each other, but is arranged in a form of spiral in which at least one of the spaces formed in the direction of tilting between two mutually adjacent and facing parts is greater than the spaces formed in the direction of rocking between the mutually adjacent parts and facing each other in the compression direction in starting from the central axis of the rocking wheel.

When the rocker wheel moves from the second position to the first position by going against the elastic force (that is to say, the compressive force) of the main spring body, the main spring body undergoes an elastic deformation so that the parts facing each other move in the direction of one another by going against the direction of compression, starting from the central axis of the rocking wheel, during the tilting of the wheel and the parts facing each other move away from each other in the direction of compression starting from the central axis of the rocker wheel. As indicated above, the main spring body produced in such a way that at least one of the spaces is arranged in the opposite direction to that of compression, starting from the central axis of the rocker wheel, so that it is possible to make the bringing together of the parts facing each other much more difficult. Thus, it is possible to cause the main spring body to undergo greater elastic deformation while preventing the facing parts from coming into mutual contact with each other. Thus, it is possible to guarantee an even greater effective spring length of the main spring body, which means that it can be produced in an even smaller shape in the plane.

Furthermore, it is possible to cause the main spring body to undergo an even greater elastic deformation while preventing the parts of the main spring body facing each other from being brought into mutual contact, so that that it is possible to cause the rocking wheel to tilt according to a greater stroke between the first position and the second position, making possible efficient use of the rocking wheel.

(5) The main spring body can be configured in the form of a spiral, in which portions curved in an Archimedean spiral around the central axis of the rocker wheel and linear portions extending linearly in the tilting direction are arranged alternately in the longitudinal direction of the main spring body.

In this case, when the rocker wheel moves from the second position to the first position, it is possible to ensure that the entire main body of the spring undergoes elastic displacement towards the first position along the tilting direction using the connecting end as the cardinal point, while causing an elastic deformation of the main spring body in the radial direction. Thus, even in the case where the compression force of the main spring body is small compared to the rocker wheel, it is possible to effectively encourage the rocker wheel to move to the second position.

(6) The connecting end being arranged in a position offset with respect to an imaginary axis passing through the central axis of the rocker wheel and extending along the tilting direction; and the main spring body as a whole being capable of elastic displacement in the tilting direction using the connecting end as a cardinal point.

In this case, when the rocker wheel moves from the second position to the first position, it is possible to ensure that the entire main body of the spring undergoes additional elastic displacement towards the first position by using the the connecting end as a cardinal point while causing elastic deformation of the main spring body in the radial direction. Thus, even in the case where the compression force of the main spring body is small compared to the rocking wheel, it is possible to effectively keep the rocking wheel in compression towards the second position.

(7) The free end may have an annular configuration surrounding the axis of the rocker wheel from the outside in the radial direction.

In this case, the shape of the free end of the main spring body is produced in an annular configuration surrounding the axis of the rocker wheel, so that it is possible, for example, to combine the rocker wheel to the return spring reliably and simply by a simple method by which the axis is passed inside the free annular end while the free end is brought into contact with the rocker wheel. This makes it easier to mount the return spring.

In addition, the free end is configured in annular form, so that, compared to the case where the free end takes the form, for example, of a simple plate, of a rod or the like, the free end is not dice

CH 714 862 A2 advantageously brought into contact, inadvertently, with the return spring, or wedged by a peripheral structure at the time of the incorporation of the return spring. Furthermore, the disadvantage that the free end can be inadvertently crushed is limited, so that it is no longer caused to bend, for example. With regard to these aspects also, it is possible to easily mount the return spring.

(8) The fixed frame may have an annular shape surrounding the main spring body from the outside in the radial direction.

In this case, the fixed frame is configured in annular form, so that it is possible to support the main spring body in a stable manner as if it were carried by a beam, which implies little vibrations, and makes it possible to achieve the aforementioned goals by using the main spring body more appropriately. Furthermore, since the fixed frame surrounds the main spring body, the main spring body does not easily interfere with other components of the timepiece. Thus, it is possible to make improvements in terms of operational reliability of the main spring body.

(9) A gear train mechanism according to the present application is equipped with the above return spring.

In this case, thanks to the provision of such a return spring, it is possible to form a gear train mechanism using little space in the plane.

(10) The gear train mechanism can comprise: a crown wheel driven in rotation following the actuation of a winding stem;

a transmission wheel transmitting energy to a ratchet wheel moving up, by means of the rotary drive, a main barrel spring housed inside the barrel of the movement; and the rocking wheel, which is disposed between the crown wheel and the transmission wheel, which transmits energy to the transmission wheel from the crown wheel, and which is compressed by the return spring, the first position can be used as a release position where the engagement of the rocking wheel with the transmission wheel is released and where the transmission of energy from the crown wheel to the transmission wheel is interrupted;

the second position can be used as a meshing position where the rocker wheel is in gear with the transmission wheel and where the transmission of energy from the crown wheel to the transmission wheel via the rocker wheel is permitted; and the rocker wheel which can be tilted between the release position and the engagement position along the tilting direction, and which can be kept in compression towards the engagement position by the return spring.

In this case, since the rocking wheel compressed by the return spring to go to the engagement position where it is engaged with the transmission wheel, thanks to the actuation in rotation of the winding rod according to a previously determined direction, it is possible to transmit energy (rotational drive torque) from the crown wheel to the transmission wheel via the rocker wheel. Therefore, it is possible to transmit energy to the röchet wheel. As a result, it is possible to wind the main barrel spring housed in the movement barrel.

On the contrary, in the case where, at the time of reassembly of the main barrel spring, the winding rod, for example, is rotated in the opposite direction to that previously determined, energy is applied to the wheel in the opposite direction via the crown wheel. The röchet wheel is regulated in rotation in the direction of the relaxation of the main barrel spring, so that the transmission wheel is also regulated in rotation, in a corresponding way, in the direction of the relaxation of the main barrel spring. Thus, the rocker wheel cannot transmit the energy which has been transmitted to it to the transmission wheel, and switches from the engagement position to the release position by turning, for example, in the direction opposite to that of the reassembly of the main barrel spring. Therefore, it is possible to interrupt the transmission of energy from the crown wheel to the transmission wheel via the rocker wheel, and to prevent any transmission of energy to the ratchet wheel.

After this, the rotary actuation of the winding rod in the opposite direction is stopped, and it is possible to automatically return the rocker wheel from the release position to the engagement position thanks to the force of compression exerted by the return spring.

Thus, it is possible to provide a gear train mechanism which is suitable for reassembly of the main barrel spring using the return spring. In particular, due to the use of the return spring, it is possible to prevent the rocking wheel from coming to bear strongly against the transmission wheel, so that it is possible to remove the load applied to the gear portion between the transmission wheel and the tilt wheel. Furthermore, it is possible to reduce the compression force of the return spring, so that the rocking wheel can be easily tilted to its release position, and smoothly.

(11) A timepiece movement according to the present application is equipped with the gear train mechanism described above.

(12) A mechanical timepiece according to the present application is equipped with the timepiece movement described above.

CH 714 862 A2 In this case, it is possible to realize the gear train mechanism itself by using a limited space in the plane, so that it is possible to provide a movement of part d watchmaking and a mechanical timepiece easily allowing an additional reduction in size and thickness.

According to the present application, it is possible to carry out the mounting operation without requiring large space in the plane, and to compress the rocker wheel in one direction while removing the load applied to the rocker wheel.

BRIEF DESCRIPTION OF THE DRAWINGS

[0046] Fig. 1 is an external view of a timepiece according to a first embodiment for the present invention. Fig. 2 is an enlarged perspective view of a peripheral part of a gear train mechanism for winding a movement shown in FIG. 1. Fig. 3 is a view in longitudinal section of the winding gear train mechanism illustrated in FIG. 2. Fig. 4 is a perspective view illustrating how a tilt wheel illustrated in FIG. 2 is tilted from a mesh position to a release position. Fig. 5 is a plan view of the return spring illustrated in FIG. 2, showing how the rocker wheel is located at the engagement position. Fig. 6 is a plan view of the return spring illustrated in FIG. 4, showing how the rocking wheel is located at the release position. Fig. 7 is a plan view of a variant for the return spring. Fig. 8 is a plan view of another variant for the return spring. Fig. 9 is a plan view of yet another variant for the return spring. Fig. 10 is a plan view of yet another variant for the return spring. Fig. 11 is a plan view of yet another variant for the return spring. Fig. 12 is an enlarged perspective view of a peripheral part of the winding train mechanism according to a second embodiment for the present invention. Fig. 13 is a view in longitudinal section of the winding gear train mechanism illustrated in FIG. 12. Fig. 14 is a perspective view illustrating a state in which the rocking wheel illustrated in FIG. 12 has switched from the engagement position to the release position. Fig. 15 is a plan view of the return spring illustrated in FIG. 12, illustrating a state in which the rocking wheel is in the engagement position. Fig. 16 is a plan view illustrating the natural state of the return spring in the state illustrated in FIG. 15. Fig. 17 is a plan view of the return spring illustrated in FIG. 14, illustrating a state in which the rocking wheel is in the release position.

