CH716597B1 - Inverter, automatic winding mechanism, timepiece movement, and timepiece - Google Patents

Abstract

An objective of the present invention is to reduce rotational load and improve winding performance. A reverse gear (60) is provided with: a rotating shaft (65) which includes a reverse gear (73); a reversing wheel (61) which rotates under the action of energy transmitted from a power source; a rotating board (62) which is secured to the rotating shaft; and a reversing pawl (63) which is pivotally mounted on the turntable (62). The reversing wheel includes a clutch part (102) having a first engagement surface (102a) facing one direction in a circumferential direction and an inclined surface (102b) facing the other direction in the circumferential direction . The reversing pawl (63) comprises a reversing arm (122) which extends in the first direction in the circumferential direction from a second axis, and an engagement part (124) which engages with the surface of engagement in the opposite direction in the circumferential direction. The reversing pawl is armed by a spring (140). The invention also relates to an automatic winding mechanism, as well as a timepiece movement and a timepiece.

Description

BACKGROUND OF THE INVENTION

1. Field of the invention

[0001] The present invention relates to an inverter, an automatic winding mechanism, a timepiece movement, and a timepiece.

2. Description of the prior art

[0002] Mechanical timepieces are known provided with an automatic winding mechanism, such as a mechanism for winding a barrel spring. Generally, the automatic winding mechanism includes an oscillating mass which can rotate in both directions, and an inverter which converts the rotation of the oscillating mass in both directions into a rotational movement in only one direction.

Various types of inverters such as those described above are known in the prior art. For example, a reverser using an automatic clutch wheel is known as disclosed in utility model JP-UM-B-46-9887 (patent document 1) below.

[0004] The automatic clutch wheel comprises: a rotating shaft which is rotatably mounted around an axis; a clutch ratchet wheel which is fixed to the rotating shaft; a wheel which is secured to the rotating shaft so as to have a degree of rotational freedom relative to the rotating shaft; a reversing pawl which is pivotally mounted on the wheel, and it has an engagement pawl engaging the clutch ratchet wheel as well as a spring which is entirely combined with the wheel, and compresses the clutch pawl engagement on the clutch ratchet wheel.

[0005] According to the automatic clutch wheel configured as described above, when the wheel rotates in one direction around the axis relative to the rotating shaft, the reversing pawl can pivot such that the pawl of commitment can be released. Therefore, only the wheel rotates in one direction, but does not rotate the rotating shaft.

[0006] On the other hand, when the wheel rotates in the other direction around the axis relative to the rotating shaft, it is possible to maintain a state of engagement between the engagement pawl and the ratchet wheel d clutch, and thus rotate the clutch ratchet wheel and the rotating shaft with the wheel in the other direction.

[0007] Thus as described above, by using the automatic clutch wheel, even if the wheel rotates in both directions around the axis following the rotation of the oscillating mass, it is possible to always rotate the rotating shaft in the same direction. As a result, the clutch ratchet wheel can always be rotated in the same direction via the rotating shaft, and the barrel spring can thus be wound.

[0008] The automatic clutch wheel described above in the prior art is of a type called "ratchet - pusher" in which the clutch ratchet wheel is turned so as to be pushed by the pawl. commitment.

[0009] Specifically, from a state in which the engagement pawl of the reversing pawl and an engagement surface of a gear portion of the clutch ratchet wheel are in mutual engagement with each other Otherwise, the wheel rotates such that the engagement pawl pushes the engagement surface in a circumferential direction. Therefore, it is possible to rotate the reversing pawl and the clutch ratchet wheel together while maintaining an engagement state between the engagement pawl and the engagement surface.

[0010] Compared to the above configuration, when the clutch ratchet wheel rotates first, in the case where the clutch ratchet wheel rotates in a direction of rotation from the engagement pawl towards a center pivoting of the reversing pawl, it is possible to rotate the reversing pawl with the clutch ratchet wheel while maintaining the engagement state between the engagement pawl and the engagement surface. In other words, the reversing pawl is formed so as to extend from the pivot center upstream relative to the direction of rotation of the clutch ratchet wheel. Then, the engagement pawl formed at one end of the reversing pawl engages with the engagement surface of the gear part of the clutch ratchet wheel from downstream according to the direction of rotation of the clutch ratchet wheel. Therefore, when the clutch ratchet wheel rotates, the engagement pawl and the engagement surface can remain in mutual engagement with each other such that a compressive force acts on the reversing pawl , and the reversing pawl and the clutch ratchet wheel can be rotated together.

[0011] As described above, the automatic clutch wheel of the prior art is of the type called "push-pawl", and thus if the reversing pawl is formed such that the greater the length of the arm taken from the pivot center toward the engagement pawl becomes longer, the more engagement (meshing) between the engagement pawl and the engagement surface of the gear portion of the clutch ratchet wheel is likely to be insufficient, and their mutual commitment is likely to be released. Therefore, it is difficult to increase arm length.

[0012] When the reversing pawl is rotated freely relative to the clutch ratchet wheel by releasing the engagement between the engagement pawl and the engagement surface, it is required to reduce the load applied on the clutch ratchet wheel as much as possible. In order to meet these needs, it is possible to extend, for example, the arm length of the reversing ratchet in order to ensure a large distance (that is to say, a length of the arm which determines the moment of inertia in rotation) between the pivot center and the engagement pawl. Indeed, by doing so it is possible to reduce the load on the clutch ratchet wheel when the engagement pawl is pushed back against the spring.

[0013] However, as described above, since the automatic clutch wheel in the prior art is of a type called "pawl - pusher" type, it is difficult to increase the length of the pawl arm inverter itself. Therefore, it is difficult to reduce the rotational load applied to such an automatic clutch wheel. As a result, an automatic winding mechanism using an automatic clutch wheel has low winding efficiency, and there is room for improvement in winding performance.

SUMMARY OF THE INVENTION

[0014] An aim of the present patent application is to provide an inverter, an automatic winding mechanism, a timepiece movement, and a timepiece which can reduce the rotational load and which can lead to the improvement winding performance. (1) An inverter according to the patent application includes: a rotating shaft which is rotatably mounted about a first axis and has an inverter gear configured to transmit power to a drive train; a reversing wheel which is secured to the rotating shaft so as to have a relative degree of freedom in rotation with respect thereto and rotates around the first axis using energy transmitted by an energy source; a rotating board which is integrally secured to the rotating shaft; and a reversing pawl which is integrally secured to the rotating board so as to be able to pivot around a second axis. The reversing wheel comprises a plurality of reversing detent portions, each having an engagement surface oriented perpendicular to a first direction in a circumferential direction extending around the first axis, and an inclined surface oriented in the opposite direction according to the circumferential direction. The reversing pawl includes a reversing arm which extends from the second axis in the first direction in the circumferential direction, and an engagement part which is formed at one end of the reversing arm, and is arranged to be able to reversibly engage with the engagement surface in the circumferential direction. The reversing pawl is spring-loaded such that the engagement portion is held compressed against the engagement surface.

[0015] According to the inverter of the patent application, the reversing wheel is rotated around the first axis in the first direction in the circumferential direction via the energy transmitted by the energy source, and parallel to this, the plurality of reversing latch portions rotate in the same direction. At this time, since the engagement part of the reversing pawl is engaged with the engagement surface of the clutch gear part in a first direction according to the circumferential direction, it is possible to maintain a state of mutual engagement between the engagement surface and the engagement part. Therefore, the reversing pawl can be rotated in the first direction in the circumferential direction when the reversing wheel rotates.

Furthermore, by rotating the reversing pawl, the rotary shaft can be rotated in the first direction in the circumferential direction via the rotating board. Therefore, the energy transmitted to the reversing gear can be transmitted to the driving gear through the reversing gear of the rotating shaft.

[0017] Then, unlike the case described above, the reversing wheel is rotated around the first axis in the other direction in the circumferential direction due to the energy transmitted by the energy source, and parallel to this, the plurality of reversing catch portions rotate in the same direction. In this case, since the inclined surface of the clutch gear part moves above the engagement part of the reversing pawl, the reversing pawl pivots about the second axis while resisting the winding force ( compression force) of the spring. Therefore, the engagement between the engagement part and the engagement surface is released, such that the reversing wheel can rotate idly around the first axis in the reverse direction along the circumferential direction.

[0018] Therefore, when the energy for rotating the reversing wheel in the first direction in the circumferential direction is transmitted to the reversing wheel, while a state in which the engagement surface of the gear part d The clutch and the engagement part are held in mutual engagement, the entire rotating board and the rotating shaft can be rotated in the same direction, and the energy can be transmitted to the driving gear.

[0019] Furthermore, on the contrary, when energy is transmitted to the reversing wheel to make it rotate in the opposite direction in the circumferential direction, only the reversing wheel can rotate empty, and it can thus be prevented from transmitting the energy to the drive cog.

