CH716597A2 - Inverter, automatic winding mechanism, timepiece movement, and timepiece - Google Patents

Abstract

An inverter (60) according to the invention comprises: a rotating shaft (65) which includes an inverter gear (73); an inverter wheel (61) which rotates under the action of energy transmitted from a power source; a turntable (62) which is integral with the rotary 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 a first direction in a circumferential direction and an inclined surface (102b) facing the other direction in the circumferential direction . The reversing pawl (63) includes 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 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 comprising such an inverter (60), as well as a timepiece movement and a timepiece. transmitted by an energy source; a turntable (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 a first direction in a circumferential direction and an inclined surface (102b) facing the other direction in the circumferential direction . The reversing pawl (63) includes 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 engagement in the opposite direction in the circumferential direction. The reversing pawl is armed by a spring (140).

Description

Description

BACKGROUND OF THE INVENTION

1. Field of the invention

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 provided with an automatic winding mechanism, such as a mechanism for winding a barrel spring, are known. Generally, the automatic winding mechanism comprises an oscillating weight which can rotate in both directions, and an inverter which makes it possible to convert the rotation of the oscillating weight in both directions into a rotational movement in one direction only.

[0003] Various types of inverters such as those described above are known in the prior art. For example, an inverter is known using an automatic clutch wheel as disclosed in utility model JP-UM-B-46-9887 (patent document 1) below.

[0004] The automatic clutch wheel comprises: a rotatable shaft which is rotatably mounted about an axis; a clutch ratchet wheel which is fixed to the rotatable shaft; a wheel which is secured to the rotating shaft so as to have a relative degree of freedom in rotation with respect to the rotating shaft; a reversing pawl which is pivotally mounted on the wheel, and it has an engagement pawl which engages the clutch ratchet wheel as well as a spring which is fully 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 a direction about the axis relative to the rotating shaft, the reversing pawl can pivot such that the engagement pawl can be released. Therefore, only the wheel is rotatable 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 axle with respect to the rotary shaft, it is possible to maintain a state of engagement between the engagement pawl and the clutch ratchet wheel. , and thereby 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 back and forth around the axle due to the rotation of the oscillating mass, it is possible to still rotate the rotating shaft. in the same way. Consequently, the clutch ratchet wheel can always be rotated in the same direction via the rotary shaft, and the mainspring can thus be wound up.

[0008] The automatic clutch wheel described above in the prior art is of a type called a "pawl-pusher" in which the clutch ratchet wheel is rotated 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 part of the clutch ratchet wheel are in mutual engagement with each other , the wheel rotates so 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 a state of engagement 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 to a center of By pivoting the reverse pawl, it is possible to rotate the reverse pawl with the clutch ratchet wheel while maintaining the state of engagement between the engagement pawl and the engagement surface. In other words, the reversing pawl is shaped to extend from the center of pivot 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 portion of the clutch ratchet wheel from downstream in 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 so 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 prior art automatic clutch wheel is of the type called a "push pawl", and so if the reversing pawl is shaped like a teile, the longer the length of the arm taken from the center of pivoting toward the engagement pawl becomes longer, the more the engagement (mesh) between the engagement pawl and the engagement surface of the gear part 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 the length of the arm.

[0012] When the reverse pawl is freely rotated 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 to the clutch ratchet wheel as much as possible. In order to meet these needs, it is conceivable to lengthen, for example, the arm length of the reversing pawl in order to ensure a large distance (i.e., a length of the arm

which determines the moment of inertia in rotation) between the center of pivoting and the engagement pawl. In effect, 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 the "pawl-push" type, it is difficult to increase the length of the reversing pawl arm. itself. Therefore, it is difficult to reduce the rotational load applied to such an automatic clutch wheel. Accordingly, an automatic winding mechanism using an automatic clutch wheel has low winding efficiency, and there is possibilities for improvement in terms of winding performance.

SUMMARY OF THE INVENTION

[0014] An object 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.

[0015] (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; an inverter wheel which is secured to the rotating shaft so as to have a relative degree of freedom in rotation with respect to the latter and rotates around the first axis thanks to energy transmitted by an energy source; a turntable which is integrally secured to the rotating shaft; and a reversing pawl which is integrally secured to the turntable so as to be able to pivot about a second axis. The reversing wheel includes a plurality of reversing pawl portions, each having an engagement surface oriented perpendicular to a first direction in a circumferential direction extending around the first axis, and an angled surface oriented in the opposite direction along the circumferential direction. The reversing pawl includes a reversing arm which extends from the second axis in the first direction along the circumferential direction, and an engagement part which is formed at one end of the reversing arm, and is arranged to be able to engage reversibly with the engagement surface in the circumferential direction. The reversing pawl is spring loaded so that the engagement portion is kept compressed against the engagement surface.

[0016] According to the inverter of the patent application, the inverter wheel is driven in rotation 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 pawl portions rotate in the same direction. At this time, since the engaging part of the reversing pawl is engaged with the engaging surface of the clutch gear part in a first direction along the circumferential direction, it is possible to maintain a state of mutual engagement between the engagement surface and the engagement portion. Consequently, the reversing pawl can be rotated in the first direction in the circumferential direction when the reversing wheel rotates.

[0017] Furthermore, by rotating the reversing pawl, the rotary shaft can be rotated in the first direction in the circumferential direction via the turntable. Therefore, the energy transmitted to the reverse wheel can be transmitted to the drive train through the reverse gear of the rotating shaft.

[0018] Then, contrary to 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 pawl portions rotate in the same direction. In this case, since the inclined surface of the clutch gear part moves above the engaging part of the reversing pawl, the reversing pawl rotates around the second axis while resisting the winding force ( compression force) of the spring. Consequently, the engagement between the engagement part and the engagement surface is released, so that the reversing wheel can idle around the first axis in the reverse direction along the circumferential direction.

[0019] 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 turntable and the rotating shaft can be rotated in the same direction, and power can be transmitted to the drive train.

[0020] On the other hand, on the contrary, when energy is transmitted to the inverter wheel to cause it to rotate in the opposite direction along the circumferential direction, only the inverter wheel can rotate idle, and it is thus possible to prevent the transmission of energy. energy to the drive train.

[0021] Consequently, even when the reversing wheel rotates in both directions, the energy can be transmitted in such a way that the drive train is only always rotated in one direction. Consequently, it is possible to use the inverter for example for an automatic winding mechanism.