DESCRIPTION OF EMBODIMENTS [First embodiment] [0048] In the following, the first embodiment for the present invention will be described with reference to the drawings.

In general, we refer to the mechanical body comprising the drive part of a timepiece as being the "movement." The complete assembly obtained after mounting the dial and the hands to this movement and placed all in a timepiece case generally called "assembly". Among the two sides of a plate constituting the base plate of the timepiece, the side where the crystal of the case of the timepiece is located (that is to say, the side where the dial) is usually called the "back side" of the movement. Among the two sides of the plate, we refer otherwise to the side where the back of the timepiece is located (that is to say, the side opposite the dial) as constituting the "front side" of the movement.

CH 714 862 A2 In the description of this embodiment, the side situated in the direction going from the dial towards the bottom of the case will be referred to as the upper face, and the opposite side will be referred to as constituting the lower side.

As illustrated in FIG. 1, a mechanical timepiece 1 according to the present embodiment has, inside a timepiece case consisting of a bottom (not shown) and a crystal 2, a movement (a movement of a part timepieces according to the present invention) 10, a dial 3 provided with a scale indicating at least one information related to time, indicator hands linked to the scale (that is to say, an hour hand 4 indicating the current time, a minute hand 5 indicating the minutes, and a second hand 6 indicating the passing seconds).

As illustrated in FIGS. 2 and 3, the movement 10 is equipped with a plate 11 constituting the base plate, and a cog bridge 12 disposed at the front of the plate 11. In FIG. 2, the gear train 12 is not shown.

At the rear of the plate 11 is arranged the dial 3. Between the gear train 12 and the plate 11, there is essentially arranged a front gear train, an exhaust controlling the rotation of the front gear train, and a regulating mechanism governing the exhaust. At the same time, a winding gear mechanism 15 (the gear train mechanism according to the present invention) winding up a main barrel spring 14 housed in a movement barrel 13. In the drawings, the front gear train, the exhaust and the regulating mechanism are not shown.

The plate 11 has a guide hole 11 a for winding rod, and a winding rod 20 is incorporated in this guide hole 11a so that it can be actuated in rotation about a first axis 01. A crown 21 illustrated in FIG. 1 is connected to the winding rod 20. Consequently, it is possible to rotate the winding rod 20 around the first axis 01 via the crown 21.

In connection with the present embodiment, a mechanical timepiece 1 known as automatic winding will be described in which the main barrel spring 14 is wound under the action of manual rotation rotation of the winding rod 20 .

The position in the axial direction of the winding rod 20 is determined by a switching device (not shown) comprising an adjustment lever, a rocker, a rocker spring, etc. A winding pinion 22 is mounted on the part of the guide shaft of the winding rod 20 so that it can be rotated relative to the winding rod 20 and be stationary in the axial direction. A clutch wheel (not shown) is mounted at the portion of the winding rod 20 located at the distal end of the winding pinion 22 so that it cannot rotate relative to the winding rod 20 and be able to move in the axial direction.

The winding pinion 22 and the clutch wheel can be brought into mutual gear engagement when, for example, the winding rod 20 is positioned at a winding position (position corresponding to the level "0 ”) Closest to movement 10 in the axial direction. Thus, in this state, the winding rod 20 is rotated via the crown 21, and this which makes it possible to rotate the winding pinion 22 via the clutch wheel around the first axis 01 which is coaxial to the winding rod 20.

Via the rotation of the winding pinion 22, it is possible to rotate the röchet wheel 23 via the winding cog mechanism 15. Furthermore, via the rotation of the röchet wheel 23, it is possible to go back the main barrel spring 14, which is the source of energy, and which is housed in the movement barrel 13.

By rotating the winding rod 20 around the first axis 01 in a first direction of rotation M1 determined beforehand, it is possible to wind the main barrel spring 14. In the case where the winding rod 20 is driven in rotation around the first axis 01 according to a second direction of rotation M2 opposite to the first direction of rotation M1, the energy transmission path from the winding rod 20 to the röchet wheel 23 is cut under the action of a rocker wheel 32 described below.

The front gear train is mainly equipped with the movement barrel 13, a center mobile (wheel & pinion), a third mobile, and a second mobile. In the drawings, the center mobile (wheel & pinion), the third mobile (wheel & pinion), and the second mobile are intentionally omitted and not shown. The center mobile (wheel & pinion), the third mobile (wheel & pinion), and the second mobile are successively driven in rotation following the rotation of the barrel of the movement 13 driven in rotation itself under the action of force elastic return of the main barrel spring 14 when the latter is raised.

The seconds hand 6 illustrated in FIG. 1 rotates according to the rotation of the second mobile - also called second mobile - and rotates at a speed regulated by the exhaust and the regulator, that is to say, at a frequency of one complete rotation per minute. The minute hand 5 rotates as a function of the rotation of the center wheel (i.e. the corresponding wheel & pinion), or the rotation of a minute wheel (not shown) rotating with the center wheel ( i.e. the corresponding wheel & pinion), and rotates at an angular speed regulated by the escapement and the regulator, that is to say, at a frequency corresponding to one complete rotation every hour. The hour wheel 4 turns as a function of the rotation of an hour wheel (not shown) rotating under the action of the rotation of the center mobile (wheel & pinion) via a minute wheel (not shown), and turns at an angular speed regulated by

CH 714 862 A2 regulator exhaust, that is to say, at a frequency corresponding to one complete rotation every 12 hours or every 24 hours.

The exhaust is equipped with an exhaust mobile (consisting of a wheel & a corresponding pinion) in gear engagement with the mobile of the seconds driven in rotation under the action of the transmitted energy. from the main barrel spring 14, and a fork ensuring that the exhaust mobile (that is to say the wheel & the pinion) is released and rotates at a regular speed, thus controlling the movement of the train '' front gear via regular oscillation of the balance-spring. The regulator is mainly equipped with a balance and a hairspring which uses the hairspring (not shown) as a source of energy and performs a rotary movement back and forth (in the normal direction / and in the direction inverse) according to a normal amplitude (oscillation angle) which is a function of the output torque applied by the barrel of the movement 13.

As illustrated in FIG. 3, the movement barrel 13 is equipped with a barrel shaft (not shown) rotatably mounted between the plate 11 and the gear train 12, and a barrel drum 13a combined with the barrel shaft so as to be able to perform a relative rotation rotation with respect to the main barrel spring 14 and housing the latter. The barrel drum 13a has a barrel teeth 13b in engagement with the center mobile (wheel & pinion).

The main barrel spring 14 is housed in the barrel drum 13a while being wound like a spiral around the barrel shaft. The main barrel spring 14 is wound up under the action of the rotation of the barrel shaft, and rotates the barrel drum 13a under the action of the elastic restoring force when it relaxes and releases the energy (rotational drive torque) transmitted to the front gear train via the center mobile.

As illustrated in FIGS. 2 and 3, the röchet wheel 23 is disposed between the barrel drum 13a and the gear train 12, and is fixed to the barrel shaft by driving or the like. The röchet wheel 23 has a röchet toothing 23a in engagement with a second transmission gear 36d of a second transmission wheel 36, and can rotate jointly with the barrel shaft according to a third direction of rotation M3 following the rotation of the second transmission wheel 36. Consequently, under the action of the rotation of the röchet wheel 23 in the third direction of rotation M3, it is possible to wind the main barrel spring 14 via the barrel shaft .

As illustrated in FIG. 2, in order to prevent the main barrel spring 14, once reassembled, from becoming empty, a pawl 24 blocking the reverse rotation of the röchet wheel 23 is engaged with the röchet wheel 23. Because of this ratchet 24, the rotation of the röchet wheel 23 according to the third direction of rotation M3 is allowed, and the rotation of the latter according to a fourth direction of rotation M4 opposite to the latter is prevented. In fig. 2, the representation of the toothed gears is simplified.

