JP6566432B1 - Constant torque mechanism, watch movement and watch - Google Patents

Abstract

A constant torque mechanism, a timepiece movement, and a timepiece in which fluctuations in torque transmitted to an escapement are suppressed are provided. A constant torque mechanism 30 is replenished with power by a carrier rotating around a first rotation axis O1 by a power from a barrel complete, a planetary gear 45 supported by the carrier so as to be able to rotate, and rotation of the carrier. The first rotation in synchronization with the rotation of the constant force spring 100, the constant force lower stage wheel 60 that rotates by the power from the constant force spring 100 and transmits the power of the constant force spring 100 to the escapement, and the constant force lower stage wheel 60. A base portion 95 of a lever spring 94 that rotates in the clockwise direction around the axis O1 and a clockwise rotation around the first rotation axis O1 along with the rotation of the base portion 95 and can be engaged with and disengaged from the planetary gear 45. An engaging claw stone 86 that can be displaced with respect to the base 95 and retracted from the rotation trajectory M of the planetary gear 45 after engaging with the planetary gear 45 within the rotation trajectory M and restricting the rotation of the planetary gear 45. Is provided. [Selection] Figure 10

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 a planetary mechanism that uses a stop vehicle as a planetary car as described in, for example, Patent Document 1 and Patent Document 2 below, and the planetary mechanism is used to escape from the power source side wheel train. It is possible to periodically control the phase difference from the machine-side wheel train. The planetary vehicle revolves so as to follow the engagement / disengagement claw provided on the sun wheel connected to the escapement side wheel train, and periodically engages / disengages with the engagement / disengagement claw.

Swiss Patent Application No. 296060 Swiss patent application 707938

  By the way, in the planetary type constant torque mechanism, the direction of the force applied between the planetary wheel and the engagement / disengagement claw in a state where the tooth tip of the planetary wheel and the engagement / disengagement claw are in contact with each other. Along the normal direction of the contact portion. Therefore, immediately before the planetary car and the engaging / disengaging claw are detached, the direction of the force applied between the planetary car and the engaging / disengaging claw when the tip of the planetary car and the corner of the engaging / disengaging claw are in contact with each other. Approaches the direction of rotation of the engagement / disengagement claw. Thereby, the torque transmitted to the escapement from the sun wheel provided with the engagement / disengagement claw increases, and the swing angle of the balance with the balance changes.

  Therefore, the present invention provides a constant torque mechanism, a timepiece movement, and a timepiece in which fluctuations in torque transmitted to the escapement are suppressed.

  The constant torque mechanism of the present invention is a carrier that rotates about a first axis by power from a power source, and is supported by the carrier so as to be able to rotate, and revolves around the first axis while rotating around the second axis. A planetary gear, a constant force spring that is replenished with power by rotation of the carrier, a constant force wheel that is rotated by power from the constant force spring and transmits the power of the constant force spring to an escapement, and the constant force A synchronous rotating portion that rotates in the first direction around the first axis in synchronization with the rotation of the vehicle, and rotates in the first direction along with the rotation of the synchronous rotating portion and can be engaged with and disengaged from the planetary gear. An engaging claw that engages with the planetary gear within the rotation trajectory of the planetary gear and restricts the rotation of the planetary gear, and then is displaced with respect to the synchronous rotating portion and can be retracted from the rotation trajectory. It is characterized by providing.

  According to this configuration, the engaging claw is displaced with respect to the synchronous rotating portion and retracted from the rotation trajectory of the planetary gear, so that the planetary gear passes through the engaging claw immediately before the planetary gear and the engaging claw are separated. The torque in the first direction transmitted to the synchronous rotating unit can be reduced. Therefore, the fluctuation | variation of the torque transmitted to an escapement from a synchronous rotation part via a constant power wheel can be suppressed. Therefore, fluctuations in torque transmitted to the escapement can be suppressed.

  In the constant torque mechanism, it is preferable that the engaging claw is displaced in a direction along the first direction with respect to the synchronous rotating portion and retracted from the rotation locus.

  According to this configuration, when the direction of the force applied between the planetary gear and the engaging claw approaches the first direction immediately before the separation of the planetary gear and the engaging claw, the planetary gear presses the engaging claw, The engaging claw can be displaced with respect to the synchronous rotating part. Therefore, the torque in the first direction transmitted from the planetary gear to the synchronous rotating portion via the engaging claw is relaxed by the displacement of the engaging claw. Therefore, the fluctuation | variation of the torque transmitted to an escapement from a synchronous rotation part via a constant power wheel can be suppressed.

  In the above-described constant torque mechanism, it is preferable that the constant torque mechanism further includes a spring portion that urges the engaging claw directly or indirectly toward the inside of the rotation locus.

  According to this structure, it can suppress that the state which the engagement nail | claw evacuated from the rotation locus | trajectory of the planetary gear is maintained. Therefore, the engagement / disengagement operation of the engagement claw with respect to the planetary gear can be stabilized.

  In the above-described constant torque mechanism, it is preferable that the engaging claw is rotatably supported with respect to the synchronous rotating portion, and further includes a lever body provided separately from the spring portion.

  According to this structure, compared with the case where an engaging claw is supported by the spring part, an engaging claw can be supported stably. Thereby, it becomes possible to stabilize the displacement of the engaging claw with respect to the synchronous rotating portion, and it is possible to stabilize the engagement / disengagement operation of the engaging claw with respect to the planetary gear.

  In the above-described constant torque mechanism, it is desirable that the engagement claw is supported by the spring portion.

  According to this configuration, the number of parts can be reduced as compared with a configuration in which the engagement claw is not supported by the spring portion.

  In the above-described constant torque mechanism, the synchronous rotating portion regulates displacement of the engaging claw engaged with the planetary gear in a direction along a second direction around the first axis with respect to the synchronous rotating portion. It is desirable to provide a regulation part.

  According to this configuration, when the engaging claw rotates in the first direction together with the synchronous rotating portion, the engaging claw is displaced in a direction along the second direction opposite to the first direction with respect to the synchronous rotating portion. It is possible to suppress the engagement claw from being disengaged from the planetary gear. Therefore, the engagement / disengagement operation of the engagement claw with respect to the planetary gear can be stabilized.

  Said constant torque mechanism WHEREIN: The said synchronous rotation part is provided with the 2nd control part which controls the displacement to the direction along the said 1st direction with respect to the said synchronous rotation part of the said engaging claw evacuated from the said rotation locus | trajectory. Is desirable.

  According to this configuration, when the engaging claw is retracted from the rotation trajectory of the planetary gear, the engaging claw is displaced in the direction along the first direction with respect to the synchronous rotating portion, so that the engaging claw is the planetary gear. It is possible to suppress the entry to the rotation locus again and the inability to engage. Therefore, the engagement / disengagement operation of the engagement claw with respect to the planetary gear can be stabilized.

  In the above constant torque mechanism, it is desirable that the engaging claw is provided so as to be swingable about the first axis with respect to the synchronous rotating portion.

  According to this configuration, the shaft member that extends along the first axis and supports the synchronous rotating portion can be used as the shaft member that supports the member to which the engaging claw is attached so as to be displaceable with respect to the synchronous rotating portion. . On the other hand, when the engaging claw is provided so as to be swingable about the axis different from the first axis with respect to the synchronous rotating part, the member to which the engaging claw is attached is attached to the synchronous rotating part. As a shaft member that is supported so as to be displaceable, it is necessary to separately provide a shaft member disposed on an axis different from the first axis in the synchronous rotating portion. Therefore, the number of parts can be reduced as compared with the case where the engaging claw is provided to be able to swing around the axis different from the first axis with respect to the synchronous rotating portion.

  In the above constant torque mechanism, it is desirable that the engaging claw is provided so as to be swingable about a third axis different from the first axis and the second axis with respect to the synchronous rotating portion.

  According to this configuration, since the rotation shaft of the engaging claw is disposed on the third axis different from the first axis, the design freedom of the constant torque mechanism can be improved.

A timepiece movement according to the present invention includes the constant torque mechanism described above.
A timepiece according to the present invention includes the timepiece movement described above.

  According to this configuration, since the constant torque mechanism in which the fluctuation of the torque transmitted to the escapement is suppressed is provided, a highly accurate timepiece movement and timepiece can be obtained.

  ADVANTAGE OF THE INVENTION According to this invention, it can be set as the constant torque mechanism in which the fluctuation | variation of the torque transmitted to an escapement was suppressed, the movement for timepieces, and a timepiece.

It is an external view of the timepiece showing the first embodiment. It is a block diagram of the movement of a 1st embodiment. It is the perspective view which looked at a part of movement of a 1st embodiment from the upper part. It is sectional drawing which shows a part of movement of 1st Embodiment. It is the top view which looked at a part of movement of a 1st embodiment from the upper part. It is the top view which looked at the engagement / disengagement lever unit of 1st Embodiment from upper direction. It is sectional drawing which shows the engagement / disengagement lever unit of 1st Embodiment. It is the perspective view which looked at the planetary vehicle and engagement / disengagement lever unit of 1st Embodiment from upper direction. It is the perspective view which looked at the planetary vehicle and engagement / disengagement lever unit of 1st Embodiment from the downward direction. It is the top view which looked at a part of constant torque mechanism of a 1st embodiment from the upper part. It is operation | movement explanatory drawing of the constant torque mechanism of 1st Embodiment. It is operation | movement explanatory drawing of the constant torque mechanism of 1st Embodiment. It is operation | movement explanatory drawing of the constant torque mechanism of 1st Embodiment. It is operation | movement explanatory drawing of the constant torque mechanism of 1st Embodiment. It is the top view which looked at the planetary vehicle and engagement / disengagement lever unit of 2nd Embodiment from upper direction. It is operation | movement explanatory drawing of the constant torque mechanism of 2nd Embodiment. It is the top view which looked at the planetary vehicle and engagement / disengagement lever unit of 3rd Embodiment from upper direction. It is operation | movement explanatory drawing of the constant torque mechanism of 3rd Embodiment. It is the top view which looked at the planetary vehicle and engagement / disengagement lever unit of 4th Embodiment from upper direction. It is operation | movement explanatory drawing of the constant torque mechanism of 4th Embodiment.

  Hereinafter, embodiments according to the present invention will be described with reference to the drawings. In the following description, the same reference numerals are given to configurations having the same or similar functions. In the present embodiment, a mechanical timepiece will be described as an example of a timepiece.

[First Embodiment]
(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.

FIG. 1 is an external view of a timepiece showing the first embodiment.
As shown in FIG. 1, the complete timepiece 1 of the present embodiment has a movement 10 (a movement for a timepiece) and a scale indicating at least information on time in a timepiece case made of a case back cover and glass 2 (not shown). A dial 3 and a pointer 4 including an hour hand 5, a minute hand 6 and a second hand 7 are provided.