[0022] In particular, the reversing pawl includes a reversing arm extending from the second axis, which is the pivot center, in the first direction along the circumferential direction, and the engagement part is formed at the end of the reverse 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. As a result,

Unlike prior art solutions, the reversing pawl can be designed to operate as a "pull pawl" type ratchet, ie, a reversing pawl which applies a pulling force to the reversing arm.

[0023] In this case, even when the length of the reversing arm is chosen to be long, unlike the pawl of the push-pawl type according to the prior art, it is easy to maintain the state of mutual engagement between the engagement surface and the part of commitment, 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 lengthened even more than 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 is idle, i.e. freewheeling, and it is possible to improve the winding performance when the reversing wheel is used in a winding mechanism. self-winding or similar.

[0024] (2) The engagement part can be configured to maintain a state of engagement with the engagement surface when the reversing wheel rotates around the first axis in a first direction along the circumferential direction, and release the engagement with the engagement surface via the inclined surface when the reversing wheel rotates around the first axis in the other direction in the circumferential direction.

[0025] In this case, the operational effects described above can be realized more reliably. Indeed, even when the reversing wheel rotates in both directions, energy can be transmitted in such a way that the drive train is always driven in rotation only in one direction, and it is possible to use the inverter, for example, in an automatic winding mechanism or the like.

[0026] (3) The turntable may be equipped with a limiter configured to limit the amount of pivoting of the reversing pawl about the second axis when the engagement between the engagement portion and the engagement surface is released.

[0027] In this case, when the reversing wheel idles by releasing the engagement between the engagement part and the engagement surface, for example, by using a limiting element such as a stopper, the pivoting of the pawl inverter around the second axis can be limited. Therefore, it is possible to prevent the reversing pawl from pivoting excessively, and therefore prevent, for example, the spring from deforming strongly and plastically. Therefore, stable operation can be achieved over a long period of time, and operational reliability can be improved.

[0028] In particular, it is assumed that the reversing pawl rotates 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.

[0029] (4) The spring can be formed separately from the reversing pawl, and then attached to the turntable.

[0030] 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 turntable.

[0032] In this case, since the reversing pawl and the spring are formed in one piece, the number of parts can be reduced, and weight reduction, cost reduction, or assembly improvement can be achieved. realized.

[0033] (6) An automatic winding mechanism according to the patent application includes: the reverser as described above; an oscillating mass which is rotatable in both directions around a third axis and acts as a source of energy; and the drive cog which connects a clutch ratchet wheel configured to wind a mainspring to the reverse gear. A pair of reversing wheels and a pair of reversing pawls are arranged on either side of the turntable in the direction of the first axis, the turntable being interposed between them. Among the pair of reversing wheels, the one located closest to the reversing pinion with respect to the turntable constitutes a first reversing wheel which rotates following the rotation of the oscillating weight, 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 vis-à-vis the turntable 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.

[0034] 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, as a result of the rotation of the oscillating weight, 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 turntable and the rotating shaft rotate in the same direction. Therefore, the energy transmitted to the

The first reverse gear may be transmitted to the drive train through the reverse gear, and may also be transmitted to the clutch ratchet gear via the drive train to wind the mainspring.

When the first reversing wheel described above rotates, the second reversing wheel rotates in the opposite direction in the circumferential direction. At this time, the second reversing pawl rotates in the first direction in the circumferential direction as a result of the rotation of the turntable 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 part of the second reverse wheel and the engagement part of the second reverse pawl are no longer in mutual engagement Tun with the other, so that the second reversing wheel does not turn and remains at rest. Consequently, the rotating shaft is not driven in rotation by that of the second reversing wheel.

[0037] Then, contrary to the case described above, when the first reversing wheel rotates in the other direction according to the circumferential direction and the second reversing wheel rotates in the first direction according to the circumferential direction following the rotation of the oscillating mass, the movement is the opposite of that in 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 remounts by rotating the clutch ratchet wheel in the same direction as before. Further, since the first reversing wheel idles, the rotary shaft is not rotated by that of the first reversing wheel.

[0038] Therefore, by using the energy resulting from the rotation of the oscillating mass which rotates in both directions, the rotary shaft including the reverse gear can always be rotated in the same direction, and the barrel spring can be reassembled 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, spinning, it is possible to improve the winding performance.

[0039] (7) A timepiece movement according to the patent application includes such an automatic winding mechanism.

[0040] (8) A timepiece according to the patent application includes such a timepiece movement.

[0041] 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.

[0042] According to the teachings of the patent application, it is possible to reduce the rotational load and improve winding performance.

BRIEF DESCRIPTION OF THE DRAWINGS

[0043]

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.

Fig. 4 is a perspective view showing a state in which a reverse gear upper gear is removed from the state shown in Fig. 3.

Figure 5 is a vertical cross-sectional view of the inverter shown in Figure 3, and is a vertical cross-sectional view seen from a line A-A shown in Figure 6.

Figure 6 is a plan view illustrating a relationship between an upper reverse gear, an upper reverse pawl and a spring shown in Figure 5.

Fig. 7 is a plan view taken along line B-B shown in Fig. 5, and is a view illustrating a relationship between a lower reverse gear, a lower reverse pawl, and the spring.

Fig. 8 is a schematic showing a second embodiment according to the invention, and is a plan view illustrating a relationship between an upper reverse gear, an upper reverse pawl, and a spring.

Fig. 9 is a schematic showing a third embodiment according to the invention, and is a plan view illustrating a relationship among an upper reverse gear, an upper reverse pawl, and a spring.

Fig. 10 is a schematic showing a fourth embodiment according to the invention, and is a plan view showing a relationship among an upper reverse gear, an upper reverse pawl, and a spring.

DESCRIPTION OF EMBODIMENTS

(First embodiment)

Hereafter, we will describe a first embodiment according to the invention with reference to the drawings. In the present embodiment, a self-winding mechanical timepiece will be described as an example of a timepiece.

(Basic configuration of a timepiece)

[0045] Generally, a mechanical body including a driving part of a timepiece is called a "movement". watchmaking to obtain a finished product, reference is made to the "assembly" of the timepiece. Of 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 located (that is to say, the side where the the dial) is called the "dial side" of the movement. Furthermore, among the two sides of the plate, the side on which the back of the case of the timepiece is located (i.e. the side opposite dial) is called the "back side" of the movement.

