JP2018169292A - Constant torque mechanism, movement for timepieces, and timepiece - Google Patents

Abstract

[PROBLEMS] To achieve compactness and space saving. A first power vehicle 21 rotating around a first rotation axis O1, a second power vehicle 26 arranged coaxially with the first power vehicle, and between the first power vehicle and the second power vehicle. A power spring 27 that transmits the stored power to the first and second motor vehicles and a cycle control mechanism 22 that intermittently rotates the second motor vehicle relative to the first motor vehicle; The mechanism includes a first control wheel 55 that rotates about the second rotation axis O2 as the first power vehicle rotates, and a second control wheel 56 that is disposed coaxially with the first control vehicle and meshes with the second power vehicle. A planetary mechanism 57 disposed between the first control vehicle and the second control vehicle and intermittently engaging and disengaging the engaging claw 80 and the stop wheel 81 based on the rotation of the first control vehicle; One power vehicle or the first control vehicle transmits power from the power spring to the escapement, and the second power vehicle or the second control vehicle is a power source. To provide a constant torque mechanism 20 to which power is transmitted. [Selection] Figure 3

Description

  The present invention relates to a constant torque mechanism, a timepiece movement, and a timepiece.

  Generally, in a mechanical timepiece, when the torque (power) transmitted from the barrel complete to the escapement fluctuates according to the unwinding of the mainspring, the swing angle of the balance changes according to the fluctuation of the torque. Change in the rate (degree of clock delay or advance). Therefore, it is known to provide a constant torque mechanism in the power transmission path from the barrel complete to the escapement in order to suppress fluctuations in torque transmitted to the escapement.

Various types of constant torque mechanisms of this type have been proposed. For example, when attention is paid to periodic control, the constant torque mechanism is roughly divided into three types: a cam method, a train wheel method, and a planetary vehicle method.
The cam-type constant torque mechanism has, for example, a follower or fork that engages with a cam connected to the escapement side train wheel and swings in response to the rotation of the cam, and is provided on the follower or fork. The engagement / disengagement cycle is controlled by periodically engaging / disengaging the detachment claw with the escapement vehicle connected to the power source side wheel train. Thereby, it is possible to wind up the constant torque spring between the power source side train wheel and the escapement side train wheel.

  The constant torque mechanism of the train wheel system is achieved by connecting the power source side train wheel and the escapement side train wheel with a differential mechanism and moving the engagement / disengagement claw that engages / disengages to / from the stop vehicle into and out of the trajectory of the stop vehicle. It is possible to periodically control the phase difference. The planetary vehicle type constant torque mechanism has, for example, a planetary mechanism using a stop vehicle as a planetary car as described in Patent Document 1 below, and the planetary mechanism uses a power source side train wheel and an escaper side train wheel. It is possible to periodically control the phase difference between and. The planetary car revolves while rotating so as to follow the engagement / disengagement claw provided in the sun wheel connected to the escapement side wheel train.

Swiss patent application 707938

However, in the cam type constant torque mechanism, when the timing of engagement / disengagement between the escapement vehicle and the engagement / disengagement claw has deviated for some reason, the constant torque spring is unexpectedly unwound excessively. There was a risk of overrelease.
In this respect, in the train wheel type constant torque mechanism, the power source side train wheel and the escapement side train wheel are connected by a differential mechanism, so that overrelease is unlikely to occur. However, since the structure requires a lot of engagement, the number of parts constituting the constant torque mechanism increases, and a large plane space is required.

  Also, in the planetary vehicle type constant torque mechanism, over-release is unlikely to occur as in the case of the train wheel type constant torque mechanism, but other major components are used so as not to impede the rotation and revolution of the stop vehicle, which is a planetary vehicle. Functional parts must be arranged in the thickness direction. For this reason, the entire constant torque mechanism becomes thick.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a constant torque mechanism, a timepiece movement, and a timepiece that can be made compact and space-saving.

(1) A constant torque mechanism according to the present invention is arranged around a first power vehicle that rotates about a first rotational axis, and coaxially with the first power vehicle, and is disposed on the first power vehicle about the first rotational axis. A second power vehicle capable of rotating relative to the first power vehicle, a power spring disposed between the first power vehicle and the second power vehicle, and transmitting stored power to the first power vehicle and the second power vehicle; A cycle control mechanism that intermittently rotates the second power vehicle with respect to the first power vehicle and replenishes the power spring with power, and the cycle control mechanism rotates the first power vehicle. Accordingly, the first control wheel that rotates about the second rotation axis and the first control wheel are arranged coaxially with the first control wheel, and can rotate relative to the first control wheel about the second rotation axis. A second control vehicle meshing with the second power vehicle, and between the first control vehicle and the second control vehicle. A planetary mechanism that intermittently engages and disengages an engaging claw provided in the first control vehicle and a stop vehicle provided in the second control vehicle based on rotation of the first control vehicle; The first power vehicle or the first control vehicle transmits power from the power spring to the escapement, and the second power vehicle or the second control vehicle receives power from the power source. Reportedly.

  According to the constant torque mechanism of the present invention, the power (torque) stored in the power spring can be transmitted to the first power vehicle to rotate the first power vehicle. Accordingly, the first power vehicle and the first control vehicle can be rotated, and the power from the power spring can be transmitted to the escapement via the first power vehicle or the first control vehicle. Thereby, an escapement can be operated. In addition, a planetary mechanism is provided between the first control vehicle and the second control vehicle to intermittently engage and disengage the engaging claw and the stop vehicle based on the rotation of the first control vehicle. By utilizing the engagement / disengagement, the cycle control can be performed by intermittently rotating the second power vehicle with respect to the first power vehicle.

Although the difference between the power transmitted from the power source and the power transmitted from the power spring acts on the second power vehicle and the second control vehicle, the engaging claw and the stop vehicle are engaged. In this case, the second power vehicle and the second control vehicle are prevented from rotating by this engagement. When the first control vehicle is rotated by the rotation of the first power vehicle from this state, the engagement between the engagement claw and the stop vehicle is released, so that the power transmitted from the power source and the power spring are transmitted. Both the second power vehicle and the second control vehicle are rotated by the power of the difference from the power. Thereby, a 2nd power vehicle can be rotated intermittently with respect to a 1st power vehicle, and power can be replenished with respect to a power spring. As a result, the power of the power spring can be maintained constant, and the escapement can be operated with a constant torque.
In addition, with the replenishment of power to the power spring, the engagement pawl and the stop wheel are engaged again by the rotation of the second control wheel. Therefore, the engagement and disengagement between the engaging claw and the stop wheel can be repeated, and the second power vehicle can be intermittently rotated with respect to the first power vehicle.

  In particular, since the cycle control is performed using a planetary mechanism, a so-called over-release phenomenon does not occur in the power spring unlike the conventional cam system. Further, a mechanism (torque generation mechanism) composed of the first power vehicle, the second power vehicle, and the power spring and the cycle control mechanism are arranged so as to be shifted in a plane. Therefore, the thickness of the entire constant torque mechanism can be suppressed as compared with the conventional planetary vehicle system. In addition, a power spring is disposed between the first power vehicle and the second power vehicle, and a planetary mechanism is disposed between the first control vehicle and the second control vehicle. Therefore, the planar spread can be suppressed, and it is possible to arrange the constant torque mechanism in a small plane space as compared with the conventional planetary vehicle system.

(2) The engaging claw rotates around the second rotation axis as the first control wheel rotates, and the stop wheel rotates while the second control wheel rotates, while the second wheel rotates. And a stop gear that revolves around a rotation axis and that can be engaged and disengaged with respect to the engaging claw, and the engaging claw is based on rotation of the first control vehicle after the stop gear is engaged. The engagement of the stop gear may be released by rotating around the second rotation axis so as to be separated from the stop gear.

In this case, from the state in which the stop gear and the engaging claw are engaged, the engaging claw is disengaged from the stop gear by the first control vehicle rotating with the rotation of the first power vehicle, The engagement between the stop gear and the engagement claw is released. Thus, the second power vehicle can be rotated with respect to the first power vehicle, and power can be supplemented to the power spring. Further, when the power for the power spring is replenished, the second control wheel rotates, so that the stop wheel revolves around the second rotation axis while following the engagement claw while rotating. Then, the stop gear of the stop wheel that has caught up with the engaging claw is engaged again with the engaging claw.
By repeating the above, the stop gear and the engaging claw can be intermittently engaged and disengaged, and the second power vehicle can be intermittently rotated with respect to the first power vehicle.

(3) A support lever that supports the engagement claw is configured to be rotatable around the second rotation axis along with the rotation of the first control wheel, and the stop claw engages and disengages the engagement claw. The support lever is configured such that the stop gear presses the engagement surface between the time when the stop gear is engaged with the engagement surface and the time when the engagement is released. The engaging claw is supported so that an imaginary line along the resultant force of the pressing force to be applied and the frictional force generated by the stop gear sliding on the engaging surface passes through the second rotation axis. You may do it.

In this case, when attention is paid to the rotational torque generated in the support lever that supports the engagement / disengagement claw when the stop gear and the engagement claw are engaged and the engagement is released in one cycle. The average torque in one cycle can be kept constant.
When the stop gear engages with the engaging surface of the engaging claw, the stop gear is deeply engaged with the engaging claw in the initial stage, and then the stop gear is engaged by the disengagement of the engaging claw as the support lever rotates. Since it moves to the toe side of the engaging claw while sliding on the surface, the engagement gradually becomes shallower. Then, when the stop gear exceeds the toe of the engaging claw, the engagement is released.

  In this series of one cycle, the angle of the engagement surface with respect to the stop gear changes, and accordingly, the direction of the resultant force changes. At this time, at the moment when the direction along the resultant force passes the second rotation axis, the rotation torque generated in the support lever is not generated. On the other hand, when the direction along the resultant force deviates from the second rotation axis, rotational torque is generated according to the amount of deviation. In particular, a reverse rotational torque is generated before and after the direction along the resultant force passes through the second rotation axis. That is, a rotational torque that pulls the support lever toward the stop wheel is generated in the support lever, and a rotational torque that pulls the support lever away from the stop wheel is generated in the support lever. Therefore, although the torque of the support lever varies when viewed in one cycle, the average torque in one cycle can be made constant. As a result, constant torque characteristics can be ensured.

(4) In the intermediate position between the engagement position where the stop gear is engaged with the engagement surface and the disengagement position where the stop gear is separated from the engagement surface, the virtual line is the second rotation axis. You may pass.

  In this case, the above-described average torque in one cycle can be more stably maintained constant, and the constant torque property can be secured more stably.

(5) A power adjustment mechanism that adjusts the power of the power spring via the first power vehicle or the second power vehicle may be provided.

  In this case, since the power of the power spring can be adjusted, the escapement can be operated with a constant torque more stably. Further, for example, after combining the first power vehicle, the second power vehicle, and the power spring, power can be applied to the power spring, so that the assemblability can be improved. Furthermore, since the second power vehicle is disposed at a position shifted in a plane from the cycle control mechanism, the power adjustment mechanism can be provided without worrying about the cycle control mechanism, and the power adjustment mechanism can be easily installed. Easy to do.

(6) The power adjustment mechanism includes an adjustment vehicle that can be engaged with the first power vehicle or the second power vehicle, and an engagement that the adjustment vehicle meshes with the first power vehicle or the second power vehicle. A moving member that moves the adjustment vehicle between a position and a release position where the engagement between the adjustment vehicle and the first power vehicle or the second power vehicle is released may be provided.