FIG. 2 is a block diagram of the movement of the first embodiment.
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, The escapement side wheel train 15 connected to the machine 14 and a constant torque mechanism 30 disposed between the power source side train wheel 12 and the escapement side train wheel 15 are provided.

  The constant torque mechanism 30 generally constitutes a part of a front wheel train including a second wheel, third wheel, fourth wheel and the like. The power source side wheel train 12 in the present 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 30 when viewed from the constant torque mechanism 30. 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 30 when viewed from the constant torque mechanism 30.

  A mainspring 16 is accommodated inside the barrel complete 11. 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 30 via the power source side train wheel 12. In the present embodiment, the case where the power from the barrel complete 11 is transmitted to the constant torque mechanism 30 via the power source side wheel train 12 will be described as an example, but the present invention is not limited to this case. For example, the power from the barrel complete 11 may be directly transmitted to the constant torque mechanism 30 without using the power source side train wheel 12.

  For example, the power source side train wheel 12 includes a first transmission wheel 18. The first transmission wheel 18 is, for example, a third wheel. The first transmission wheel 18 is pivotally supported between a main plate 23 (see FIG. 4) and a train wheel bridge (not shown). The first transmission wheel 18 rotates based on the rotation of the barrel complete 11. When the first transmission wheel 18 rotates, a cylindrical pinion (not shown) rotates based on this 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.

  When the first transmission wheel 18 rotates, 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 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.

  The escapement side wheel train 15 mainly includes a second transmission wheel 19. The second transmission wheel 19 is, for example, a fourth wheel. The second transmission wheel 19 is pivotally supported between the main plate 23 and the train wheel bridge, and rotates based on the rotation of a constant-force lower car 60 described later of the constant torque mechanism 30. When the second transmission wheel 19 is the fourth wheel, the second transmission wheel 19 is attached with the second hand 7 shown in FIG. 1, and the second hand 7 indicates “second” based on the rotation of the second transmission wheel 19. indicate. 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 and an ankle (both not shown).
The escape wheel is pivotally supported between the main plate 23 and the train wheel bridge and meshes with the second transmission wheel 19, for example. As a result, power from a constant force spring 100 described later in the constant torque mechanism 30 is transmitted to the escape wheel via the escapement side wheel train 15. As a result, the escape wheel is rotated by the power from the constant force spring 100.

  The ankle is rotatably supported (swingable) between the main plate 23 and the 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 includes a main balance (not shown).
The balance with a balance, a balance wheel, and a hairspring is pivotally supported between the main plate 23 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)
The constant torque mechanism 30 is a mechanism that suppresses fluctuation (torque fluctuation) of power transmitted to the escapement 14.

FIG. 3 is a perspective view of a part of the movement of the first embodiment as viewed from above.
As shown in FIG. 3, the constant torque mechanism 30 includes a fixed gear 31 having a first rotation axis O1 extending in the vertical direction as a central axis, a constant force upper stage wheel 40 that rotates about the first rotation axis O1, and a constant force upper stage. A constant force lower car 60 (constant power car), which is arranged coaxially with the car 40 and is rotatable relative to the constant force upper car 40 around the first rotation axis O1, and a constant force upper car 40 and a constant force lower car 60. An engaging / disengaging lever unit 80, a constant force spring 100 that transmits the stored power to the constant force upper stage wheel 40 and the constant force lower stage wheel 60, and a torque adjustment mechanism 110 that adjusts the torque of the constant force spring 100. Prepare. The first rotation axis O1 is arranged at a position shifted in the in-plane direction of the main plate 23 (see FIG. 4) with respect to the rotation axes of the first transmission wheel 18 and the second transmission wheel 19 (see FIG. 2). Yes.

FIG. 4 is a cross-sectional view showing a part of the movement of the first embodiment.
As shown in FIG. 4, the fixed gear 31 is disposed between the main plate 23 and the constant force unit receiver 24. The constant force unit receiver 24 is disposed above the base plate 23. The fixed gear 31 includes a cylindrical body 32 disposed coaxially with the first rotation axis O <b> 1 and a gear body 33 formed integrally with the cylindrical body 32.

  The cylindrical body 32 is fixed to the lower surface of the constant force unit receiver 24 by a fixed gear pin 34 protruding downward from the constant force unit receiver 24. The cylindrical body 32 is formed with a center hole 35 and a window portion 36. The center hole 35 extends vertically with a constant inner diameter around the first rotation axis O1, and penetrates the cylindrical body 32 vertically. The window 36 is adjacent to the center hole 35 in the direction in which the first rotation axis O1 and the rotation axis of the first transmission wheel 18 are aligned when viewed from the top and bottom (see FIG. 3). The window portion 36 penetrates the cylindrical body 32 in the vertical direction and continues to the center hole 35. Thereby, the hole penetrating the fixed gear 31 in the vertical direction is a long hole when viewed from the vertical direction.

  The gear body 33 is formed coaxially with the first rotation axis O <b> 1 and projects from the lower end portion of the cylindrical body 32 toward the outside in the radial direction. On the outer peripheral surface of the gear body 33, fixed teeth 33a are formed over the entire circumference. That is, the fixed gear 31 is an external gear type gear.

  The constant force upper car 40 is pivotally supported between the main plate 23 and the constant force unit receiver 24. The constant force upper stage car 40 includes a rotary shaft 41 that rotates around the first rotary axis O1, a planetary car 43 that revolves around the first rotary axis O1, and a carrier 47 that pivotally supports the planetary car 43. .

  The rotation shaft 41 extends along the first rotation axis O1. The rotary shaft 41 is pivotally supported by the main plate 23 and the constant force unit receiver 24 via hole stones 25A and 25B. The hole stones 25A and 25B are made of artificial gems such as ruby, for example. The hole stones 25A and 25B are 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. A constant force upper pinion 41 a is formed on the upper portion of the rotating shaft 41. The constant force upper kana 41 a meshes with the first transmission wheel 18. As a result, the power from the barrel complete 11 (see FIG. 2) is transmitted to the rotating shaft 41 via the power source-side wheel train 12. Power of torque Tb is transmitted to the rotating shaft 41 from the barrel complete 11. Hereinafter, the torque Tb is referred to as the rotational torque Tb of the barrel complete 11. The rotating shaft 41 is rotated clockwise by the power from the barrel complete 11.

  Here, at least one of the constant force unit receiver 24 and the cylindrical body 32 is formed with a recess 27 that is recessed in a direction from the rotation axis of the first transmission wheel 18 toward the first rotation axis O1. In the present embodiment, the recess 27 is formed across both the constant force unit receiver 24 and the cylindrical body 32. The recess 27 opens toward the rotation axis of the first transmission wheel 18. A portion of the constant force upper pinion 41 a is disposed inside the recess 27. As a result, when the movement 10 is assembled, the first transmission wheel 18 is inserted so as to slide into the recess 27 even when the constant force unit receiver 24 and the rotary shaft 41 are arranged at predetermined positions. It can be connected to the constant force upper kana 41a.

  The carrier 47 is fixedly supported on the rotating shaft 41. A clockwise rotation torque Tb from the rotation shaft 41 is transmitted to the carrier 47. Thereby, the carrier 47 rotates around the first rotation axis O <b> 1 together with the rotation shaft 41 by the power from the barrel complete 11. The carrier 47 includes a lower seat 48 that is integrally connected to the rotation shaft 41, and an upper seat 54 that is disposed above the lower seat 48 and is fixed to the lower seat 48.

  The lower seat 48 is disposed below the fixed gear 31. The lower seat 48 includes a planetary vehicle support portion 49 that supports the planetary wheel 43, a spring support portion 50 that supports the constant force spring 100, a connecting portion 51 that connects the planetary vehicle support portion 49 and the spring support portion 50, and Is provided.

FIG. 5 is a plan view of a part of the movement of the first embodiment as viewed from above.
As shown in FIGS. 3 and 5, the planetary vehicle support portion 49 extends in an arc shape along the circumferential direction around the first rotation axis O <b> 1 when viewed in the vertical direction. The planetary vehicle support part 49 is formed such that an intermediate part viewed from the up-down direction is lowered one step below the both end parts.

  As shown in FIG. 4, the spring support portion 50 is provided on the opposite side of the planetary vehicle support portion 49 with the first rotation axis O1 interposed therebetween. The spring support portion 50 is formed with a pin insertion hole 50a through which a constant force spring pin 103 described later is inserted. A central hole through which the rotation shaft 41 is inserted is formed in the connecting portion 51. The connecting portion 51 is fixed to a lower portion than the constant force upper pinion 41 a of the rotating shaft 41. Thereby, the lower seat 48 rotates integrally with the rotating shaft 41. A carrier window 52 is formed in the lower seat 48. The carrier window portion 52 is formed on the first rotation axis O1 side with respect to the planetary vehicle support portion 49. The carrier window 52 penetrates the lower seat 48 up and down. The carrier window 52 avoids contact between the lower seat 48 and an engagement claw stone 86 (engagement claw) described later.

  As shown in FIG. 3, the upper seat 54 is disposed above the planetary wheel support portion 49 of the lower seat 48 and above the gear body 33 of the fixed gear 31. The upper seat 54 extends in an arc shape along the circumferential direction around the first rotation axis O <b> 1 when viewed from the vertical direction. The upper seat 54 is stacked with a plurality of collars 55 spaced from the planetary support 49 of the lower seat 48. Both ends of the upper seat 54 are fixed to both ends of the planetary vehicle support portion 49 by a plurality of bolts 56 inserted through a plurality of collars 55.

  As shown in FIG. 4, the planetary wheel 43 is supported by a carrier 47 so as to be able to rotate. Specifically, the planetary wheel 43 is pivotally supported by the planetary wheel support part 49 and the upper seat 54 of the lower seat 48 via the hole stones 59A and 59B, and is rotatable around the second rotation axis O2. The second rotation axis O <b> 2 is disposed at a position that is displaced in the in-plane direction of the ground plane 23 with respect to the first rotation axis O <b> 1 and is fixed with respect to the carrier 47. The planetary wheel 43 is disposed between an intermediate portion of the planetary vehicle support portion 49 of the lower seat 48 as viewed from the vertical direction and an intermediate portion of the upper seat 54 as viewed from the vertical direction (see FIG. 3). The planetary wheel 43 includes a planetary pinion 44 and a planetary gear 45.

  The planetary kana 44 meshes with the fixed teeth 33 a of the fixed gear 31. Since the fixed gear 31 is of an external tooth type, the planetary wheel 43 rotates clockwise around the second rotation axis O2 with the clockwise rotation of the carrier 47 due to the meshing of the planetary pinion 44 and the fixed gear 31. And revolves clockwise around the first rotation axis O1.