[0046] 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 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 bottom (not represented) 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 bottom side of the plate, or the like. Between the plate and the gear train bridge and the balance bridge, there are mainly a front gear train, also called the finishing gear train, an escapement to control the rotation of the front gear train, a regulation unit to adjust the escapement, a mechanism for manual winding, and an automatic winding mechanism 11 illustrated in Figure 2. In the present embodiment, the front wheel, the escapement, the regulation unit, and the manual winding mechanism are not represented.

[0049] A rear cog (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.

[0050] A winding stem guide hole (not shown) is formed in the plate, and a winding stem 12 shown in Figure 1 is inserted into this winding stem guide hole 12 so as to be rotating around an axis. A crown 13 is connected to the winding stem 12. Consequently, the winding stem 12 can be turned via the crown 13.

[0051] The position of the winding stem 12 in the axial direction is determined by a switching device (not shown) including a pull tab, a rocker, a rocker spring or the like. A winding pinion (not shown) is fixed to a guide shaft portion of winding stem 12 so as to be rotatable with respect to 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.

[0052] For example, when the winding stem 12 is set in its position closest to the movement 10 in the axial direction (level position 0), the winding pinion and the clutch wheel can mesh Tun with the other. Consequently, by rotating the winding stem 12 via the crown 13 in this state, the winding pinion can be rotated about an axis coaxial with the winding stem 12 via the clutch wheel.

[0053] By rotating the winding pinion, it is possible to rotate a clutch ratchet wheel 20 shown in Figure 2 via the manual winding mechanism. Furthermore, by rotating the clutch ratchet wheel 20, it is possible to wind up a barrel spring (constituting a source of energy for the movement) housed inside the movement barrel 21.

[0054] The front gear train mainly includes the movement barrel 21, a center wheel set, a third wheel set, and a fourth wheel set, 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 reassembled condition.

[0055] The seconds hand 7 represented in FIG. 1 rotates following the rotation of the fourth mobile, and rotates at a speed of rotation adjusted by the escapement and the regulation unit, that is to say, one rotation per minute. The minute hand 6 rotates following the rotation of the center wheel or the rotation of a center wheel (not shown) which rotates following the rotation of the center wheel, and rotates at a speed of rotation adjusted by the escapement and the unit of regulation, ie, 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 exhaust and regulating unit, ie one rotation every 12 or 24 hours.

[0056] The escapement includes an escapement wheel which meshes with the fourth wheel and is driven in rotation under the impulse of an energy transmitted by the mainspring, via an anchor which lets a predetermined quantity escape and turn the exhaust mobile evenly. The escapement controls the front gear train with regular oscillations via a spiral balance wheel. The regulation unit primarily uses a balance spring (not shown) as a power source, and includes the balance-spring which alternately rotates back and forth (forward rotation followed by backward rotation) according to a constant amplitude (that is to say a predetermined oscillation angle) according to the torque applied at the output of the movement barrel 21.

[0057] As illustrated in FIG. 2, the movement barrel 21 includes a barrel arbor 23 which is rotatably mounted between the plate and the gear-train bridge, and a drum 22 which is combined with the barrel arbor 23 so as to to have a relative degree of freedom in rotation with respect to the barrel arbor, 23 and in which the barrel spring is housed. Drum 22 has a barrel gear wheel 22a for meshing with the center wheel set.

[0058] The barrel spring is housed in the drum 22 while being wound around the barrel arbor 23 in a spiral shape. The barrel spring is wound under the action of the rotation of the barrel arbor 23, and the drum 22 is driven in rotation 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 gear train through the center wheel set.

[0059] The clutch ratchet wheel 20 is disposed between the drum 22 and the gear bridge, and is fixed to the barrel shaft 23 via, for example, a driving-in or crimping operation. The clutch ratchet wheel 20 comprises a ratchet gear toothing 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.

[0060] In the present embodiment, a case is described where the clutch ratchet wheel 20 rotates clockwise as illustrated by the arrow visible in Fig. 2 (to which reference will simply be made). hereinafter as corresponding to the clockwise direction) when the latter is seen from above (bottom side) by way of example.

[0061] Accordingly, the mainspring can be wound up via the mainspring arbor 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 later meshes with the ratchet gear teeth 20a. Consequently, the clutch ratchet wheel 20 can be rotated clockwise via the second reduction wheel set 52, and the mainspring can be wound via the automatic winding mechanism 11.

[0062] In order to prevent the mainspring from disarming, a pawl (not shown) which limits the opposite rotation of the clutch ratchet wheel 20 is in engagement with the clutch ratchet wheel 20. The pawl allows the clutch ratchet wheel 20 from rotating clockwise, and limits counterclockwise rotation (hereinafter referred to simply as counterclockwise). of a watch), which is the opposite direction to that of the hands of a watch.

(automatic winding mechanism)

[0063] 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 an arm of a user. . This mechanism includes the oscillating mass 30, an inverter 60, an intermediate gear train 40 which is arranged between the oscillating mass 30 and the inverter 60, and a transmission gear train (a drive train according to the invention) 50 which is arranged between clutch ratchet wheel 20 and reverse gear 60.

[0064] 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.

[0065] Specifically, the oscillating mass 30 comprises a ball bearing 31, a oscillating mass body 35, and a weight 36, and rotates both clockwise and counterclockwise. clockwise around Tax O2 depending, for example, on the movements of the user's arm.

The ball bearing 31 includes an inner ring 32 fixed to a catwalk (not shown), an outer ring 33 surmounting the inner 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 degree of freedom in rotation

relative vis-à-vis the inner ring 32 around Tax 02 via the balls. On an outer peripheral surface of the outer ring 33, a rocker gear 33a is formed around the entire circumference.

[0067] The oscillating mass body 35 has a fan shape in plan view, that is to say extends over a strictly interior angular sector at 360 degrees, and is inserted on the outer ring 33. Weight 36 is attached to an outer peripheral edge of oscillating mass body 35. Accordingly, weight 36, oscillating mass body 35, and outer ring 33 can be integrally rotated about Tax 02.

[0068] The intermediate gear 40 includes a first reverser gear 41 which rotates around an axis 03, a second reverser gear 42 which rotates around an axis 04, and a third reverser gear 43 which rotates around an axis 05 The first reversing idler 41, the second reversing idler 42, and the third reversing idler 43 are rotatably supported by bridges (not shown), respectively.

The first reversing idler 41 includes a first reversing idler gear wheel 41a which meshes with the oscillating mass pinion 33a, and a first reversing idler gear 41b. Consequently, the first reversing gear 41 can rotate around axis 03 following the rotation of the oscillating mass 30, and can rotate in the opposite direction 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 axis 04 following the rotation of the first reversing gear 41, and can rotate in the same direction as that of the rotation of the oscillating weight 30.