[0020] Consequently, even when the reversing wheel rotates in both directions, energy can be transmitted in such a way that the drive cog is still only rotated in one direction. Therefore, it is possible to use the inverter for example for an automatic winding mechanism.

[0021] In particular, the reversing pawl includes a reversing arm extending from the second axis, which is the pivot center, in the first direction in the circumferential direction, and the engagement part is formed at the level of the end of the reversing arm. Therefore, when the reversing wheel rotates in the first direction in the circumferential direction, the reversing pawl can be rotated so as to pull the reversing arm. Therefore, unlike the solutions of the prior art, the reversing pawl can be designed to operate as a “pull pawl” type pawl, that is to say a reversing pawl which applies a traction force to the reversing arm .

[0022] In this case, even when the length of the reversing arm is chosen to be long, unlike the ratchet of the push-pawl type according to the prior art, it is easy to maintain the state of mutual engagement between the surface of commitment and the commitment part, and it is possible to secure a state in which such mutual commitment is difficult to release. Therefore, the length of the reversing arm can be extended even further compared to what is commonly done according to the prior art, and therefore the engagement part can be pushed back with a small force against the force spring winding. Therefore, it is possible to reduce the rotational load when the reversing wheel rotates idly, i.e., freewheeling, and it is possible to improve the winding performance when the reversing wheel is used in a mechanism automatic winding or similar. (2) The engagement part can be configured to maintain a state of engagement with the engagement surface when the reversing wheel rotates about the first axis in a first direction in the circumferential direction, and release engagement with the surface engagement via the inclined surface when the reversing wheel rotates around the first axis in the other direction in the circumferential direction.

[0023] In this case, the operational effects described above can be achieved more reliably. Indeed, even when the reversing wheel rotates in both directions, the energy can be transmitted in such a way that the drive cog is still only rotated in one direction, and it is possible to use the reverser, for example, in an automatic winding mechanism or the like. (3) The rotating board may be equipped with a limiter configured to limit the amplitude of pivoting of the reversing pawl about the second axis when the engagement between the engagement part and the engagement surface is released.

[0024] In this case, when the reversing wheel rotates empty by releasing the engagement between the engagement part and the engagement surface, for example, by using a limiting element such as a stop, the pivoting of the pawl inverter around the second axis can be limited. Therefore, it is possible to prevent the reversing pawl from rotating excessively, and thereby prevent, for example, the spring from strongly and plastically deforming. Therefore, stable operation can be achieved over a long period of time, and operational reliability can be improved.

In particular, it is assumed that the reversing pawl pivots excessively when an impact due to a fall is applied or when a manual winding operation is carried out, for example. However, even in such a case, it is possible to effectively prevent the spring from being greatly deformed. (4) The spring can be formed separately from the reversing pawl, and then secured to the rotating board.

[0026] In this case, since the spring is arranged separately from the reversing pawl, the spring can be designed independently and, for example, a material, coating, or the like different from that of the reversing pawl can be selected. (5) The spring can be formed in one piece with the reversing pawl, and be integral with the rotating board.

[0027] In this case, since the reversing pawl and the spring are formed in one piece, the number of parts can be reduced, and a reduction in weight, a reduction in costs, or an improvement in the assembly can be carried out. (6) An automatic winding mechanism according to the patent application includes: the inverter as described above; an oscillating mass which is capable of rotating in both directions around a third axis and acts as a source of energy; and the drive train that connects a clutch ratchet wheel configured to wind a barrel spring to the reversing gear. A pair of reversing wheels and a pair of reversing pawls are arranged on either side of the rotating board in the direction of the first axis, the rotating board being interposed between them. Among the pair of reversing wheels, the one located closest to the reversing pinion relative to the rotating board constitutes a first reversing wheel which rotates following the rotation of the oscillating mass, and the other reversing wheel constitutes a second reversing wheel which rotates in the opposite direction to the first reversing wheel following the rotation of the oscillating mass. Among the pair of reversing pawls, the one closest to the reversing pinion opposite the rotating board constitutes a first reversing pawl which cooperates with the first reversing wheel, and the other reversing pawl constitutes a second reversing pawl which cooperates with the second reversing wheel.

[0028] According to the automatic winding mechanism of the patent application, when the oscillating mass rotates in two directions around the third axis, the first reversing wheel and the second reversing wheel rotate in opposite directions around the first axis of rotation following this rotation. Therefore, following the rotation of the oscillating mass, when the first reversing wheel rotates in the first direction in the circumferential direction, the second reversing wheel rotates in the other direction in the circumferential direction, for example.

When the first reversing wheel rotates in the first direction in the circumferential direction, the first reversing pawl rotates in the same direction with the first reversing wheel as in the case described above. Therefore, the rotating board and the rotating shaft rotate in the same direction. Therefore, the energy transmitted to the first reversing gear can be transmitted to the drive gear via the reversing gear, and can also be transmitted to the clutch ratchet wheel via the driving gear in order to move up the barrel spring.

When the first reversing wheel described above turns, the second reversing wheel turns in the other direction in the circumferential direction. At this time, the second reversing pawl rotates in the first direction in the circumferential direction following the rotation of the rotating board described above. Consequently, the second reversing wheel rotates, relative to the second reversing pawl which rotates in the first direction in the circumferential direction, in the opposite direction in the circumferential direction. Therefore, as in the case described above, the engagement surface of the clutch gear portion of the second reversing wheel and the engagement portion of the second reversing pawl are no longer in mutual engagement with each other. with the other, so that the second reversing wheel does not turn and remains at rest. Consequently, the rotating shaft is not rotated by that of the second reversing wheel.

Then, unlike the case described above, when the first reversing wheel rotates in the other direction in the circumferential direction and the second reversing wheel rotates in the first direction in the circumferential direction following the rotation of the oscillating mass , the movement is the opposite of that of the case described above, so that the energy transmitted to the second reversing wheel can be transmitted to the clutch ratchet wheel via the reversing pinion, and the barrel spring can be reassembled by rotating the clutch ratchet wheel in the same direction as before. Furthermore, since the first reversing wheel rotates empty, the rotating shaft is not rotated by that of the first reversing wheel.

Consequently, by using the energy resulting from the rotation of the oscillating mass which rotates in both directions, the rotating shaft including the reversing pinion can always be rotated in the same direction, and the barrel spring can be rewound by rotating the clutch ratchet wheel. In particular, since it is possible to reduce the rotational load when the first reversing wheel and the second reversing wheel are freewheeling, that is to say rotating empty, it is possible to improve the winding performance. (7) A timepiece movement according to the patent application includes such an automatic winding mechanism. (8) A timepiece according to the patent application includes such a timepiece movement.

[0033] In this case, since the automatic winding mechanism described above is provided, it is possible to obtain a timepiece movement and a timepiece whose winding performance is improved and which has a high reliability.

[0034] According to the teachings of the patent application, it is possible to reduce the rotational load and improve the winding performance.

BRIEF DESCRIPTION OF THE DRAWINGS

Figure 1 is a diagram representing a first embodiment according to the invention and consists of an external view of a timepiece. Figure 2 is a perspective view of an automatic winding mechanism integrated into a movement shown in Figure 1. Figure 3 is a perspective view of an inverter shown in Figure 2. Figure 4 is a view in perspective showing a state in which an upper gear of a reversing wheel is removed compared to the state shown in Figure 3. Figure 5 is a vertical sectional view of the reverser shown in Figure 3, and is a view in vertical section seen from a line A-A shown in Figure 6. Figure 6 is a plan view illustrating a relationship between an upper reversing gear, an upper reversing pawl and a spring shown in Figure 5. Figure 7 is a view in plane taken along the line B-B shown in Figure 5, and is a view illustrating a relationship between a lower reversing gear, a lower reversing pawl, and the spring. Figure 8 is a diagram representing a second embodiment according to the invention, and is a plan view illustrating a relationship between an upper reversing pinion, an upper reversing pawl, and a spring. Figure 9 is a diagram showing a third embodiment according to the invention, and is a plan view illustrating a relationship among an upper reversing gear, an upper reversing pawl, and a spring. Figure 10 is a diagram showing a fourth embodiment according to the invention, and is a plan view showing a relationship among an upper reversing gear, an upper reversing pawl, and a spring.

DESCRIPTION OF THE EMBODIMENTS

(First embodiment)

[0036] Below, a first embodiment according to the invention will be described with reference to the drawings. In the present embodiment, a mechanical timepiece with automatic winding will be described as an example of a timepiece.