(Winding gear mechanism) As illustrated in FIGS. 2 and 3, the winding gear mechanism 15 is equipped with a crown wheel 30 driven in rotation under the rotary actuation of the winding rod 20, a manual winding gear 31 having a rocker wheel 32 and transmitting energy to the röchet wheel 23 from the crown wheel 30, and a return spring 33 compressing the rocking wheel 32 in one direction.

The crown wheel 30 is disposed between the winding rod 20 and the gear train 12, and is supported by the gear train 12 so as to be able to drive in rotation about a second axis 02 via a guide ring 40.

The cog bridge 12 has a screw hole 41 arranged to extend vertically through the cog bridge 12, and a cylindrical guide tube 42 extending downward. The unscrewing hole 41 and the guide tube 42 arranged coaxially with respect to the second axis 02.

The guide ring 40 is arranged coaxially with respect to the second axis 02, and is secured to the gear train 12 using a connecting screw 43 while being inserted from the outside of the guide tube 42 by - below the gear train 12.

The connecting screw 43 is equipped with a head 43a in contact with the guide ring 40 from below, and a rod 43b engaged by screwing in the screw hole 41, and is connected to the gear train 12 while maintaining the guide ring 40 between itself and the gear train 12.

The crown wheel 30 is mounted outside the guide ring 40 in order to be able to have a degree of freedom in relative rotation relative to the guide ring 40 around the second axis 02. The crown wheel 30 has a toothed gear 30a engaged with the winding pinion 22. Consequently, the crown wheel 30 is driven in rotation around the second axis 02 by means of the rotation of the winding pinion 22.

Thanks to the rotation of the winding rod 20 and the winding pinion 22 clockwise in the first direction of rotation M1 around the first axis 01 at the time of reassembly of the main barrel spring 14 , the crown wheel 30 rotates clockwise as indicated by the arrow in fig. 2 which is seen from above (from the bottom) (direction to which we will simply refer, in the following, as being the clockwise direction). Thus, in the case where the winding rod 20 and the winding pinion 22 are rotated around the first axis 01 in the second direction of rotation M2 which is opposite to the first direction of rotation M1, the crown wheel 30 is driven rotating counterclockwise (which will simply be referred to as clockwise).

CH 714 862 A2 In addition to the rocking wheel 32, the manual winding train 31 is also equipped with a first transmission wheel (the transmission wheel according to the present invention) 35 disposed between the plate 11 and the gear train 12, and the second transmission wheel (the transmission wheel according to the present invention) 36. The first transmission wheel 35 can rotate around the third axis 03. The second transmission wheel 36 can rotate around the fourth axis 04.

On the first transmission wheel 35, a lower lug 35a is pivotally supported by a first mortise 45a of the first bearing 45 retained by the plate 11, and an upper lug 35b is supported by a second mortise 46a of a second bearing 46 retained by the gear train 12. Examples of first bearing 45 and second bearing 46 include stones with holes formed, for example, of rubies.

The first transmission wheel 35 is equipped with a first transmission toothed gear 35c engaged with a rocker gear 32c of the rocker wheel 32 described below. Consequently, the first transmission wheel 35 can rotate around the third axis 03 under the action of the rotation of the tilt wheel 32.

On the second transmission wheel 36, a lower stud 36a is pivotally supported by a third mortise 47a of a third bearing 47 retained by the plate 11, and an upper stud 36b is pivotally supported by a fourth mortise 48a of a fourth bearing 48 retained by the gear train 12. Examples of third bearing 47 and fourth bearing 48 include stones with a hole formed, for example, from rubies.

The second transmission wheel 36 is equipped with a second transmission pinion 36c engaged with the first transmission gear 35c, and a second transmission gear 36d engaged with the teeth 23a of the röchet wheel 23 Consequently, the second transmission wheel 36 can rotate around a fourth axis 04 under the action of the rotation of the first transmission wheel 35, and can rotate the röchet wheel 23.

When reassembling the main barrel spring 14, the crown wheel 30 rotates clockwise around the second axis 02, and in doing so, the first transmission wheel 35 rotates in the direction of clockwise around the third axis 03 as indicated by the arrow in fig. 2 via the rocker wheel 32. Consequently, at the time of reassembly of the main barrel spring 14, the second transmission wheel 36 rotates anti-clockwise around the fourth axis 04 as indicated by the arrow of fig. 2. Thus, as described above, at the time of reassembly of the main barrel spring 14, the röchet wheel 23 is rotated in the third direction of rotation M3 under the action of the rotation of the second transmission wheel 36, which makes it possible to reassemble the main barrel spring 14.

(Rocking wheel) The rocking wheel 32 is arranged between the plate 11 and the gear train 12 so as to be located between the crown wheel 30 and the first transmission wheel 35, and it is movable in rotation around a fifth axis 05. The rocking wheel 32 can switch between the release position illustrated in FIG. 4 (the first position of the present invention) P1 and the engagement position illustrated in FIG. 2 (the second position according to the present invention) P2 along a first tilting hole 50 and a second tilting hole 51 in the form of elongated holes in a plan view, formed respectively in the plate 11 and the bridge cog 12.

The release position P1 is a position where the gear take-off of the rocker wheel 32 with the first transmission wheel 35 is released and where the transmission of energy to the first transmission wheel 35 from the wheel crown 30 via the rocking wheel is interrupted. The engagement position P2 is a position where the rocker wheel 32 is in gear engagement with the first transmission wheel 35 and where the transmission of energy from the crown wheel 30 to the first transmission wheel 35 via the tilt wheel 32 is permitted.

As illustrated in FIGS. 3 and 5, the first tilting hole 50 is formed in the plate 11 so as to extend in the peripheral direction of the crown wheel 30. The second tilting hole 51 is formed in the gear train 12 so as to correspond to the first tilting hole 50, and extends along the peripheral direction of the crown wheel 30. Thus, the tilting direction L of the tilting wheel 32 along the first tilting hole 50 and the second hole tilt 51 is directed along the peripheral direction of the crown wheel 30. In the drawings including FIG. 5, the radius of curvature in the tilting direction L of the rocking wheel 32 is small, so that it is schematically represented as being linear.

As illustrated in FIGS. 2 and 3, a tilting ring 55 is fitted in a first tilting hole 50 so as to be able to make a relative movement therein along the tilting direction L. The lower pin 32a of the axis of the rocking wheel 32 is fixed inside the tilting ring 55 at a predetermined interference level by plugging in or the like. Furthermore, the upper lug 32b of the axis of the rocker wheel 32 is supported by the interior of the second tilting hole 51 formed in the gear train 12 so as to be able to effect a relative movement thereon along the direction tilting L.

Thus, the axis of the rocking wheel 32 and the tilting ring 55 can move as a unit in the tilting direction L along the first tilting hole 50 and the second tilting hole 51.

CH 714 862 A2 In addition, the rocking wheel 32 is equipped with the toothed gear 32c which can be brought into engagement with the toothed gear 30a of the crown wheel 30 and the toothed gear 35c of the first transmission wheel 35. The rocking gear 32c is connected so as to be able to perform a relative rotation about the fifth axis 05 relative to the axis at which the lower stud 32a and the upper stud 32b are formed.

Consequently, the rocker wheel 32 can be rocked in the rocking direction L along the first rocker hole 50 and the second rocker hole 51 in a state in which the rocker gear 32c can rotate around of the fifth axis 05. In the present embodiment, the rotation of the rocking gear 32c around the fifth axis 05 is referred to as simply the rotation of the rocking wheel 32.

As illustrated in FIG. 2, the toothed gear 32c of the rocking wheel is engaged with the toothed gear 35c of the first transmission wheel when the rocking wheel 32 is located in the engagement position P2. As illustrated in fig. 4, it is separated and disengaged from the toothed gear 35c of the first transmission wheel when the rocker wheel 32 is located in the release position P1. As illustrated in fig. 2 and 4, however, the toothed gear 32c of the rocker wheel is constantly engaged with the toothed gear 30a of the crown wheel regardless of the tilting position of the rocker wheel 32.

Consequently, the rocker wheel 32 can switch between the release position P1 and the engagement position P2 along the tilting direction L while engaging the crown wheel 30. Consequently, the wheel rocker 32 can transmit the energy from the crown wheel 30 to the first transmission wheel 35 when it is located in the engagement position P2, and can cut this energy transmission path from the crown wheel 30 to the first transmission wheel 35 and interrupt the transmission of energy to the first transmission wheel 35 when it is located in the release position P1.