The third reversing idler 43 includes a third reversing idler gear wheel 43a which meshes with the second reversing idler gear 42b. Consequently, the third reversing gear 43 can rotate around axis 05 following the rotation of the second reversing gear 42, and can rotate in a direction opposite to that of the rotation of the oscillating weight 30.

The transmission train 50 includes a first reduction mobile 51 which rotates around an axis 06, and the second reduction mobile 52 which rotates around an axis 07. The first reduction mobile 51 and the second mobile reducers 52 are rotatably supported by bridges (not shown), respectively.

The first reduction mobile 51 includes: a first reduction wheel 51 a which meshes with an inverter pinion 73 - described later - of the inverter 60; and a first reduction pinion 51b. Consequently, the first reduction mobile 51 can be driven in rotation around axis 06 following a rotation of the inverter pinion 73.

[0074] In particular, the inverter pinion 73, which will be described in detail later, is configured to always rotate counterclockwise. Consequently, the first reduction mobile 51 is always driven in rotation in the direction of clockwise around axis 06 following the rotation of the inverter pinion 73.

[0075] The second reduction wheel set 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 axis 07 following the rotation of the first reduction mobile 51. Thus, the second reduction mobile 52 can always rotate the wheel at clutch ratchet 20 clockwise as described above.

(Inverter)

As shown in Figure 2, the inverter 60 rotates around an axis (first axis) 08 under the impulse of the energy of the oscillating mass 30 transmitted through the intermediate 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 cog 50 in a state where the bidirectional rotation of the oscillating mass 30 is switched to unidirectional rotational movement.

As shown in Figures 3 to 5, the inverter 60 includes: an axis (rotating shaft according to the invention) 65 which is rotatable about axis 08; a pair of reversing wheels 61 which are secured to axle 65 so as to be rotatable with respect to axle 65, and which turn around axle 08 under the impulse of the energy transmitted by the oscillating weight 30 through the intermediate gear train 40 ; a turntable 62 which is integrally secured to the post 65; and a pair of reversing pawls 63 which are integrally secured to the turntable 62 so as to be able to pivot around a pivot axis (second axis according to the invention) 09.

[0078] According to a plan view taken along the direction of Tax 08, which is a central axis of the inverter 60, a secant direction with respect to Tax 08 is called a radial direction, and a direction following a movement of revolution around Tax 08 is called a circumferential direction.

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

[0080] A cylindrical upper seat 80 is fixed to the first shoulder 74 of Tax 65 by crimping, driving in or the like. The upper seat 80 includes: a first upper support cylinder 81 which is fixed 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.

[0081] 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 reverse gear 73 from below.

[0082] A cylindrical lower support 85 is fixed to the second shoulder 75 of Tax 65 by crimping, driving in or the like. The lower seat 85 includes a lower support cylinder 86 which is fixed 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.

[0084] The turntable 62 is fixed to the second upper support cylinder 82 by crimping, driving in or the like. Consequently, the turntable 62 is made entirely integral with the fax 65 via the upper seat 80.

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

[0086] Three connecting pins 90, 91 and 92, which are arranged at regular intervals along the circumferential direction at the outer peripheral edge, are fixed to the turntable 62 by crimping, driving in or the like. These connecting pins 90, 91 and 92 have cylindrical shapes, and are shaped to project above and below the turntable 62.

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

[0088] Among the pair of reversing wheels 61, the reversing wheel 61 closest to the reversing pinion 73 with respect to the turntable 62 is referred to as the upper reversing wheel (first reversing wheel according to the invention) 100. the pair of reversing wheels 61, the reversing wheel 61 located below the turntable 62 is qualified as the lower reversing wheel (second reversing wheel according to the invention) 110.

[0089] The pair of reversing pawls 63 are disposed on both sides of the turntable, ie the upper and lower side, and the turntable 62 is again interposed between the two pawls.

[0090] Among the pair of reversing pawls 63, the reversing pawl 63 closest to the reversing pinion 73 with respect to the turntable 62 is referred to 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 turntable 62 is referred to as the lower reversing pawl (second reversing pawl according to the invention) 130 which cooperates with the lower reversing wheel 110.

In the following, the relationship between the upper reversing wheel 100 and the upper reversing pawl 120 will be described in detail.

[0092] As illustrated in Figures 5 and 6, the upper inverter wheel 100 comprises an upper inverter pinion 101 which is combined with the first upper support cylinder 81 of the upper seat 80 so as to maintain a relative rotational degree of freedom against to the first upper support cylinder 81, and an upper reverse gear wheel 105 fixed to the upper reverse gear 101.

[0093] The upper reverse gear 101 has a plurality of reversing pawl portions 102 around its entire circumference and also has an upper link cylinder 103 projecting upward from a lower peripheral edge. The switching gear portion 102 is a gear portion having an engagement surface 102a oriented perpendicular to the counterclockwise direction, which is a direction of revolution in the circumferential direction around the axis. 08, and an inclined surface 102b facing clockwise, which is the opposite direction in the circumferential direction.

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

[0095] Consequently, the whole of the upper reversing wheel 100 can rotate around axle 08 following a rotation of the second reversing idler gear 42b, and can rotate in the opposite direction to the direction of rotation of the second reversing idler 42 (this is that is, rotate in a direction opposite to the direction of rotation of the oscillating mass 30).

[0096] As shown in Figures 5 and 6, the upper reverse pawl 120 is positioned on the upper surface side of the turntable 62 so as to be disposed in a clearance between the turntable 62 and the upper wheel gear. reversing gear 105. Therefore, the upper reversing pawl 120 is disposed towards the outside of the upper reversing pinion 101 in the radial direction.

[0097] The upper reversing pawl 120 has a substantially arcuate shape so as to extend along the circumferential direction, and its central portion 121 is integral with the connecting pin 90 fixed to the turntable 62 so as to be rotatable. relative to the link pin 90. Accordingly, the upper reversing pawl 120 can pivot in the radial direction about the link pin 90.

[0098] The central axis of the link pin 90 is a pivot axis 09. The upper reversing pawl 120 is fully secured to the turntable 62 via the link pin 90 so as to be able to pivot about the pivot pin 09 .