  In this case, since the power of the power spring can be adjusted by the rotation of the adjusting wheel, the adjustment can be performed minutely and intuitively, and the adjustment work can be easily performed. Furthermore, since the engagement between the first power vehicle or the second power vehicle and the adjustment vehicle can be separated by keeping the adjustment vehicle in the release position, the first power vehicle can be used when power adjustment is not performed. It is possible to prevent an excessive rotational load from being applied to the vehicle or the second power vehicle.

(7) A timepiece movement according to the present invention includes the constant torque mechanism.
(8) A timepiece according to the present invention includes the above-described timepiece movement.

  In this case, since the constant torque mechanism capable of achieving compactness and space saving is provided, it is possible to provide a timepiece movement and a timepiece that can be easily reduced in size and thickness.

  ADVANTAGE OF THE INVENTION According to this invention, it can be set as the constant torque mechanism, the movement for timepieces, and a timepiece which can achieve size reduction and space saving.

1 is an external view of a timepiece showing an embodiment of the present invention. It is a block diagram of the movement shown in FIG. It is a perspective view of the constant torque mechanism shown in FIG. FIG. 4 is a top view of the constant torque mechanism shown in FIG. 3. It is sectional drawing of the constant torque mechanism along the AB line shown in FIG. It is a perspective view which shows a part of 2nd power vehicle shown in FIG. FIG. 4 is a bottom view of the constant torque mechanism shown in FIG. 3. FIG. 4 is a perspective view showing a part of a second control vehicle and a second power vehicle shown in FIG. 3. It is a perspective view which shows a part of 2nd power vehicle shown in FIG. It is a perspective view which shows the 2nd control vehicle and planetary mechanism which are shown in FIG. It is a top view which shows the engagement state of the engaging claw stone shown in FIG. 10, and a stop tooth | gear. It is sectional drawing with the 2nd control vehicle and stop vehicle which are shown in FIG. It is a top view which shows the engagement state of the engaging claw stone shown in FIG. 11, and a stop tooth | gear. It is a top view which shows the state from which the engagement claw stone began to detach | leave from a stop tooth | gear from the state shown in FIG. FIG. 15 is a plan view showing a state where the engaging claw stone is further detached from the stop teeth from the state shown in FIG. 14. It is a top view which shows the state by which engagement with the engaging claw stone and the stop tooth was cancelled | released from the state shown in FIG. It is a top view which shows the state which the support member of the stop vehicle and the 2nd lever piece contact | abutted from the state shown in FIG. It is sectional drawing of the constant torque mechanism along the AC line shown in FIG. It is a perspective view of a constant torque mechanism, and is a figure for explaining a power adjustment mechanism. It is a figure which shows the torque fluctuation accompanying engagement / disengagement of an engaging claw stone and a stop tooth | gear. FIG. 4 is a perspective view showing a state before assembly of the torque generating mechanism shown in FIG. 3, and shows a state in which the first power vehicle is set above the second power vehicle combined with a constant torque spring. It is a figure which shows the state which accumulated the 1st power vehicle and the 2nd power vehicle from the state shown in FIG. 21 so that a prescription | regulation part may be located in the opening part of a slide hole. It is a figure which shows the state which rotated the 1st power vehicle and the 2nd power vehicle in the opposite direction relatively from the state shown in FIG. 22, and engaged the prescription | regulation part inside the slide hole. It is a figure which shows the modification which concerns on this invention, Comprising: It is a top view which shows the engagement state of an engagement claw stone and a stop tooth | gear in the external gear type fixed gear. It is a top view which shows the state from which the engagement claw stone began to detach | leave from a stop tooth | gear from the state shown in FIG. FIG. 26 is a plan view showing a state where the engaging claw stone is further detached from the stop teeth from the state shown in FIG. 25. It is a perspective view which shows the modification of the torque generation mechanism which concerns on this invention. It is a perspective view which shows another modification of the torque generation mechanism which concerns on this invention.

  Hereinafter, embodiments according to the present invention will be described with reference to the drawings. In the present embodiment, a mechanical timepiece will be described as an example of a timepiece. In each drawing, the scale of each component is appropriately changed as necessary in order to make each component visible.

(Basic clock configuration)
In general, a machine body including a driving part of a timepiece is referred to as a “movement”. A state in which a dial and hands are attached to the movement, and put into a watch case to form a finished product, is referred to as “complete” of the watch.
Of the two sides of the main plate constituting the watch substrate, the side of the watch case with the glass (that is, the side with the dial) is referred to as the “back side” of the movement. Further, of the both sides of the main plate, the side of the watch case with the case back (that is, the side opposite to the dial) is referred to as the “front side” of the movement.

  In the present embodiment, the direction from the dial toward the case back cover is defined as the upper side, and the opposite side is defined as the lower side. In addition, a direction that rotates clockwise about each rotation axis when viewed from above is referred to as a clockwise direction, and a direction that rotates counterclockwise when viewed from above is referred to as a counterclockwise direction.

  As shown in FIG. 1, the timepiece 1 according to the present embodiment includes a movement (timepiece movement according to the present invention) 10 and at least information about time in a timepiece case made of a case back and a glass 2 (not shown). A dial 3 having a graduation shown, and a pointer 4 including an hour hand 5, a minute hand 6 and a second hand 7 are provided.

  As shown in FIG. 2, the movement 10 includes a barrel wheel 11 as a power source, a power source side train wheel 12 connected to the barrel wheel 11, an escapement 14 controlled by a governor 13, And a constant torque mechanism 20 disposed between the power source side wheel train 12 and the escapement side wheel train 15.

Note that the power source side train wheel 12 in this embodiment refers to a train wheel that is located closer to the barrel wheel 11 that is the power source than the constant torque mechanism 20 when viewed from the constant torque mechanism 20. Similarly, the escapement side train wheel 15 in the present embodiment refers to a train wheel that is located closer to the escapement 14 than the constant torque mechanism 20 when viewed from the constant torque mechanism 20.
In the present embodiment, a constant torque mechanism 20 is generally provided at a position corresponding to the third wheel constituting the front train wheel, and a first power vehicle 25, a second power vehicle 26, a first control vehicle 55, and a first control vehicle which will be described later. The entire 2 control wheel 56 functions as a third wheel.
As shown in FIG. 3, the first power wheel 25 and the second power wheel 26 rotate around the first rotation axis O1, and the first control wheel 55 and the second control wheel 56 move relative to the first rotation axis O1. Then, it rotates around the second rotation axis O2 arranged at a position shifted in the in-plane direction of the ground plate (not shown).

As shown in FIG. 2, the barrel complete 11 is pivotally supported between a main plate and a barrel holder (not shown), and a mainspring 16 is accommodated therein. The mainspring 16 is wound up by rotation of a winding stem (not shown) connected to the crown 17 shown in FIG. The barrel complete 11 is rotated by power (torque) accompanying unwinding of the mainspring 16 and transmits the power to the constant torque mechanism 20 via the power source side wheel train 12.
In the present embodiment, the case where the power from the barrel complete 11 is transmitted to the constant torque mechanism 20 via the power source side wheel train 12 will be described as an example. However, the present invention is not limited to this case. The power from the barrel complete 11 may be directly transmitted to the constant torque mechanism 20 without using the source-side wheel train 12.

The power source side wheel train 12 mainly includes a second wheel & pinion 18.
As shown in FIGS. 3 and 4, the center wheel & pinion 18 is pivotally supported between the main plate and a train wheel bridge (not shown), and rotates around the third rotation axis O <b> 3 based on the rotation of the barrel complete 11. The third rotation axis O3 is arranged at a position shifted in the in-plane direction of the main plate with respect to the second rotation axis O2.
When the center wheel & pinion 18 is rotated, a cylindrical pinion (not shown) is rotated based on the rotation. The minute hand 6 shown in FIG. 1 is attached to the cylindrical pinion, and the minute hand 6 displays “minute” by the rotation of the cylindrical pinion. The minute hand 6 rotates once by the rotational speed adjusted by the escapement 14 and the speed governor 13, that is, by one hour.

  Further, when the center wheel & pinion 18 is rotated, a minute wheel (not shown) is rotated based on this rotation, and an hour wheel (not illustrated) is rotated based on the rotation of the minute wheel. The minute wheel and the hour wheel are timepiece components constituting the power source side wheel train 12. The hour hand 5 shown in FIG. 1 is attached to the hour wheel, and the hour hand 5 displays “hour” by the rotation of the hour wheel. The hour hand 5 rotates once by the rotational speed adjusted by the escapement 14 and the speed governor 13, for example, 12 hours.

As shown in FIG. 2, the escapement side wheel train 15 mainly includes a fourth wheel 19.
As shown in FIGS. 3 and 4, the fourth wheel 19 is pivotally supported between the main plate and the train wheel bridge, and is based on the rotation of a first power wheel 25 (described later) of the constant torque mechanism 20. Rotate around. The fourth rotation axis O4 is arranged at a position shifted in the in-plane direction of the main plate with respect to the first rotation axis O1. A second hand 7 shown in FIG. 1 is attached to the fourth wheel 19, and the second hand 7 displays “second” based on the rotation of the fourth wheel 19. The second hand 7 rotates once by the rotational speed adjusted by the escapement 14 and the speed governor 13, for example, 1 minute.

The escapement 14 mainly includes a escape wheel (not shown) and an ankle (not shown).
The escape wheel is pivotally supported between the main plate and the train wheel bridge, and meshes with the fourth wheel & pinion 19. As a result, power from a constant torque spring 27 described later in the constant torque mechanism 20 is transmitted to the escape wheel & pinion through the fourth wheel & pinion 19. Thereby, the escape wheel is rotated by the power from the constant torque spring 27.
The ankle is supported so as to be rotatable (swingable) between a ground plane and an ankle receiver (not shown), and has a pair of claw stones (not shown). The pair of claw stones are alternately engaged and disengaged at predetermined intervals with respect to the escape teeth in the escape wheel by the governor 13. Thereby, the escape wheel can escape at a predetermined cycle.

The governor 13 is mainly provided with a balance not shown.
The balance with a balance, a balance wheel, and a hairspring is pivotally supported between a main plate and a balance holder (not shown). The balance with hairspring is reciprocally rotated (forward / reverse rotation) at a fixed swing angle using a hairspring as a power source.

(Configuration of constant torque mechanism)
As shown in FIGS. 2 to 4, the constant torque mechanism 20 is a mechanism for suppressing fluctuation (torque fluctuation) of power transmitted to the escapement 14, and mainly includes a torque generation mechanism 21 and a cycle control mechanism 22. I have.

(Configuration of torque generation mechanism)
The torque generating mechanism 21 is disposed coaxially with the first power wheel 25 that rotates about the first rotation axis O1 and the first power wheel 25, and rotates relative to the first power wheel 25 about the first rotation axis O1. A constant torque spring disposed between the possible second power vehicle 26 and the first power vehicle 25 and the second power vehicle 26 to transmit the stored power to the first power vehicle 25 and the second power vehicle 26 (the present invention); Power spring) 27).
The first power vehicle 25 is disposed above the second power vehicle 26.

As shown in FIGS. 3 to 6, the second power vehicle 26 is pivotally supported between the main plate and the train wheel bridge, and extends along the first rotation axis O <b> 1, and is integrated with the shaft 30. A coupling gear 31 formed on the coupling gear 31, a first torque adjustment gear 33 integrally combined with the coupling gear 31, and a torque adjustment jumper 34 releasably engaged with the coupling teeth 32 of the coupling gear 31; And a second power gear 35 linked to the connecting gear 31 via a torque adjustment jumper 34.
The second power wheel 26 is rotated by the power transmitted from the constant torque spring 27.