  The planetary gear 45 is formed below the planetary pinion 44 and can rotate (rotate and revolve) without contacting the fixed gear 31. The planetary gear 45 has a plurality of stop teeth 45a that can be engaged with and disengaged from an engagement surface 86a (see FIG. 8) of an engagement claw stone 86 to be described later. The number of teeth of the stop teeth 45a is 8. However, the present invention is not limited to this case, and the number of teeth may be changed as appropriate.

  As shown in FIG. 5, the stop teeth 45a extend in the clockwise direction around the second rotation axis O2 as the distance from the second rotation axis O2 as viewed in the vertical direction. The tip of the stop tooth 45a is an action surface that engages and disengages with respect to the engaging surface 86a of the engaging claw stone 86. The tooth tips of the stop teeth 45a are formed in a convex curved surface shape when viewed from the up-down direction. Hereinafter, the rotation locus M drawn by the tip of the stop tooth 45 a as the planetary wheel 43 rotates is referred to as the rotation locus M of the planetary gear 45.

  As shown in FIG. 4, the constant force lower car 60 is rotatably supported on the rotating shaft 41 of the constant force upper car 40 between the main plate 23 and the constant force unit receiver 24. The constant force lower car 60 is located below the carrier 47 of the constant force upper car 40 and is disposed between the carrier 47 and the main plate 23. The constant-force lower stage wheel 60 includes a constant-force lower stage cylinder 61 that is extrapolated to the rotating shaft 41, and a constant-force lower stage gear 62 that is integrally connected to the constant-force lower stage cylinder 61. The constant-force lower car 60 rotates clockwise around the first rotation axis O1 by the power transmitted from the constant-force spring 100.

  A rotating shaft 41 is inserted into the constant force lower tube 61 from above and protrudes below the constant force lower tube 61. Ring-shaped hole stones 69 </ b> A and 69 </ b> B are press-fitted inside the upper end portion and the lower end portion of the constant force lower tube 61. The rotating shaft 41 is inserted through the hole stones 69A and 69B.

  The constant force lower gear 62 is integrally connected to the lower end of the constant force lower tube 61. On the outer peripheral surface of the constant force lower gear 62, constant force lower step teeth 62a with which the second transmission wheel 19 is engaged are formed over the entire circumference. Thus, the constant-force lower stage car 60 can transmit the power from the constant-force spring 100 to the second transmission wheel 19 connected to the escapement 14, that is, the escapement-side wheel train 15.

  In the present embodiment, the case where the power from the constant force spring 100 is transmitted to the escapement 14 via the escapement-side wheel train 15 will be described as an example, but 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 force spring 100 may be directly transmitted to the escapement 14.

  The engaging / disengaging lever unit 80 includes an engaging claw stone 86 that engages / disengages with the stop teeth 45a of the planetary gear 45, and supports the engaging claw stone 86 so as to be rotatable about the first rotation axis O1. The engagement / disengagement lever unit 80 includes a lever bush 81 and a lever spring 94 that are provided so as not to rotate relative to the constant force lower tube 61, and an engagement / disengagement lever 84 provided relative to the constant force lower tube 61. And comprising.

  The lever bush 81 is formed in a cylindrical shape coaxial with the first rotation axis O1. The lever bush 81 is extrapolated to the upper end portion of the constant force lower stage cylinder 61 of the constant force lower stage car 60 and is integrally connected to the constant force lower stage cylinder 61. As a result, the lever bush 81 rotates in the clockwise direction around the first rotation axis O <b> 1 in synchronization with the rotation of the constant force lower car 60. A flange 82 that protrudes outward in the radial direction is formed at the upper end of the lever bush 81.

FIG. 6 is a plan view of the engaging / disengaging lever unit of the first embodiment as viewed from above. FIG. 7 is a cross-sectional view showing the engagement / disengagement lever unit of the first embodiment.
As shown in FIGS. 6 and 7, the engagement / disengagement lever 84 is provided to be rotatable relative to the lever bush 81 and the lever spring 94 around the first rotation axis O <b> 1. The engaging / disengaging lever 84 includes a lever main body 85 (lever body), an engaging claw stone 86 supported by the lever main body 85, and a lever pin 87.

  The lever body 85 is disposed below the planetary gear 45 of the planetary wheel 43 (see FIG. 4). The lever body 85 is rotatably supported by the upper and lower intermediate portions of the lever bush 81. The lever main body 85 is restricted from moving upward with respect to the constant-force lower-stage cylinder 61 by the flange 82 of the lever bush 81. The lever body 85 includes a first lever piece 90, a second lever piece 91, and a third lever piece 92 that extend from the lever bush 81 side toward the outside in the radial direction. The 1st lever piece 90, the 2nd lever piece 91, and the 3rd lever piece 92 are mutually arrange | positioned at intervals in the circumferential direction around the 1st rotating shaft O1. In the example shown in the drawing, a through-hole penetrating vertically is formed in the base end portion of the first lever piece 90, the second lever piece 91, and the third lever piece 92. However, the shape of the 1st lever piece 90, the 2nd lever piece 91, and the 3rd lever piece 92 is not limited to this case, You may change freely. Further, the shape of the lever main body 85 is not limited to the shape described above, and may be freely changed. For example, the lever body may not include the third lever piece 92.

  A stone holding portion 90 a that holds the engaging claw stone 86 is formed at the distal end portion of the first lever piece 90. The stone holding part 90a penetrates the first lever piece 90 up and down. A pin holding portion 91 a that holds the lever pin 87 is formed at the tip of the second lever piece 91. The pin holding portion 91a penetrates the second lever piece 91 up and down.

FIG. 8 is a perspective view of the planetary vehicle and the engagement / disengagement lever unit according to the first embodiment as viewed from above. FIG. 9 is a perspective view of the planetary vehicle and the engagement / disengagement lever unit according to the first embodiment viewed from below.
As shown in FIGS. 8 and 9, the engaging claw stone 86 is attached to the stone holding portion 90 a of the first lever piece 90 and is rotatably supported by the lever main body 85 with respect to the lever bush 81 and the lever spring 94. ing. Thus, the engaging claw stone 86 is provided so as to be swingable around the first rotation axis O1. The engaging claw stone 86 is made of an artificial gem such as a ruby, for example. In addition, the engaging claw stone 86 is not limited to the case where it is formed of artificial gemstone like the hole stone described above, and may be formed of a metal material such as other brittle materials or iron alloys. Absent. Further, the engaging claw stone 86 may be formed integrally with the lever main body 85 instead of being separated from the lever main body 85. The engaging claw stone 86 is held in a state protruding from the stone holding portion 90a toward the planetary gear 45 (upward). The engaging claw stone 86 is disposed inside the carrier window 52 of the carrier 47 of the constant-force upper car 40 (see FIG. 4).

FIG. 10 is a plan view of a part of the constant torque mechanism of the first embodiment as viewed from above.
As shown in FIGS. 8 and 10, the tip of the stop tooth 45a of the planetary gear 45 is engaged and disengaged on the side surface facing the side opposite to the first rotation axis O1 of the protruding portion of the engaging claw stone 86. The engagement surface 86a is made possible. In the illustrated example, the engagement surface 86a has a substantially flat surface and both ends are rounded as viewed from the top and bottom. That is, the edges on both sides in the circumferential direction around the first rotation axis O1 of the engaging surface 86a are formed in a convex curved shape when viewed from the top and bottom. Hereinafter, the counterclockwise edge around the first rotation axis O1 on the engagement surface 86a is referred to as a first edge 86a1. The engaging claw stone 86 engages with the planetary gear 45 within the rotation locus M of the planetary gear 45 and regulates the rotation of the planetary wheel 43. Further, the engaging claw stone 86 is displaced in the clockwise direction around the first rotation axis O1 with respect to the planetary wheel 43 and retracts from the rotation locus M of the planetary gear 45, thereby separating from the stop tooth 45a and the planetary gear. 45 is disengaged.

  As shown in FIG. 7, the lever pin 87 is formed in a column shape extending vertically and inserted into the pin holding portion 91 a of the lever main body 85, and a head that is enlarged in diameter at the lower end portion of the shaft body 87 a. 87b. The shaft body 87a protrudes from the second lever piece 91 in the upper and lower sides. The head portion 87 b is disposed with a space from the lower surface of the second lever piece 91.

  As shown in FIGS. 7 and 9, the lever spring 94 is disposed below the lever body 85 and is fixedly supported by the lower end portion of the lever bush 81. As a result, the lever spring 94 rotates in the clockwise direction around the first rotation axis O <b> 1 in synchronization with the rotation of the constant-force lower car 60. The lever spring 94 includes a base portion 95 (synchronous rotating portion) fixed to the lever bush 81 and a spring body 97 (spring portion) extending from the base portion 95.

  As shown in FIG. 9, the base 95 is formed in an annular shape surrounding the first rotation axis O1. The base 95 is extrapolated to the lower end of the lever bush 81 and is integrally connected to the lever bush 81. The base 95 can be brought into contact with the lever main body 85 of the engagement / disengagement lever 84 from below, and restricts the downward movement of the lever main body 85 with respect to the lever bush 81. An arm 96 is formed on the base 95.

  As shown in FIG. 6, the arm 96 extends along the direction in which the second lever piece 91 of the engagement / disengagement lever 84 extends when viewed in the vertical direction. The distal end portion of the arm 96 is in contact with the shaft body 87a of the lever pin 87 in the counterclockwise direction around the first rotation axis O1 between the distal end portion of the second lever piece 91 and the head portion 87b of the lever pin 87 ( See also FIG. 9). As a result, the arm 96 restricts the counterclockwise rotation of the engagement / disengagement lever 84 relative to the base 95 around the first rotation axis O1. That is, the arm 96 restricts the displacement of the engaging claw stone 86 (see FIG. 8) engaged with the planetary gear 45 in the counterclockwise direction around the first rotation axis O1 with respect to the base 95. The lever spring 94 presses and rotates the engagement / disengagement lever 84 in the clockwise direction around the first rotation axis O1.

  The spring body 97 is a thin plate spring. The spring body 97 extends from the tip of the arm 96 along the counterclockwise direction around the first rotation axis O1. The spring body 97 wraps around the base portion 95 on the radially outer side, and clockwise between the distal end portion of the second lever piece 91 and the head portion 87b of the lever pin 87 around the first rotation axis O1 on the shaft body 87a of the lever pin 87. (See also FIG. 9). As a result, the spring body 97 urges the engagement / disengagement lever 84 counterclockwise around the first rotation axis O <b> 1 with respect to the base portion 95, while the timepiece around the first rotation axis O <b> 1 of the engagement / disengagement lever 84 relative to the base portion 95. Displacement in the direction is allowed. As described above, the engaging claw stone 86 included in the engagement / disengagement lever 84 is in a state having a play in the clockwise direction around the first rotation axis O <b> 1 with respect to the base 95.