(Basic configuration of a timepiece)

[0037] Generally, a mechanical body including a driving part of a timepiece is called a “movement”. In a state where a dial and hands are attached to the movement, and the movement is placed in a timepiece case to obtain a finished product, it is referred to as the “whole” timepiece. Among the two sides of a plate which constitutes an assembly plate for the timepiece, the side where the crystal of the case of the timepiece is placed (that is to say, the side where is arranged the dial) is called the “dial side” of the movement. Furthermore, among two sides of the plate, the side where the bottom of the case of the timepiece is placed (i.e. the side opposite the dial) is called the “back side” of the movement.

[0038] In the present embodiment, the direction going from the dial towards the bottom is described as the upper direction, that is to say directed towards the upper side, and the opposite side is described as being the lower side.

As shown in Figure 1, the assembly of a timepiece 1 according to the present embodiment comprises: a movement (timepiece movement according to the invention) 10; a dial 4 having an indicator or the like indicating at least one piece of information relating to the time; and hands including an hour hand 5 indicating the hours, a minute hand 6 indicating the minutes, and a seconds hand 7 indicating the seconds, which are integrated into a case 2 of a timepiece 1 comprising a back (not shown) and an ice cream 3.

The movement 10 includes a plate (not shown), a gear train bridge (not shown) and a balance bridge (not shown) arranged on the back side of the plate, or the like. Between the plate and the train bridge and the balance bridge, there are mainly arranged a front train, also called finishing train, an escapement to control the rotation of the front train, a regulation unit to adjust the escapement, a mechanism of manual winding, and an automatic winding mechanism 11 illustrated in Figure 2. In the present embodiment, the front gear, the escapement, the regulation unit, and the manual winding mechanism are not shown.

[0041] A rear gear train (not shown) or the like is arranged on the dial side of the plate, and the dial 4 is arranged so as to be visible through the glass 3.

[0042] A guide hole for the winding stem (not shown) is formed in the plate, and a winding stem 12 shown in Figure 1 is inserted into this guide hole of the winding stem 12 so as to be rotating around an axis. A crown 13 is connected to the winding stem 12. Therefore, the winding stem 12 can be rotated via the crown 13.

The position of the winding stem 12 in the axial direction is determined by a switching device (not shown) including a pull, a rocker, a rocker spring or the like. A winding pinion (not shown) is attached to a guide shaft portion of the winding stem 12 so as to be rotatable relative to the winding stem 12, but not movable in the axial direction. A clutch wheel (not shown) is attached to a portion of the winding stem 12 located closer to the distal end than the winding pinion so as not to rotate relative to the winding stem 12 and to be movable in the axial direction.

[0044] For example, when the winding rod 12 is adjusted in its position closest to the movement 10 in the axial direction (level 0 position), the winding pinion and the clutch wheel can mesh with one another. the other. Therefore, by rotating the winding stem 12 via the crown 13 in this state, the winding pinion can be rotated about a coaxial axis with the winding stem 12 via the clutch wheel.

[0045] By rotating the winding pinion, it is possible to rotate a clutch ratchet wheel 20 shown in Figure 2 via the manual winding mechanism. In addition, by rotating the clutch ratchet wheel 20, it is possible to wind a barrel spring (constituting a source of energy for the movement) housed inside the movement barrel 21.

The front gear mainly includes the movement barrel 21, a center mobile, a third mobile, and a fourth mobile, each formed of a wheel and a pinion. In the present embodiment, an illustration of the center mobile, the third mobile, and the fourth mobile is omitted. The center mobile, the third mobile, and the fourth mobile rotate in this order following the rotation of the movement barrel 21 which is rotated under the impulse of the elastic return force of the barrel spring wound on itself in the reassembled state.

The seconds hand 7 shown in Figure 1 rotates following the rotation of the fourth mobile, and rotates at a rotation speed adjusted by the escapement and the regulation unit, that is to say, one rotation per minute. The minute hand 6 turns following the rotation of the center mobile or the rotation of a center wheel (not shown) which rotates following the rotation of the center mobile, and rotates at a rotation speed adjusted by the exhaust and the regulation unit, that is to say, one rotation per hour. The hour hand 5 rotates on the basis of the rotation of an hour wheel (not shown), which rotates following the rotation of the center mobile, via a minute wheel (not shown), and rotates at a speed of rotation adjusted by the exhaust and the regulation unit, that is to say, one rotation every 12 hours or 24 hours.

[0048] The escapement includes an escapement mobile which meshes with the fourth mobile and is rotated under the impulse of energy transmitted by the barrel spring, via an anchor which lets a predetermined quantity escape and causes turn the exhaust mobile regularly. The escapement controls the front gear with regular oscillations by a balance spring. The regulating unit primarily uses a hairspring (not shown) as a power source, and includes the hairspring balance which rotates alternately in a back-and-forth motion (forward rotation followed by a backward rotation) at a constant amplitude (that is to say a predetermined oscillation angle) according to the torque applied at the output of the movement barrel 21.

[0049] As illustrated in Figure 2, the movement barrel 21 includes a barrel shaft 23 which is rotatably mounted between the plate and the gear train bridge, and a drum 22 which is combined with the barrel shaft 23 so as to to have a degree of freedom in rotation relative to the barrel shaft, 23 and in which the barrel spring is housed. The drum 22 has a barrel gear wheel 22a intended to mesh with the center mobile.

The barrel spring is housed in the drum 22 while being wound around the barrel shaft 23 in the form of a hairspring. The barrel spring is wound under the action of the rotation of the barrel shaft 23, and the drum 22 is rotated under the action of the elastic return force when the spring relaxes during operation of the watch , so as to transmit the energy (rotational torque) to the front cog through the center wheel.

The clutch ratchet wheel 20 is arranged between the drum 22 and the gear bridge, and is fixed to the barrel shaft 23 via, for example, a driving or crimping operation. The clutch ratchet wheel 20 has ratchet gear teeth 20a intended to mesh with a transmission gear wheel (not shown) which constitutes the manual winding mechanism, and can rotate around an axis 01 in a predetermined meaning.

[0052] In the present embodiment, a case is described where the clutch ratchet wheel 20 rotates clockwise as illustrated by the arrow visible in Figure 2 (to which we will simply refer below as corresponding to clockwise direction) when seen from above (bottom side) as an example.

[0053] Consequently, the barrel spring can be wound via the barrel shaft 23 by rotating the clutch ratchet wheel 20 clockwise. A second reduction wheel 52a of a second reduction mobile 52 in the automatic winding mechanism 11 described below meshes with the ratchet gear teeth 20a. Therefore, the clutch ratchet wheel 20 can be rotated clockwise via the second reduction wheel 52, and the barrel spring can be wound via the automatic winding mechanism 11.

[0054] In order to prevent the barrel spring from being uncocked, a pawl (not shown) which limits the opposite rotation of the clutch ratchet wheel 20 is engaged with the clutch ratchet wheel 20. The pawl allows allows the clutch ratchet wheel 20 to rotate clockwise, and limits counterclockwise rotation (hereinafter referred to simply as counterclockwise). clockwise), which is the direction opposite to that of the clockwise hands.

(Automatic winding mechanism)

The automatic winding mechanism 11 is a mechanism for automatically winding the barrel spring under the action of the rotation of an oscillating mass 30 whose operation results, for example, from the movement of a user's arm . This mechanism includes the oscillating mass 30, an inverter 60, an intermediate cog 40 which is arranged between the oscillating mass 30 and the inverter 60, and a transmission cog (a drive cog according to the invention) 50 which is arranged between the clutch ratchet wheel 20 and the reverser 60.

The oscillating mass 30 can rotate in both directions around an axis (third axis according to the invention) O2, and acts as a source of energy to operate the automatic winding mechanism 11.

[0057] Specifically, the oscillating mass 30 comprises a ball bearing 31, an oscillating mass body 35, and a weight 36, and rotates both clockwise and counterclockwise. clockwise around the O2 axis depending, for example, on the movements of the user's arm.

[0058] The ball bearing 31 includes an internal ring 32 fixed to a bridge (not shown), an external ring 33 surmounting the internal ring 32, and a plurality of balls (not shown) rotatably interposed between the ring internal ring 32 and the external ring 33. Consequently, the external ring 33 has a relative degree of freedom in rotation with respect to the internal ring 32 around the axis O2 via the balls. On an outer peripheral surface of the outer ring 33, an oscillating mass gear 33a is formed around the entire circumference.

The oscillating mass body 35 has a fan shape in a plan view, that is to say it extends over an angular sector strictly less than 360 degrees, and is inserted on the external ring 33 The weight 36 is attached to an outer peripheral edge of the oscillating mass body 35. Consequently, the weight 36, the oscillating mass body 35, and the outer ring 33 can be rotated integrally around of the O2 axis.

The intermediate gear 40 includes a first reversing gear 41 which rotates around an axis O3, a second reversing gear 42 which rotates around an axis O4, and a third reversing gear 43 which rotates around an axis O5 . The first reversing gear 41, the second reversing gear 42, and the third reversing gear 43 are rotatably supported by bridges (not shown), respectively.