[0099] The upper reversing pawl 120 includes a first reversing arm (reversing arm according to the invention) 122 shaped so as to extend clockwise from the central portion 121 secured to the locking pin. link 90, and a second inverter arm 123 shaped to extend from central portion 121 in a clockwise direction. An engagement portion 124 is formed at the end of the first reverse arm 122 so as to protrude inward in the radial direction and reversibly engages with the switching gear portion 102 of the pinion. upper inverter 101.

[0100] The engagement portion 124 is reversibly engaged with the engagement surface 102a of a switch gear portion 102 in a counterclockwise direction while contacting the surface. 102b of a switch gear portion 102. Accordingly, the engagement portion 124 becomes gear-engaged so as to enter a gap between the reversing latch portions 102 adjacent in the direction circumferential from the outside in the radial direction.

[0101] The upper reversing pawl 120 configured as described above is cocked around the pivot pin 09 by a spring 140 such that the engagement portion 124 is held compressed against the engagement surface 102a of the reverse portion. switching gear 102.

[0102] The spring 140 is formed separately from the upper reversing pawl 120, and is combined with the upper surface of the turntable 62 using the two remaining connecting pins 91 and 92 so as to fit into the gap between the turntable. rotating wheel 62 and the upper reversing wheel gear 105.

[0103] The spring 140 includes: a base 141 which is arranged on the opposite side to the upper reversing pawl 120 in the radial direction, with Pin 08 interposed between them; and a spring body 142 which is shaped 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.

[0104] The base portion 141 has a substantially arcuate shape so as to extend along the circumferential direction, and the two ends along the circumferential direction are inserted into the connecting pins 91 and 92 respectively. the spring 140 is integrally fixed to the turntable 62 using the two connecting pins 91 and 92.

[0105] 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 to extend counterclockwise along the direction circumferential 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.

[0106] Consequently, the spring body 142 compresses the second reversing arm 123 outwards in the radial direction using its own elastic restoring force. Therefore, the upper reversing pawl 120 is always cocked so that the engagement portion 124 is compressed toward the switching gear portion 102.

[0107] 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 engaging surface 102a is maintained in a state of engagement when the upper reversing wheel 100 rotates about axis 08 counterclockwise, and this engagement state between the engagement portion 124 and the engagement surface 102a is released through the inclined surface 102b when the upper reversing wheel 100 rotates around axis 08 in a clockwise direction. This point will be described later in detail.

[0108] In addition, the base portion 141 of the spring 140 has a stopper (limiter according to the invention) 143 which should project clockwise so as to be located outside the end of the spring. distal of the first reversing arm 122 of the upper reversing pawl 120 seien the radial direction.

[0109] The stopper 143 can limit the amplitude of the pivoting of the upper reversing pawl 120 around pivot axis 09 when the engagement between the engagement part 124 and the engagement surface 102a is released.

[0110] Specifically, the upper reversing pawl 120 pivots about the pivot pin 09 countering a compressive force (preloading or winding force) of the spring 140 such that the first arm inverter 122 moves outward in the radial direction when the engagement between the engagement portion 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 over-rotating.

[0111] In the following, a relationship between the lower reversing wheel 110 and the lower part of the reversing pawl, i.e., the lower reversing pawl 130, will be described.

[0112] Lower idler wheel 110 and lower idler pawl 130 are configured similarly to upper idler wheel 100 described above and upper idler pawl 120, and have the same relative positional relationship.

[0113] However, in the present embodiment, the lower reversing pawl 130 is disposed 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 08. Therefore , the lower reversing pawl 130 is secured using the link pin 91 instead of the link pin 90 to which the upper reversing pawl 120 is connected.

[0114] The invention is however not limited to such a configuration, and the lower reversing pawl 130 could be secured using the same connecting pin 90 so as to be placed below and facing the upper reversing pawl 120 with the turntable 62 interposed between them.

[0115] As illustrated in Figures 4, 5 and 7, the lower inverter wheel 110 includes a lower inverter 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 reverse gear wheel 115 fixed to the lower reverse gear 111.

[0116] The lower reverse gear 111 has a plurality of reversing detent portions 112 around its entire circumference and also has a lower connecting cylinder 113 projecting downward from a lower peripheral edge.

The reversing ratchet portion 112 is a gear portion having a clockwise-facing engagement surface 112a, which is one of the directions for performing a revolution in the circumferential direction around of Tax 08, and an inclined surface 112b facing clockwise, which is the other direction to follow the circumferential direction.

[0118] The lower reverse wheel gear 115 is fixed to the lower connecting cylinder 113 by crimping, driving in or the like. Consequently, the whole of the lower reversing wheel 110 is integral with Taxe 65 so as to maintain a relative degree of freedom in rotation with respect to Taxe 65 via the lower seat 85. In addition, the lower reversing gear wheel 115 has portions lower reversing pawls 115a which mesh with the third reversing idler gear 43a of the third reversing idler 43.

[0119] Consequently, the entire lower reversing wheel 110 can be rotated around shaft 08 following the rotation of the third reversing gearbox 43, and can rotate in a direction opposite to that of the rotation of the third reversing gearbox 43 (c that is, rotate in the same direction as the oscillating weight 30 rotates).

[0120] The lower reverse pawl 130 is disposed on the upper surface side of the lower reverse gear wheel 115, so as to be disposed in a clearance between the turntable 62 and the lower reverse gear wheel 115.

[0121] The lower reversing pawl 130 is secured with the link pin 91 fixed to the turntable 62 so as to maintain a relative degree of freedom in rotation with respect to the link pin 91, and can pivot in the direction radial around the link pin 91. Consequently, the lower reversing pawl 130 is fully secured with the turntable 62 via the link pin 91 so as to be able to pivot around a pivot axis 010 which is a central axis of the connecting pin 91.

[0122] The lower reversing pawl 130 includes a first reversing arm (reversing arm according to the invention) 132 shaped to extend from a central portion 131 secured with the link pin 91 in a counterclockwise direction. watch, and a second inverter arm 133 is shaped to extend from the central portion 131 in a clockwise direction.

[0123] An engagement portion 134 is formed at a distal end of the first reverse arm 132 so as to project inward in the radial direction, and reversibly engages the gear portion. switch 112 of the lower reverse gear 111.

[0124] Engagement portion 134 is reversibly engaged with engagement surface 112a of switch gear portion 112 from a clockwise direction while contacting inclined surface 112b. of each switching gear portion 112. Accordingly, the engagement portion 134 is engaged so as to enter an interspace between the reversing pawl portions 112 which are adjacent to each other in the circumferential direction from outward in the radial direction.