As shown in FIG. 5, the shaft portion 30 extends upward from the first power vehicle 25.
The connecting gear 31 is formed between the vertical center portion and the lower end portion of the shaft portion 30 and has a predetermined thickness. A plurality of the connecting teeth 32 are formed on the outer peripheral surface of the connecting gear 31 on the upper end side as shown in FIG.

Each connecting tooth 32 includes a first engagement surface 32a facing the counterclockwise direction around the first rotation axis O1 and a second engagement surface 32b facing the clockwise direction.
The first engagement surface 32a is formed along a radial direction orthogonal to the first rotation axis O1. On the other hand, the second engagement surface 32b is inclined so as to gradually extend counterclockwise from the outer peripheral surface of the coupling gear 31 toward the outer side in the radial direction.

As shown in FIG. 5, the first torque adjusting gear 33 is formed in an annular shape surrounding the connecting gear 31 from the outside in the radial direction, and is fitted to a portion of the connecting gear 31 positioned below the connecting teeth 32. doing. Thereby, the 1st torque adjustment gear 33 and the connection gear 31 are united together as mentioned above.
As shown in FIGS. 5 and 7, the first torque adjustment gear 33 a that meshes with the second torque adjustment gear 111 a of the second torque adjustment gear 111 (described later) is formed on the outer peripheral surface of the first torque adjustment gear 33 over the entire circumference. Is formed.

As shown in FIGS. 5 and 6, the second power gear 35 is formed in an annular shape surrounding the coupling teeth 32 from the outside in the radial direction, and is rotatable on the first torque adjustment gear 33 so as to be rotatable around the first rotation axis O <b> 1. It is placed. In the illustrated example, the second power gear 35 is formed to have a larger diameter than the first torque adjustment gear 33.
On the outer peripheral surface of the second power gear 35, second power teeth 35a that engage with second control teeth 62a in the second control gear 62 described later are formed over the entire circumference.

  The second power gear 35 is formed with an opening 36 that vertically penetrates the second power gear 35 and exposes the coupling teeth 32 over a certain range. The torque adjustment jumper 34 is formed integrally with the second power gear 35 so as to be disposed in the opening 36.

In detail, the torque adjustment jumper 34 is elastically formed around the base end portion 34a so that the base end portion 34a is formed integrally with the second power gear 35 and the free end end portion 34b moves in the radial direction. It can be deformed.
A part of the tip end portion 34b of the torque adjustment jumper 34 protrudes toward the connecting gear 31 side, and is arranged so as to enter between the connecting teeth 32 adjacent in the circumferential direction. At this time, the tip 34b of the torque adjustment jumper 34 is pressed so as to enter between the connecting teeth 32 adjacent in the circumferential direction by a predetermined spring force.

  Thereby, the front-end | tip part 34b of the torque adjustment jumper 34 is the 1st engagement of one connection tooth 32 located in the clockwise direction rather than the front-end | tip part 34b of the torque adjustment jumper 34 among the connection teeth 32 adjacent to the circumferential direction. In addition to being engaged with the surface 32 a, it is engaged with the second engagement surface 32 b of the other connecting tooth 32 positioned on the counterclockwise side of the tip end portion 34 b of the torque adjustment jumper 34.

  As described above, the first engagement surface 32a is formed along the radial direction, and the second engagement surface 32b is inclined. Therefore, when the connection gear 31 rotates counterclockwise, the first engagement of the tip end portion 34b of the torque adjustment jumper 34 and the connection tooth 32 positioned on the clockwise side of the tip end portion 34b of the torque adjustment jumper 34 is performed. The surface 32a can be engaged in the circumferential direction, and the second power gear 35 is counterclockwise via the torque adjustment jumper 34 as long as the engagement between the tip 34b and the first engagement surface 32a is not released. It can be rotated in the same direction.

  In addition, when a counterclockwise torque that releases the engagement between the tip end portion 34b of the torque adjustment jumper 34 and the first engagement surface 32a of the connection tooth 32 is applied to the connection gear 31, the torque The engagement between the tip end portion 34b of the adjustment jumper 34 and the first engagement surface 32a is released. Thereby, the connecting tooth 32 moves counterclockwise while getting over the tip 34b of the torque adjustment jumper 34 in the circumferential direction. Therefore, the connecting gear 31 can be rotated counterclockwise relative to the second power gear 35.

On the other hand, when the connecting gear 31 is rotated in the clockwise direction, the tip end portion 34b of the torque adjustment jumper 34 is the first of the connecting teeth 32 located on the counterclockwise side of the tip end portion 34b of the torque adjustment jumper 34. 2 Due to the inclination of the engaging surface 32b, it is pressed toward the outside in the radial direction while sliding on the second engaging surface 32b.
As a result, the engagement between the tip end portion 34b of the torque adjustment jumper 34 and the second engagement surface 32b is released, and the connecting tooth 32 moves clockwise while getting over the tip end portion 34b of the torque adjustment jumper 34 in the circumferential direction. Therefore, it becomes possible to rotate the connecting gear 31 in the clockwise direction relative to the second power gear 35.

That is, the torque adjusting jumper 34 and the connecting teeth 32 cause the second power gear 35 to rotate together when the connecting gear 31 rotates counterclockwise, and the second power when the connecting gear 31 rotates clockwise. It functions as a ratchet mechanism that allows the connection gear 31 to rotate relative to the gear 35.
The spring force of the torque adjustment jumper 34 is such that when the connecting gear 31 is rotated counterclockwise with the torque Tj, the tip end portion 34b of the torque adjusting jumper 34 and the first engagement surface 32a of the connecting tooth 32 are provided. The engagement is set to be released. Hereinafter, the torque Tj is referred to as a jumper torque Tj of the torque adjustment jumper 34.
Further, the spring force of the torque adjusting jumper 34 is such that when the connecting gear 31 is rotated clockwise with the torque Tk, the tip 34b of the torque adjusting jumper 34 and the second engaging surface 32b of the connecting tooth 32 are engaged. It is set to cancel the connection. Hereinafter, the torque Tk is referred to as a jumper torque Tk of the torque adjustment jumper 34.

As shown in FIG. 5, a restriction ring 37 that restricts the movement of the tip end portion 34 b of the torque adjustment jumper 34 upward is disposed above the second power gear 35.
The restriction ring 37 is formed in an annular shape surrounding the coupling gear 31 from the outside in the radial direction, and is in a non-contact state with respect to the second power gear 35, with respect to a portion of the coupling gear 31 positioned above the coupling teeth 32. Are mated.
As a result, the tip end portion 34b of the torque adjustment jumper 34 can be restricted from jumping upward or floating, and the engagement between the tip end portion 34b of the torque adjustment jumper 34 and the connecting tooth 32 can be stabilized.

As shown in FIGS. 3 to 5, the first power vehicle 25 includes a rotating cylinder 40 disposed coaxially with the first rotation axis O <b> 1, and a first power gear 41 integrally connected to the rotating cylinder 40. It is equipped with.
The first power wheel 25 rotates clockwise by the power transmitted from the constant torque spring 27. The first power wheel 25 and the second power wheel 26 can be rotated in opposite directions around the first rotation axis O <b> 1 by the power transmitted from the constant torque spring 27.

The shaft portion 30 of the second power vehicle 26 is inserted into the rotary cylinder 40 from below and protrudes above the rotary cylinder 40. On the inner side of the upper end and the lower end of the rotating cylinder 40, for example, a ring-shaped hole stone 42 made of artificial jewel such as ruby is press-fitted. The shaft portion 30 of the second power vehicle 26 passes through the inside of these hole stones 42. As a result, the first power vehicle 25 and the second power vehicle 26 are combined so as to be relatively rotatable around the first rotation axis O1 with little backlash.
The hole stone 42 is not limited to the case of being formed of artificial gemstones, and may be formed of other brittle materials or metal materials such as iron alloys.

The first power gear 41 includes a plurality of arm portions 41a that are spaced circumferentially about the first rotation axis O1, and a ring-shaped gear body 41b that is coupled to the outer end of the arm portion 41a. I have.
In the illustrated example, four arm portions 41a are formed at an interval of 90 degrees around the first rotation axis O1. However, the number, arrangement, and shape of the arm portions 41a are not limited to this case, and may be freely changed.

  On the outer peripheral surface of the gear body 41b, first power teeth 41c that engage with first control teeth 71c in a first control gear 71 described later are formed over the entire circumference. The first power teeth 41 c are also engaged with the fourth pinion 19 a in the fourth wheel 19. Thus, the first power vehicle 25 transmits the power from the constant torque spring 27 to the fourth wheel 19 connected to the escapement 14, that is, the escapement side wheel train 15 as indicated by an arrow R1 shown in FIG. It is possible.

In the present embodiment, the case where the power from the constant torque spring 27 is transmitted to the escapement 14 via the escapement side wheel train 15 will be described as an example. However, the present invention is not limited to this case. For example, the escapement side wheel train 15 may not be provided, and the power from the constant torque spring 27 may be directly transmitted to the escapement 14.
Further, the first power gear 41 is formed to have the same diameter as the second power gear 35. However, the present invention is not limited to this case, and the first power gear 41 and the second power gear 35 may be formed with different diameters.

  The constant torque spring 27 is a thin plate spring made of a metal or alloy such as iron or nickel, and is formed in a spiral shape. Specifically, the constant torque spring 27 is formed in a spiral shape along the Archimedes curve in a polar coordinate system with the first rotation axis O1 as the origin. Thereby, the constant torque spring 27 is wound with a plurality of turns so as to be adjacent to each other at substantially equal intervals in the radial direction when viewed from the direction of the first rotation axis O1.

As shown in FIGS. 8 and 9, the constant torque spring 27 has an outer end (one end) 27 b that is one peripheral end connected to the first power vehicle 25 side and the other peripheral end. A certain inner end (other end) 27a is connected to the second power vehicle 26 side. As a result, the constant torque spring 27 can transmit the stored power to the first power vehicle 25 and the second power vehicle 26, respectively. The arcuate part is spaced apart radially outward via the attaching part 27c and has a radius of curvature larger than that of the other part. An end portion of the arc portion is an outer end portion 27 b of the constant torque spring 27.

The constant torque spring 27 is wound with a predetermined winding amount in the counterclockwise direction toward the outer end portion 27b with the inner end portion 27a as the unwinding position. The constant torque spring 27 is elastically deformed so as to be reduced in diameter by being wound up, and a preload is applied thereto. Therefore, the constant torque spring 27 generates a power of torque Tc and stores the power.
The stored power is transmitted to the first power vehicle 25 and the second power vehicle 26 along with the elastic restoring deformation of the constant torque spring 27. Thus, the first power wheel 25 can be rotated in the clockwise direction, and the second power wheel 26 can be rotated in the counterclockwise direction. Hereinafter, the torque Tc is referred to as the rotational torque Tc of the constant torque spring 27.

A structure for fixing the constant torque spring 27 to the first power vehicle 25 and the second power vehicle 26 will be described in detail.
As shown in FIGS. 5, 8 and 9, the inner end portion 27 a of the constant torque spring 27 is fixed to a fixing ring 45 attached to the shaft portion 30 of the second power wheel 26.
The fixing ring 45 is fitted to, for example, a portion of the shaft portion 30 that is located between the regulation ring 37 and the rotary cylinder 40 in the first power vehicle 25. The inner end portion 27a of the constant torque spring 27 is fixed to the fixing ring 45 by, for example, caulking or welding.