The first reversing gear 41 includes a first reversing gear wheel 41a which meshes with the oscillating mass pinion 33a, and a first reversing gear pinion 41b. Consequently, the first reversing gear 41 can rotate around the axis O3 following the rotation of the oscillating mass 30, and can rotate in the direction opposite to that of rotation of the oscillating mass 30.

The second reversing gear 42 includes a second reversing gear wheel 42a which meshes with the first reversing gear 41b, and a second reversing gear 42b. Consequently, the second reversing gear 42 can rotate around the axis O4 following the rotation of the first reversing gear 41, and can rotate in the same direction as that of the rotation of the oscillating mass 30.

The third reversing gear 43 includes a third reversing gear wheel 43a which meshes with the second reversing gear 42b. Consequently, the third reversing gear 43 can rotate around the axis O5 following the rotation of the second reversing gear 42, and can rotate in a direction opposite to that of the rotation of the oscillating mass 30.

The transmission gear 50 includes a first reduction mobile 51 which rotates around an axis O6, and the second reduction mobile 52 which rotates around an axis O7. The first reduction mobile 51 and the second reduction mobile 52 are rotatably supported by bridges (not shown), respectively.

The first reduction wheel 51 includes: a first reduction wheel 51a which meshes with an inverter pinion 73 - described below - of the inverter 60; and a first reduction gear 51b. Consequently, the first reduction mobile 51 can be rotated around the axis O6 following a rotation of the reversing pinion 73.

[0066] In particular, the reversing pinion 73, which will be described in detail later, is configured to always rotate counterclockwise. Consequently, the first reduction mobile 51 is always rotated clockwise around the axis O6 following the rotation of the reversing pinion 73.

The second reduction wheel 52 includes the second reduction wheel 52a which meshes with the first reduction pinion 51b and the ratchet gear teeth 20a, respectively. Consequently, the second reduction mobile 52 can rotate clockwise around the axis O7 following the rotation of the first reduction mobile 51. Thus, the second reduction mobile 52 can always rotate the clutch ratchet wheel 20 clockwise as described above.

(Inverter)

[0068] As shown in Figure 2, the inverter 60 rotates around an axis (first axis) O8 under the impulse of the energy of the oscillating mass 30 transmitted through the intermediate gear train 40 described above, and plays a role of transmitting energy from the oscillating mass 30 to the clutch ratchet wheel 20 via the transmission gear 50 in a state where the two-way rotation of the oscillating mass 30 is switched to a unidirectional rotational movement .

[0069] As shown in Figures 3 to 5, the inverter 60 includes: an axis (rotary shaft according to the invention) 65 which is rotatable around the axis O8; a pair of reversing wheels 61 which are secured to the axis 65 so as to be rotatable relative to the axis 65, and which rotate around the axis O8 under the impulse of the energy transmitted by the oscillating mass 30 through the intermediate gear 40; a rotating board 62 which is integrally secured to the axis 65; and a pair of reversing pawls 63 which are integrally secured to the rotating board 62 so as to be able to pivot around a pivot axis (second axis according to the invention) O9.

[0070] According to a plan view taken in the direction of the axis O8, which is a central axis of the inverter 60, a secant direction with respect to the axis O8 is called a radial direction, and a direction following a revolutionary movement around the axis O8 is called a circumferential direction.

The axis 65 has an upper tenon 70 and a lower tenon 71 supported respectively in a rotary manner by bridges (not shown). The reversing pinion 73, with which the first reduction wheel 51a of the first reduction mobile 51 meshes, is formed on a part of the axis 65 located below the upper tenon 70. In addition, a first shoulder 74 is formed on a portion of the axis 65 located below the reversing pinion 73, and a second shoulder 75 is formed on a portion of the axis 65 located below the first shoulder 74.

[0072] A cylindrical upper seat 80 is fixed to the first shoulder 74 of the axis 65 by crimping, driving or the like. The upper seat 80 includes: a first upper support cylinder 81 which is attached to the first shoulder 74; a second upper support cylinder 82 which extends downward from a lower end of the first upper support cylinder 81 and has a diameter smaller than that of the first upper support cylinder 81; and an annular upper support flange 83 which extends outward in the radial direction from an upper end of the first upper support cylinder 81.

The upper seat 80 thus configured is fixed to the first shoulder 74 in a state where the annular upper support flange 83 comes into contact with the reversing pinion 73 from below.

[0074] A cylindrical lower support 85 is fixed to the second shoulder 75 of the axis 65 by crimping, driving or the like. The lower seat 85 includes a lower support cylinder 86 which is attached to the second shoulder 75, and an annular lower support flange 87 which extends outward in the radial direction from a lower end of the lower support cylinder 86.

The lower support 85 thus configured is fixed to the second shoulder 75 in a state located below the upper seat 80.

The rotating board 62 is fixed to the second upper support cylinder 82 by crimping, driving or the like. Consequently, the rotating board 62 is made entirely integral with the axis 65 via the upper seat 80.

[0077] In the example shown in the figure, the rotating board 62 is configured in the form of a disc having a diameter larger than that of the upper flange 83 and the lower flange 87. However, the invention is not limited to in such a case, and for example, the upper flange 83 and the lower flange 87 can be arranged so as to have diameters larger than those of the rotating board 62.

[0078] Three connecting pins 90, 91 and 92, which are arranged at regular intervals in the circumferential direction at the level of the outer peripheral edge, are fixed to the rotating board 62 by crimping, driving or the like. These connection pins 90, 91 and 92 have cylindrical shapes, and are formed so as to project towards the top and bottom of the rotating board 62.

The pair of reversing wheels 61 is arranged respectively on the upper and lower side of the rotating board 62, the latter being interposed between the two wheels.

[0080] Among the pair of reversing wheels 61, the reversing wheel 61 closest to the reversing pinion 73 relative to the rotating board 62 is described as the upper reversing wheel (first reversing wheel according to the invention) 100. Furthermore, among the pair of reversing wheels 61, the reversing wheel 61 located below the rotating board 62 is qualified as a lower reversing wheel (second reversing wheel according to the invention) 110.

The pair of reversing pawls 63 is arranged on both sides of the rotating board, that is to say the upper and lower side, and the rotating board 62 is once again interposed between the two pawls.

[0082] Among the pair of reversing pawls 63, the reversing pawl 63 closest to the reversing pinion 73 relative to the rotating board 62 is described as the upper reversing pawl (first reversing pawl according to the invention) 120 which cooperates with the wheel upper reversing pawl 100. Furthermore, among the pair of reversing pawls 63, the reversing pawl 63 located below the rotating board 62 is qualified as a lower reversing pawl (second reversing pawl according to the invention) 130 which cooperates with the reversing wheel lower 110.

[0083] In what follows, the relationship between the upper reversing wheel 100 and the upper reversing pawl 120 will be described in detail.

[0084] As illustrated in Figures 5 and 6, the upper reversing wheel 100 comprises an upper reversing pinion 101 which is combined with the first upper support cylinder 81 of the upper seat 80 so as to maintain a relative degree of freedom in rotation vis -vis the first upper support cylinder 81, and an upper reversing gear wheel 105 fixed to the upper reversing pinion 101.

[0085] The upper reversing pinion 101 has a plurality of reversing detent portions 102 over its entire circumference and also has an upper connecting cylinder 103 projecting upwards from an inner peripheral edge. The switching gear part 102 is a gear part having an engaging surface 102a oriented perpendicularly to the counterclockwise direction, which is a direction of revolution according to the circumferential direction around the axis 08, and an inclined surface 102b oriented facing clockwise, which is the opposite direction in the circumferential direction.

[0086] As illustrated in Figures 3 and 5, the upper reversing wheel gear 105 is fixed to the upper connecting cylinder 103 by crimping, driving or the like. Consequently, the entire upper reversing wheel 100 is secured to the axis 65 so as to maintain a relative degree of freedom in rotation with respect to the axis 65 through the upper seat 80. Furthermore, the gear upper reversing wheel 105 has upper reversing detent portions 105a which mesh with the second reversing gear 42b of the second reversing gear 42.

[0087] Consequently, the entire upper reversing wheel 100 can rotate around the axis O8 following rotation of the second reversing gear 42b, and can rotate in the direction opposite to the direction of rotation of the second reversing gear 42 (c that is to say, rotate in a direction opposite to the direction of rotation of the oscillating mass 30).

[0088] As shown in Figures 5 and 6, the upper reversing pawl 120 is placed on the side of the upper surface of the rotating board 62 so as to be arranged in a spacing between the rotating board 62 and the upper wheel gear reverser 105. Consequently, the upper reverser pawl 120 is arranged towards the outside of the upper reverser pinion 101 in the radial direction.