  As shown in FIG. 10, the constant force spring 100 is a thin plate spring made of a metal or an alloy such as iron or nickel, and is formed in a spiral shape. Specifically, the constant force spring 100 is formed in a spiral shape along the Archimedes curve in a polar coordinate system with the first rotation axis O1 as the origin. Accordingly, the constant force spring 100 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 vertical direction.

  As shown in FIG. 4, the constant force spring 100 is disposed below the engaging / disengaging lever unit 80 and between the engaging / disengaging lever unit 80 and the constant force lower gear 62. The constant force spring 100 is connected to the lower seat 48 of the carrier 47 of the constant force upper car 40 through the constant force spring pin 103 at the outer end 101 which is one peripheral end, and at the other peripheral end. A certain inner end 102 is connected to the constant force lower car 60 via the fixing ring 104 and the torque adjusting mechanism 110. Thereby, the constant force spring 100 can transmit the stored power to the constant force upper stage car 40 and the constant force lower stage car 60, respectively.

  The constant force spring pin 103 is held by the spring support 50 in a state of projecting downward from a pin insertion hole 50a formed in the spring support 50 of the constant force upper car 40. The outer end portion 101 of the constant force spring 100 is fixed to the protruding portion of the constant force spring pin 103.

  The fixing ring 104 is fixed to the inner end portion 102 of the constant force spring 100. The fixing ring 104 is formed in an annular shape coaxial with the first rotation axis O1. The fixing ring 104 is integrally connected to a constant force spring bush 111 described later of the torque adjustment mechanism 110.

  The constant force spring 100 is wound with a predetermined winding amount in the clockwise direction toward the outer end portion 101 with the inner end portion 102 as the unwinding position. The constant force spring 100 is elastically deformed so as to be reduced in diameter by being wound up, and a preload is applied thereto. Therefore, the constant force spring 100 generates a power of torque Tc and stores the power. The power stored in the constant force spring 100 is transmitted to the constant force upper car 40 and the constant force lower car 60 as the constant force spring 100 is elastically deformed. Thereby, the constant force upper stage wheel 40 and the constant force lower stage wheel 60 can be rotated in the opposite directions around the first rotation axis O <b> 1 by the power transmitted from the constant force spring 100. Specifically, the constant force lower car 60 can be rotated in the clockwise direction, and the constant force upper car 40 can be rotated in the counterclockwise direction. Hereinafter, the torque Tc is referred to as the rotational torque Tc of the constant force spring 100. When the mainspring 16 in the barrel complete 11 is wound with a predetermined winding amount, the rotational torque Tc is smaller than the rotational torque Tb of the rotating shaft 41.

  The torque adjustment mechanism 110 applies a preload to the constant force spring 100 to adjust the rotational torque Tc of the constant force spring 100. The torque adjustment mechanism 110 includes a constant force spring bush 111 supported by a constant force lower stage cylinder 61 of the constant force lower stage wheel 60, a first torque adjustment gear 112 integrally connected to the constant force spring bush 111, and a constant force lower stage. A second torque adjustment gear 113 integrally connected to the cylinder 61, and a torque adjustment jumper 114 that links the first torque adjustment gear 112 and the second torque adjustment gear 113 are provided.

  The constant force spring bush 111 is formed in a cylindrical shape coaxial with the first rotation axis O1. The constant force spring bush 111 is externally inserted into the constant force lower stage cylinder 61 between the constant force lower stage gear 62 and the engagement / disengagement lever unit 80. The constant force spring bush 111 is provided so as to be rotatable around the first rotation axis O <b> 1 with respect to the constant force lower tube 61. The above-described fixing ring 104 is extrapolated at the upper and lower intermediate portions of the constant force spring bush 111, and the constant force spring bush 111 and the fixing ring 104 are integrally connected.

  The first torque adjustment gear 112 is integrally connected to the lower end portion of the constant force spring bush 111. On the outer peripheral surface of the first torque adjustment gear 112, first torque adjustment teeth 112a are formed over the entire circumference. A torque adjusting gear (not shown) meshes with the first torque adjusting teeth 112a.

  The second torque adjustment gear 113 is disposed between the constant force lower gear 62, the constant force spring bush 111 and the first torque adjustment gear 112. The second torque adjusting gear 113 is integrally connected to the constant force lower tube 61. The second torque adjustment gear 113 is formed with a smaller diameter than the first torque adjustment gear 112. On the outer peripheral surface of the second torque adjusting gear 113, second torque adjusting teeth 113a are formed over the entire circumference. A torque adjustment jumper 114 is detachably engaged with the second torque adjustment tooth 113a.

  The torque adjustment jumper 114 is supported by the first torque adjustment gear 112, and can revolve around the first rotation axis O1 around the second torque adjustment gear 113. The torque adjustment jumper 114 can restrict the first torque adjustment gear 112 from rotating clockwise with respect to the second torque adjustment gear 113. Further, the torque adjustment jumper 114 is allowed to allow the first torque adjustment gear 112 to rotate counterclockwise with respect to the second torque adjustment gear 113.

  Thus, when the constant force spring bush 111 and the first torque adjustment gear 112 receive clockwise power from the constant force spring 100, the power is transmitted to the second torque adjustment gear 113 via the torque adjustment jumper 114. Then, the torque adjustment jumper 114 restricts the clockwise rotation of the first torque adjustment gear 112 relative to the second torque adjustment gear 113, and the first torque adjustment gear 112 and the second torque adjustment gear 113 are integrally rotated in the clockwise direction. Rotate. As a result, the constant-force lower stage wheel 60 also rotates in the clockwise direction together with the second torque adjustment gear 113.

  Further, when a preload is applied to the constant force spring 100, a torque adjusting gear (not shown) is engaged with the first torque adjusting gear 112, and the torque adjusting gear is rotated to rotate the first torque adjusting gear 112. Rotate counterclockwise. Then, the torque adjustment jumper 114 allows the first torque adjustment gear 112 to rotate counterclockwise with respect to the second torque adjustment gear 113, so that the constant force spring bush 111 and the fixed force spring bush 111 can be fixed without rotating the constant force lower wheel 60. The ring 104 is rotated counterclockwise. Thereby, the inner end part 102 of the constant force spring 100 can be rotated counterclockwise. As a result, the constant force spring 100 can be wound up, and the preload of the constant force spring 100 can be increased to adjust the rotational torque Tc to increase.

(Operation of constant torque mechanism)
The operation of the constant torque mechanism 30 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 carrier 47 of the constant force upper stage train 40 via the power source side train 12. It is assumed that it is transmitted. Further, the constant force spring 100 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 force spring 100 to the carrier 47 and the constant force lower wheel 60 of the constant force upper wheel 40. It shall be.

  According to the constant torque mechanism 30 of the present embodiment, since the constant force spring 100 is provided, the power stored in the constant force spring 100 is transmitted to the constant force lower stage car 60, and the constant force lower stage car 60 is rotated in the first rotation. It can be rotated clockwise around the axis O1. Specifically, the power from the constant force spring 100 is transmitted to the torque adjustment mechanism 110 via the fixing ring 104. The power transmitted to the torque adjustment mechanism 110 is transmitted to the constant force lower car 60. As a result, the constant force lower stage wheel 60 is transmitted from the constant force spring 100 such that it rotates clockwise around the first rotation axis O1 with the rotational torque Tc. Furthermore, the power of the constant force spring 100 can be transmitted from the constant force lower stage wheel 60 to the second transmission wheel 19, and the second transmission wheel 19 can be rotated with the rotation of the constant force lower stage wheel 60. That is, the power from the constant force spring 100 can be transmitted to the escapement side wheel train 15 via the constant force lower car 60, and the escapement 14 can be operated.

  Further, since the power from the constant force spring 100 is also transmitted to the constant force upper stage wheel 40, the constant force upper stage wheel 40 is rotated counterclockwise around the first rotation axis O1 by the rotational torque Tc.

  However, a rotational torque Tb that rotates clockwise around the first rotation axis O1 is transmitted from the power source side train wheel 12 to the constant-power upper stage wheel 40. Since the rotational torque Tb is larger than the rotational torque Tc, the constant force upper stage wheel 40 is prevented from rotating counterclockwise around the first rotational axis O1.

  The constant-power upper stage wheel 40 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 force spring 100 (rotational torque Tb−rotational torque Tc). Works. However, since the engaging claw stone 86 of the engagement / disengagement lever unit 80 is engaged with the planetary gear 45 within the rotation trajectory M of the planetary gear 45 of the constant-power upper stage vehicle 40, the rotation and revolution of the planetary wheel 43 are restricted. Is done. As a result, the constant force upper stage car 40 and the constant force lower stage car 60 can be linked together, and the constant force upper stage car 40 is prevented from rotating clockwise around the first rotation axis O1.

  From the above, at the stage where the planetary gear 45 and the engaging claw stone 86 are engaged, the constant force upper stage wheel 40 is prevented from rotating around the first rotation axis O1. In addition, since the power of the difference mentioned above acts on the constant force upper stage wheel 40, the tip of the stop tooth 45a of the planetary gear 45 is in a state where it strongly presses against the engaging surface 86a of the engaging claw stone 86. Engage.

FIGS. 11 to 14 are operation explanatory views of the constant torque mechanism of the first embodiment, and are plan views of the fixed gear, the planetary gear, and the engagement / disengagement lever unit as viewed from above. In addition, in FIGS. 11-14, the fixed gear, the planetary gear, and the engagement / disengagement lever unit are illustrated in a simplified manner.
When the constant force lower wheel 60 is rotated by the power from the constant force spring 100, the lever bush 81 and the lever spring 94 of the engagement / disengagement lever unit 80 are rotated clockwise around the first rotation axis O1. When the lever spring 94 rotates, the engagement / disengagement lever 84 of the engagement / disengagement lever unit 80 is pushed by the arm 96 of the lever spring 94 and rotates around the first rotation axis O1 in the clockwise direction. When the engagement / disengagement lever 84 rotates in the clockwise direction, the engagement claw stone 86 of the engagement / disengagement lever 84 has a clockwise play around the first rotation axis O1 and a clock around the first rotation axis O1. Displace in the direction. Thereby, the engagement / disengagement lever unit 80 can be gradually detached from the planetary gear 45 so as to retract the engagement claw stone 86 from the rotation locus M of the planetary gear 45. As a result, as shown in FIGS. 11 to 13, the tooth tip of the stop tooth 45a slides on the engagement surface 86a as the engagement claw stone 86 is disengaged, and the first rotation with respect to the engagement surface 86a. It moves counterclockwise around the axis O1.