When reassembling the main barrel spring 14, the crown wheel 30 rotates clockwise around the second axis 02, while the rocker wheel 32 rotates counterclockwise d 'a watch around the fifth axis 05, as indicated by the arrow in fig. 2.

The rocker wheel 32 formed as described above is constantly encouraged to move from the release position P1 to the engagement position P2 under the action of the compressive force exerted by the return spring 33 illustrated in fig. 5.

(Return spring) As illustrated in FIGS. 2, 3, and 5, the return spring 33 encourages the rocker wheel 32 to move towards the engagement position P2 via the tilting ring 55 while it is housed in a recessed part 60 formed in the plate 11 , while keeping the rocking wheel 32 in compression towards the first transmission wheel 35. The first tilting hole 50 is formed in the bottom wall of the recessed part 60.

According to a plan view taken along the direction of the fifth axis 05 which is the central axis of the rocker wheel 32, reference is made to the direction intersecting the fifth axis 05 as being the radial direction, and refers to the direction around the fifth axis 05 as being the peripheral direction.

The return spring 33 is equipped with a fixed frame 70 in the form of a ring fixed inside the recessed part 60, and a main spring body 71 elastically deformable arranged inside the frame fixed 70 and supported in the manner of a beam relative to the fixed frame 70.

The main spring body 71 is a thin flat spring formed from a metal such as iron or nickel. Its proximal end is a connecting end 72 connected to the fixed frame 70, and its distal end is a free end 73 which can be brought into contact with the rocking wheel 32 via the tilting ring 55.

The main spring body 71 is configured in a curved shape having at least two stages of parts facing each other and adjacent to each other at a spacing in the radial direction from the free end 73 to the connecting end 72. According to the present embodiment, the main spring body 71 is configured in the form of a spiral, extending in an Archimedean spiral shape according to a polar coordinate system having as center (origin) the fifth axis 05 of the rocker wheel 32 located in the engagement position P2. Consequently, the main spring body 71 is wound so as to have several turns (windings) arranged at substantially equal radial intervals.

More specifically, the main spring body 71 has a configuration in the form of a spiral surrounding the rocker wheel 32 having four stages (multi-stage structure) from the outside in the radial direction.

As illustrated in FIG. 5, the main spring body 71 is equipped with an inner peripheral spring part 75 including the free end 73 and located at the innermost part in the radial direction, a first intermediate spring part 76 surrounding the part inner peripheral spring 75 from the outside in the radial direction, a second intermediate spring portion 77 surrounding the first intermediate spring portion 76 from the outside in the radial direction, and an outer peripheral spring portion 78 including the end link 72, surrounding the second intermediate spring portion 77 from the outside in the radial direction, and located at the outermost portion in the radial direction, and has a spiral configuration, in which these portions are connected to each other without discontinuity along the Archimedes spiral.

CH 714 862 A2 [0102] The inner peripheral spring part 75, the first intermediate spring part 76, the second intermediate spring part 77, and the outer peripheral spring part 78, respectively, function as the mutually facing parts mentioned above. Thus, the main spring body 71 according to the present embodiment has a spiral configuration with four stages, that is to say having four parts facing each other.

Furthermore, the main spring body 71 is connected to the fixed armature 70 via the connecting end 72 so that the free end 73 maintains the rocker wheel 32 in compression towards the engagement position P2. More specifically, the main spring body 71 is connected to the fixed armature 70 via the connection end 72 so that the free end 73 is arranged in the release position P1 of the rocking wheel 32, and qu 'It comes into contact with the rocking wheel 32 via the tilting ring 55 from the side of the release position P1.

Furthermore, according to a plan view taken in the direction of the fifth axis 05, the connecting end 72 is arranged in a position offset with respect to an imaginary axis V intersecting with the fifth axis 05 and extending the along the tilting direction L. Consequently, the main spring body 71 is connected to the fixed armature 70 so that the entire main spring body is elastically deformable in the tilting direction L, using the link end 72 as a cardinal point.

The fixed frame 70 is configured in annular form, surrounding the main spring body 71 from the outside in the radial direction. According to the present embodiment, the fixed armature 70 is configured in annular form so as to extend along a side wall 61 defining the hollowed out part 60 formed in the plate 11, and is arranged towards the interior of the side wall 61.

The fixed frame 70 has a plurality of protrusions 79 slightly swollen in the direction of the side wall 61 and formed at regular intervals along the fixed frame 70. The protrusions 79 are, for example, in close contact with the side wall 61. Consequently, the fixed frame 70 is disposed inside the hollowed-out part 60 while being parallel fitted with the inside of the side wall 61 via the plurality of protrusions 79.

(Operation of the mechanical timepiece) In the following, a description will be given of how the mechanical timepiece 1 equipped with the winding gear train mechanism 15 includes the return spring 33 constructed as described below. -above.

In the mechanical timepiece 1 according to this embodiment, in the case where the winding of the main barrel spring 14 must be carried out manually, the winding rod 20 is moved in the direction of the first axis 01 via the crown 21 in order to adjust the winding rod 20 in its position closest to the movement 10 (the position corresponding to the stage "0"). Consequently, it is possible to bring the winding pinion 22 and the rocking wheel into the mutual gear position. Thus, as illustrated in FIG. 2, the winding rod 20 is actuated in rotation in the first operating direction M1 around the first axis 01 in the position corresponding to the stage "0", whereby it is possible to transmit the energy to the wheel crown wheel 30 via the clutch wheel and the winding pinion 22, thus making it possible to rotate the crown wheel 30 clockwise around the second axis 02.

The rocker wheel 32 is encouraged to move towards the engagement position P2 under the action of the return spring 33, so that it is engaged with both the crown wheel 30 and the first transmission wheel 35. Thus, it is possible to rotate the rocking wheel 32 counterclockwise around the fifth axis 05 by rotating the crown wheel 30 and, at the same time, it is possible to rotate the first transmission wheel 35 clockwise around the third axis 03 via the rotation of the rocker wheel 32. In this way, the energy transmitted to the crown wheel 30 can be transmitted to the first transmission wheel 35 via the tilt wheel 32.

By means of the rotation of the first transmission wheel 35, it is possible to rotate the second transmission wheel 36 anticlockwise around the fourth axis 04 and, at the same time, it is possible to rotate the röchet wheel 23 in the third direction of rotation M3 following the rotation of the second transmission wheel 36. In this way, the energy transmitted to the first transmission wheel 35 can be transmitted to the röchet wheel 23 via the second transmission wheel 36.

Then, the röchet wheel 23 is rotated in the third direction of rotation M3, whereby it is possible to wind the main barrel spring 14 housed in the movement barrel 13 via the barrel shaft .

As illustrated in FIG. 4, at the time of reassembly of the main barrel spring 14, in the case where the winding rod 20 is actuated in rotation in the second direction of rotation M2, which is opposite to the first direction of rotation M1 determined previously, energy is exerted in the opposite direction on the crown wheel 30 via the clutch wheel and the winding pinion 22. Consequently, as indicated by the arrow in FIG. 4, the crown wheel 30 rotates anti-clockwise around the second axis 02. Thus, energy is exerted on the rocker wheel 32 in the reverse direction from the crown wheel 30.

Here, the röchet wheel 23 is controlled in rotation by the pawl 24 in the fourth direction of rotation M4 which is the direction of expansion of the main barrel spring 14. Thus, in correspondence with this, the first wheel of transmission

CH 714 862 A2 and the second transmission wheel 36 are regulated in rotation in the direction of expansion of the main barrel spring 14. In other words, the first transmission wheel 35 is regulated in an anticlockwise direction. rotation around the third axis 03, and the second transmission wheel 36 is regulated in rotation clockwise around the fourth axis 04.

Thus, the rocker wheel 32 cannot transmit the energy which has been transmitted to it from the crown wheel 30 to the first transmission wheel 35. The energy transmitted to the rocker wheel 32 from the wheel crown 30 is exerted so as to cause the rocking wheel 32 to move away from the first transmission wheel 35.

Consequently, the rocker wheel 32 passes from the engagement position P2 to the release position P1 along the tilting direction L by turning around the fifth axis 05 in a clockwise direction which is opposite to the direction of rotation when the main barrel spring 14 is reassembled. Consequently, it is possible to prevent the energy from the winding rod 20 from being transmitted to the röchet wheel 23.