[0089] The upper reversing pawl 120 has a substantially arcuate shape so as to extend along the circumferential direction, and its central portion 121 is secured to the connecting pin 90 fixed to the rotating board 62 so as to be able to rotate relative to the connecting pin 90. Consequently, the upper reversing pawl 120 can pivot in the radial direction around the connecting pin 90.

The central axis of the connecting pin 90 is a pivot axis O9. The upper reversing pawl 120 is entirely secured to the rotating board 62 via the connecting pin 90 so as to be able to pivot around the pivot axis O9.

[0091] The upper reversing pawl 120 includes a first reversing arm (reversing arm according to the invention) 122 formed so as to extend in a clockwise direction from the central portion 121 secured to the pin. connection 90, and a second reversing arm 123 formed so as to extend from the central portion 121 in a clockwise direction. An engagement part 124 is formed at the end of the first reversing arm 122 so as to protrude inwardly in the radial direction and reversibly engages with the switching gear part 102 of the pinion upper reverser 101.

[0092] The engagement portion 124 reversibly engages the engagement surface 102a of a switching gear portion 102 in a counterclockwise direction while being in contact with the surface inclined 102b of a switching gear part 102. Therefore, the engagement part 124 engages gear so as to enter an interposed space between the adjacent reversing catch portions 102 in the direction circumferential from the outside in the radial direction.

[0093] The upper reversing pawl 120 configured as described above is armed around the pivot axis O9 by a spring 140 such that the engagement part 124 is kept compressed against the engagement surface 102a of the switching gear part 102.

[0094] The spring 140 is formed separately from the upper reversing pawl 120, and is combined with the upper surface of the rotating board 62 using the two remaining connecting pins 91 and 92 so as to be disposed in the spacing between the board rotating wheel 62 and the upper reversing wheel gear 105.

[0095] The spring 140 includes: a base 141 which is arranged on the side opposite the upper reversing pawl 120 in the radial direction, with the axis O8 interposed between them; and a spring body 142 which is formed so as to extend along the circumferential direction, and in which a proximal end 142a is connected to the base 141 and a distal end 142b compresses the second reversing arm 123 of the reversing pawl upper 120 outwards in the radial direction.

[0096] The base portion 141 has a substantially arcuate shape so as to extend along the circumferential direction, and the two ends in the circumferential direction are respectively inserted into the connection pins 91 and 92. Consequently, all the spring 140 is integrally fixed to the rotating board 62 using the two connecting pins 91 and 92.

[0097] The spring body 142 is, for example, a flat spring extending along the circumferential direction, and the distal end 142a is connected to the base 141 as described above. In the present embodiment, the spring body 142 is formed entirely with the base 141. Further, the spring body 142 is formed so as to extend counterclockwise along the circumferential direction and to wrap the base 141 from the outside from the proximal end 142a, and its distal end 142b is in contact with the second reversing arm 123 of the upper reversing pawl 120 from the inside in the radial direction.

[0098] Consequently, the spring body 142 compresses the second reversing arm 123 outwards in the radial direction using its own elastic return force. Therefore, the upper reversing pawl 120 is always cocked such that the engagement portion 124 is compressed toward the switching gear portion 102.

[0099] Since the upper reversing wheel 100 and the upper reversing pawl 120 are configured as described above, the relationship between the engagement portion 124 of the upper reversing pawl 120 and the engagement surface 102a is maintained in a state of engagement when the upper reversing wheel 100 rotates around the axis O8 counterclockwise, and this state of engagement between the engagement part 124 and the engagement surface 102a is released by the intermediate the inclined surface 102b when the upper reversing wheel 100 rotates around the axis O8 in the direction of clockwise. This point will be described in detail later.

[0100] Furthermore, the base portion 141 of the spring 140 has a stop (limiter according to the invention) 143 which projects clockwise so as to be located outside the end distal of the first reversing arm 122 of the upper reversing pawl 120 in the radial direction.

[0101] The stop 143 can limit the amplitude of the pivoting of the upper reversing pawl 120 around the pivot axis O9 when the engagement between the engagement part 124 and the engagement surface 102a is released.

[0102] Specifically, the upper reversing pawl 120 pivots around the pivot axis O9 going against a compression force (pre-tensioning or arming force) of the spring 140 such that the first reversing arm 122 moves outward in the radial direction when the engagement between the engagement part 124 and the engagement surface 102a is released. At this time, when the upper reversing pawl 120 rotates a certain degree, the first reversing arm 122 can be brought into contact with the stopper 143. Therefore, it is possible to use the stopper 143 to limit the pivoting of the upper reversing pawl 120 and preventing the upper reversing pawl 120 from rotating excessively.

[0103] In what follows, we will describe a relationship between the lower reversing wheel 110 and the lower part of the reversing pawl, that is to say the lower reversing pawl 130.

[0104] The lower reversing wheel 110 and the lower reversing pawl 130 are configured similarly to the upper reversing wheel 100 described above and the upper reversing pawl 120, and have the same relative positional relationship.

[0105] However, in the present embodiment, the lower reversing pawl 130 is arranged at a position angularly offset from the position of the upper reversing pawl 120 by an angle of 120° in the circumferential direction around the axis O8. Therefore, the lower reversing pawl 130 is secured using the connecting pin 91 instead of the connecting pin 90 to which the upper reversing pawl 120 is connected.

[0106] The invention is not, however, limited to such a configuration, and the lower reversing pawl 130 could be secured using the same connecting pin 90 so as to be arranged below and facing the upper reversing pawl 120 with the rotating board 62 interposed between them.

[0107] As illustrated in Figures 4, 5 and 7, the lower reversing wheel 110 includes a lower reversing pinion 111 which is secured to the lower support cylinder 86 of the lower seat 85 so as to be able to maintain a relative degree of freedom in rotation relative to the lower support cylinder 86, and a lower reversing gear wheel 115 fixed to the lower reversing pinion 111.

[0108] The lower reversing gear 111 has a plurality of reversing detent portions 112 over its entire circumference and also has a lower connecting cylinder 113 projecting downwards from an inner peripheral edge.

[0109] The reversal detent portion 112 is a gear part having an engagement surface 112a facing clockwise, which is one of the directions for making a revolution according to the direction circumferential around the axis 08, and an inclined surface 112b facing clockwise, which is the other direction to follow the circumferential direction.

[0110] The lower reversing wheel gear 115 is fixed to the lower connecting cylinder 113 by crimping, driving or the like. Consequently, the entire lower reversing gear 110 is secured to the axis 65 so as to maintain a relative degree of freedom in rotation with respect to the axis 65 via the lower seat 85. In addition, the lower reversing gear wheel 115 has lower reversing detent portions 115a which mesh with the third reversing gear 43a of the third reversing gear 43.

[0111] Consequently, the entire lower reversing wheel 110 can be rotated around the axis O8 following the rotation of the third reversing gear 43, and can rotate in a direction opposite to that of the rotation of the third reversing gear 43 (that is to say, rotate in the same direction as that in which the oscillating mass 30 rotates).

[0112] The lower reversing pawl 130 is arranged on the side of the upper surface of the lower reversing gear wheel 115, so as to be arranged in a spacing between the rotating board 62 and the lower reversing gear wheel 115.

[0113] The lower reversing pawl 130 is secured to the connecting pin 91 fixed to the rotating board 62 so as to maintain a relative degree of freedom in rotation with respect to the connecting pin 91, and can pivot in the radial direction around the connecting pin 91. Consequently, the lower reversing pawl 130 is entirely secured with the rotating board 62 via the connecting pin 91 so as to be able to pivot around a pivot axis 010 which is a central axis of the connecting pin 91.

[0114] The lower reversing pawl 130 includes a first reversing arm (reversing arm according to the invention) 132 formed so as to extend from a central portion 131 secured to the connecting pin 91 in the counterclockwise direction of a watch, and a second reversing arm 133 formed so as to extend from the central portion 131 in a clockwise direction.

[0115] An engagement part 134 is formed at a distal end of the first reversing arm 132 so as to protrude inwardly in the radial direction, and reversibly engages with the gear part switching 112 of the lower reversing pinion 111.

[0116] The engagement portion 134 reversibly engages the engagement surface 112a of the switching gear portion 112 from clockwise while being in contact with the inclined surface 112b of each switching gear part 112. Therefore, the engagement part 134 is engaged so as to penetrate an interposed space between the reversing catch portions 112 which are adjacent to each other in the circumferential direction from outward in the radial direction.

[0117] The lower reversing pawl 130 configured as described above is armed around the pivot axis 010 by a spring 150 so that the engagement part 134 is compressed against the engagement surface 112a of the switching gear part 112.

[0118] The spring 150 is formed separately from the lower reversing pawl 130, and is combined with an upper surface of the lower reversing gear wheel 115 using the two connecting pins 90 and 92.

[0119] The spring 150 includes a base 151 and a spring body 152.