  Here, the force F applied between the stop tooth 45a and the engaging claw stone 86 is that the stop tooth 45a presses the engaging surface 86a and the stop tooth 45a slides on the engaging surface 86a. This is the resultant force of the frictional force generated by. The pressing force is a force parallel to the normal direction at the contact portion between the stop tooth 45a and the engagement surface 86a. The frictional force is a force parallel to the tangential direction at the contact portion between the stop tooth 45a and the engagement surface 86a. Since the tooth tip of the stop tooth 45a and the first end edge 86a1 of the engagement surface 86a are formed in a convex curved shape when viewed from the top and bottom direction, the tooth tip of the stop tooth 45a is the first end of the engagement surface 86a. When coming into contact with the edge 86a1, the force F approaches the clockwise direction around the first rotation axis O1 (see FIG. 13). As a result, the engagement / disengagement lever 84 including the engagement claw stone 86 rotates clockwise around the first rotation axis O <b> 1 relative to the base 95 while resisting the biasing force of the spring body 97 of the lever spring 94. Then, as shown in FIG. 14, when the tooth tip of the stop tooth 45a exceeds the first end edge 86a1 of the engagement surface 86a, the engagement between the stop tooth 45a and the engagement claw stone 86 is released. As a result, the linkage between the constant force upper stage car 40 and the constant force lower stage car 60 via the engaging claw stone 86 and the planetary wheel 43 is released.

  Therefore, the constant-power upper stage vehicle 40 is driven by 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 force spring 100 (rotational torque Tb−rotational torque Tc). It rotates clockwise around the first rotation axis O1.

  The constant force upper stage wheel 40 rotates clockwise around the first rotation axis O <b> 1, whereby the constant force spring 100 can be wound up via the constant force spring pin 103 fixed to the carrier 47. Can be refilled with power. That is, the loss of power lost by transmitting power to the constant power lower car 60 can be supplemented using the power transmitted from the barrel wheel 11 side that is the power source. Thereby, the power of the constant force spring 100 can be maintained constant, and the escapement 14 can be operated with a constant torque.

  Even when the power to the constant force spring 100 is replenished, the constant force lower car 60 is rotated by the power from the constant force spring 100, and the escapement side wheel train 15 is moved from the constant force spring 100. The power of

Further, when the power of the constant force spring 100 is replenished, the planetary wheel 43 rotates around the second rotation axis O2 in the clockwise direction as the constant force upper wheel 40 rotates around the first rotation axis O1. Rotating around the first rotation axis O1 in the clockwise direction, the engagement claw stone 86 is followed. Then, the planetary wheel 43 rotates by one tooth of the stop tooth 45 a to catch up with the engaging stone 86, and the tip of the stop tooth 45 a is engaged again with the engaging surface 86 a of the engaging tooth 86.
As a result, the constant force upper stage car 40 and the constant force lower stage car 60 are linked again, so that the constant force upper stage car 40 is prevented from rotating and the replenishment of power to the constant force spring 100 is completed.

  By repeating the above, the planetary gear 45 and the engaging claw stone 86 can be intermittently engaged and disengaged. In other words, the planetary gear 45 and the engaging claw stone 86 are intermittently engaged and disengaged based on the rotation of the constant-force lower car 60, and the constant-force upper car 40 is intermittently rotated with respect to the constant-force lower car 60. Can be made. Thereby, replenishment of the power to the constant force spring 100 can be performed intermittently.

  As described above, the constant torque mechanism 30 of the present embodiment includes the base 95 of the lever spring 94 that rotates in the clockwise direction around the first rotation axis O1 in synchronization with the rotation of the constant-force lower-stage car 60, and the base 95 Along with the rotation, it rotates in the clockwise direction around the first rotation axis O 1 and can be engaged with and disengaged from the planetary gear 45, and engages with the planetary gear 45 within the rotation locus M of the planetary gear 45 to rotate the planetary gear 45. And an engaging claw stone 86 that can be displaced with respect to the base portion 95 and retracted from the rotation locus M of the planetary gear 45 after the restriction. According to this configuration, the engaging claw stone 86 is displaced with respect to the base portion 95 and retracts from the rotation locus M of the planetary gear 45, so that the planetary gear 45 is immediately before the planetary gear 45 and the engaging claw stone 86 are detached. The torque in the clockwise direction around the first rotation axis O <b> 1 transmitted to the base 95 through the engaging claw stone 86 can be reduced. Therefore, the fluctuation | variation of the torque transmitted to the escapement 14 via the constant force lower stage car 60 from the base 95 can be suppressed. Therefore, the fluctuation | variation of the torque transmitted to the escapement 14 can be suppressed.

  In particular, in the present embodiment, the tip of the stop tooth 45a of the planetary gear 45 and the first end edge 86a1 of the engagement surface 86a of the engagement claw stone 86 are formed in a convex curved surface shape when viewed from the up-down direction. For this reason, the planetary gear 45 and the engaging claw stone 86 are compared with the case where the tips of the stop teeth of the planetary gear and the first end edge of the engaging surface of the engaging claw stone are not formed in a convex curve shape. The contact surface pressure can be reduced, and the planetary gear 45 and the engaging claw stone 86 can be prevented from being scraped. In this case, the stop of the planetary gear 45 is compared with the case where the tips of the stop teeth of the planetary gear and the first edge of the engagement surface of the engagement claw stone are not formed in a convex curved surface shape. The sliding distance between the tooth tip of the tooth 45a and the first end edge 86a1 of the engaging surface 86a of the engaging claw stone 86 is increased. For this reason, the period during which the direction of the force F applied between the planetary gear 45 and the engaging claw stone 86 approaches the clockwise direction around the first rotation axis O1 becomes longer. Here, in the present embodiment, as described above, the engaging claw stone 86 retreats from the rotation locus M of the planetary gear 45 immediately before the planetary gear 45 and the engaging claw stone 86 are detached, and the base 95 is removed from the planetary gear 45. The torque in the clockwise direction around the first rotation axis O1 transmitted to can be reduced. Therefore, it is possible to achieve both improvement in durability of the constant torque mechanism 30 and suppression of torque fluctuation.

  Furthermore, since the scraping of the planetary gear 45 and the engaging claw stone 86 is suppressed, there is a margin for increasing the force applied to the contact portion between the planetary gear 45 and the engaging claw stone 86. For this reason, the distance between the contact portion of the planetary gear 45 and the engaging claw stone 86 and the first rotation axis O1 can be reduced, and the constant torque mechanism 30 can be reduced in size.

  Further, the engaging claw stone 86 is displaced from the rotation locus M by being displaced in the clockwise direction around the first rotation axis O <b> 1 with respect to the base portion 95. According to this configuration, the direction of the force F applied between the planetary gear 45 and the engaging claw stone 86 approaches the clockwise direction around the first rotation axis O1 immediately before the planetary gear 45 and the engaging clawstone 86 are detached. At this time, the engaging claw stone 86 can be pressed by the planetary gear 45 to displace the engaging claw stone 86 with respect to the base 95. Therefore, the torque in the clockwise direction around the first rotation axis O <b> 1 transmitted from the planetary gear 45 to the base portion 95 via the engaging claw stone 86 is relieved by the displacement of the engaging claw stone 86. Therefore, fluctuations in torque transmitted from the base 95 to the escapement 14 via the constant force lower car 60 can be suppressed.

  The constant torque mechanism 30 further includes a spring body 97 that indirectly biases the engaging claw stone 86 toward the inside of the rotation locus M via the lever body 85. According to this configuration, the state in which the engaging claw stone 86 is retracted from the rotation locus M of the planetary gear 45 can be suppressed. Therefore, the engagement / disengagement operation of the engaging claw stone 86 with respect to the planetary gear 45 can be stabilized.

  The constant torque mechanism 30 further includes a lever main body 85 that supports the engaging claw stone 86 rotatably with respect to the base 95 of the lever spring 94 and is provided separately from the spring main body 97. According to this structure, compared with the case where the engaging claw stone 86 is supported by the spring part, the engaging claw stone 86 can be supported stably. Thereby, it becomes possible to stabilize the displacement of the engaging claw stone 86 with respect to the base 95, and the engagement / disengagement operation of the engaging cobble stone 86 with respect to the planetary gear 45 can be stabilized.

  In addition, the base portion 95 of the lever spring 94 includes an arm 96 that restricts the displacement of the engaging claw stone 86 engaged with the planetary gear 45 in the counterclockwise direction around the first rotation axis O <b> 1 with respect to the base portion 95. According to this configuration, when the engaging claw stone 86 rotates together with the base 95 around the first rotation axis O <b> 1 in the clockwise direction, the engaging claw stone 86 rotates counterclockwise around the first rotation axis O <b> 1 with respect to the base 95. It is possible to prevent the engaging claw stone 86 from being disengaged from the planetary gear 45 by being displaced in the direction. Therefore, the engagement / disengagement operation of the engaging claw stone 86 with respect to the planetary gear 45 can be stabilized.

  Further, the engaging claw stone 86 is provided so as to be swingable about the first rotation axis O <b> 1 with respect to the base portion 95 of the lever spring 94. According to this configuration, the base body 95 extending along the first rotation axis O1 is supported as a shaft member that supports the lever main body 85 to which the engaging claw stone 86 is attached to the base portion 95 of the lever spring 94 so as to be displaceable. A lever bush 81 can be used. On the other hand, when the engaging claw stone is provided so as to be able to swing around an axis different from the first rotation axis O1, the shaft member that supports the member attached with the engaging claw stone so as to be able to swing. As a result, it is necessary to separately provide a shaft member (for example, the lever rotation shaft 389 according to the fourth embodiment shown in FIG. 19) disposed on an axis different from the first rotation axis O1. Therefore, the number of parts can be reduced as compared with the case where the engaging claw stone 86 is provided to be swingable about an axis different from the first rotation axis O1.

  Here, the assembly of the constant torque mechanism 30 will be briefly described. When assembling the constant torque mechanism 30, first, the constant force lower car 60 is assembled to the main plate 23 together with the torque adjustment mechanism 110, the constant force spring 100, and the engagement / disengagement lever unit 80. Subsequently, the constant force upper car 40 is assembled to the constant force lower car 61 of the constant power lower car 60. Subsequently, the fixed gear 31 assembled to the constant force unit receiver 24 is assembled to the constant force upper car 40. At this time, the gear body 33 of the fixed gear 31 is connected to the planetary gear 45 of the planetary wheel 43 while avoiding the upper seat 54 of the carrier 47 while inserting the rotating shaft 41 into the center hole 35 of the fixed gear 31. For this reason, it is necessary to insert the rotation shaft 41 into the center hole 35 of the fixed gear 31 in a state where the fixed gear 31 is inclined with respect to the first rotation axis O1. In the present embodiment, the window 36 is connected to the center hole 35 of the fixed gear 31 through which the rotating shaft 41 is inserted, and is a long hole when viewed from the up and down direction. For this reason, the rotation shaft 41 can be inserted into the center hole 35 of the fixed gear 31 in a state where the fixed gear 31 is inclined with respect to the first rotation axis O1. Therefore, it is possible to provide the constant torque mechanism 30 with improved assembly workability.