[0125] The lower reversing pawl 130 configured as described above is cocked around the pivot pin 010 by a spring 150 so that the engagement portion 134 is compressed against the engagement surface 112a of the reverse portion. switching gear 112.

The spring 150 is formed separately from the lower reverse pawl 130, and is combined with an upper surface of the lower reverse gear 115 using the two link pins 90 and 92.

The spring 150 includes a base 151 and a spring body 152.

[0128] 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 to the link pins 90 and 92 respectively. is fully fixed to the turntable 62 using the two connecting pins 90 and 92.

[0129] Further, the spring body 152 is, for example, a flat spring extending along the circumferential direction, is shaped so as to extend counterclockwise along the circumferential direction. 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.

[0130] Therefore, the spring body 152 compresses the second reverse arm 133 outward in the radial direction using its own elastic restoring force. Therefore, the lower reverse pawl 130 is always cocked around the pivot pin 010 so that the engagement portion 134 is compressed toward the switching gear portion 112.

[0131] Since the lower reverse gear 110 and the lower reverse pawl 130 are configured as described above, the relationship between the engagement portion 134 of the lower reverse pawl 130 and the engagement surface 112a maintains an engaged state when the lower reverse wheel 110 rotates about axis 08 counterclockwise, and this state of engagement between the engagement portion 134 and the engagement surface 112a is released by the inclined surface 112b when the reverse wheel lower inverter 110 rotates around fax 08 clockwise.

[0132] In addition, the base 151 of the spring 150 has a stopper (limiter according to the invention) 153 which protrudes clockwise so as to be located outside the distal end of the spring 150. first reversing arm 132 of the lower reversing pawl 130 in the radial direction.

(Operation of the automatic winding mechanism)

In what follows, the operation of the automatic winding mechanism 11 including the inverter 60 configured as described above will be described.

[0134] As illustrated in Figure 2, the oscillating mass 30 suitably rotates back and forth about the axis O2 according to, for example, the movement of a user's arm. When the oscillating weight 30 rotates, energy (rotational torque) is transmitted to the reverser 60 through the first reverser idler 41, the second reverser idler 42, and the third reverser idler 43, so that the reverser wheel upper 100 and the lower reversing wheel 110 can be rotated in opposite directions around axis 08.

In what follows, its operation will be described specifically.

[0136] When the oscillating mass 30 shown in Figure 2 rotates clockwise, the first reversing transmission 41 can be rotated counterclockwise, the second reversing transmission 42 can in turn be driven clockwise, and the third reversing transmission 43 counterclockwise. Therefore, the upper inverter wheel 100 meshing with the second inverter idler gear 42b can be rotated counterclockwise, and the lower inverter wheel 110 meshing with the third inverter idler gear 43a can be rotated counterclockwise. rotated in turn clockwise.

[0137] 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 therefore, the upper reversing wheel 100 and the lower reversing wheel 110 can be driven. rotating in opposite directions.

[0138] For example, when the upper inverter wheel 100 rotates counter-clockwise following the rotation of the oscillating weight 30 clockwise, as shown in FIG. At this, the upper reverse gear 101 having the reverse pawl portions 102 rotates counterclockwise. At this time, since the engagement portion 124 of the upper reversing pawl 120 is engaged with the engagement surface 102a of the switching gear portion 102 counterclockwise, the state of engagement between engagement surface 102a and engagement portion 124 can be maintained. Therefore, as shown by the arrow F1 shown in Fig. 6, 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.

[0139] Next, turntable 62 is rotated as upper reversing pawl 120 rotates, and therefore, as shown in Figure 2, post 65 can be rotated counterclockwise. Accordingly, power transmitted to the upper reverse gear 100 can be transmitted to the side of the transmission cog 50 through the reverse gear 73, and can be transmitted to the clutch ratchet wheel 20 through the transmission cog 50 to wind the mainspring.

[0140] In other words, fax 65 and inverter pinion 73 rotate counterclockwise, so that first reduction mobile 51 can be rotated clockwise and the second reduction mobile 52 in turn drives counterclockwise. Therefore, the clutch ratchet wheel 20 can be rotated clockwise, and the mainspring can be wound up.

[0141] In this connection, it will be noted that the turntable 62 rotates in the counterclockwise direction, so that, as shown in Figure 7, parallel thereto, the lower reversing pawl 130 also rotates in counterclockwise. Additionally, when the oscillating weight 30 rotates clockwise, the lower idler wheel 110 rotates clockwise as described above. For these reasons, the lower idler wheel 110 rotates clockwise. clockwise relative to the lower reversing pawl 130 which rotates counterclockwise.

[0142] In this case, the engagement surface 112a of the switching gear portion 112 of the lower reverse wheel gear 115 and the engagement portion 134 of the lower reverse pawl 130 are not in mutual engagement Tun with the other, so that the lower inverter wheel 110 is at rest, that is to say in a state where it does not rotate. Therefore, axle 65 and idler gear 73 cannot be rotated by rotation of lower idler wheel 110.

[0143] In what follows, some additional details will be given on the performance of the switching operation for reassembly.

[0144] When the lower reverse gear 110 rotates clockwise relative to the lower reverse pawl 130 which rotates counterclockwise, the inclined surface 112b of the gear portion of switch 112 moves on the engagement portion 134 in the circumferential direction while pushing the engagement portion 134 of the lower reversing pawl 130 outward in the radial direction, as shown by an arrow F2 in Fig. 7. therefore, lower reversing pawl 130 is pivoted about pivot pin 010 against a so-called winding preload force (compression force) of spring 150. engagement 112a is free.

[0145] As a result, the lower reverse wheel 110 can spin idle, ie, coast in a counter-clockwise direction.

[0146] As described above, when the upper idler wheel 100 rotates counterclockwise due to the rotation of the oscillating weight 30, all of the turntable 62, idler 65, and idler gear 73 can be rotated counterclockwise, and power can be transmitted to the transmission gear 50 while maintaining the state in which the engagement surface 102a of the gear part of the switch 102 and the engagement portion 124 of the upper reversing pawl 120 are engaged. Further, at the same time, even when the lower inverter wheel 110 rotates clockwise, the lower inverter wheel 110 can idle clockwise, that is, say in such a way that the energy is not able to be transmitted from the lower inverter wheel 110 to the transmission cog 50.