[0120] The base 151 has a substantially arcuate shape so as to extend along the circumferential direction, and the two ends in the circumferential direction are inserted respectively at the connecting pins 90 and 92. Therefore, the entire spring 150 is fully attached to the turntable 62 using the two connecting pins 90 and 92.

[0121] Furthermore, the spring body 152 is, for example, a flat spring extending along the circumferential direction, is formed so as to extend counterclockwise along the circumferential direction to wrap the base 151 from the outside from a proximal end 152a, and its distal end 152b is in contact with the second reversing arm 133 of the lower reversing pawl 130 from the inside in the radial direction.

[0122] Consequently, the spring body 152 compresses the second reversing arm 133 outwardly in the radial direction using its own elastic restoring force. Therefore, the lower reversing pawl 130 is always cocked around the pivot axis 010 such that the engagement portion 134 is compressed toward the switching gear portion 112.

[0123] Since the lower reversing wheel 110 and the lower reversing pawl 130 are configured as described above, the relationship between the engagement portion 134 of the lower reversing pawl 130 and the engagement surface 112a maintains an engaged state. when the lower reversing wheel 110 rotates around the axis O8 counterclockwise, and this state of engagement between the engagement part 134 and the engagement surface 112a is released by the inclined surface 112b when the lower reversing wheel 110 rotates around the axis O8 clockwise.

[0124] Furthermore, the base 151 of the spring 150 has a stop (limiter according to the invention) 153 which projects clockwise so as to be located outside the distal end of the first reversing arm 132 of the lower reversing pawl 130 in the radial direction.

(Operation of the automatic winding mechanism)

[0125] In what follows, we will describe the operation of the automatic winding mechanism 11 including the inverter 60 configured as described above.

[0126] As illustrated in Figure 2, the oscillating mass 30 rotates suitably in both directions around the axis O2 depending, for example, on the movement of a user's arm. When the oscillating mass 30 rotates, the energy (rotational torque) is transmitted to the inverter 60 through the first reversing gear 41, the second reversing gear 42, and the third reversing gear 43, such that the reversing wheel upper 100 and the lower reversing wheel 110 can be rotated in opposite directions around the axis O8.

[0127] In what follows, its operation will be described specifically.

[0128] When the oscillating mass 30 shown in Figure 2 rotates in the direction of clockwise, the first reversing gear 41 can be rotated in the counterclockwise direction, the second reversing gear 42 can in turn be driven in a clockwise direction, and the third reversing gear 43 in an anti-clockwise direction. Therefore, the upper reversing gear 100 meshing with the second reversing idler gear 42b can be rotated counterclockwise, and the lower reversing gear 110 meshing with the third reversing idler gear 43a can be rotated counterclockwise, and the lower reversing gear 110 meshing with the third reversing idler gear 43a can be driven in turn in a clockwise direction.

[0129] Consequently, the upper reversing wheel 100 and the lower reversing wheel 110 can be rotated in opposite directions. Even when the oscillating mass 30 rotates counterclockwise, the directions of rotation of the respective wheels described above are only reversed, and accordingly, the upper reversing wheel 100 and the lower reversing wheel 110 can be driven to rotate in opposite directions.

[0130] For example, when the upper reversing wheel 100 turns counterclockwise following the rotation of the oscillating mass 30 in the clockwise direction, as shown in Figure 6, parallel to this, the upper reversing pinion 101 having the reversing detent portions 102 rotates counterclockwise. At this time, since the engagement part 124 of the upper reversing pawl 120 is engaged with the engagement surface 102a of the switching gear part 102 counterclockwise, the state engagement between the engagement surface 102a and the engagement part 124 can be maintained. Therefore, as shown by the arrow F1 shown in Figure 6, a rotational torque of the upper reversing wheel 100 can be transmitted to the upper reversing pawl 120, and the upper reversing pawl 120 can be rotated so as to be pulled counterclockwise.

[0131] Then, the rotating board 62 is rotated when the upper reversing pawl 120 rotates, and consequently, as shown in Figure 2, the axis 65 can be rotated counterclockwise. Therefore, energy transmitted to the upper reversing gear 100 can be transmitted to the transmission gear side 50 through the reversing gear 73, and can be transmitted to the clutch ratchet wheel 20 through the transmission gear 50 to wind the barrel spring.

[0132] In other words, the axis 65 and the reversing pinion 73 rotate in the counterclockwise direction, such that the first reduction mobile 51 can be rotated in the clockwise direction. watch and the second reduction mobile 52 driven in turn counterclockwise. Therefore, the clutch ratchet wheel 20 can be rotated clockwise, and the barrel spring can be wound.

[0133] In this regard, it will be noted that the rotating board 62 turns counterclockwise, such that, as shown in Figure 7, parallel to this, the lower reversing pawl 130 also turns in counterclockwise. In addition, when the oscillating mass 30 rotates clockwise, the lower reversing wheel 110 rotates clockwise as described above. For these reasons, the lower reversing wheel 110 rotates clockwise relative to the lower reversing pawl 130 which rotates counterclockwise.

[0134] In this case, the engagement surface 112a of the switching gear portion 112 of the lower reversing wheel gear 115 and the engagement portion 134 of the lower reversing pawl 130 are not in mutual engagement. one with the other, so that the lower reversing wheel 110 is at rest, that is to say in a state where it does not rotate. Consequently, the axis 65 and the reversing pinion 73 cannot be rotated following the rotation of the lower reversing wheel 110.

[0135] In what follows we will give some additional details on carrying out the switching operation for reassembly.

[0136] When the lower reversing wheel 110 rotates clockwise relative to the lower reversing pawl 130 which rotates counterclockwise, the inclined surface 112b of the gear part of switching 112 moves on the engagement part 134 in the circumferential direction while pushing the engagement part 134 of the lower reversing pawl 130 outward in the radial direction, as shown by an arrow F2 in Figure 7. By consequently, the lower reversing pawl 130 pivots around the pivot axis 010 against a so-called arming prestressing force (compression force) of the spring 150. Consequently, the engagement between the engagement part 134 and the surface commitment 112a is released.

[0137] Consequently, the lower reversing wheel 110 can rotate empty, that is to say freewheeling in the counterclockwise direction.

[0138] As described above, when the upper reversing wheel 100 rotates counterclockwise following the rotation of the oscillating mass 30, all the elements among the rotating board 62, the axis 65 and the reversing gear 73 can be rotated counterclockwise, and the energy can be transmitted to the transmission gear 50 while maintaining the state in which the engagement surface 102a of the part d The switching gear 102 and the engagement portion 124 of the upper reversing pawl 120 are engaged. Furthermore, at the same time, even when the lower reversing wheel 110 rotates clockwise, the lower reversing wheel 110 can rotate clockwise idle, i.e. say freewheeling so that energy cannot be transmitted from the lower reversing wheel 110 to the transmission cog 50.

[0139] Consequently, even when the upper reversing wheel 100 and the lower reversing wheel 110 rotate in opposite directions, the energy can be transmitted such that the transmission cog 50 always rotates in one and the same direction. Therefore, as shown in Figure 2, the clutch ratchet wheel 20 can be driven clockwise to wind the barrel spring.

[0140] In what follows, we will describe a case where the oscillating mass 30 illustrated in Figure 2 rotates counterclockwise.

[0141] In this case, unlike the case described above, the upper reversing wheel 100 rotates clockwise and the lower reversing wheel 110 rotates counterclockwise under the impulse of the rotation of the oscillating mass 30. Consequently, since the movement is the opposite of that corresponding to the case described above, all the elements among the rotating board 62, the axis 65 and the reversing pinion 73 can be rotated counterclockwise, and energy can be transmitted to the transmission gear 50 while maintaining an engagement state between the engagement surface 112a of the switching gear part 112 of the lower reversing wheel 110 and the engagement part 134 of the lower reversing pawl 130.

[0142] Furthermore, at the same time, the upper reversing wheel 100 can be left at rest in the direction of clockwise, such that energy cannot be transmitted from the upper reversing wheel 100 to the cog. transmission 50.

[0143] Therefore, in this case, similarly, the energy can be transmitted such that the transmission cog 50 always rotates in one direction, such that the clutch ratchet wheel 20 can be rotated clockwise to wind the barrel spring.

[0144] From the above, it will be understood that the axis 65 including the reversing pinion 73 can always be rotated in the same direction, which corresponds to the counterclockwise direction, using the energy of the oscillating mass 30 which rotates in both directions, so that the barrel spring can be wound automatically by rotating the clutch ratchet wheel 20 clockwise.

[0145] In particular, according to the reverser 60 described in the context of the present embodiment, as illustrated in Figures 6 and 7, the upper reverser pawl 120 and the lower reverser pawl 130 have first reverser arm parts 122 and 132 formed to extend counterclockwise from pivot axes O9 and 010, and engagement portions 124 and 134 are formed at their respective ends.