  Since the timepiece 1 and the movement 10 of the present embodiment are provided with the constant torque mechanism 30 that suppresses fluctuations in torque transmitted to the escapement 14 and has improved durability, it is highly accurate and durable. An excellent movement 10 and timepiece 1 can be obtained.

[Second Embodiment]
Next, a second embodiment will be described with reference to FIGS. 15 and 16. The second embodiment differs from the first embodiment in that the engagement / disengagement lever 184 is not biased. The configurations other than those described below are the same as those in the first embodiment.

(Configuration of engagement / disengagement lever unit)
FIG. 15 is a plan view of the planetary vehicle and the engagement / disengagement lever unit according to the second embodiment as viewed from above. In addition, in FIG. 15, the planetary vehicle and the engagement / disengagement lever unit are illustrated in a simplified manner (the same applies to the following drawings).
As shown in FIG. 15, the engagement / disengagement lever unit 180 includes a determination lever 194 (synchronous rotation unit) instead of the lever spring 94 of the first embodiment.

  The degree determining lever 194 is disposed below the lever body 85 and is integrally connected to the lower end portion of the lever bush 81. As a result, the degree determining lever 194 rotates in the clockwise direction around the first rotation axis O <b> 1 in synchronization with the rotation of the constant-speed lower car 60. A fork portion 195 divided into two forks is formed at one end portion of the degree determining lever 194. A lever pin 87 is disposed inside the fork portion 195. The inside of the fork portion 195 is formed larger than the lever pin 87 in the circumferential direction around the first rotation axis O1. As a result, the fork portion 195 can rotate the engagement / disengagement lever 84 including the lever pin 87 within a predetermined angle range with respect to the determination lever 194.

  The fork portion 195 contacts the lever pin 87 from the counterclockwise direction around the first rotation axis O1 by rotating around the first rotation axis O1 in the clockwise direction. As a result, the degree determining lever 194 rotates the engagement / disengagement lever 84 by pressing it clockwise around the first rotation axis O1. Further, the fork portion 195 restricts the counterclockwise rotation of the engagement / disengagement lever 84 relative to the degree determining lever 194 around the first rotation axis O1. That is, the fork portion 195 restricts the displacement of the engaging claw stone 86 engaged with the planetary gear 45 in the counterclockwise direction around the first rotation axis O1 with respect to the degree determining lever 194. As described above, the engaging claw stone 86 included in the engagement / disengagement lever 84 has a play in the clockwise direction around the first rotation axis O <b> 1 with respect to the determination lever 194.

  Further, the fork portion 195 restricts the clockwise rotation of the engagement / disengagement lever 84 relative to the degree determining lever 194 around the first rotation axis O1. That is, the fork portion 195 restricts the clockwise displacement around the first rotation axis O <b> 1 with respect to the degreeing lever 194 of the engaging claw stone 86 retracted from the rotation locus M of the planetary gear 45.

(Operation of the engagement / disengagement lever unit)
The operation of the engaging / disengaging lever unit 180 configured as described above will be described.
As in the first embodiment, at the stage where the planetary gear 45 and the engaging claw stone 86 are engaged, the tip of the stop tooth 45a of the planetary gear 45 is in contact with the engaging surface 86a of the engaging claw stone 86. Engage in a strongly pressed state.

  When the constant-force lower car 60 is rotated by the power from the constant-force spring 100, the lever bush 81 and the determining lever 194 of the engagement / disengagement lever unit 180 are rotated clockwise around the first rotation axis O1. When the positioning lever 194 rotates, the engaging claw stone 86 of the engagement / disengagement lever 84 is displaced clockwise around the first rotation axis O1 with play in the clockwise direction around the first rotation axis O1. To do. Thereby, the engagement / disengagement lever unit 180 can gradually disengage the engaging claw stone 86 from the planetary gear 45 so as to retract from the rotation locus M of the planetary gear 45. The tip of the stop tooth 45a moves counterclockwise with respect to the engagement surface 86a while sliding on the engagement surface 86a.

FIG. 16 is an operation explanatory view of the constant torque mechanism of the second embodiment, and is a plan view of the planetary car and the engaging / disengaging lever unit as viewed from above.
When the tip of the stop tooth 45a contacts the first end edge 86a1 of the engagement surface 86a, the force F applied between the stop tooth 45a and the engagement claw stone 86 approaches the clockwise direction around the first rotation axis O1. . As a result, the engagement / disengagement lever 84 is displaced in the clockwise direction around the first rotation axis O1 with respect to the degree determining lever 194 by play in the clockwise direction around the first rotation axis O1. Then, as shown in FIG. 16, when the tip of the stop tooth 45a exceeds the first end edge 86a1 of the engaging surface 86a, the engagement between the stop tooth 45a and the engaging claw stone 86 is released.

  As described above, the constant torque mechanism 130 according to the present embodiment rotates in the clockwise direction around the first rotation axis O1 in synchronization with the rotation of the constant force lower car 60 instead of the lever spring 94 according to the first embodiment. A determination lever 194 is provided each time. Further, the engaging claw stone 86 rotates in the clockwise direction around the first rotation axis O 1 as the degree determining lever 194 rotates, and can be engaged with and disengaged from the planetary gear 45. After engaging with the planetary gear 45 and restricting the rotation of the planetary gear 45, the planetary gear 45 is displaced with respect to the degree determining lever 194 and can be retracted from the rotation locus M of the planetary gear 45. Thereby, similarly to 1st Embodiment, the fluctuation | variation of the torque transmitted to the escapement 14 from the degree determination lever 194 via the constant force lower stage car 60 can be suppressed. Therefore, the fluctuation | variation of the torque transmitted to the escapement 14 can be suppressed.

  Further, the degree determining lever 194 includes a fork portion 195 for restricting the counterclockwise displacement of the engaging claw stone 86 engaged with the planetary gear 45 around the first rotation axis O1 with respect to the degree determining lever 194. According to this configuration, when the engaging claw stone 86 rotates around the first rotation axis O <b> 1 together with the degree determining lever 194 in the clockwise direction, the engaging claw stone 86 moves relative to the degree determining lever 194 with respect to the first rotation axis O <b> 1. It is possible to prevent the engaging claw stone 86 from being disengaged from the planetary gear 45 by being displaced counterclockwise. Therefore, the engagement / disengagement operation of the engaging claw stone 86 with respect to the planetary gear 45 can be stabilized.

  Further, the degree determining lever 194 includes a fork portion 195 that regulates the clockwise displacement of the engaging claw stone 86 retracted from the rotation locus M of the planetary gear 45 around the first rotation axis O1 with respect to the degree determining lever 194. . According to this configuration, when the engaging claw stone 86 is retracted from the rotation locus M of the planetary gear 45, the engaging claw stone 86 is displaced in the clockwise direction around the first rotation axis O1 with respect to the determination lever 194. Accordingly, it is possible to prevent the engaging claw stone 86 from reentering the rotation locus M of the planetary gear 45 and being unable to engage with it. Therefore, the engagement / disengagement operation of the engaging claw stone 86 with respect to the planetary gear 45 can be stabilized.

[Third Embodiment]
Next, a third embodiment will be described with reference to FIGS. 17 and 18. In the first embodiment, the engaging claw stone 86 is indirectly biased by the spring main body 97 of the lever spring 94 via the lever main body 85. On the other hand, the third embodiment is different from the first embodiment in that the engaging claw stone 86 is directly urged by the spring portion 294. The configurations other than those described below are the same as those in the first embodiment.

(Configuration of engagement / disengagement lever unit)
FIG. 17 is a plan view of the planetary vehicle and the engagement / disengagement lever unit according to the third embodiment as viewed from above.
As shown in FIG. 17, the engagement / disengagement lever unit 280 includes a base portion 284 (synchronous rotation portion) and a spring portion 294 instead of the engagement / disengagement lever 84 and the lever spring 94 of the first embodiment.

  The base 284 is formed in an annular shape surrounding the first rotation axis O1. The base 284 is extrapolated to the lever bush 81 and is integrally connected to the lever bush 81. Thereby, the base 284 rotates in the clockwise direction around the first rotation axis O <b> 1 in synchronization with the rotation of the constant-force lower car 60. An end edge 284a of the base portion 284 facing the engaging claw stone 86 when viewed from the top and bottom extends along the circumferential direction around the first rotation axis O1. The base 284 includes a protruding portion 284b that protrudes outward in the radial direction from the end edge 284a. The protruding portion 284b is adjacent to the end edge 284a in the clockwise direction around the first rotation axis O1. The engagement / disengagement lever unit 280 may not include the lever bush 81, and the base 284 may be directly connected to the constant-force lower-stage cylinder 61 of the constant-force lower-stage car 60.

  The spring portion 294 is a thin plate spring. The spring portion 294 extends along the counterclockwise direction around the first rotation axis O <b> 1 from the end portion of the base portion 284 on the engagement calculus 86 side. The spring portion 294 extends around the base portion 284 from the outside in the radial direction to a position facing the end edge 284a of the base portion 284 from the outside in the radial direction. An engaging claw stone 86 is attached to the distal end portion 294 a of the spring portion 294. Thereby, the spring part 294 is supporting the engaging claw stone 86 with respect to the base part 284 so that a displacement is possible. The engaging claw stone 86 protrudes from the tip end portion 294a of the spring portion 294 to the planetary gear 45 side (upward). The distal end portion 294 a of the spring portion 294 is in contact with the end edge 284 a of the base portion 284. As a result, the distal end portion 294a of the spring portion 294 can be displaced in the circumferential direction around the first rotation axis O1 by slidingly contacting the end edge 284a of the base portion 284.

  The distal end portion 294a of the spring portion 294 is disposed with a spacing in the counterclockwise direction around the first rotation axis O1 with respect to the protruding portion 284b of the base portion 284. Further, a location on the proximal end side of the distal end portion 294a in the spring portion 294 is in contact with the protruding portion 284b of the base portion 284 from the clockwise direction around the first rotation axis O1. Thereby, the front-end | tip part 294a of the spring part 294 can be rotated in a predetermined angle range with respect to the base part 284.