After that, the rotary actuation of the winding rod 20 in the second direction of rotation M2 is stopped, and at the same time, thanks to the compression force attributable to the return spring 33, it is possible to reposition automatically the rocking wheel 32 in the engagement position P2 from the release position P1. Thus, as illustrated in FIG. 2, it is possible to return the rocker wheel 32 to a state of gear taking state both with respect to the crown wheel 30 and the first transmission wheel 35.

In what follows, the return spring 33 will be described in detail.

When the rocker wheel 32 passes from the engagement position P2 illustrated in FIGS. 2 and 5 to the release position P1 illustrated in figs. 4 and 6, the main spring body 71 undergoes elastic deformation in the radial direction following the tilting of the rocking wheel 32, the free end 73 being in contact with the rocking wheel 32 from the release position P1 via the tilting ring 55. At this time, the main spring body 71 undergoes elastic deformation such that the parts facing each other and which are adjacent to each other in the radial direction at a spacing in the radial direction (c i.e., the inner peripheral spring portion 75, the first intermediate spring portion 76, the second intermediate spring portion 77, and the outer peripheral spring portion 78) move away from or closer to each other in the tilting direction L.

Consequently, by using the elastic return force of the main spring body 71, it is possible to encourage the rocker wheel 32 to move from the release position P1 illustrated in FIGS. 4 and 6 towards the engagement position P2 illustrated in FIGS. 2 and 5 via the free end 73.

[0121] Consequently, it is possible to return the rocker wheel 32 to its engagement position P2.

In particular, the main spring body 71 is configured in curved form having at least two stages of parts facing each other and adjacent to each other at a spacing in the radial direction from the free end 73 to the end of the link 72, and more specifically, configured in the form of a hairspring having four stages of mutually facing parts: the inner peripheral spring part 75, the first intermediate spring part 76, the second spring part intermediate 77 and the outer peripheral spring portion 78. Thus, it is possible to give the relatively small main spring body 71 in a plan view, while ensuring a sufficient effective spring length of the main spring body 71 of the free end 73 at connection end 72.

Since it is possible to guarantee the sufficient effective spring length of the main spring body 71, it is possible to reduce the compression force (the elastic restoring force) with which the main spring body 71 comes to compress the rocker wheel 32, thereby making it possible to compress the rocker wheel 32 in a direction towards the engagement position P2, while removing the load applied to the rocker wheel 32.

Furthermore, since it is possible to give the main spring body 71 a small shape according to a plan view, it is possible to mount the return spring 33 without requiring large space in the plane. Thus, it is possible to mount the return spring 33 in a more restricted space than in the case of a conventional lateral spring.

As described above, in the return spring 33 of this embodiment, it is possible to mount the return spring without requiring very large space in the plane and, at the same time, to compress the wheel. rocker 32 in a direction to the engagement position P2 while removing the load applied to the rocker wheel 32. In particular, in the return spring 33 of this embodiment, the main spring body 71 has a spiral configuration, so that it is possible to further increase the effective length of the spring from the free end 73 to the connecting end 72 of the main spring body 71. Furthermore, the spring of recall can take an even smaller form in plan view.

As illustrated in FIG. 5, the connecting end 72 is arranged in a position offset from the imaginary axis V, and the main spring body 71 as a whole is capable of elastic movement in the tilting direction L using the connecting end 72 as the cardinal point. Thus, as illustrated in FIG. 6, when the rocking wheel 32 tilts towards the release position P1, it is more possible to subject the whole of the main spring body 71 to an elastic displacement towards the release position P1 along the direction of

CH 714 862 A2 tilting L using the connecting end 72 as a cardinal point while subjecting the main spring body 71 to elastic deformation in the radial direction. Thus, even in the case where the compression force of the main spring body 71 is small relative to the rocker wheel 32, it is possible to effectively compress the rocker wheel 32 to the engagement position P2.

Furthermore, since the fixed frame 70 has a shape of annular configuration, it is possible to support the main spring body 71 in a stable manner in the manner of a beam involving little vibration or jolts, and properly achieve the above effect further by using the main spring body 71.

Furthermore, the winding gear mechanism 15 of this embodiment is equipped with the return spring 33 described above, so that, as illustrated in FIG. 2, the winding gear mechanism 15 itself can be produced using a reduced space in the plane. Moreover, since the return spring 33 is used, it is possible to prevent the rocker wheel 32 from being strongly compressed against the first transmission wheel 35, so that it is possible to remove the load applied to the part intended for the gear between the first transmission wheel 35 and the rocker wheel 32. Furthermore, it is possible to reduce the compression force of the return spring 33, so that it is also possible to make tip rocker wheel 32 smoothly from the release position P1.

Furthermore, in movement 10 and the mechanical timepiece 1 of this embodiment, the winding gear mechanism 15 itself can be produced using little space in the plane, so that that it is possible to provide a movement and a mechanical timepiece allowing even more reduction in size and thickness.

[Variant of the first embodiment) [0132] As illustrated in FIG. 5, in the above embodiment, the free end 73 is disposed on the side of the release position P1 of the rocker wheel 32, and is brought into contact with the rocker wheel 32 from the release position P1 via the tilting ring 55, while the rocking wheel 32 is pushed towards the engagement position P2, such a configuration should not be interpreted in a limiting manner.

For example, in FIG. 5, the free end 73 can be disposed on the side of the engagement position P2 of the rocking wheel 32, and the free end 73 can be integrally fixed to the tilting ring 55 fully secured thereto by welding or similar, or by engagement or similar. Consequently, due to the free end 73, it is possible to push the rocker wheel 32 so as to pull it into its engagement position P2 via the tilting ring 55. Thus, in this case too, it is possible to achieve the same effects.

In any event, as it is possible to compress the rocking wheel 32 towards the engagement position P2, the relative positioning of the free end 73 relative to the rocking wheel 32 can be modified according to needs. In the case of the above structure of this embodiment, however, it is possible to combine the return spring 33 with the rocker wheel 32 in a simple structure in which the free end 73 is simply held against the rocking wheel 32 from the side of the release position P1, so that the return spring 33 can be easily mounted.

Furthermore, the configuration of the return spring 33 is not limited to the form of the first embodiment described above.

For example, as illustrated in FIG. 7, it is possible to provide a return spring 80 in which a fixed frame 81 has an elliptical configuration elongated in the tilting direction L in a plan view. In this case, the size of the fixed frame 81 can be easily reduced, so that it is possible to provide a return spring 80 of even smaller construction according to a plan view. The fixed frame 81 can be configured to take, for example, a circular or rectangular shape according to a plan view.

Furthermore, instead of forming, for example, a fixed frame 91 having an annular configuration as illustrated in FIG. 8, it is also possible to provide a return spring 90 having a fixed frame 91 configured to have a shape partially surrounding the main spring body 71 from the outside in the radial direction.

In this way, according to the present invention, the configuration of the fixed frame is not limited to a specific type of construction. It can be modified as required depending, for example, on the configuration of the plate 11 or on the configuration of the recessed part 60 formed in the plate 11.

Furthermore, as illustrated in FIG. 9, it is possible to provide a return spring 100 equipped with a main spring body 101 in a spiral in which curved portions 102 are curved along an Archimedes spiral around the fifth axis 05 acting as a center (origin) of the rocker wheel 32 located at the engagement position P2, are arranged alternately with linear portions 103 extending linearly along the tilting direction L.

In this case, the inner peripheral spring part 75, the first intermediate spring part 76, the second intermediate spring part 77, and the outer peripheral spring part 78 are formed by the combination of the curved portions 102 and linear portions 103.

CH 714 862 A2 In the case of the return spring 100 thus formed, the main spring body 101 has a spiral configuration equipped with linear portions 103 extending linearly along the tilting direction L, so that as the rocking wheel 32 rocks from the engagement position P2 to the release position P1, it can easily be ensured that the entire main body of spring 101 undergoes positive elastic deformation in the tilting direction L. Par Therefore, it is possible to cause the rocker wheel 32 to move efficiently from the release position P1 to the engagement position P2 along the tilting direction L, thus making it possible to compress the wheel correctly. lever 32 to the engagement position P2 even in the case where the compression force of the main spring body 101 with respect to the lever wheel 32 is t small.

Furthermore, as illustrated in FIG. 10, it is possible to provide a return spring 110 in which the fixed frame 81 illustrated in FIG. 8 and the main spring body 101 illustrated in FIG. 9 are combined with each other.