  As shown in FIGS. 3, 4, 8 and 9, the outer end portion 27 b of the constant torque spring 27 is detachably engaged in a slide hole 46 provided on the first power vehicle 25 side, A regulating portion 47 that regulates the radial position of the outer end portion 27b and the rotating cylinder 40 in the first power wheel 25 are in contact with each other, and the outer end portion 27b becomes the first when the constant torque spring 27 is elastically deformed. A regulating lever 48 that regulates rotation around the rotation axis O1 is provided.

  The slide hole 46 is formed in the arm portion 41 a of the first power gear 41. The slide hole 46 is formed along the circumferential direction that circulates around the first rotation axis O1, and is formed so as to open counterclockwise.

  As shown in FIGS. 8 and 9, the defining portion 47 is formed in a columnar shape that extends vertically, and includes a shaft body 50 that engages with the inside of the slide hole 46, and a head formed on the upper end portion of the shaft body 50. 51 and a bifurcated leg portion 52 formed at the lower end portion of the shaft body 50. The shaft body 50 is formed with a diameter-enlarged portion 53 having a diameter larger than that of the head portion 51 at a portion located between the head portion 51 and the leg portion 52.

  The outer end portion 27b of the constant torque spring 27 is fixed to the leg portion 52 by, for example, adhesion or caulking while being inserted inside the leg portion 52. Thereby, the outer end portion 27b of the constant torque spring 27 and the defining portion 47 are combined together.

  The defining portion 47 configured in this manner is inserted into the slide hole 46 by sliding movement. Thereby, the shaft body 50 is engaged with the inside of the slide hole 46. In particular, the outer end portion 27 b of the constant torque spring 27 is pulled clockwise by the rotational torque (winding torque) accompanying the elastic restoring deformation of the constant torque spring 27. Therefore, the defining portion 47 is pulled toward the peripheral end wall of the slide hole 46, and the shaft body 50 is pressed against and engages with the peripheral end wall. In this way, the defining portion 47 engages with the inside of the slide hole 46 and defines the radial position of the outer end portion 27 b of the constant torque spring 27.

  The arm portion 41a in which the slide hole 46 is formed is arranged so as to be sandwiched between the head portion 51 and the enlarged diameter portion 53, so that the defining portion 47 engaged inside the slide hole 46 is It is prevented from coming off upward and downward.

As shown in FIG. 9, the regulation lever 48 is integrally combined with the defining portion 47. In the illustrated example, the base end portion of the regulating lever 48 is combined with a portion of the shaft portion 30 in the defining portion 47 located between the enlarged diameter portion 53 and the leg portion 52. The front end 48 a of the restriction lever 48 is in contact with the rotating cylinder 40 in the first power vehicle 25 from the outside in the radial direction.
Thus, the regulation lever 48 is used to regulate the rotation of the outer end portion 27b of the constant torque spring 27 around the first rotation axis O1 by the rotational torque accompanying the elastic restoring deformation of the constant torque spring 27.

(Configuration of periodic control mechanism)
As shown in FIGS. 2 to 5, the cycle control mechanism 22 intermittently rotates the second power vehicle 26 with respect to the first power vehicle 25, thereby causing a constant torque spring 27 as indicated by an arrow R <b> 2 shown in FIG. 2. This is a mechanism for replenishing power to the constant torque mechanism 20 and is disposed at a position shifted in a plane.

The cycle control mechanism 22 is arranged coaxially with the first control wheel 55 that rotates around the second rotation axis O2 as the first power wheel 25 rotates, and around the second rotation axis O2. A second control wheel 56 that is rotatable relative to the first control wheel 55 and a planetary mechanism 57 disposed between the first control wheel 55 and the second control wheel 56 are provided.
The first control wheel 55 is disposed above the second control wheel 56.

  As shown in FIGS. 3 and 5, the second control wheel 56 is pivotally supported between the main plate and the train wheel bridge, and is integrally formed with the shaft portion 60 extending along the second rotation axis O2. A second control pinion 61 that is formed and meshes with the center wheel 18 and a second control gear 62 having second control teeth 62 a that mesh with the second power teeth 35 a of the second power wheel 26 are provided.

The shaft portion 60 extends upward from the first control wheel 55.
The second control kana 61 is formed between the central portion and the lower end of the shaft portion 60 in the vertical direction. Since the second control pinion 61 is engaged with the center wheel & pinion 18, it rotates based on the rotation of the center wheel & pinion 18. Thereby, the power from the barrel complete 11 is transmitted to the second control wheel 56 via the second wheel 18, that is, the power source side wheel train 12.

  The second control wheel 56 rotates counterclockwise around the second rotation axis O2. Further, the power of torque Tb is transmitted from the barrel complete 11 to the second control wheel 56. Hereinafter, the torque Tb is referred to as the rotational torque Tb of the barrel complete 11. When the mainspring 16 in the barrel complete 11 is wound with a predetermined winding amount, the rotational torque Tb is set to be larger than the rotational torque Tc of the constant torque spring 27.

  As shown in FIGS. 5, 7, and 8, the second control gear 62 includes a plurality of arm portions 62 b that are spaced in the circumferential direction around the second rotation axis O <b> 2 and an outer end portion of the arm portion 62 b. A ring-shaped gear body 62c coupled to the arm portion 62b, and a support plate 62d formed integrally with the arm portion 62b.

The second control teeth 62a are formed on the outer peripheral surface of the gear body 62c over the entire circumference. As a result, a rotational torque Tc that rotates clockwise is transmitted to the second control wheel 56 from the second power wheel 26 that rotates counterclockwise.
At this time, the rotational torque Tb that is larger than the rotational torque Tc and opposite to the rotational torque Tc is transmitted to the second control wheel 56 via the power source side wheel train 12 as described above. Therefore, the second control wheel 56 is prevented from rotating clockwise.

  However, when the mainspring 16 in the barrel complete 11 is unwound or the like, so that the rotational torque Tb of the barrel complete becomes smaller than the rotational torque Tc of the constant torque spring 27, or by the power adjustment mechanism 110 described later. When the 2-torque adjustment gear 111 is forcibly rotated counterclockwise, the second control wheel 56 can be rotated clockwise.

  As shown in FIGS. 3 and 5, the first control wheel 55 includes a rotary cylinder 70 disposed coaxially with the second rotation axis O <b> 2, and a first control gear 71 integrally connected to the rotary cylinder 70. It is equipped with.

  A shaft portion 60 of the second control wheel 56 is inserted into the rotary cylinder 70 from below and protrudes above the rotary cylinder 70. A cobblestone 72 similar to the cobblestone 42 is press-fitted inside the upper end portion and the lower end portion of the rotary cylinder 70. The shaft portion 60 of the second control wheel 56 passes through the inside of these hole stones 72. As a result, the first control wheel 55 and the second control wheel 56 are combined so as to be relatively rotatable around the second rotation axis O2 with little backlash.

The first control gear 71 includes a plurality of arm portions 71a that are spaced circumferentially around the second rotation axis O2, and a ring gear body 71b that is coupled to the outer end of the arm portion 71a. ing.
In the illustrated example, three arm parts 71a are formed. Of these, the two arm portions 71a are formed with an interval of 180 degrees about the second rotation axis O2. As a result, an opening space 73 that is greatly opened in the circumferential direction is secured between the arm portions 71a that are arranged with an interval of 180 degrees around the second rotation axis O2.
However, the number, arrangement, and shape of the arm portions 71a are not limited to this case, and may be freely changed.

On the outer peripheral surface of the gear body 71b, first control teeth 71c that mesh with the first power teeth 41c in the first power vehicle 25 are formed over the entire circumference. Thereby, the first control wheel 55 rotates around the second rotation axis O2 in the counterclockwise direction based on the rotation of the first power wheel 25.
The first control gear 71 is formed to have the same diameter as the second control gear 62. However, the present invention is not limited to this case, and the first control gear 71 and the second control gear 62 may be formed with different diameters.

  The planetary mechanism 57 is provided on the first control wheel 55 side, and an engagement claw stone (engagement claw according to the present invention) 80 that rotates around the second rotation axis O2 as the first control wheel 55 rotates. A stop wheel 81 which is a planetary gear provided on the second control wheel 56 side and revolves around the second rotation axis O2 while rotating along with the rotation of the second control wheel 56, and for rotating and revolving the stop wheel 81. The engaging wheel 80 and the stop wheel 81 are intermittently engaged and disengaged based on the rotation of the first control wheel 55.

The engaging claw stone 80 is formed of an artificial gem such as ruby, for example, and is attached to a support lever 85 that rotates around the second rotation axis O2 as the first control wheel 55 rotates.
Note that the engaging claw stone 80 is not limited to the case of being formed of artificial gemstones like the hole stones 42 and 72, and may be formed of other brittle materials or metal materials such as iron-based alloys. Absent.
Further, the engaging claw stone 80 may be formed integrally with the support lever 85 instead of being separated from the support lever 85.

As shown in FIGS. 5, 8, 10, and 11, the support lever 85 is integrally connected to a portion of the rotary cylinder 70 in the first control wheel 55 that is positioned below the first control gear 71. ing.
The support lever 85 includes a first lever piece 86 and a second lever piece 87 extending along the radial direction of the first control wheel 55 from the rotary cylinder 70 toward the gear body 71b. The first lever piece 86 and the second lever piece 87 are arranged at a constant interval in the circumferential direction, and are arranged so as to fit inside the opening space 73 in plan view.

  In the illustrated example, the first lever piece 86 and the second lever piece 87 are formed to have the same shape and the same size. However, the present invention is not limited to this case, and the first lever piece 86 and the second lever piece 87 may be formed in different shapes and sizes.

  The stop wheel 81 is disposed between the first lever piece 86 and the second lever piece 87. The first lever piece 86 is disposed on the counterclockwise side with respect to the stop wheel 81, and the second lever piece 87 is disposed on the clockwise side with respect to the stop wheel 81.

  As shown in FIG. 11, a clawstone holding portion 88 opened toward the stop wheel 81 side is provided on the outer end side of the first lever piece 86. The clawstone holding part 88 holds the engaging clawstone 80 using this opening. The engaging claw stone 80 is held in a state protruding from the claw stone holding portion 88 to the stop wheel 81 side. Of the protruding portion of the engaging claw stone 80, the side surface facing inward in the radial direction is an engaging surface 80a in which a later-described action surface 95a of the stop wheel 81 can be engaged and disengaged. In the illustrated example, the engaging surface 80a is a flat surface formed flat over the entire surface.

  As shown in FIGS. 8, 10 and 12, the stop wheel 81 is provided between the first lever piece 86 and the second lever piece 87, and the support plate 62d in the second control wheel 56 and the support plate 62d. It is pivotally supported between the support member 90 and the fixed support member 90.

The support member 90 includes a lower plate 91 fixed on the support plate 62d, and an upper plate 92 that rises upward from the lower plate 91 and protrudes above the stop wheel 81. In the illustrated example, the lower plate 91 is fixed by fastening means such as a fixing pin and a fixing screw, but is not limited to this case.
The support plate 62d and the upper plate 92 are each provided with a hole stone 93 made of an artificial gem such as ruby so as to face each other vertically. The hole stone 93 may also be formed of other brittle materials or metal materials such as iron-based alloys.