  The spring portion 294 is pressed by the protruding portion 284b of the base portion 284 and rotates clockwise around the first rotation axis O1 when the base portion 284 rotates around the first rotation axis O1 in the clockwise direction. Further, the distal end portion 294a of the spring portion 294 is restricted from being displaced counterclockwise around the first rotation axis O1 with respect to the base portion 284. In other words, the protruding portion 284 b of the base portion 284 regulates the displacement of the engaging claw stone 86 engaged with the planetary gear 45 in the counterclockwise direction around the first rotation axis O <b> 1 with respect to the base portion 284.

  Further, the spring portion 294 urges the engaging claw stone 86 counterclockwise around the first rotation axis O1 relative to the base portion 284, while energizing the engaging claw stone 86 around the first rotation axis O1 relative to the base portion 284. Displacement in the clockwise direction is allowed. In other words, the engaging claw stone 86 attached to the distal end portion 294a of the spring portion 294 has a play in the clockwise direction around the first rotation axis O1 with respect to the base portion 284. The spring portion 294 is restricted from rotating in the clockwise direction around the first rotation axis O1 with respect to the base portion 284 by the protruding portion 284b. That is, the protruding portion 284 b of the base portion 284 restricts the counterclockwise displacement of the engaging claw stone 86 retracted from the rotation locus M of the planetary gear 45 around the first rotation axis O <b> 1 with respect to the base portion 284.

(Operation of the engagement / disengagement lever unit)
The operation of the engaging / disengaging lever unit 280 configured as described above will be described.
As in the first embodiment, at the stage where the planetary gear 45 and the engaging claw stone 86 are engaged, the tip of the stop tooth 45a of the planetary gear 45 is in contact with the engaging surface 86a of the engaging claw stone 86. Engage in a strongly pressed state.

  When the constant force lower car 60 is rotated by the power from the constant force spring 100, the lever bush 81 and the base 284 are rotated clockwise around the first rotation axis O1. When the base portion 284 rotates, the engaging claw stone 86 supported by the spring portion 294 is displaced clockwise around the first rotation axis O1 with play in the clockwise direction around the first rotation axis O1. . Thereby, the engagement / disengagement lever unit 280 can be gradually detached from the planetary gear 45 so as to retract the engagement claw stone 86 from the rotation locus M of the planetary gear 45. The tip of the stop tooth 45a moves counterclockwise with respect to the engagement surface 86a while sliding on the engagement surface 86a.

FIG. 18 is an operation explanatory view of the constant torque mechanism of the third embodiment, and is a plan view of the planetary wheel and the engaging / disengaging lever unit as viewed from above.
When the tip of the stop tooth 45a contacts the first end edge 86a1 of the engagement surface 86a, the force F applied between the stop tooth 45a and the engagement claw stone 86 approaches the clockwise direction around the first rotation axis O1. . Thereby, the engaging claw stone 86 is displaced in the clockwise direction around the first rotation axis O1 with respect to the base 284 by the play in the clockwise direction around the first rotation axis O1. Then, as shown in FIG. 18, when the tip of the stop tooth 45a exceeds the first end edge 86a1 of the engagement surface 86a, the engagement between the stop tooth 45a and the engagement claw stone 86 is released.

  As described above, the constant torque mechanism 230 according to the present embodiment replaces the base portion 95 of the lever spring 94 according to the first embodiment with the timepiece around the first rotation axis O1 in synchronization with the rotation of the constant force lower stage wheel 60. The base 284 of the engaging / disengaging lever unit 280 rotating in the direction is provided. Further, the engaging claw stone 86 rotates in the clockwise direction around the first rotation axis O <b> 1 with the rotation of the base 284 and can be engaged with and disengaged from the planetary gear 45, and the planetary gear within the rotation locus M of the planetary gear 45. 45, the rotation of the planetary gear 45 is restricted, and then the planetary gear 45 is displaced with respect to the base 284 so that it can be retracted from the rotation locus M of the planetary gear 45. Thereby, similarly to 1st Embodiment, the fluctuation | variation of the torque transmitted to the escapement 14 from the base 284 via the constant force lower stage car 60 can be suppressed. Therefore, the fluctuation | variation of the torque transmitted to the escapement 14 can be suppressed.

  The constant torque mechanism 30 further includes a spring portion 294 that urges the engaging claw stone 86 directly toward the inside of the rotation locus M of the planetary gear 45. According to this configuration, the state in which the engaging claw stone 86 is retracted from the rotation locus M of the planetary gear 45 can be suppressed. Therefore, the engagement / disengagement operation of the engaging claw stone 86 with respect to the planetary gear 45 can be stabilized.

  Further, the engaging claw stone 86 is supported by the spring portion 294. According to this configuration, the number of parts can be reduced as compared with a configuration in which the engaging claw stone 86 is not supported by the spring portion.

  The base 284 of the engagement / disengagement lever unit 280 includes a protrusion 284b that restricts the counterclockwise displacement of the engaging claw stone 86 engaged with the planetary gear 45 about the first rotation axis O1 with respect to the base 284. . According to this configuration, when the engaging claw stone 86 rotates around the first rotation axis O1 in the clockwise direction together with the base 284, the engaging claw stone 86 counterclockwise around the first rotation axis O1 with respect to the base 284. It is possible to prevent the engaging claw stone 86 from being disengaged from the planetary gear 45 by being displaced in the direction. Therefore, the engagement / disengagement operation of the engaging claw stone 86 with respect to the planetary gear 45 can be stabilized.

  In addition, the base 284 of the engagement / disengagement lever unit 280 has a protrusion 284b that restricts the displacement of the engaging claw stone 86 retracted from the rotation locus M of the planetary gear 45 in the clockwise direction around the first rotation axis O1 with respect to the base 284. Prepare. According to this configuration, when the engaging claw stone 86 is retracted from the rotation locus M of the planetary gear 45, the engaging claw stone 86 is displaced in the clockwise direction around the first rotation axis O1 with respect to the base 284. Therefore, it is possible to prevent the engaging claw stone 86 from entering again and engaging with the rotation locus M of the planetary gear 45. Therefore, the engagement / disengagement operation of the engaging claw stone 86 with respect to the planetary gear 45 can be stabilized.

[Fourth Embodiment]
Next, a fourth embodiment will be described with reference to FIGS. 19 and 20. The fourth embodiment is different from the first embodiment in that the engaging claw stone 86 is provided so as to be swingable around a third rotation axis O3 different from the first rotation axis O1. The configurations other than those described below are the same as those in the first embodiment.

(Configuration of engagement / disengagement lever unit)
FIG. 19 is a plan view of the planetary vehicle and the engagement / disengagement lever unit according to the fourth embodiment as viewed from above.
As shown in FIG. 19, the engagement / disengagement lever unit 380 supports the engagement claw stone 86 so as to be swingable about the third rotation axis O3. The third rotation axis O3 is a position shifted in the in-plane direction of the ground plane 23 (see FIG. 4) with respect to the first rotation axis O1 and the second rotation axis O2. The engagement / disengagement lever unit 380 is fixedly supported on the upper end portion of the constant force lower stage cylinder 61 of the constant force lower stage wheel 60. The engaging / disengaging lever unit 380 includes an engaging / disengaging lever 384 and a lever spring 394 instead of the engaging / disengaging lever 84 and the lever spring 94 of the first embodiment.

  The lever spring 394 is fixedly supported by the lever bush 81. The lever spring 394 includes a base portion 395 (synchronous rotating portion) fixed to the lever bush 81 and a spring body 397 (spring portion) extending from the base portion 395.

  The base 395 is formed in an annular shape surrounding the first rotation axis O1. The base 395 is extrapolated to the lever bush 81 and is integrally connected to the lever bush 81. Thereby, the base 395 rotates in the clockwise direction around the first rotation axis O <b> 1 in synchronization with the rotation of the constant-force lower car 60. A lever pin 398 (first restricting portion) is protruded from the base portion 395. The lever pin 398 is provided between the engaging claw stone 86 and the first rotation axis O1 when viewed from the vertical direction. The lever pin 398 is formed in a cylindrical shape and protrudes upward from the base 395. The engagement / disengagement lever unit 380 may not include the lever bush 81, and the base 395 may be directly connected to the constant force lower stage cylinder 61 of the constant force lower stage wheel 60.

  The spring body 397 is a thin plate spring. The spring main body 397 extends along the counterclockwise direction from the end portion of the base portion 395 on the engaging claw stone 86 side. The spring body 397 wraps around the base portion 395 on the radially outer side and extends to a position facing the engaging claw stone 86 in the counterclockwise direction around the first rotation axis O1 when viewed from above and below.

  The engagement / disengagement lever 384 is provided to be rotatable about the third rotation axis O3 with respect to the base 395 of the lever spring 394. The third rotation axis O3 is disposed at a position fixed to the base 395 of the lever spring 394. Thereby, the engagement / disengagement lever 384 is provided so as to be able to revolve around the first rotation axis O1. In the illustrated example, the third rotation axis O <b> 3 is disposed outside the lever bush 398 in the radial direction of the lever bush 81. The engagement / disengagement lever 384 includes a lever main body 385 and an engaging claw stone 86 supported by the lever main body 385.

  The lever main body 385 is disposed below the planetary gear 45 of the planetary wheel 43 and above the base 395 of the lever spring 394. The lever body 385 is rotatably supported with respect to the base 395 by a lever rotation shaft 389 extending along the third rotation axis O3. An engaging claw stone 86 is attached to the lever main body 385. Thus, the engaging claw stone 86 is provided so as to be swingable around the third rotation axis O3. The engaging claw stone 86 protrudes from the lever body 385 to the planetary gear 45 side (upward). The engaging claw stone 86 is disposed on the outer side in the radial direction of the lever bush 81 with respect to the third rotation axis O3.

  The lever main body 385 is in contact with the lever pin 398 from the clockwise direction around the third rotation axis O3. As a result, the lever main body 385 is restricted by the lever pin 398 from counterclockwise displacement around the third rotation axis O3. That is, the lever spring 394 including the lever pin 398 regulates the displacement of the engaging claw stone 86 engaged with the planetary gear 45 in the counterclockwise direction around the third rotation axis O3 with respect to the base 395.

  The lever main body 385 is in contact with the tip of the spring main body 397 of the lever spring 394 from the counterclockwise direction around the third rotation axis O3. Accordingly, the lever main body 385 is urged counterclockwise around the third rotation axis O3 by the spring main body 397 with respect to the base 395 of the lever spring 394, and clockwise around the third rotation axis O3 relative to the base 395. Displacement is allowed. Thus, the engaging claw stone 86 attached to the lever main body 385 has a play in the clockwise direction around the third rotation axis O3 with respect to the base 395.