Furthermore, as illustrated in FIG. 11, it is possible to provide a return spring 120 in which the main spring body 101 illustrated in FIG. 9 is combined with the fixed frame 121 in a configuration in which the outer peripheral spring part 78 is elongated.

In the return spring 120 illustrated in FIG. 11, there is a third intermediate spring portion 122 between the second intermediate spring portion 77 and the outer peripheral spring portion 78, thereby providing a return spring 120 in which the number of windings of the main spring body 101 is larger by one. In the case of a return spring 120 having a configuration like that described above, the entire return spring 120 including the fixed frame 121 can be configured in the form of a hairspring, so that it it is possible to provide an even smaller return spring 120 according to a plan view.

(Second embodiment) [0146] In the following, a second embodiment will be described for the present invention with reference to the drawings. In this second embodiment, the parts which are the same as those of the components of the first embodiment will be indicated by the same reference numbers, and their description will not be repeated.

While in the first embodiment, the rocker wheel 32 is arranged so as to be located between the crown wheel 30 and the first transmission wheel 35, in this present embodiment, the rocker wheel 32 is arranged so as to be located between the first transmission wheel 35 and the second transmission wheel 36. Furthermore, while in the first embodiment we take as an example a return spring 33 wound with a number of turns such that the main bodies of the spring 71 are adjacent to each other and spaced at substantially identical intervals in the radial direction, according to the present embodiment described below, an example is taken of a return spring in which the main spring body is formed in such a way that the parts which face each other and which are adjacent to each other are arranged at separate intervals.

As illustrated in FIGS. 12 and 13, the winding gear mechanism of the present embodiment (the gear train mechanism of the present invention) 130 has a construction in which the rocker wheel 32 is disposed between the first transmission wheel 35 and the second transmission wheel 36. The first transmission wheel 35 is arranged so as to be engaged with the crown wheel 30, and the second transmission wheel 36 is arranged so as to be engaged with the röchet wheel 23.

In the first transmission wheel 35 of the present embodiment, the first transmission gear 35c is engaged with the gear 30a of the crown wheel 30. Consequently, the first transmission wheel 35 can rotate around the third axis 03 following the rotation of the crown wheel 30. When reassembling the main barrel spring 14, the crown wheel 30 rotates clockwise around the second axis 02, as indicated by the arrow in FIG. 12, while the first transmission wheel 35 rotates anti-clockwise around the third axis 03, as indicated by the arrow in FIG. 2.

The rocker wheel 32 can be tilted along a first tilting hole 50 and a second tilting hole 51 formed respectively in the plate 11 and the gear train 12 between the engagement position P2 illustrated in fig. 12 and 13 and the release position P1 illustrated in FIG. 14.

As illustrated in FIG. 14, the release position P1 is the position where the gear take-off of the rocking wheel 32 relative to the second transmission wheel 36 is released, and where the transmission of energy from the crown wheel 30 to the second wheel transmission 36 via the first transmission wheel 35 and the tilt wheel 32 is interrupted. As illustrated in fig. 12, the engagement position P2 is the position where the rocker wheel 32 is engaged with the second transmission wheel 36 and where the transmission of energy from the crown wheel 30 to the second transmission wheel 36 via the first transmission wheel 35 and tilt wheel 32 is permitted.

As illustrated in FIGS. 12 and 13, in the rocker wheel 32 according to the present embodiment, a rocker gear 32c is respectively engaged with a first transmission gear 35c of the first transmission wheel 35 and a second transmission pinion 36c of the second transmission wheel 36. In particular, the rocking gear 32c is engaged with the second transmission gear 36c when the rocker wheel 32 is located in the engagement position P2, and is separated from the second gear transmission 36c and is released when the rocker wheel 32 is located in the release position P1.

CH 714 862 A2 [0153] As illustrated in figs. 12 and 14, however, the rocker gear 32c is constantly engaged with the first transmission gear 35c regardless of the rocking position of the rocker wheel 32. Therefore, the rocker wheel 32 can be tilted along the tilting direction L between the release position P1 and the engagement position P2 while being in engagement with the first transmission wheel 35.

Thus, when it is located in its engagement position P2, the rocker wheel 32 can transmit energy from the crown wheel 30 via the first transmission wheel 35 to the second transmission wheel 36, and can, when it is in its release position P1, cut off any energy transmission path from the crown wheel 30 to the second transmission wheel 36 via the first transmission wheel 35 and interrupt any energy transmission to the second transmission wheel 36.

At the time of reassembly of the main barrel spring 14, the first transmission wheel 35 rotates anti-clockwise around the third axis 03, while the rocker wheel 32 rotates clockwise of a watch around the fifth axis 05 as indicated by the arrow in fig. 12. Consequently, when the main barrel spring 14 is reassembled, the second transmission wheel 36 rotates anti-clockwise around the fourth axis 04 as indicated by the arrow in FIG. 12. Thus, at the time of reassembly of the main barrel spring 14, it is possible to reassemble the main barrel spring 14 by rotating the röchet wheel 23 in the third direction of rotation M3 following the rotation of the second wheel. transmission 36.

The rocker wheel 32 having a construction like that described above is constantly caused to move from the release position P1 to the engagement position P2 under the action of the return spring 140 illustrated in FIG. 12.

[Return spring] [0159] As illustrated in FIGS. 12, 13, and 15, the return spring 140 is housed in a recess 135 for a spring formed in the plate 11. The return spring 140 encourages the rocker wheel 32 to move towards the engagement position P2 via the ring tilting 55, keeping the tilting wheel 32 in compression against the second transmission wheel 36. The first tilting hole 50 is formed in the bottom wall of the recess 135 of the spring.

A plurality of other recesses provided for housing purposes are formed in the plate 11 so as to be located side by side relative to the recess 135 of the spring. For example, one of the plurality of housing recesses is formed so as to be deeper than the recess 135 provided for the spring, and constitutes a positioning recess 136 used when incorporating the return spring 140 in the recess 135 of the spring when it is desired to disassemble the return spring 140 and remove it from its recess 135.

The return spring 140 is equipped with an annular fixed frame 141 fixed inside the recess 135 of the spring, and an elastically deformable spring main body 142 arranged inside the fixed frame 141 and supported like a beam relative to the fixed frame 141.

The fixed frame 141 has an annular configuration surrounding the main spring body 142 from the outside in the radial direction. The fixed frame 141 is configured in an annular shape extending along a side wall 135a defining the recess 135 for the spring and is at least partially fitted with the inside of the side wall 135a. Consequently, the return spring 140 is housed in the recess 135 of the spring without being detached from the latter.

A side 143 penetrating into the positioning recess 136 is formed in one piece with the fixed frame 141. As indicated above, the positioning recess 136 is formed so that it is deeper than the recess 135 of the spring, so that a spacing is formed in the direction of the fifth axis 05 between the bottom wall of the positioning recess and the flank 143. Consequently, by using this spacing , it is possible to ensure that the tip of a finger, a tool or the like can penetrate a portion above the sidewall 143, thus making it possible to push the return spring 140 upwards via the sidewall 143. Consequently, it is possible to easily release the return spring 140 from the interior of its housing, that is to say from the recess 135.

The main spring body 142 is a thin flat spring formed from a metal such as iron or nickel. Its proximal end is a connecting end 145 connected to the fixed frame 141, and its distal end is a free end 146 capable of coming into contact with the rocker wheel 32 via the tilting ring 55.

The main spring body 142 has a curved shape having, from the free end 146 to the connecting end 145, at least two stages of parts facing each other, adjacent to each other at a spacing in the radial direction. In the present embodiment, the main spring body 142 has a spiral shape surrounding the rocker wheel 32 having four stages (multi-stage structure) from the outside in the radial direction.

The free end 146 is configured in an annular shape surrounding the axis of the rocker wheel 32 from the outside in the radial direction. More specifically, the free end 146 takes the form of a ring whose internal diameter is slightly greater than that of the external diameter of the tilting ring 55, surrounding the axis of the rocking wheel 32 via the tilting ring 55 .

CH 714 862 A2 [0167] While according to the example illustrated, the free end 146 is in contact with the external peripheral surface of the tilting ring 55 without there being any spacing, slight spacing may be formed between the free end 146 and the tilting ring 55.