[0147] Consequently, even when the upper inverter wheel 100 and the lower inverter wheel 110 rotate in opposite directions, the energy can be transmitted so that the transmission gear 50 always rotates in one and the same direction. Therefore, as illustrated in Figure 2, the clutch ratchet wheel 20 can be driven clockwise to wind the mainspring.

[0148] In the following, a case will be described where the oscillating weight 30 shown in Fig. 2 rotates counterclockwise.

[0149] In this case, contrary to the case described above, the upper reversing wheel 100 rotates clockwise and the inner 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 turntable 62, axle 65 and the reverse gear 73 can be rotated in counterclockwise, and power can be transmitted to the transmission gear 50 while maintaining an engagement state between the engagement surface 112a of the switching gear portion 112 of the reverse wheel 110 and the engagement portion 134 of the lower reversing pawl 130.

[0150] Furthermore, at the same time, the upper inverter wheel 100 can be left at rest in the clockwise direction, so that energy cannot be transmitted from the upper inverter wheel 100 to the gear train. transmission 50.

[0151] Therefore, in this case, similarly, power can be transmitted so that the transmission cog 50 always rotates in one direction, so that the clutch ratchet wheel 20 can be rotated. clockwise to wind the mainspring.

[0152] From the foregoing, it will be understood that Tax 65 including the reverse gear 73 can always be driven in rotation in the same direction, which is corresponds to the counter-clockwise direction, using the energy of the mass 30 which rotates in both directions, so that the mainspring can be wound automatically by rotating the clutch ratchet wheel 20 clockwise.

[0153] In particular, according to the reverser 60 described within the framework of the present embodiment, as illustrated in FIGS. 6 and 7, the upper reversing pawl 120 and the lower reversing pawl 130 have first portions of reversing arm 122 and 132 formed to extend counterclockwise from the pivot axes 09 and 010, and the engagement portions 124 and 134 are formed at their respective ends.

[0154] Therefore, for example, when the upper reversing pawl 120 is exemplified, as shown in Figure 6, when the upper reversing wheel 100 rotates counterclockwise, the first reversing pawl 63 can be rotated to pull first reversing arm 122. Therefore, unlike prior art solutions, first reversing pawl 63 can be configured to operate as a pull-type pawl reversing pawl, which applies a pulling force to the first inverter arm 122.

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 between the engagement surface 102a and the engagement portion 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 to the upper reversing wheel 100 when the engagement surface 102a pushes the first reversing pawl 63 against the spring preload force 140.

[0156] Therefore, since it is possible to reduce the Rotational Load when the upper idler wheel 100 and the lower idler wheel 110 are idling, i.e. coasting, it is possible to improve the winding performance.

[0157] 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 winding performance can be improved.

Further, as shown in Figures 6 and 7, reverser 60 of this embodiment includes stops 143 and 153 to limit pivoting of upper reverser pawl 120 and lower reverser pawl 130.

[0159] Therefore, when the upper reversing wheel 100 and the lower reversing wheel 110 are idle, 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, any large deformation or substantial plastic deformation of the spring bodies 142 and 152 of the spring members 140 and 150 can be prevented. and operational reliability can be improved accordingly.

[0160] In particular, it is believed that when an impact due to a fall or a manual winding operation using the crown 13 is performed, the upper reversing pawl 120 and the lower reversing pawl 130 pivot excessively.

[0161] In fact, when the clutch ratchet wheel 20 is turned clockwise by the manual winding operation, axis 65 of the reverser 60 is forced to turn counterclockwise. clockwise via the transmission cog 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 with respect 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 rotate by a large amount while being pushed back by the reversing pawl portions 102 and 112 Therefore, the spring bodies 142 and 152 tend to be easily plastically deformed.

[0162] However, even in such a case, by using the stoppers 143 and 153, it is possible to effectively prevent the spring bodies 142 and 152 from being greatly deformed.

[0163] 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 material, coating or the like different from that of the upper reversing pawl 120 and the lower reversing pawl 130 can be selected.

(Second embodiment)

In the following, a second embodiment according to the invention will be described 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.

[0165] In the first embodiment, the spring bodies 142 and 152 are configured to cock the second reversing arms 123 and 133 of the upper reversing pawl 120 and the lower reversing pawl 130 outward in the radial direction so as to come to compress the engagement portions 124 and 134 in the direction of the reversing 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 inwardly in the radial direction.

[0166] In this present embodiment, the upper reversing pawl 120 will be described by way of example.

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

[0168] Spring body 162 extends clockwise from proximal end 162a to distal end 162b to wrap around base 141 and first reversing arm 122 of the pawl. upper inverter 120 from outside. Then, the distal end 162b of the spring body 162 exerts a compressive force against the first reversing arm 122 from outside to 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 compression force against the switching gear part 102.

[0169] Further, the stopper 143 is formed to project counter-clockwise from the base 141 so as to be located within the distal end of the second reversing arm 123 of the upper reversing pawl 120 in the radial direction.

[0170] 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)

In the following, a third embodiment according to the invention will be described 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.

[0172] 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.

[0173] In this present embodiment, the upper reversing pawl 120 will be described by way of example.

As illustrated in Fig. 9, 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. .

[0175] The upper reversing pawls 120 are arranged symmetrically so as to face each other in the radial direction, with Tax 08 interposed between them. Accordingly, the two upper reversing pawls 120 are secured to the turntable 62 via the link pins 90, respectively.

[0176] Further, a flat spring 171 is integrally formed 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. Next, the spring 171 is shaped to extend clockwise relative to the second reversing arm 123 while wrapping around the second reversing arm 123 by the outside, and is arranged, in the radial direction, outside the first reversing arm 122 of the other adjacent upper reversing pawl 120 in the circumferential direction.

[0177] Then, a distal end 171b of the spring 171 comes to exert a compression 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 exerts a compressive force toward the reversing latch portions 102, respectively.

[0178] 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 with respect to the first reversing arm 122 of the another upper reversing pawl 120 adjacent in the circumferential direction.

[0179] 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.

[0180] Further, 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 is engaged with the engagement 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.

[0181] Therefore, when the engagement portion 124 of one of the upper reverse pawls 120 is released from the engagement surface 102a of the switching gear portion 102 and is brought into engagement with the engagement surface 102a of the adjacent switch gear portion 102, the engagement portion 124 of the other upper reverse pawl 120 can engage the engagement surface 102a of the switch gear portion 102.