[0146] Consequently, for example, when the upper reversing pawl 120 is described by way of example, as shown in Figure 6, when the upper reversing wheel 100 turns counterclockwise, the first reversing pawl 63 can be rotated so as to pull the first reversing arm 122. Consequently, unlike the solutions of the prior art, the first reversing pawl 63 can be designed to operate as a traction pawl type reversing pawl, which applies a traction force to the first reversing arm 122.

[0147] In this case, even when the arm length H of the first reversing arm 122 is chosen to be substantial, unlike the “push-pawl” type pawl known from the prior art, it is easy to maintain the state engagement between the engagement surface 102a and the engagement part 124, and it is possible to secure a state in which their mutual grip is difficult to release. Therefore, the arm length H of the first reversing arm 122 can be chosen to be longer than that of the prior art, and therefore, it is possible to reduce the load applied on the upper reversing wheel 100 when the surface d The engagement 102a pushes the first reversing pawl 63 against the preloading force of the spring 140.

[0148] Consequently, since it is possible to reduce the rotational load when the upper reversing wheel 100 and the lower reversing wheel 110 rotate empty, that is to say freewheeling, it is possible to improve the winding performance.

[0149] As described above, according to the automatic winding mechanism 11 including the inverter 60 of the present embodiment and the movement 10 and the timepiece 1 including the automatic winding mechanism 11, the rotational load can be reduced and the winding performance can be improved.

[0150] Furthermore, as shown in Figures 6 and 7, the reverser 60 of the present embodiment includes the stops 143 and 153 to limit the pivoting of the upper reversing pawl 120 and the lower reversing pawl 130.

[0151] Consequently, when the upper reversing wheel 100 and the lower reversing wheel 110 rotate empty, the pivoting of the upper reversing pawl 120 and the lower reversing pawl 130 can be limited by using the stops 143 and 153, thus preventing any amplitude excessive pivoting. Therefore, for example, large deformation or substantial plastic deformation of the spring bodies 142 and 152 of the spring members 140 and 150 can be prevented. Therefore, the inverter 60 can operate stably over a long period of time, and operational reliability can be improved accordingly.

[0152] In particular, it is assumed that when an impact due to a fall or a manual winding operation using the crown 13 is carried out, the upper reversing pawl 120 and the lower reversing pawl 130 pivot excessively.

[0153] Indeed, when the clutch ratchet wheel 20 is turned clockwise by the manual winding operation, the axis 65 of the reverser 60 is forced to turn clockwise. counterclockwise via the transmission train 50. In this case, since the oscillating mass 30 is at rest, the upper reversing pawl 120 and the lower reversing pawl 130 rotate counterclockwise by relative to the upper reversing wheel 100 which is stopped and the lower reversing wheel 110, and the upper reversing pawl 120 and the lower reversing pawl 130 can easily pivot to a large amplitude while being pushed back by the reversing catch portions 102 and 112. Therefore, the spring bodies 142 and 152 tend to be easily plastically deformed.

[0154] However, even in such a case, by using the stops 143 and 153, it is possible to effectively prevent the spring bodies 142 and 152 from being greatly deformed.

[0155] Furthermore, since the spring elements 140 and 150 are formed separately from the upper reversing pawl 120 and the lower reversing pawl 130, the spring elements 140 and 150 can be designed independently of each other and, for example, a different material, coating or the like than the upper reversing pawl 120 and the lower reversing pawl 130 may be selected.

(Second embodiment)

[0156] In the following, we will describe a second embodiment according to the invention with reference to the drawings. In this second embodiment, the same components as those of the first embodiment are indicated by the same reference numbers and their description will not be repeated.

[0157] In the first embodiment, the spring bodies 142 and 152 are configured to arm the second reversing arms 123 and 133 of the upper reversing pawl 120 and the lower reversing pawl 130 outwards in the radial direction so as to come to compress the engagement parts 124 and 134 towards the reversal detent portions 102 and 112. In the second embodiment, however, the spring bodies are configured to arm the first reversing arms 122 and 132 of the pawl upper reverser 120 and the lower reverser pawl 130 inwards in the radial direction.

[0158] In this present embodiment, the upper reversing pawl 120 will be described by way of example.

[0159] As illustrated in Figure 8, an inverter 160 of the present embodiment includes a spring 161 having a spring body 162 which extends in the circumferential direction clockwise from a proximal end 162a connected to base 141.

[0160] The spring body 162 extends clockwise from the proximal end 162a towards a distal end 162b so as to wrap around the base 141 and the first reversing arm 122 of the pawl upper diverter 120 from the outside. Then, the distal end 162b of the spring body 162 exerts a compressive force against the first reversing arm 122 from the outside to the inside in the radial direction. Therefore, the engagement part 124 formed at the end of the first reversing arm 122 is armed to exert a compressive force against the switching gear part 102.

[0161] Furthermore, the stop 143 is formed so as to project counterclockwise from the base 141 so as to be located inside the distal end of the second reversing arm 123 of the upper reversing pawl 120 in the radial direction.

[0162] With the inverter 160 of the present embodiment configured as described above, it is possible to obtain the same beneficial operational effects as via the first embodiment.

(Third embodiment)

[0163] In the following, we will describe a third embodiment according to the invention with reference to the drawings. In this third embodiment, the same components as those in the second embodiment are indicated by the same reference numbers and their description will not be repeated.

[0164] In the second embodiment, an upper reversing pawl 120 and a lower reversing pawl 130 are provided, but in this present embodiment, a plurality of upper reversing pawls 120 and a plurality of lower reversing pawls 130 are provided.

[0165] In this present embodiment, the upper reversing pawl 120 will be described by way of example.

[0166] As illustrated in Figure 9, the reverser 170 of the present embodiment includes two upper reverser pawls 120. The number of upper reverser pawls 120 is not limited to two, and for example, could be three or more .

[0167] The upper reversing pawls 120 are arranged symmetrically so as to face each other in the radial direction, with the axis O8 interposed between them. Consequently, the two upper reversing pawls 120 are secured to the rotating board 62 via the connecting pins 90, respectively.

[0168] Furthermore, a flat spring 171 is formed in one piece with the upper reversing pawl 120. The spring 171 has a substantially arcuate shape extending in the circumferential direction, and a proximal end 171a disposed at its base is connected to the second reversing arm 123. Then, the spring 171 is formed so as to extend clockwise relative to the second reversing arm 123 while winding around the second reversing arm 123 by the exterior, and is arranged, in the radial direction, outside the first reversing arm 122 of the other adjacent upper reversing pawl 120 following the circumferential direction.

[0169] Then, a distal end 171b of the spring 171 exerts a compressive force against the first reversing arm 122 of the other upper reversing pawl 120 adjacent in the circumferential direction from the outside towards the inside according to the radial direction. Therefore, the engagement portions 124 formed at the distal ends of the first reversing arm 122 exert a compressive force toward the reversing snap portions 102, respectively.

[0170] Furthermore, the distal end of the second reversing arm 123 of the upper reversing pawl 120 acts as a stop (limiting element according to the invention) 173 located inside in the radial direction relative to the first reversing arm 122 of the another upper reversing pawl 120 adjacent in the circumferential direction.

[0171] With the inverter 170 according to this present embodiment configured as described above, the same beneficial operational effects can be obtained as in the first embodiment.

[0172] Furthermore, according to this present embodiment, the number of gear elements of the switching gear part 102 is an odd number. Therefore, when the engagement portion 124 of one upper reversing pawl 120 engages with the engaging surface 102a of the switching gear portion 102, the engagement portion 124 of the other upper reversing pawl 120 is released from the engagement surface 102a of the switching gear part 102.

[0173] Consequently, when the engagement part 124 of one of the upper reversing pawls 120 is released from the engagement surface 102a of the switching gear part 102 and is brought into engagement with the surface of engagement 102a of the adjacent switching gear part 102, the engagement part 124 of the other upper reversing pawl 120 can engage with the engagement surface 102a of the switching gear part 102.

[0174] Consequently, it is possible to reduce an angle called a blind angle. Indeed, the angle of rotation of the oscillating mass 30 required from the start of the inversion of the oscillating mass 30 to the restart of the rotation of the axis 65 in the counterclockwise direction is made smaller , so that it is possible to rotate the clutch ratchet wheel 20 more efficiently and wind the barrel spring.

[0175] In the third embodiment, a case is described by way of example, in which the two upper reversing pawls 120 are arranged symmetrically so as to face each other in the radial direction, with the axis O8 interposed between them, and the number of gears of the switching gear part 102 is set to be an odd number, so that when the engagement part 124 of the upper reversing pawl 120 is engaged with the surface of engagement 102a of the switching gear part 102, the engagement part 124 of the other upper reversing pawl 120 is disengaged from the engagement surface 102a of the switching gear part 102.