As illustrated in FIG. 15, the main spring body 142 is equipped with an inner peripheral spring part 150 comprising the free end 146 and situated inwards in the radial direction, a first intermediate spring part 151 surrounding the inner peripheral spring part 150 from the outside in the radial direction, a second intermediate spring part 152 surrounding the first intermediate spring part 151 from the outside in the radial direction, and an external peripheral spring part 153 including the connection end 145, surrounding the second intermediate spring portion 152 from the outside in the radial direction, and located outward in the radial direction. These parts are successively connected to each other to obtain the shape of a spiral.

The inner peripheral spring part 150, the first intermediate spring part 151, the second intermediate spring part 152, and the outer peripheral spring part 153 operate like the mutually facing parts mentioned above. Thus, together with the fact that the free end 146 has an annular shape, the main spring body 142 according to the present embodiment is configured in the form of a hairspring having four stages of parts facing each other.

The main spring body 142 is connected to the fixed frame 141 via the connection end 145 so that the free end 146 causes the rocker wheel 32 to move towards the engagement position P2. According to a plan view taken in the direction of the fifth axis 05, the connecting end 145 is disposed in a position offset with respect to an imaginary axis V intersecting with the fifth axis 05, and extending along the direction of tilting L. Consequently, the main spring body 142 is connected to the fixed frame 141 so that the main spring body taken as a whole can deform elastically in the tilting direction L using the connecting end 145 as the cardinal point.

As mentioned above, the main spring body 142 according to the present embodiment is produced in such a way that the parts facing each other and adjacent to each other are spaced from one another at unequal intervals .

More specifically, the main spring body 142 is formed as follows: on the side of the fifth axis 05 of the rocking wheel 32 in the opposite direction to that of the compressive force (that is to say, at the opposite of the direction from the release position to the engagement position P2), at least one of the spacing intervals H1, H2, and H3 along the tilting direction L formed between the mutually facing and adjacent parts relative to each other (the inner peripheral spring part 150, the first intermediate spring part 151, the second intermediate spring part 152, and the outer peripheral spring part 153) is wider than the spacing intervals H4 , H5, and H6 along the tilting direction L formed between the parts facing each other and adjacent to each other (the inner peripheral spring portion 150, the first intermediate spring portion 151, the second intermediate spring portion 152, and the outer peripheral spring portion 153) in the direction of compression (i.e., the direction from the release position P1 to the position d P2) of the fifth axis 05 of the rocking wheel 32.

Among the spacing intervals along the tilting direction L between the inner peripheral spring part 150 and the first intermediate spring part 151, the spacing interval between the parts located on the side of the fifth axis 05 opposite to the direction of compression is equal to H1, and the spacing interval of the parts located in the direction of compression with respect to the fifth axis 05 is equal to H4.

Among the spacing intervals along the tilting direction L between the first part of intermediate spring 151 and the second part of intermediate spring 152, the spacing interval of the parts located on the side of the fifth axis 05 to the opposite of the direction of compression is equal to H2, and the spacing interval of the parts located in the direction of compression with respect to the fifth axis 05 is equal to H5.

Among the spacing intervals along the tilting direction L between the second intermediate spring part 152 and the outer peripheral spring part 153, the spacing interval between the parts located on the side of the fifth axis 05 opposite to the direction of compression is equal to H3, and the spacing interval between the portions located in the direction of compression relative to the fifth axis 05 is the spacing interval H6.

According to the present embodiment, the main spring body 142 is formed in such a way that all the spacing intervals H1, H2, and H3 are larger than the spacing intervals H4, H5, and H6 ci -above. This should not however be interpreted in a limiting way. Other types of structures are acceptable as long as at least one of the spacing intervals H1, H2, and H3 is larger than the other spacing intervals H4, H5, and H6 above. As illustrated in FIG. 16, the relationship between the above spacing intervals is naturally maintained from the time the main spring body 142 is in its natural state at rest before the rocker wheel 32 is combined with the main spring body 142 In its natural state, the main spring body 142 is at rest in a position slightly offset with respect to the first tilting hole 50 in the direction of compression. Thus, by combining the main spring body 142 with the rocker wheel 32 as illustrated in FIG. 15, it is possible

CH 714 862 A2 that the main spring body 142 can cause the rocker wheel 32 to move to the engagement position P2 while maintaining the relationship between the above spacing intervals.

(Operation of the mechanical timepiece) [0179] In what follows, even in the case where the mechanical timepiece 1 equipped with the winding gear train mechanism 130 including the return spring 140 having a construction like that described above, it is possible to obtain the same effects as those of the first embodiment.

In other words, in the case where the winding of the main barrel spring 14 is carried out manually, the winding rod 20 is turned in the first direction of rotation M1 via the crown 21 as in the first embodiment, and the crown wheel 30 is driven clockwise around the second axis 02 as shown in fig. 12.

The rocker wheel 32 is encouraged to move towards the engagement position P2 under the action of the return spring 140, so that it is engaged with both the first transmission wheel 35 and the second transmission wheel 36. Thus, when the crown wheel 30 rotates, it is possible to rotate the first transmission wheel 35 anti-clockwise around the third axis 03, and, at the same time , to rotate the rocker wheel 32 clockwise around the fifth axis 05, rotating the second transmission wheel 36 counterclockwise around the fourth axis 04 when the wheel scale 32 turns. And, when the second transmission wheel 36 rotates, it is possible to rotate the röchet wheel 23 in the third direction of rotation M3.

In this way, it is possible to transmit the energy transmitted to the crown wheel 30 to the second transmission wheel 36 via the first transmission wheel 35 and the tilt wheel 32 and, moreover, it is possible to transmit energy to the röchet wheel 23 via the second transmission wheel 36. And, by turning the röchet wheel 23 in the third direction of rotation M3, it is possible to wind the main barrel spring 14 housed in the barrel of the movement 13 via the barrel shaft.

At the time of reassembly of the main barrel spring 14, in the case where, as illustrated in FIG. 14, the winding rod 20 is rotated in the second direction of rotation M2 which is opposite to the first operating direction M1 determined previously, the crown wheel 30 rotates anti-clockwise around the second axis 02, as indicated by the arrow in fig. 14. Thus, energy in the opposite direction acts on the first transmission wheel 35 from the crown wheel 30, so that the first transmission wheel 35 rotates clockwise around the third axis 03 as indicated by the arrow in fig. 14.

On the other hand, the röchet wheel 23 is regulated in the fourth direction of rotation M4 which is the direction of expansion of the main barrel spring 14 by the pawl 24, so that, correspondingly, the second transmission wheel 36 is also regulated in rotation in the direction of expansion of the main barrel spring 14. In other words, the second transmission wheel 36 is regulated in the direction of rotation of the needles of a watch around the fourth axis 04.

Thus, the rocker wheel 32 cannot transmit the energy transmitted from the first transmission wheel 35 to the second transmission wheel 36. The energy transmitted from the first transmission wheel 35 to the rocker wheel 32 is exerted so as to cause the tilt wheel 32 to move away from the second transmission wheel 36.

Therefore, while it rotates around the fifth axis 05 in the direction of clockwise which is the opposite direction to that applied at the time of reassembly of the main barrel spring 14, the rocking wheel 32 rocking along the tilting direction L from the engagement position P2 to the release position P1 illustrated in FIGS. 14 and 17. This helps to prevent energy from the winding rod 20 from being transmitted to the ratchet wheel 23.

After this, the rotation of the winding rod 20 in the second direction of rotation M2 is stopped, and in parallel, due to the compression force of the return spring 140, it is possible to automatically turn the wheel. rocker 32 from its release position P1 to its engagement position P2. Thus, as illustrated in FIG. 12, it is possible to return the tilt wheel 32 again to a state in which it is engaged with the first transmission wheel 35 and the second transmission wheel 36.

[0188] In particular, in the return spring 140 according to the present embodiment, it is possible to obtain the same effects as those of the first embodiment. In addition, it is possible to obtain the following technical effect.

When the rocker wheel 32 passes from the engagement position P2 illustrated in FIGS. 12 and 15 in the release position P1. illustrated in fig. 14 and 17 by going against the elastic force (compression force) of the main spring body 142, the main spring body 142 undergoes radial elastic deformation in correspondence with the tilting of the rocking wheel 32. At this time there, the main spring body 142 undergoes elastic deformation so that the parts facing each other and adjacent to each other at intervals in the radial direction (i.e., the spring part inner peripheral 150, the first intermediate spring portion 151, the second intermediate spring portion 152, and the outer peripheral spring portion 153) move away from or closer to each other.