[0182] Consequently, it is possible to reduce an angle called a blind spot. In effect, the angle of rotation of the oscillating mass 30 required from the start of the inversion of the oscillating mass 30 to the restarting of the rotation of the axis 65 in the counter-clockwise direction is made smaller, by This makes it possible to rotate the clutch ratchet wheel 20 more efficiently and to wind up the mainspring.

[0183] In the third embodiment, an exemplary case is described in which the two upper reversing pawls 120 are arranged symmetrically so as to face each other in the radial direction, with Pin 08 interposed between them, and the number of gears of the switching gear portion 102 is fixed as an odd number, so that when the engagement portion 124 of the upper reverse pawl 120 is engaged with the engagement surface 102a of the switch gear portion 102, the engagement portion 124 of the other upper reverse pawl 120 is disengaged from the engagement surface 102a of the switch gear portion 102.

[0184] However, the invention is not limited to such a configuration. For example, two upper reversing pawls 120 may be arranged to be offset Tun from each other in the circumferential direction by a predetermined angle corresponding to half of a gear element of the switching gear portion. 102 from a symmetrical position with respect to the axis 08, and the number of gear elements of the switching gear part 102 may be an even number. Even in such a case, as in the case described above, the so-called dead angle can be reduced, and the same beneficial operational effects as described above can be obtained.

(Fourth Embodiment)

In what follows, a fourth embodiment according to the invention will be described with reference to the drawings. In the fourth embodiment, the same components as those in the first embodiment are indicated by the same reference numerals and their description will not be repeated.

[0186] 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, a spring is integrally formed with the upper reversing pawl 120 and the lower reversing pawl 130.

[0187] In this present embodiment, the upper reversing pawl 120 will be described by way of example.

[0188] As shown in Figure 10, a reverser 180 according to this present embodiment includes an upper reverser pawl 120 integrally combined with a flat spring 181 to form a single integral piece. The upper reversing pawl 120 is formed integrally 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 turntable 62 so as to be able to pivot relative to it.

[0189] Link 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. to each other. On the other hand, a connection hole 195 through which the link pin 190 is inserted is formed in the central portion 121 of the upper reversing pawl 120. The connection hole 195 has an elliptical shape in 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 link pin 190.

[0190] Consequently, the upper reversing pawl 120 can be pivoted in a predefined angular range, within which a connection part P1 between the straight part 196 and the arcuate part 197 is in contact with a part

Claims (8)

of connection P2 between the cutting surface 191 and the arcuate surface 192, around pivot axis 09 which constitutes the central axis of the connecting pin 190. [0191] The spring 181 is shaped to extend clockwise from a proximal end 181a to a distal end 181b such that the proximal end 181a is connected to the central portion. 121 of upper reversing pawl 120. Next, the distal end 181b of spring 181 is inserted into a link pin 200 attached to turntable 62. [0192] Accordingly, the spring 181 will exert a compressive force against the upper reverse pawl 120 so as to compress the engagement portion 124 of the upper reverse pawl 120 against the shift gear portion 102 using its own elastic restoring force. [0193] 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. [0194] In addition, in the case of the present embodiment, since the upper reversing pawl 120 and the spring 181 are integrally formed, 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. [0195] 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. claimed. 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 that can be readily designed by those skilled in the art, those that are substantially the same, those that fall within the scope of equivalents, or the like. [0196] 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 winding mechanism. automatic and could be adopted for other timepiece mechanisms. [0197] In particular, in each of the embodiments described above, in order to be adopted in the automatic winding mechanism, a pair of inverter wheels and a pair of inverter pawls are provided such that the inverter including the upper reversing wheel, lower reversing wheel, upper reversing pawl and lower reversing pawl are provided. However, when the inverter is adopted in a timepiece mechanism other than the automatic winding mechanism, the inverter could include only an inverter wheel and an inverter pawl. Claims 1. Inverter (60) comprising: a rotary shaft (65) which is rotatably mounted about a first axis and has an inverter gear (73) configured to transmit power to a drive train; an inverting wheel (61) which is integral with the rotary shaft (65) so as to have a relative degree of freedom in rotation with respect to the latter, and rotates around the first axis due to the energy transmitted by a power source (21); a turntable (62) which is integrally integral with the rotating shaft; And a reversing pawl (63) which is integrally secured to the turntable (62) so as to be able to be pivoted around a second axis, in which the reversing wheel comprises a plurality of reversing pawl 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: an inverter arm (122) which extends from the second axis in the first direction in the circumferential direction; And an engagement portion (124) which is formed at one end of the inverter 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 portion (124) is held in compression against the engagement surface (102a). 2. Inverter (60) according to claim 1, wherein the engagement portion (124) is configured to maintain a state of engagement with the engagement surface (102a) when the reverse wheel rotates around the first axis in a first direction taken in the circumferential direction, and releasing the engagement with the engagement surface (102a) via the inclined surface (102b) when the reversing wheel rotates around the first axis in the opposite direction taken in the circumferential direction. 3. Inverter (60) according to claim 1 or 2, wherein the turntable (62) is equipped with a limiter configured to limit the amount of pivoting of the reversing pawl (63) about the second axis when engagement between the engagement portion (124) and the engagement surface ( 102a) is released. 4. Inverter (60) according to one of claims 1 to 3, wherein the spring (140) is arranged separately from the reversing pawl (63), and is secured to the turntable (62). 5. Inverter (60) according to one of claims 1 to 3, wherein the spring (140) is formed integrally with the reversing pawl (63), and is integral with the turntable (62). 6. Automatic winding mechanism (11) comprising: the inverter (60) according to one of claims 1 to 5; an oscillating mass (30) which is rotatable in both directions around a third axis and acts as a source of energy; And the drive cog which connects a clutch ratchet wheel configured to wind a mainspring to the reverse gear (73), wherein: a pair of reversing wheels and a pair of reversing pawls are arranged on either side of the turntable (62) in the direction of the first axis, the turntable (62) being interposed between them, among the pair of reversing wheels, the reversing wheel arranged closest to the reversing pinion (73) vis-à-vis the rotating plate (62) constitutes a first reversing wheel rotating following the rotation of the oscillating mass (30), the the other inverting wheel constituting a second inverting wheel which rotates in the opposite direction to the first inverting wheel following the rotation of the oscillating weight (30), among the pair of reversing pawls, the reversing pawl (63) closest to the reversing pinion (73) with respect to the turntable (62) constitutes a first reversing pawl (63) which cooperates with the first reversing wheel, and the another 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 the timepiece (1) according to claim 7.