The stop wheel 81 is disposed between the support plate 62d and the upper plate 92, is pivotally supported by a hole stone 93 formed in the support plate 62d and the upper plate 92, and can rotate about the fifth rotation axis O5. It is said that.
The stop wheel 81 includes a stop gear 96 having a plurality of stop teeth 95 that can be engaged with and disengaged from the engagement surface 80 a of the engagement stone 80, and a stop that is formed below the stop gear 96 and meshes with the fixed gear 82. Kana 97.

  As shown in FIGS. 5 and 10, the fixed gear 82 is disposed between the first control wheel 55 and the second control wheel 56, and is a ring-shaped gear body 100 disposed coaxially with the second rotation axis O2. And a fixed arm 101 formed integrally with the gear body 100 and fixed to a fixed component (not shown). In the illustrated example, the gear body 100 is formed to have a diameter slightly smaller than that of the first control gear 71 and the second control gear 62, and a fixed tooth 100a is formed in which the stop pinion 97 is engaged with the entire circumference of the inner peripheral surface. Has been. Therefore, the fixed gear 82 of this embodiment is an internal tooth type.

  Since the fixed gear 82 is an internal tooth type, as shown in FIG. 11, the stop wheel 81 rotates around the fifth rotation axis O5 in the clockwise direction as the second control wheel 56 rotates counterclockwise. However, it revolves around the second rotation axis O2 in the counterclockwise direction. As shown in FIG. 10, the stop gear 96 is disposed above the fixed gear 82 and can rotate (rotate and revolve) without contacting the fixed gear 82 and the support member 90. .

  As shown in FIG. 11, the number of teeth of the stop teeth 95 is 12. However, the present invention is not limited to this case, and the number of teeth may be changed as appropriate. Of the stop teeth 95, the side surface facing in the clockwise direction is an action surface 95a that engages with and disengages from the engagement surface 80a of the engagement stone 80. The rotation locus M drawn by the tip of the stop tooth 95 as the stop wheel 81 rotates is referred to as the rotation locus M of the stop gear 96.

  The engaging claw stone 80 and the stop wheel 81 configured as described above are in a relationship of intermittent engagement / disengagement based on the rotation of the first control wheel 55. This point will be described in detail.

  By the rotation and revolution of the stop wheel 81, the action surface 95 a of the stop tooth 95 is engaged with the engagement surface 80 a of the engagement stone 80. After this engagement, the support lever 85 and the engaging claw stone 80 rotate counterclockwise around the second rotation axis O2 as the first control wheel 55 rotates counterclockwise. It gradually leaves (that is, gradually retracts from the rotation locus M).

Therefore, at the initial stage of engagement as shown in FIG. 13, the working surface 95a of the stop tooth 95 is deeply engaged with the engagement stone 80, and then the engagement stone 80 is disengaged as shown in FIG. Accordingly, the action surface 95a of the stop tooth 95 moves to the toe side of the engaging claw stone 80 while sliding on the engaging surface 80a. Thereby, the engagement between the stop tooth 95 and the engaging claw stone 80 gradually becomes shallower. Then, as shown in FIG. 15, the engagement is released when the action surface 95 a of the stop tooth 95 exceeds the toe of the engaging claw stone 80.
13 to 15, the illustration of the support lever 85 is simplified, and the illustration of the second lever piece 87 is omitted.

  When the engagement between the stop tooth 95 and the engaging pawl 80 is released, the first control wheel 55 and the second control wheel 56 via the engaging pawl 80 and the stop wheel 81 as shown in FIG. Therefore, the second control wheel 56 can be rotated counterclockwise around the second rotation axis O2. Therefore, the stop wheel 81 rotates counterclockwise around the second rotation axis O2 so as to follow the engagement stone 80 while rotating clockwise around the fifth rotation axis O5 as the second control wheel 56 rotates. Rotate to. Thereby, the action surface 95a of the next stop tooth 95 can be engaged with the engagement surface 80a of the engagement stone 80.

  By repeating the above-described operation, the engaging claw stone 80 and the stop wheel 81 can be intermittently engaged / disengaged. The stop teeth 95 are engaged with the engaging claw stone 80 one by one.

  By the way, the support lever 85 is disengaged as shown in FIGS. 14 and 15 after the action surface 95a of the stop tooth 95 is engaged with the engagement surface 80a of the engaging claw stone 80 as shown in FIG. Until the stop tooth 95 presses the engagement surface 80a and the frictional force F2 generated by the stop tooth 95 sliding on the engagement surface 80a along the resultant force F3. The engaging stone 80 is held so that the virtual line L passes through the second rotation axis O2.

  In the present embodiment, the engagement position P1 shown in FIG. 13 where the stop tooth 95 is engaged with the engagement surface 80a and the disengagement position P2 shown in FIG. 15 where the stop tooth 95 is disengaged from the engagement surface 80a. The imaginary line L is configured to pass through the second rotation axis O2 at an intermediate position P3 shown in FIG.

As described above, when the mainspring 16 in the barrel complete 11 is unwound, etc., the rotational torque Tb of the barrel complete becomes smaller than the rotational torque Tc of the constant torque spring 27, or will be described later. When the second torque adjustment gear 111 is forcibly rotated counterclockwise by the power adjustment mechanism 110, the second control wheel 56 rotates clockwise.
In this case, as the second control wheel 56 rotates, the upper plate 92 of the support member 90 moves toward the second lever piece 87 of the support lever 85, and then the second lever piece as shown in FIG. The upper plate 92 comes into contact with the 87. Accordingly, it is possible to restrict the second control wheel 56 from rotating further clockwise by using the second lever piece 87.

(Configuration of power adjustment mechanism)
The constant torque mechanism 20 of the present embodiment is a power that adjusts the power of the constant torque spring 27 via the first power vehicle 25 or the second power vehicle 26 as shown in FIGS. 3, 4, 18 and 19. An adjustment mechanism 110 is further provided.
In the present embodiment, the case where the power of the constant torque spring 27 is adjusted via the second power vehicle 26 will be described as an example. However, the present invention is not limited to this case, and the power of the constant torque spring 27 may be adjusted via the first power wheel 25 as described above.

  The power adjustment mechanism 110 includes a second torque adjustment gear 111 (the adjustment wheel according to the present invention) that can mesh with the first torque adjustment gear 33 in the second power vehicle 26, the second torque adjustment gear 111, Between the meshing position P4 (see FIG. 19) where the first torque adjusting gear 33 meshes and the release position P5 (see FIG. 19) where the meshing between the second torque adjusting gear 111 and the first torque adjusting gear 33 is released. And a rocking lever (moving member according to the present invention) 113 for moving the second torque adjusting gear 111.

The swing lever 113 is disposed between the main plate 115 and the torque adjustment receiver 116 and can swing about a swing pin 117 fixed to the main plate 115. At one end of the swing lever 113, a fork portion 118 divided into two forks is formed.
An eccentric pin 119 that is rotatably attached to the main plate 115 is disposed inside the fork portion 118. The inner peripheral surface of the fork part 118 and the outer peripheral surface of the eccentric pin 119 are slidably in contact with each other.

  The eccentric pin 119 is exposed to the outside of the torque adjustment receiver 116, and, for example, a minus groove 119a is formed at the upper end portion thereof. Thereby, for example, the eccentric pin 119 can be arbitrarily rotated using the minus groove 119a by a driver or the like. However, the present invention is not limited to the minus groove 119a, and any means that can arbitrarily rotate the eccentric pin 119 may be formed at the upper end portion of the eccentric pin 119.

  By rotating the eccentric pin 119 described above, the swing lever 113 can be swung around the swing pin 117 as shown in FIG. 19, and the other end of the swing lever 113 is adjusted to the first torque. The gear 33 can be approached or separated.

  As shown in FIGS. 7, 18, and 19, the second torque adjusting gear 111 is rotatably attached to a guide pin 112 having a lower end portion fixed to the other end portion of the swing lever 113. On the outer peripheral surface of the second torque adjusting gear 111, a second torque adjusting tooth 111a capable of meshing with the first torque adjusting tooth 33a is formed over the entire circumference.

Since the second torque adjustment gear 111 is disposed at the other end of the swing lever 113 via the guide pin 112, the second torque adjustment gear 111 can be moved by swinging the swing lever 113. it can. The position at which the other end of the swing lever 113 is closest to the first torque adjusting gear 33 is the meshing position P4, and the first torque adjusting tooth 33a and the second torque adjusting tooth 111a are engaged. Can do.
On the other hand, the position where the other end portion of the swing lever 113 is farthest from the first torque adjustment gear 33 is the release position P5, and the first torque adjustment tooth 33a and the second torque adjustment tooth 111a The mesh can be released.

  As shown in FIG. 4, the upper end portion of the guide pin 112 is inserted into the swing groove 120 formed in the torque adjustment receiver 116 so as to be movable along the swing groove 120. The swing groove 120 is formed to extend along the swing direction of the other end of the swing lever 113. As a result, the second torque adjusting gear 111 is stably supported with little wobbling through the guide pin 112, and moves between the meshing position P4 and the release position P5 as the swing lever 113 swings.

As shown in FIGS. 7, 18, and 19, an operation wheel 121 that rotates the second torque adjustment gear 111 is disposed between the second torque adjustment gear 111 and the swing pin 117.
The operation wheel 121 has an operation gear 122 in which operation teeth 122a meshing with the second torque adjustment teeth 111a are formed over the entire outer peripheral surface, and is supported between the main plate 115 and the torque adjustment receiver 116. Yes.

The operation wheel 121 is arranged so as to penetrate up and down through a through hole 123 formed in the swing lever 113. The through hole 123 is formed so as to extend along the swing direction of the swing lever 113.
Thereby, the operation wheel 121 is pivotally supported between the main plate 115 and the torque adjustment receiver 116 without being influenced by the swing of the swing lever 113. The operation tooth 122a of the operation wheel 121 is always meshed with the second torque adjustment tooth 111a regardless of the position of the second torque adjustment gear 111.

  As shown in FIG. 4, the upper end portion of the operation wheel 121 is exposed on the upper surface side of the torque adjustment receiver 116, and can be rotated from the outside. In the illustrated example, a minus groove 121a is formed at the upper end portion of the operation wheel 121, and the operation wheel 121 can be arbitrarily rotated using the minus groove 121a by, for example, a driver. However, the present invention is not limited to the minus groove 121a, and any means that can arbitrarily rotate the operation wheel 121 may be formed at the upper end portion of the operation wheel 121.

Since the power adjustment mechanism 110 is configured as described above, as shown in FIG. 19, the second torque adjustment gear 111 is moved to the meshing position P4, and then the operation wheel 121 is rotated, whereby the second The first torque adjusting gear 33 can be rotated via the torque adjusting gear 111, and the constant torque spring 27 can be wound or unwound to arbitrarily adjust the power of the constant torque spring 27.
This adjustment will be described later in detail.

(Operation of constant torque mechanism)
The operation of the constant torque mechanism 20 configured as described above will be described.
As an initial state, the mainspring 16 in the barrel complete 11 is wound up with a predetermined winding amount, and the power of the rotational torque Tb is transmitted from the barrel complete 11 to the second control wheel 56 via the power source side train 12. It shall be. The constant torque spring 27 is wound up by a predetermined winding amount, and the power of the rotational torque Tc smaller than the rotational torque Tb is transmitted from the constant torque spring 27 to the first power vehicle 25 and the second power vehicle 26. And Furthermore, it is assumed that the second torque adjustment gear 111 is located at the release position P5 and the meshing between the first torque adjustment gear 33 and the second torque adjustment gear 111 in the second power vehicle 26 is disengaged.