CH 714 862 A2 [0190] More specifically, the elastic deformation takes place as follows: on the side of the fifth axis 05 of the rocking wheel 32 opposite the direction of compression, the parts facing each other (the part of inner peripheral spring 150, the first intermediate spring part 151, the second intermediate spring part 152 and the outer peripheral spring part 153) move away from each other, and, on the side of the direction of compression relative to the fifth axis 05 of the rocker wheel 32, the parts facing each other (the inner peripheral spring part 150, the first intermediate spring part 151, the second intermediate spring part 152, and the external peripheral spring part 153) move away from each other.

[0191] At this time, as illustrated in FIG. 15, in the main spring body 142, on the side of the fifth axis 05 of the rocking wheel 32 going opposite to the direction of compression, the spacing intervals H1, H2, and H3 between the parts facing each other (the inner peripheral spring part 150, the first intermediate spring part 151, the second intermediate spring part 152, and the outer peripheral spring part 153) is formed to be wide, so that, as illustrated in FIG . 17, it is possible to make it much more difficult to be able to bring the mutually facing parts (the inner peripheral spring part 150, the first intermediate spring part 151, the second intermediate spring part 152, and the outer peripheral spring 153) to be in mutual contact.

Thus, it is possible to cause the main spring body 142 to undergo greater elastic deformation while preventing the parts of the main spring body 142 from facing each other (the inner peripheral spring part 150, the first intermediate spring part 151, the second intermediate spring part 152, and the outer peripheral spring part 153) are not brought to come into mutual contact. Thus, it is possible to guarantee an even greater effective spring length for the main spring body 142, thus making it possible to produce it in an even smaller form according to a plan view.

Furthermore, since it is possible to cause the main spring body 142 to undergo an even greater elastic deformation while preventing the parts of the main spring body 142 facing each other (the peripheral spring part internal 150, the first intermediate spring part 151, the second intermediate spring part 152, and the external peripheral spring part 153) to be brought into mutual contact, it is possible to cause the rocking wheel 32 to rock at a greater amplitude, thus making it possible to use the tilt wheel more effectively.

Furthermore, the free end 146 of the main spring body 142 of this embodiment is configured in the form of a ring surrounding the axis of the rocker wheel 32 via the tilting ring 55, so that that it is possible to combine the rocker wheel 32 with the return spring 140 reliably and easily by bringing the free end 146 into contact with the rocker wheel 32 by a simple method, for example, of insertion of an axis inside the free end 146 in the form of a ring. Thus, it is possible to mount the return spring 140 even more easily.

In addition, the free end 146 is configured in the form of a ring, so that, compared for example to the case where the free end 146 is produced simply in the form of a plate, bar or the like, the free end 146 cannot disadvantageously be brought into inadvertent contact with a peripheral structure, or be trapped by the latter (for example, the first tilting hole 50) when the return spring 140 is incorporated. moreover, the free end 146 is not disadvantageously crushed inadvertently to undergo, for example, deformation by folding. According to this aspect also, it is possible to easily mount the return spring 140.

The embodiment of the present invention described above is given only by way of example, and is not intended to restrict the protective field of the invention. The embodiment can be implemented according to different variants, and allow various omissions, replacements, and modifications without departing from the technical scope of the present invention or departing from its spirit. The embodiment and related modifications include, for example, what can be easily designed by those skilled in the art, which is substantially identical, which is within the scope of the doctrine of equivalents etc.

For example, each of the embodiments described above by way of example consist of mechanical timepieces of the manual winding type; this should not be interpreted in a limiting manner. For example, they could consist of these mechanical timepieces suitable for both manual winding and automatic winding. In this case, at the time, for example, of automatic winding using the rotational drive torque of an oscillating weight, the rocking wheel can pass from a meshing position to a disengaging position by going against d 'a compression force of the return spring.

Furthermore, while according to the embodiments have been described in connection with the case where the rocker wheel constituting the winding gear train is compressed in one direction using the return spring, the present invention does not is not limited to the case where the return spring is used in the winding gear train mechanism.

It is only necessary that the return spring is capable of maintaining in compression the rocking wheel passing between the first position and the second position along the tilting direction, and this is applicable to various undercarriage mechanisms. gear.

CH 714 862 A2 [0200] Furthermore, while in the above embodiment, the main spring body is configured in the form of a spiral, this should not be interpreted in a limiting manner. For example, by bending multiple times, it is possible to provide a bellows-shaped spring main body in which the mutually facing parts are arranged in at least two stages at radial spacing intervals. In this case too, it is possible to obtain the same effects as those produced using the spiral configuration.

In any event, it is only necessary that the main spring body has a curved shape having at least two stages of parts facing each other and adjacent to each other at a radial spacing from the end free at the connection end.

claims

Claims (12)

1. Return spring (33) exerting a compressive force on a rocker wheel (32) arranged so as to be able to switch between a first position (P1) and a second position (P2) in a tilting direction (L) going from the first position (P1) to the second position (P2), the return spring (33) comprising: a fixed frame (70); and a spring main body (71) elastically deformable in the form of a beam, one proximal end of which forms a connecting end (72) connected to the fixed frame (70), and one distal end of which is configured as a free end (73) being able to come into contact with the rocking wheel (32), the free end being capable of coming into contact with the rocking wheel (32) when it pushes the rocking wheel (32) towards its second position ( P2); and the main spring body (71), seen in the axial direction of the rocker wheel (32), being configured, from the free end towards the connecting end, in a curved shape having at least two stepped series of parts facing each other (75, 76, 77,78), these parts being adjacent to each other, and spaced from each other in a radial direction passing through the central axis (05) of the wheel rocker (32). 2. Return spring (33) according to claim 1, the free end being arranged on the side of the first position (P1) of the rocker wheel, and being capable of coming into contact with the rocker wheel from the first position (P1). 3. Return spring (33) according to claim 1 or 2, the main spring body (71) taking the form of a multi-spiral spiral extending radially around the rocker wheel (32). 4. Return spring (33) according to claim 3, the main spring body (71) being formed so that, going in the opposite direction to that of the direction of compression from the central axis (05) of the rocking wheel (32), at least one of the spaces formed along the tilting direction (L) between the portions (75,76,77,78) facing each other and adjacent to each other is more large that the spacings formed along the tilting direction between the portions (75,76,77,78) facing each other and adjacent to each other going from the central axis (05) of the wheel rocker (32) and following the direction of compression. 5. Return spring (33) according to claim 3 or 4, the main spring body (71) having the shape of a spiral in which portions bent in an Archimedean spiral around the central axis of the wheel. rocker, and linear portions extending linearly in the tilting direction are arranged alternately in the longitudinal direction of the main spring body (71). 6. return spring (33) according to one of claims 3 to 5, the connecting end being arranged in a position offset with respect to an imaginary axis intersecting with the central axis of the rocker wheel and extending in the tilting direction; and the main spring body (71) as a whole being capable of elastic displacement in the tilting direction using the connecting end as a cardinal point. 7. Return spring (33) according to one of claims 1 to 6, the free end having an annular shape surrounding the axis of the rocker wheel (32) from the outside in the radial direction. 8. Return spring (33) according to one of claims 1 to 7, the fixed frame (70) having an annular shape surrounding the main body of the spring (71) from the outside in the radial direction. 9. Gear train mechanism comprising a return spring (33) according to one of claims 1 to 8. 10. Gear train mechanism according to claim 9, comprising: a crown wheel (30) driven in rotation following the actuation of a winding rod (20); a transmission wheel transmitting energy to a röchet wheel (23) rising, by means of its rotation, a main barrel spring (14) housed inside the barrel (13) of the movement; and the rocking wheel (32), which is arranged between the crown wheel (30) and the transmission wheel, which transmits energy to the transmission wheel from the crown wheel (30), and which is compressed by the return spring (33), CH 714 862 A2 the first position (P1) being used as the release position where the engagement of the rocking wheel with the transmission wheel is released, and where the transmission of energy from the crown wheel to the transmission wheel is interrupted; the second position (P2) being used as a meshing position where the rocking wheel is in gear engagement with the transmission wheel and where energy transmission is permitted between the crown wheel and the transmission wheel via the rocking wheel; and the rocker wheel which can be tilted between the release position and the engagement position in the tilting direction, and is kept in compression towards the engagement position by the return spring (33). 11. Timepiece movement comprising a gear train mechanism according to claim 9 or 10. 12. Mechanical timepiece comprising a timepiece movement according to claim 11.