  Here, the third rotation axis O3 is disposed between the engaging claw stone 86 and the first rotation axis O1 in the radial direction of the lever bush 81. For this reason, the lever pin 398 of the lever spring 394 restricts the displacement of the engagement claw stone 86 engaged with the planetary gear 45 in the counterclockwise direction around the first rotation axis O1 with respect to the base 395. Further, the engaging claw stone 86 has a play in the clockwise direction around the first rotation axis O1 with respect to the constant-force lower car 60. The direction along the clockwise direction around the first rotation axis O1 is a direction parallel to the clockwise direction around the first rotation axis O1 or slightly inclined with respect to the clockwise direction around the first rotation axis O1. The same applies to the direction along the counterclockwise direction around the first rotation axis O1.

(Operation of the engagement / disengagement lever unit)
The operation of the engaging / disengaging lever unit 380 configured as described above will be described.
As in the first embodiment, at the stage where the planetary gear 45 and the engaging claw stone 86 are engaged, the tip of the stop tooth 45a of the planetary gear 45 is in contact with the engaging surface 86a of the engaging claw stone 86. Engage in a strongly pressed state.

  When the constant force lower wheel 60 is rotated by the power from the constant force spring 100, the base 395 of the lever spring 394 is rotated clockwise around the first rotation axis O1. When the base 395 rotates, the engagement / disengagement lever 384 revolves clockwise around the first rotation axis O1. Then, the engaging claw stone 86 included in the engagement / disengagement lever 384 is displaced in the clockwise direction around the first rotation axis O1 with a play in the clockwise direction around the first rotation axis O1. Thereby, the engagement / disengagement lever unit 380 can be gradually detached from the planetary gear 45 so as to retract the engagement claw stone 86 from the rotation locus M of the planetary gear 45. The tip of the stop tooth 45a moves counterclockwise with respect to the engagement surface 86a while sliding on the engagement surface 86a.

FIG. 20 is an operation explanatory view of the constant torque mechanism of the fourth embodiment, and is a plan view of the planetary wheel and the engaging / disengaging lever unit as viewed from above.
When the tip of the stop tooth 45a contacts the first end edge 86a1 of the engagement surface 86a, the force F applied between the stop tooth 45a and the engagement claw stone 86 approaches the clockwise direction around the first rotation axis O1. . Thereby, the engaging claw stone 86 is displaced in the clockwise direction around the first rotation axis O1 with respect to the base portion 395 of the lever spring 394 by play in the clockwise direction around the first rotation axis O1. As shown in FIG. 20, when the tip of the stop tooth 45a exceeds the first end edge 86a1 of the engagement surface 86a, the engagement between the stop tooth 45a and the engagement claw stone 86 is released.

  As described above, the constant torque mechanism 330 according to the present embodiment replaces the base portion 95 of the lever spring 94 according to the first embodiment with a timepiece around the first rotation axis O1 in synchronization with the rotation of the constant force lower wheel 60. A base 395 of a lever spring 394 that rotates in a direction is provided. Further, the engaging claw stone 86 rotates in the clockwise direction around the first rotation axis O 1 along with the rotation of the base 395 and can be engaged with and disengaged from the planetary gear 45, and the planetary gear within the rotation locus M of the planetary gear 45. 45, the rotation of the planetary gear 45 is restricted, and then the planetary gear 45 is displaced from the rotation locus M of the planetary gear 45 by being displaced with respect to the base 395. Thereby, similarly to 1st Embodiment, the fluctuation | variation of the torque transmitted to the escapement 14 from the base 395 via the constant power lower stage car 60 can be suppressed. Therefore, the fluctuation | variation of the torque transmitted to the escapement 14 can be suppressed.

  The constant torque mechanism 30 further includes a spring body 397 that indirectly biases the engaging claw stone 86 toward the inside of the rotation locus M via the lever body 385. According to this configuration, the state in which the engaging claw stone 86 is retracted from the rotation locus M of the planetary gear 45 can be suppressed. Therefore, the engagement / disengagement operation of the engaging claw stone 86 with respect to the planetary gear 45 can be stabilized.

  The base portion 395 of the lever spring 394 includes a lever pin 398 that restricts the displacement of the engaging claw stone 86 engaged with the planetary gear 45 in the counterclockwise direction around the first rotation axis O1 with respect to the base portion 395. . According to this configuration, when the engaging claw stone 86 rotates around the first rotation axis O1 with the base 395 in the clockwise direction, the engaging claw stone 86 counterclockwise around the first rotation axis O1 with respect to the base 395. It is possible to suppress the engagement claw stone 86 from being disengaged from the planetary gear 45 by being displaced in the direction along the direction. Therefore, the engagement / disengagement operation of the engaging claw stone 86 with respect to the planetary gear 45 can be stabilized.

  Further, the engaging claw stone 86 is provided so as to be swingable around a third rotation axis O3 different from the first rotation axis O1 and the second rotation axis O2 with respect to the base 395 of the lever spring 394. According to this configuration, since the rotation shaft of the engaging claw stone 86 is arranged on the third rotation axis O3 different from the first rotation axis O1, the design freedom of the constant torque mechanism 30 can be improved. Further, the direction of displacement when the engaging claw stone 86 is disengaged from the planetary gear 45 can be inclined with respect to the clockwise direction around the first rotation axis O1. Thus, the direction of the force F applied between the planetary gear 45 and the engaging claw stone 86 immediately before the separation of the planetary gear 45 and the engaging clawstone 86 is made to follow the direction of displacement of the engaging clawstone 86. Is possible. Therefore, the engaging claw stone 86 can be retreated more reliably from the rotation locus M of the planetary gear 45, and the engagement / disengagement operation of the engaging claw stone 86 with respect to the planetary gear 45 can be stabilized.

The present invention is not limited to the above-described embodiment described with reference to the drawings, and various modifications can be considered within the technical scope thereof.
For example, in the above embodiment, the fixed gear 31 is an external tooth type, but the present invention is not limited to this, and the fixed gear 31 may be an internal tooth type.

  Moreover, in the said embodiment, although the constant force upper stage wheel 40 and the constant force lower stage wheel 60 are arrange | positioned coaxially, it is not limited to this. A gear connected to the constant force upper stage car or the constant force lower stage car may be interposed between the constant force upper stage car and the constant force spring, or between the constant force lower stage car and the constant force spring.

  Moreover, in the said embodiment, although both the tooth tip of the stop tooth | gear 45a of the planetary gear 45 and the 1st end edge 86a1 of the engagement surface 86a of the engagement claw stone 86 are formed in the convex curve shape, It is not limited. The tips of the stop teeth of the planetary gear and the edge of the engaging surface of the engaging claw stone may not be formed in a convex curved surface shape. However, it is possible to reduce the contact surface pressure between the planetary gear and the engaging claw stone and to suppress the scraping of the planetary gear and the engaging clawstone. It is desirable that at least one of the edges of the surface is formed in a convex curved surface shape.

  Moreover, in the said embodiment, although the torque adjustment mechanism 110 is provided in the constant torque mechanism, the torque adjustment mechanism 110 does not need to be provided. In this case, the inner end portion 102 of the constant force spring 100 may be fixed to the constant force lower tube 61 in a state where a predetermined preload is applied to the constant force spring 100.

  In addition, in the range which does not deviate from the meaning of this invention, it is possible to replace suitably the component in above-mentioned embodiment with a well-known component, and you may combine each embodiment mentioned above suitably.

  DESCRIPTION OF SYMBOLS 1 ... Clock 10 ... Movement 11 ... Barrel wheel (power source) 14 ... Escapement machine 30, 130, 230, 330 ... Constant torque mechanism 45 ... Planetary gear 47 ... Carrier 60 ... Constant power lower stage car (constant power car) 85 ... Lever body (lever body) 86 ... engaging claw stone (engaging claw) 95 ... base (synchronous rotating part) 96 ... arm (first regulating part) 97 ... spring body (spring part) 100 ... constant force spring 194 ... degree Decisive lever (synchronous rotating part) 195 ... Fork part (first restricting part, second restricting part) 284 ... Base part (synchronous rotating part) 284b ... Protruding part (first restricting part, second restricting part) 294 ... Spring part 385 ... Lever body (lever body) 395 ... Base (synchronous rotating part) 397 ... Spring body (spring part) 398 ... Lever pin (first restricting part) O1 ... First rotating axis (first axis) O2 ... Second rotating axis ( Second axis) 3 ... third rotary axis (third axis)

Claims (11)

A carrier that rotates about a first axis by power from a power source;
A planetary gear supported by the carrier so as to be capable of rotating, revolving around the first axis while revolving around the second axis;
A constant force spring whose power is replenished by rotation of the carrier;
A constant force wheel that is rotated by the power from the constant force spring and transmits the power of the constant force spring to the escapement;
A synchronous rotating part that rotates in the first direction around the first axis in synchronization with the rotation of the constant force wheel;
The planetary gear rotates in the first direction along with the rotation of the synchronous rotation unit and can be engaged with and disengaged from the planetary gear. The planetary gear engages with the planetary gear within the rotation locus of the planetary gear and restricts the rotation of the planetary gear. Then, an engaging claw that can be displaced with respect to the synchronous rotating portion and retracted from the rotation locus,
A constant torque mechanism comprising: The engaging claw is displaced in a direction along the first direction with respect to the synchronous rotating part and retracts from the rotation locus.
The constant torque mechanism according to claim 1. A spring portion that urges the engaging claw directly or indirectly toward the inside of the rotation locus;
The constant torque mechanism according to claim 1, wherein the constant torque mechanism is provided. The engaging claw is rotatably supported with respect to the synchronous rotating part, and further includes a lever body provided separately from the spring part.
The constant torque mechanism according to claim 3. The engaging claw is supported by the spring portion,
The constant torque mechanism according to claim 3. The synchronous rotating portion includes a first restricting portion that restricts displacement of the engaging claw engaged with the planetary gear in a direction along a second direction around the first axis with respect to the synchronous rotating portion.
The constant torque mechanism according to any one of claims 1 to 5, wherein: The synchronous rotating part includes a second restricting part that restricts displacement of the engaging claw retracted from the rotation locus in a direction along the first direction with respect to the synchronous rotating part.
The constant torque mechanism according to any one of claims 1 to 6, wherein the constant torque mechanism is provided. The engaging claw is provided so as to be swingable around the first axis with respect to the synchronous rotating portion.
The constant torque mechanism according to any one of claims 1 to 7, wherein the constant torque mechanism is provided. The engaging claw is provided so as to be swingable around a third axis different from the first axis and the second axis with respect to the synchronous rotating part.
The constant torque mechanism according to any one of claims 1 to 7, wherein the constant torque mechanism is provided.   A timepiece movement comprising the constant torque mechanism according to any one of claims 1 to 9.   A timepiece comprising the timepiece movement according to claim 10.

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