Since the constant torque mechanism 20 of the present embodiment has the constant torque spring 27 as shown in FIGS. 2 to 4, the power stored in the constant torque spring 27 is transmitted to the first power vehicle 25. The first power wheel 25 can be rotated clockwise around the first rotation axis O1. Thereby, the power of the constant torque spring 27 can be transmitted from the first power wheel 25 to the fourth wheel 19 and the fourth wheel 19 is rotated around the fourth rotation axis O4 as the first power wheel 25 rotates. be able to.
That is, as indicated by an arrow R1 shown in FIG. 2, the power from the constant torque spring 27 can be transmitted to the escapement side wheel train 15 via the first power vehicle 25, and the escapement 14 can be operated. it can.

Further, since the power from the constant torque spring 27 is also transmitted to the second power vehicle 26, the second power vehicle 26 is rotated counterclockwise around the first rotation axis O1 by the rotational torque Tc.
Specifically, the power from the constant torque spring 27 is transmitted to the shaft portion 30 and the connecting gear 31 via the fixing ring 45. Further, the power transmitted to the connection gear 31 is transmitted to the second power gear 35 via the torque adjustment jumper 34 and then to the second control gear 62 of the second control wheel 56. As a result, power that rotates clockwise around the second rotation axis O <b> 2 with the rotational torque Tc is transmitted from the constant torque spring 27 to the second control wheel 56.

  However, a rotational torque Tb (torque larger than the rotational torque Tc) that rotates counterclockwise around the second rotational axis O2 is transmitted from the power source side train wheel 12 to the second control wheel 56. Therefore, the second control wheel 56 is prevented from rotating clockwise.

  The second control wheel 56 has a power difference between the rotational torque Tb transmitted from the power source side wheel train 12 and the rotational torque Tc transmitted from the constant torque spring 27 (rotational torque Tb−rotational torque Tc). Works. However, since the stop wheel 81 and the engaging claw stone 80 are engaged, the second control wheel 56 and the first control wheel 55 can be linked by this engagement, and the second control wheel 56 It is prevented from rotating counterclockwise around the two rotation axis O2.

From the above, at the stage where the stop wheel 81 and the engaging claw stone 80 are engaged, the second control wheel 56 is prevented from rotating around the second rotation axis O2. Therefore, the second power vehicle 26 is also prevented from rotating around the first rotation axis O1.
In addition, since the power of the difference mentioned above acts on the 2nd control wheel 56, the action surface 95a of the stop tooth | gear 95 of the stop wheel 81 pressed against the engagement surface 80a of the engagement claw stone 80 strongly. Engage with.

  Further, when the first power wheel 25 is rotated by the power from the constant torque spring 27, the first control wheel 55 is rotated counterclockwise around the second rotation axis O2. When the first control wheel 55 is rotated, the support lever 85 is rotated counterclockwise around the second rotation axis O2, so that the engaging claw stone 80 is retracted from the rotation locus M of the stop gear 96. The stop gear 96 can be gradually detached.

  Accordingly, as shown in FIG. 14 from the state shown in FIG. 13, the action surface 95a of the stop tooth 95 slides on the engagement surface 80a as the engagement stone 80 is disengaged. Move to the toe side. Then, as shown in FIG. 15, when the action surface 95 a of the stop tooth 95 exceeds the toe of the engagement stone 80, the engagement between the stop tooth 95 and the engagement stone 80 is released. As a result, the linkage between the first control wheel 55 and the second control wheel 56 via the engaging claw stone 80 and the stop wheel 81 is released.

  Therefore, the second control wheel 56 uses the difference power between the rotational torque Tb transmitted from the power source side wheel train 12 and the rotational torque Tc transmitted from the constant torque spring 27 (rotational torque Tb−rotational torque Tc). As shown in FIG. 16, it rotates around the second rotation axis O2 in the counterclockwise direction.

As the second control wheel 56 rotates, the second power gear 35 can be rotated clockwise around the first rotation axis O1. As shown in FIG. 6, the second power gear 35 is linked to the connection gear 31 through the engagement of the torque adjustment jumper 34 and the connection teeth 32, and thus the connection teeth 32 are rotated by rotating clockwise. The first engagement surface 32a moves relatively toward the tip end 34b side of the torque adjustment jumper 34 and tries to get over the tip end 34b.
However, the power acting on the second power gear 35 is the difference power (rotation) between the rotational torque Tb transmitted from the power source side train wheel 12 and the rotational torque Tc transmitted from the constant torque spring 27 as described above. Torque Tb−rotational torque Tc), which is smaller than the jumper torque Tj of the torque adjustment jumper 34. Accordingly, the engagement state between the tip end portion 34b of the torque adjustment jumper 34 and the first engagement surface 32a of the connecting tooth 32 can be maintained.

As a result, the power transmitted to the second power gear 35 can be transmitted to the connecting gear 31 via the torque adjustment jumper 34. Thereby, the connection gear 31 and the shaft part 30 can be rotated clockwise around the first rotation axis O1.
Accordingly, the constant torque spring 27 can be wound up via the fixing ring 45 fixed to the shaft portion 30, and power can be supplemented to the constant torque spring 27. That is, the loss of power lost by transmitting power to the first power vehicle 25 is replenished by using the power transmitted from the barrel wheel 11 as the power source, as shown by the arrow R2 shown in FIG. can do. Thereby, the power of the constant torque spring 27 can be maintained constant, and the escapement 14 can be operated with a constant torque.

  Even when power is replenished to the constant torque spring 27, the first power wheel 25 is rotated by the power from the constant torque spring 27, and the escapement side wheel train 15 is moved from the constant torque spring 27 to the escapement side wheel train 15. The power of

In addition, when the above-described constant torque spring 27 is replenished with power, as shown in FIG. 16, the stop wheel 81 rotates around the fifth rotation axis O5 in the clockwise direction as the second control wheel 56 rotates. Rotating around the second rotation axis O2, revolving counterclockwise and following the engaging claw stone 80. Then, the stop wheel 81 rotates by one tooth of the stop tooth 95 to catch up with the engagement stone 80, and the action surface 95a of the stop tooth 95 is engaged again with the engagement surface 80a of the engagement tooth 80.
As a result, the first control wheel 55 and the second control wheel 56 are linked again, so that the rotation of the second control wheel 56 and the second power wheel 26 is prevented, and the replenishment of power to the constant torque spring 27 is completed. .

  By repeating the above, engagement / disengagement of the stop wheel 81 and the engaging claw stone 80 can be performed intermittently. That is, the planetary mechanism 57 intermittently engages and disengages the stop wheel 81 and the engaging claw stone 80 based on the rotation of the first power wheel 25 and the first control wheel 55, The second power vehicle 26 can be intermittently rotated. Thereby, the power to the constant torque spring 27 can be supplemented intermittently.

  As described above, according to the constant torque mechanism 20 of the present embodiment, the escapement 14 can be operated using the power stored in the constant torque spring 27, and the constant torque spring is intermittently used. 27, the power transmitted from the barrel complete 11 can be supplemented. Therefore, the power of the constant torque spring 27 can be maintained constant, the constant torque characteristic can be maintained, and the escapement 14 can be operated in a state where torque fluctuation is suppressed.

Further, in the constant torque mechanism 20 of this embodiment, since the periodic control is performed using the planetary mechanism 57, a so-called over-release phenomenon may occur in the constant torque spring 27, unlike the conventional cam type. There is no.
Further, as shown in FIGS. 3 and 4, since the torque generating mechanism 21 and the cycle control mechanism 22 are arranged so as to be shifted in a plane, the overall thickness of the constant torque mechanism 20 is suppressed as compared with the conventional planetary vehicle system. can do. In addition, a constant torque spring 27 is disposed between the first power wheel 25 and the second power wheel 26, and a planetary mechanism 57 is disposed between the first control wheel 55 and the second control wheel 56. Therefore, the planar spread can be suppressed, and the constant torque mechanism 20 can be arranged in a small plane space as compared with the conventional planetary vehicle system.

  Accordingly, the constant torque mechanism 20 can be made compact and space-saving in both the planar direction and the thickness direction of the timepiece 1, and the movement 10 and the timepiece that can be easily reduced in size and thickness. 1 can be used.

  Further, in the constant torque mechanism 20 according to the present embodiment, the support lever 85 is engaged with the engagement surface 80a of the engagement claw stone 80 after the action surface 95a of the stop tooth 95 is engaged as shown in FIG. Until the engagement is released, the pressing force F1 that the stop tooth 95 presses the engagement surface 80a, and the frictional force F2 that is generated when the stop tooth 95 slides on the engagement surface 80a. The engaging claw stone 80 is held so that the virtual line L along the resultant force F3 passes through the second rotation axis O2.

  Accordingly, when one cycle is from the engagement of the stop tooth 95 and the engagement stone 80 to the release of the engagement, the rotational torque generated in the support lever 85 is reduced as shown in FIG. When attention is paid, the average torque in one cycle can be kept constant.

  As described above, in the initial stage of engagement as shown in FIG. 13, the working surface 95a of the stop tooth 95 is deeply engaged with the engaging claw stone 80, and thereafter, as shown in FIG. With the separation of the stone 80, the action surface 95a of the stop tooth 95 moves to the toe side of the engaging claw stone 80 while sliding on the engaging surface 80a. Then, as shown in FIG. 15, the engagement is released when the action surface 95 a of the stop tooth 95 exceeds the toe of the engaging claw stone 80. In this series of one cycle, the angle of the engagement surface 80a with respect to the stop tooth 95 slightly changes, and accordingly, the direction of the resultant force F3 changes.

At this time, when the direction along the resultant force F3 passes through the second rotation axis O2 as shown in FIG. 14, the rotational torque generated in the support lever 85 is not generated. On the other hand, when the direction along the resultant force F3 deviates from the second rotation axis O2 as shown in FIGS. 13 and 15, rotational torque is generated according to the deviation amount.
In particular, a reverse rotational torque is generated before and after the direction along the resultant force F3 passes through the second rotation axis O2. That is, a rotation torque T that pulls the support lever 85 toward the stop wheel 81 as shown in FIG. 13 is generated in the support lever 85, and a rotation that pulls the support lever 85 away from the stop wheel 81 as shown in FIG. Torque T is generated at the support lever 85.

Accordingly, as shown in FIG. 20, although the torque of the support lever 85 varies when viewed in one cycle, the average torque in one cycle can be made constant. As a result, constant torque characteristics can be ensured.
Moreover, in the present embodiment, the engagement position P1 shown in FIG. 13 where the stop teeth 95 are engaged with the engagement surface 80a, and the disengagement position P2 shown in FIG. 15 where the stop teeth 95 are disengaged from the engagement surface 80a. The imaginary line L is configured to pass through the second rotation axis O2 at an intermediate position P3 shown in FIG. Thereby, the average torque in one cycle mentioned above can be maintained more stably and constant, and the constant torque property can be secured more stably.

  Furthermore, as shown in FIG. 19, the constant torque mechanism 20 of the present embodiment includes a power adjustment mechanism 110, so that the power of the constant torque spring 27 can be adjusted as necessary.

For example, the case where the constant torque spring 27 is wound up to increase the power will be described.
In this case, first, the eccentric pin 119 is rotated to swing the swing lever 113 around the swing pin 117, and the second torque adjusting gear 111 is moved from the release position P5 to the meshing position P4. Thereby, the 1st torque adjustment tooth 33a of the 1st torque adjustment gear 33 and the 2nd torque adjustment tooth 111a of the 2nd torque adjustment gear 111 can be meshed | engaged.