[0176] However, the invention is not limited to such a configuration. For example, two upper reversing pawls 120 may be arranged so as to be offset relative to each other in the circumferential direction at a predetermined angle corresponding to half of a gear member of the gear portion switching gear 102 from a symmetrical position with respect to the axis O8, and the number of gear elements of the switching gear part 102 may be an even number. Even in such a case, as for the case described above, the so-called blind angle can be reduced, and the same beneficial operational effects as described above can be achieved.

(Fourth embodiment)

[0177] In the following, we will describe a fourth embodiment according to the invention with reference to the drawings. In the fourth embodiment, the same components as those in the first embodiment are indicated by the same reference numbers and their description will not be repeated.

[0178] In the first embodiment, the upper reversing pawl 120 and the lower reversing pawl 130 are provided separately from each other, and the springs 140 and 150 are provided respectively, but in this present embodiment embodiment, a spring is integrally formed with the upper reversing pawl 120 and the lower reversing pawl 130.

[0179] In this present embodiment, the upper reversing pawl 120 will be described by way of example.

[0180] As shown in Figure 10, an inverter 180 according to this present embodiment includes an upper inverter pawl 120 combined integrally with a flat spring 181 to form a single, single piece. The upper reversing pawl 120 is formed in one piece with the spring 181 in place of the second reversing arm 123 according to the first embodiment, and is secured to a connecting pin 190 fixed to the rotating board 62 so as to be able to pivot relative to it.

[0181] The connecting pin 190 has an elliptical shape in plan view, having a pair of planar cutting surfaces 191 facing each other, and a pair of arcuate surfaces 192 also facing each other. 'one to the other. On the other hand, a connection hole 195 through which the connection pin 190 is inserted is formed in the central part 121 of the upper reversing pawl 120. The connection hole 195 has an elliptical shape in the plan view, which has a pair of straight portions 196 facing each other, and a pair of arcuate portions 197 also facing each other, corresponding to the shape of the connecting pin 190.

[0182] Consequently, the upper reversing pawl 120 can be pivoted within a predefined angular range, within which a connection part P1 between the rectilinear part 196 and the arcuate part 197 is in contact with a connection part P2 between the cutting surface 191 and the arcuate surface 192, around the pivot axis O9 which constitutes the central axis of the connecting pin 190.

[0183] The spring 181 is formed so as to extend clockwise from a proximal end 181a towards a distal end 181b such that the proximal end 181a is connected to the central part 121 of the upper reversing pawl 120. Then, the distal end 181b of the spring 181 is inserted into a connecting pin 200 fixed to the rotating board 62.

[0184] Consequently, the spring 181 will exert a compressive force against the upper reversing pawl 120 so as to compress the engagement part 124 of the upper reversing pawl 120 against the switching gear part 102 using its own elastic restoring force.

[0185] Again, with the inverter 180 according to this present embodiment configured as described above, the same beneficial operational effects as those achieved via the first embodiment can be obtained.

[0186] Furthermore, in the case of the present embodiment, since the upper reversing pawl 120 and the spring 181 are formed in one piece, the number of parts can be reduced, and a reduction in weight, a reduction in costs, and an improvement in the assembly of the inverter 180 can be achieved.

[0187] Although the embodiments of the invention have been described above, these embodiments have been presented by way of example only, and are not intended to limit the scope of the invention. invention claimed. The embodiments may be implemented in a variety of other forms, and various omissions, substitutions and changes may be provided without departing from the spirit of the invention. Alternative embodiments and modifications include, for example, those which can be readily designed by those skilled in the art, those which are substantially the same, those which remain within the realm of equivalents, or the like.

[0188] For example, in each of the embodiments described above, the case where the inverter is used for the automatic winding mechanism has been described as an example, but the invention is not limited to such a mechanism. automatic winding and could be adopted for other timepiece mechanisms.

[0189] In particular, in each of the embodiments described above, in order to be adopted in the automatic winding mechanism, a pair of reversing wheels and a pair of reversing pawls are provided such that the reverser including the upper reversing wheel, the lower reversing wheel, the upper reversing pawl and the lower reversing pawl are provided. However, when the inverter is adopted in a timepiece mechanism other than the automatic winding mechanism, the inverter could only include a reversing wheel and a reversing pawl.

Claims (8)

1. Inverter (60) comprising: a rotating shaft (65) which is rotatably mounted about a first axis and has a reversing gear (73) configured to transmit power to a drive train; a reversing wheel (61) which is secured to the rotating shaft (65) so as to have a relative degree of freedom in rotation with respect thereto, and rotates around the first axis due to the energy transmitted by a energy source (21); a rotating board (62) which is integrally secured to the rotating shaft; And a reversing pawl (63) which is integrally secured to the rotating board (62) so as to be able to be pivoted around a second axis, in which the reversing wheel comprises a plurality of reversing detent portions, each having an engagement surface (102a) oriented perpendicular to a first direction in a circumferential direction extending around the first axis, and an inclined surface (102b) oriented in the opposite direction according to the circumferential direction, the reversing pawl (63) includes: a reversing arm (122) which extends from the second axis in the first direction in the circumferential direction; And an engagement part (124) which is formed at one end of the reversing arm (122), and is arranged to reversibly engage with the engagement surface (102a) in the circumferential direction, and the reversing pawl (63) is armed by a spring (140) such that the engagement part (124) is held in compression against the engagement surface (102a). 2. Inverter (60) according to claim 1, in which the engagement part (124) is configured to maintain a state of engagement with the engagement surface (102a) when the reversing wheel rotates around the first axis in a first direction taken in the circumferential direction, and releasing engagement with the engagement surface (102a) via the inclined surface (102b) when the reversing wheel rotates about the first axis in the opposite direction taken in the circumferential direction. 3. Inverter (60) according to claim 2, in which the rotating board (62) is equipped with a limiter configured to limit the amplitude of the pivoting of the reversing pawl (63) around the second axis when the engagement between the engagement part (124) and the engagement surface ( 102a) is released. 4. Inverter (60) according to one of claims 1 to 3, in which the spring (140) is arranged separately from the reversing pawl (63), and is secured to the rotating board (62). 5. Inverter (60) according to one of claims 1 to 3, in which the spring (140) is formed in one piece with the reversing pawl (63), and is integral with the rotating board (62). 6. Automatic winding mechanism (11) comprising: (i) an inverter (60) comprising: a rotating shaft (65) which is rotatably mounted about a first axis and has a reversing gear (73) configured to transmit power to a drive train (50); a pair of reversing wheels (61) which are secured to the rotating shaft (65) so as to have a relative degree of freedom in rotation with respect thereto, and rotate around the first axis due to the transmitted energy by an energy source (21); a rotating board (62) which is integrally secured to the rotating shaft; And a pair of reversing pawls (63) which are integrally secured to the rotating board (62) so as to be able to be pivoted around a second axis, in which each of the reversing wheels (61) comprises a plurality of reversing detent portions, each having an engagement surface (102a) oriented perpendicular to a first direction in a circumferential direction extending around the first axis, and a surface inclined (102b) oriented in the opposite direction in the circumferential direction, each of the reversing pawls (63) includes: a reversing arm (122) which extends from the second axis in the first direction in the circumferential direction; And an engagement part (124) which is formed at one end of the reversing arm (122), and is arranged to reversibly engage with the engagement surface (102a) in the circumferential direction, and each of the reversing pawls (63) is armed by a spring (171) such that the engagement part (124) is held in compression against the engagement surface (102a); the automatic winding mechanism (11) further comprising: (ii) an oscillating mass (30) which is capable of rotating in both directions around a third axis and acts as a source of energy; And (iii) a drive train (50) which connects a clutch ratchet wheel (20) configured to wind a barrel spring to the reverser pinion (73); in which : the pair of reversing wheels and the pair of reversing pawls are arranged on either side of the rotating board (62) following the direction of the first axis, the rotating board (62) being interposed between them, among the pair of reversing wheels, the reversing wheel arranged closest to the reversing pinion (73) opposite the rotating board (62) constitutes a first reversing wheel rotating following the rotation of the oscillating mass (30), the other reversing wheel constituting a second reversing wheel which rotates in the opposite direction to the first reversing wheel following the rotation of the oscillating mass (30), among the pair of reversing pawls, the reversing pawl (63) closest to the reversing pinion (73) relative to the rotating board (62) constitutes a first reversing pawl (63) which cooperates with the first reversing wheel, and the other reversing pawl (63) constituting a second reversing pawl (63) which cooperates with the second reversing wheel. 7. Movement (10) of timepiece (1) comprising: the automatic winding mechanism (11) according to claim 6. 8. Timepiece (1) comprising: the movement (10) of a timepiece (1) according to claim 7.