  Next, the operation wheel 121 is rotated clockwise. At this time, the operation wheel 121 is rotated with an input torque higher than the torque obtained by adding the rotational torque Tc of the constant torque spring 27 and the jumper torque Tk of the torque adjustment jumper 34. As a result, the second torque adjusting gear 111 can be rotated counterclockwise, and power that rotates around the first rotation axis O1 in the clockwise direction is transmitted via the second torque adjusting gear 111 to the first torque. This can be transmitted to the adjustment gear 33.

Since the first torque adjusting gear 33 is integrally combined with the connecting gear 31, power that rotates clockwise around the first rotation axis O <b> 1 is transmitted to the connecting gear 31. At this time, since the power transmitted to the connection gear 31 is the input torque, the connection gear 31 shown in FIG. 6 rotates in the clockwise direction relative to the second power gear 35. That is, the engagement between the tip end portion 34b of the torque adjustment jumper 34 and the second engagement surface 32b of the connection tooth 32 can be released, and the connection gear 31 is moved clockwise while releasing the rotation restriction by the torque adjustment jumper 34. Can be rotated.
In addition, the connection tooth 32 moves while getting over the tip part 34b of the torque adjustment jumper 34 one after another in the circumferential direction as the connection gear 31 rotates.

  Since the connecting gear 31 can be rotated in this way, the fixing ring 45 fixed to the shaft portion 30 can be rotated clockwise, and the inner end portion 27a of the constant torque spring 27 can be rotated clockwise. Can do. As a result, the constant torque spring 27 can be wound up, and the preload of the constant torque spring 27 can be increased to adjust the rotational torque Tc to increase.

  During the adjustment described above, the second power gear 35 does not rotate, but the second power gear 35 is transmitted with power that rotates the second power gear 35 in the clockwise direction. The power at this time is a rotational torque greater than the jumper torque Tk. This power is transmitted to the second control wheel 56, and acts to rotate the second control wheel 56 counterclockwise around the second rotation axis O2. At this time, as described above, power is transmitted to the second control wheel 56 from the power source side train wheel 12 so as to rotate counterclockwise around the second rotation axis O2 with the rotational torque Tb.

  Accordingly, the second control wheel 56 is subjected to power obtained by adding the power transmitted from the second power gear 35 and the power transmitted from the power source side wheel train 12. As a result, the operating surface 95a of the stop tooth 95 of the stop wheel 81 is engaged with the engaging surface 80a of the engaging claw stone 80 more strongly. Thereby, it is possible to appropriately prevent the second power gear 35 from rotating, and the constant torque spring 27 can be quickly wound up with good response.

Next, the case where the constant torque spring 27 is unwound to reduce the power will be described.
In this case, the operation wheel 121 shown in FIG. 19 is rotated counterclockwise. At this time, the operation wheel 121 is rotated with an input torque smaller than the difference (Tj−Tc) between the jumper torque Tj of the torque adjustment jumper 34 and the rotational torque Tc of the constant torque spring 27.
As a result, the second torque adjusting gear 111 can be rotated in the clockwise direction, and power that rotates counterclockwise around the first rotation axis O <b> 1 is transmitted via the second torque adjusting gear 111 to the first torque. This can be transmitted to the adjustment gear 33.

  As a result, power that rotates counterclockwise around the first rotation axis O <b> 1 is transmitted to the connecting gear 31. At this time, since the power transmitted to the connection gear 31 is the input torque, the engagement between the tip end portion 34b of the torque adjustment jumper 34 and the first engagement surface 32a of the connection tooth 32 shown in FIG. The connecting gear 31 and the second power gear 35 can be rotated together in the counterclockwise direction.

As a result, the second control wheel 56 rotates clockwise around the second rotation axis O2. For this reason, as the second control wheel 56 rotates, the upper plate 92 of the support member 90 moves toward the second lever piece 87 of the support lever 85 and then moves relative to the second lever piece 87 as shown in FIG. The upper plate 92 comes into contact.
Accordingly, it is possible to restrict the second control wheel 56 from rotating further clockwise by using the second lever piece 87.

Next, after restricting the rotation of the second control wheel 56 in the clockwise direction as described above, the operation wheel 121 is further subjected to a difference between the jumper torque Tj of the torque adjustment jumper 34 and the rotation torque Tc of the constant torque spring 27 ( Rotate counterclockwise with an input torque greater than Tj-Tc). At this time, since the rotation of the second control wheel 56 and the second power wheel 26 is restricted, the connecting gear 31 shown in FIG. 6 rotates counterclockwise relative to the second power gear 35. That is, the engagement between the tip end portion 34b of the torque adjustment jumper 34 and the first engagement surface 32a of the connection tooth 32 can be released, and the connection gear 31 is rotated counterclockwise while releasing the rotation restriction by the torque adjustment jumper 34. Can be rotated.
In addition, the connection tooth 32 moves while getting over the tip part 34b of the torque adjustment jumper 34 one after another in the circumferential direction as the connection gear 31 rotates.

  Since the connecting gear 31 can be rotated as described above, the fixing ring 45 fixed to the shaft portion 30 can be rotated counterclockwise, and the inner end portion 27a of the constant torque spring 27 can be rotated counterclockwise. Can rotate. As a result, the constant torque spring 27 can be unwound, and the preload of the constant torque spring 27 can be reduced and adjusted so that the rotational torque Tc decreases.

  Note that the present invention is not limited to the adjustment of power. For example, when the mainspring 16 in the barrel complete 11 is unwound, the rotational torque Tb of the barrel complete 11 becomes smaller than the rotational torque Tc of the constant torque spring 27. Even if it exists, since the excessive rotation to the clockwise direction of the 2nd control wheel 56 can be controlled similarly to the above-mentioned case, it can prevent that constant torque spring 27 will completely open.

As described above, since the power adjustment mechanism 110 is provided, the power of the constant torque spring 27 can be adjusted as necessary, and the escapement 14 can be operated with a constant torque more stably. In addition, since the power can be applied to the constant torque spring 27 after the torque generating mechanism 21 to be described later is assembled, the assemblability can be improved. Furthermore, since the second power wheel 26 is disposed at a position that is shifted in a plane from the cycle control mechanism 22, the power adjustment mechanism 110 can be provided without worrying about the cycle control mechanism 22. 110 is easy to install.
In addition, since the power of the constant torque spring 27 can be adjusted by the rotation of the second torque adjustment gear 111 via the operation wheel 121, the adjustment can be performed finely and intuitively, and the adjustment work can be easily performed. Furthermore, by placing the second torque adjustment gear 111 at the release position P5, it is possible to prevent an excessive rotational load from being applied to the second power vehicle 26 when power adjustment is not performed.

Furthermore, according to the constant torque mechanism 20 of the present embodiment, since the torque generating mechanism 21 is provided, the following effects can be further achieved.
That is, as shown in FIGS. 3 and 4, the defining portion 47 provided at the outer end portion 27 b of the constant torque spring 27 is detachably engaged with the slide hole 46 provided in the first power vehicle 25. Therefore, the constant torque spring 27 and the first power vehicle 25 can be easily disassembled by a simple operation that only removes the defining portion 47 from the slide hole 46.
Therefore, maintainability of the torque generation mechanism 21 can be improved, and overhaul and the like can be easily performed. Further, since the constant torque spring 27 and the first power vehicle 25 can be easily disassembled, maintenance work such as lubrication can be easily performed.

  Further, when assembling the torque generating mechanism 21, the constant torque spring 27, the first power vehicle 25, and the second power vehicle 26 are combined together simply by engaging the defining portion 47 in the slide hole 46. In addition, the radial position of the outer end portion 27b of the constant torque spring 27 can be defined and appropriately positioned.

Specifically, as shown in FIG. 21, the first power vehicle 25 is set above the second power vehicle 26 combined with the constant torque spring 27. At this stage, the constant torque spring 27 is not elastically deformed. Next, as shown in FIG. 22, the first power vehicle 25 and the second power vehicle 26 are overlapped so that the defining portion 47 is positioned at the opening portion of the slide hole 46. Next, as shown in FIG. 23, the first power wheel 25 and the second power wheel 26 are rotated in the opposite directions around the first rotation axis O1 so that the defining portion 47 enters the slide hole 46. . Thereby, the defining portion 47 can be easily entered into the slide hole 46 by sliding movement, and the defining portion 47 can be engaged with the inside of the slide hole 46 as shown in FIGS.
Accordingly, the first power wheel 25, the second power wheel 26, and the constant torque spring 27 can be assembled together, and the radial position of the outer end portion 27b of the constant torque spring 27 can be defined and positioned. .

  Next, while the outer end portion 27b of the constant torque spring 27 is positioned, the first power wheel 25 and the second power wheel 26 are further rotated in the relatively opposite directions around the first rotation axis O1. The torque spring 27 can be wound up to give a preload to the constant torque spring 27 and power can be stored. In this case, for example, the constant torque spring 27 may be wound up by the power adjustment mechanism 110 described above.

From the above, the torque generating mechanism 21 can be easily assembled, and the assembly workability can be improved.
In addition, when the constant torque spring 27 is wound up, the regulating lever 48 provided at the outer end portion 27b of the constant torque spring 27 can be brought into contact with the rotating cylinder 40 of the first power wheel 25, so that the constant torque spring It is possible to restrict the rotation of the outer end portion 27b around the first rotation axis O1 by the rotational torque accompanying the elastic restoring deformation of 27. Thereby, the constant torque spring 27 can be wound up while preventing the spring portions of the constant torque spring 27 from contacting each other.

  Therefore, it is possible to prevent a torque difference (hysteresis) from occurring when the constant torque spring 27 is wound up and when the power is released. In addition, when the constant torque spring 27 is wound up, the regulating lever 48 gradually and strongly abuts on the rotating cylinder 40 as the constant torque spring 27 is wound up, so that the winding amount of the constant torque spring 27, that is, the preload can be easily made constant.

  Further, when the power stored in the constant torque spring 27 decreases for some reason, that is, when the preload decreases, the defining portion 47 is detached from the slide hole 46 and the defining portion 47 is moved to the slide hole 46. It can be separated from the inside. As a result, a change in the relative positional relationship between the slide hole 46 and the defining portion 47 can be quickly grasped by visual recognition, and the power stored in the constant torque spring 27 has decreased, for example, the winding amount. It is possible to easily and surely grasp that it has become zero.

  As described above, maintenance performance, maintenance workability, and assembly workability are improved, and the torque generating mechanism 21 having excellent handleability can be obtained. Accordingly, the useful constant torque mechanism 20, the movement 10, and the timepiece 1 that are similarly excellent in handleability can be obtained.

  As mentioned above, although embodiment of this invention was described, these embodiment is shown as an example and is not intending limiting the range of invention. The embodiment can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. Embodiments and modifications thereof include, for example, those that can be easily assumed by those skilled in the art, substantially the same, and equivalents.

  For example, in the above-described embodiment, the configuration in which the power of the mainspring 16 accommodated in the barrel complete 11 is transmitted to the constant torque mechanism 20 is described as an example. However, the configuration is not limited to this case. The power may be transmitted from the mainspring 16 provided to the constant torque mechanism 20 to the constant torque mechanism 20.

  In the above embodiment, the hand-wound movement 10 for manually winding the mainspring 16 using the crown 17 is used. However, the present invention is not limited to this case. For example, an automatic-winding movement provided with a rotating weight is used. It does not matter.

In the above embodiment, the power from the barrel complete 11 is transmitted to the second control wheel 56 via the power source side wheel train 12, and the power from the constant torque spring 27 is transferred from the first power wheel 25 to the escapement side. Although the information is transmitted to the escapement 14 via the train wheel 15, the present invention is not limited to this case. For example, the power from the barrel complete 11 is transmitted to the second power vehicle 26 via the power source side train 12, and the power from the constant torque spring 27 is transmitted to the first control vehicle 55 via the first power vehicle 25. It may be transmitted from the first control wheel 55 to the escapement 14 via the escapement-side wheel train 15.
In any case, the power from the barrel complete 11 is transmitted to the second control wheel 56 or the second power wheel 26, and the power from the constant torque spring 27 escapes from the first power wheel 25 or the first control wheel 55. It may be configured to be transmitted to the machine 14.

  In the above embodiment, the constant torque mechanism 20 is provided at a position corresponding to the third wheel, but the present invention is not limited to this case. It doesn't matter. In any case, a constant torque mechanism 20 may be provided between the barrel complete 11 and the escapement 14. At this time, the constant torque mechanism 20 may be arranged so as to be included in the series wheel train that connects the barrel wheel 11 and the escapement 14 in series, or power transmission is performed even at a position that is out of the series wheel train. The constant torque mechanism 20 may be freely arranged as long as the power transmission path is capable of.

  In the above embodiment, the coupling gear 31 and the second power gear 35 are linked using the torque adjustment jumper 34. However, the present invention is not limited to this case. For example, the coupling gear 31 is coupled using a friction slip structure. The gear 31 and the second power gear 35 may be linked.

In the above embodiment, the stop gear 81 is rotated and revolved using the internal gear type fixed gear 82. However, the present invention is not limited to this case, and the external gear type fixed gear 82 may be used. .
In this case, as shown in FIGS. 24 to 26, the stop wheel 81 can be revolved clockwise around the second rotation axis O2 while rotating counterclockwise around the fifth rotation axis O5. Even in this case, only the rotation direction of the stop wheel 81 is opposite to that in the above embodiment, and the same effect can be achieved. In this case, the engagement surface 80a of the engagement claw stone 80 faces outward in the radial direction.

That is, in the initial stage of engagement as shown in FIG. 24, the working surface 95a of the stop tooth 95 is deeply engaged with the engagement stone 80, and then the engagement stone 80 is detached as shown in FIG. Accordingly, the action surface 95a of the stop tooth 95 moves to the toe side of the engaging claw stone 80 while sliding on the engaging surface 80a. Then, as shown in FIG. 26, the engagement is released when the action surface 95 a of the stop tooth 95 exceeds the toe of the engaging claw stone 80.
At this time, the support lever 85 follows the resultant force F3 of the pressing force F1 that the stop tooth 95 presses the engagement surface 80a and the frictional force F2 that is generated when the stop tooth 95 slides on the engagement surface 80a. The engaging pallet stone 80 is held so that the virtual line L passes through the second rotation axis O2. In the case of the external gear type fixed gear 82, the rotation direction of the stop wheel 81 is opposite to that in the above embodiment, so that the resultant force F3 is directed in the direction of the second rotation axis O2.

Even in the case of the external gear type fixed gear 82, when the direction along the resultant force F3 passes through the second rotation axis O2 as shown in FIG. 25, the rotational torque generated in the support lever 85 is not generated. It becomes. When the direction along the resultant force F3 deviates from the second rotation axis O2 as shown in FIGS. 24 and 26, a rotational torque is generated according to the deviation amount.
In particular, a reverse rotational torque is generated before and after the direction along the resultant force F3 passes through the second rotation axis O2. That is, a rotation torque T that pulls the support lever 85 toward the stop wheel 81 as shown in FIG. 26 is generated in the support lever 85, and a rotation that pulls the support lever 85 away from the stop wheel 81 as shown in FIG. Torque T is generated at the support lever 85.

  Therefore, even in the case of the external gear type fixed gear 82, when the stop gear 96 and the engaging claw stone 80 are engaged and the engagement is released in one cycle, the support is provided. The average torque in one cycle in the rotational torque generated in the lever 85 can be kept constant.

  Moreover, in the said embodiment, although the front-end | tip part 48a of the control lever 48 was contact | abutted with respect to the rotating cylinder 40 in the 1st power vehicle 25, it is not limited to this case. For example, as shown in FIG. 27, a restriction pin 130 that protrudes upward is provided at the tip 48 a of the restriction lever 48, and this restriction pin 130 abuts against the inner wall surface 131 of the opening in the first power gear 41. It does n’t matter. Even in this case, the same effect can be achieved.

  Furthermore, as shown in FIG. 28, the tip end portion 48a of the regulating lever 48 may be brought into contact with a regulating pin 135 that protrudes downward from the arm portion 41a of the first power vehicle 25. Even in this case, the same effect can be achieved.

In FIG. 28, an elongated through-hole 136 extending in a direction perpendicular to the radial direction of the first rotation axis O1 is formed in the arm portion 41a in plan view. The head portion 51 of the defining portion 47 is formed in a rectangular shape in plan view corresponding to the through hole 136 and is rotatable about the central axis of the shaft body 50. Accordingly, by rotating the head 51 after being inserted into the through hole 136, the defining portion 47 can be engaged with the inside of the through hole 136 and the retaining portion 47 can be prevented from coming off from the through hole 136. It can be carried out.
Therefore, even in this case, the radial position of the outer end portion 27b of the constant torque spring 27 can be defined, and the same effect can be achieved.

In the above embodiment, the inner end 27 a of the constant torque spring 27 is fixed to the second power wheel 26 via the fixing ring 45, and the diameter of the outer end 27 b is fixed to the outer end 27 b of the constant torque spring 27. A regulating portion 47 that regulates the directional position and a regulating lever 48 that regulates the rotation of the outer end portion 27b around the first rotation axis O1 in accordance with the elastic restoring deformation of the constant torque spring 27 are provided. It is not limited.
For example, the outer end portion 27b of the constant torque spring 27 is fixed to the first power wheel 25 through a whisker, for example, and the radial position of the inner end portion 27a is defined on the inner end portion 27a of the constant torque spring 27. A regulating lever that regulates the inner end portion 27a from rotating about the first rotation axis O1 in accordance with the elastic restoring deformation of the constant torque spring 27 may be provided.
Even if it is a case where it comprises in this way, the same effect can be achieved.

In the above embodiment, the case where the constant torque spring 27 is wound up by the winding operation by the torque generating mechanism 21 (that is, the number of windings is increased) is described. However, the present invention is not limited to this case. The spring 27 may be configured to be loosened (that is, to reduce the number of turns).
In this case, for example, the constant torque spring 27 only needs to be attached in the opposite direction to the above embodiment, and it is not necessary to change the configuration of the slide hole 46, the defining portion 47, the regulating lever 48, etc. It is not necessary to change the positional relationship of the constant torque spring 27 with respect to the vehicle 25 and the second power vehicle 26.
In any case, the torque generating mechanism 21 according to the present invention can be applied to any case where winding or loosening is performed by a winding operation, and elastic energy can be stored in the constant torque spring 27. Note that reducing the elastic energy of the constant torque spring 27 is called so-called unwinding.

L ... Virtual line of resultant force F1 ... Pressing force F2 ... Friction force F3 ... Combined force O1 ... First rotation axis O2 ... Second rotation axis P1 ... Engagement position P2 ... Disengagement position P3 ... Intermediate position P4 ... Engaging position P5 ... Release position 1 ... Clock (mechanical clock)
10 ... Movement (watch movement)
11 ... barrel car (power source)
DESCRIPTION OF SYMBOLS 12 ... Power source side train wheel 14 ... Escapement machine 15 ... Escapement machine side train wheel 20 ... Constant torque mechanism 21 ... Torque generation mechanism 22 ... Period control mechanism 25 ... First power vehicle 26 ... Second power vehicle 27 ... Constant Torque spring (power spring)
55 ... First control wheel 56 ... Second control wheel 57 ... Planetary mechanism 80 ... Engaging claw stone (engaging claw)
80a: engagement surface of engagement claw stone (engagement surface of engagement claw)
81 ... Stop wheel 85 ... Support lever 96 ... Stop gear 110 ... Power adjustment mechanism 111 ... Second torque adjustment gear (adjustment wheel)
113 ... Swing lever (moving member)

Claims (8)

A first motor vehicle that rotates about a first rotational axis;
A second power vehicle disposed coaxially with the first power vehicle and rotatable relative to the first power vehicle about the first rotational axis;
A power spring disposed between the first power vehicle and the second power vehicle and transmitting stored power to the first power vehicle and the second power vehicle;
A cycle control mechanism for intermittently rotating the second power vehicle with respect to the first power vehicle and replenishing the power spring with power,
The cycle control mechanism is
A first control vehicle that rotates about a second rotation axis along with the rotation of the first power vehicle;
A second control vehicle disposed coaxially with the first control vehicle, capable of rotating relative to the first control vehicle about the second rotation axis, and meshing with the second power vehicle;
An engagement claw provided in the first control vehicle and provided in the second control vehicle, disposed between the first control vehicle and the second control vehicle, based on rotation of the first control vehicle. A planetary mechanism that intermittently engages and disengages the stop vehicle,
The first power vehicle or the first control vehicle transmits power from the power spring to the escapement,
A constant torque mechanism in which power from the power source is transmitted to the second power vehicle or the second control vehicle. The constant torque mechanism according to claim 1,
The engaging claw rotates around the second rotation axis along with the rotation of the first control wheel,
The stop wheel revolves around the second rotation axis while rotating along with the rotation of the second control wheel, and has a stop gear that can be engaged with and disengaged from the engagement claw,
The engaging claw rotates around the second rotation axis so as to be disengaged from the stop gear based on the rotation of the first control wheel after the stop gear is engaged. A constant torque mechanism that releases The constant torque mechanism according to claim 2,
A support lever configured to be rotatable about the second rotation axis along with the rotation of the first control wheel and supporting the engaging claw;
The engagement claw has an engagement surface on which the stop gear is engaged and disengaged,
The support lever includes a pressing force by which the stop gear presses the engagement surface between the time when the stop gear is engaged with the engagement surface and the time when the engagement is released. A constant torque mechanism that supports the engagement claw so that a virtual line along a resultant force of a frictional force generated by sliding on the engagement surface passes through the second rotation axis. In the constant torque mechanism according to claim 3,
The imaginary line passes through the second rotation axis at an intermediate position between an engagement position where the stop gear is engaged with the engagement surface and a disengagement position where the stop gear is separated from the engagement surface; Constant torque mechanism. The constant torque mechanism according to any one of claims 1 to 4,
A constant torque mechanism comprising a power adjustment mechanism for adjusting the power of the power spring via the first power vehicle or the second power vehicle. The constant torque mechanism according to claim 5,
The power adjustment mechanism is
An adjustment vehicle capable of meshing with the first power vehicle or the second power vehicle;
Between a meshing position where the adjustment vehicle meshes with the first power vehicle or the second power vehicle, and a release position where the meshing between the adjustment vehicle and the first power vehicle or the second power vehicle is released. A constant torque mechanism comprising: a moving member that moves the adjustment wheel.   A timepiece movement comprising the constant torque mechanism according to any one of claims 1 to 6.   A timepiece comprising the timepiece movement according to claim 7.

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