JP2014174118A - Torque adjustment device, movement, and mechanical timepiece - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a torque adjustment device which can grasp the winding-up amount of a sub-spring and which is excellent in volumetric efficiency.SOLUTION: A torque adjustment device 6 includes: a sub-spring 65; an output gear 66 to which an inner-peripheral end part of the sub-spring 65 is connected and which is connected to an escapement 50; a ratchet wheel 64 to which an outer-peripheral end part of the sub-spring 65 is connected and which intermittently rotates in a manner relative to the output gear 66; a winding-up amount adjustment mechanism 80 adjusting the winding-up amount of the sub-spring 65; and a planetary gear mechanism 90 connected to the ratchet wheel 64, a barrel wheel 10, and the winding-up amount adjustment mechanism 80. The winding-up amount adjustment mechanism 80 includes: a winding-up amount maintenance part for maintaining the winding-up amount of the sub-spring 65; and the winding-up amount display part for displaying the winding-up amount of the sub-spring 65.

Description

  The present invention relates to a torque adjusting device for a movement and a mechanical timepiece.

  In the mechanical timepiece, when the operating torque transmitted from the barrel to the escapement fluctuates according to the unwinding of the mainspring of the barrel, the balance angle of the balance changes and the rate of the watch changes. Therefore, a constant torque mechanism (torque adjustment device) in which a sub-spring (torque adjustment mainspring) is arranged between the barrel and the escapement has been proposed in order to suppress fluctuations in the operating torque transmitted to the escapement. . The constant torque mechanism is roughly classified into a method using a flywheel (see, for example, Patent Document 1) and a method involving periodic control by a cam or the like (see, for example, Patent Document 2).

  The constant load device (torque adjustment device) of the invention of Patent Document 2 will be described using terms and symbols used in Patent Document 2. The constant load device of the invention of Patent Document 2 includes a third spring (third wheel) 9 and a spiral spring (torque adjusting mainspring) 18. The outer peripheral end of the spiral spring 18 is connected to the stop wheel 22, and the inner peripheral end of the spiral spring 18 is connected to the adjustment member 20. The stop wheel 22 is fixed to the main shaft (third true) 8 of the third moving element 9, and the adjusting member 20 is rotatable relative to the main shaft 8 of the third moving element 9. The adjusting member 20 supports the second member (third gear) 10 by friction.

  The third moving element 9 is connected to the first second moving element (fourth wheel) 13, and the first second moving element 13 is connected to the escape wheel 2 and the second second moving element 25. A cam 26 is fixed to the main shaft of the second second moving element 25, and a control pawl 31 is disposed so as to sandwich the outer periphery of the cam 26. A second fork 32 extends from the control pawl 31 toward the stop wheel 22. The tip of the second fork 32 is locked to a sawtooth formed on the outer periphery of the stop wheel 22.

  As the spiral spring 18 is unwound, an operating torque is applied to the second member (third gear) 10 supported by the adjusting member 20, and the mechanical timepiece operates. Along with the operation of the mechanical timepiece, the cam 26 rotates together with the second second moving element 25. The rotation of the cam 26 causes the control pawl 31 and the second fork 32 to reciprocate, and the second fork 32 repeats locking and releasing of the stop wheel 22 at a predetermined cycle. While the lock is released, the stop wheel 22 winds up the spiral spring 18 by a certain amount by the regular winding torque transmitted from the mainspring of the barrel 1. As described above, the spiral spring 18 of the constant load device returns to a predetermined winding amount every predetermined period. By operating the mechanical timepiece by the spiral spring 18, the rate of the mechanical timepiece is stabilized.

  FIG. 11 is a graph showing the relationship between the mainspring torque and the rate. As shown in FIG. 11, since the rate of the mechanical timepiece changes according to the mainspring torque, the setting of the amount of winding of the auxiliary mainspring is important in the mechanical timepiece equipped with the torque adjusting device. Therefore, in the constant load device according to the invention of Patent Document 2, the load state (winding amount) of the spiral spring 18 can be adjusted. Specifically, the adjustment member 20 includes a support surface 41, and a tooth portion is formed on the outer periphery of the support surface 41. A control mover 42 is disposed next to the adjusting member 20, and a toothed pinion 44 that meshes with the outer peripheral tooth portion of the support surface 41 is formed on the control mover 42.

  The load state of the spiral spring 18 is adjusted while the mechanical timepiece is stopped. First, the control moving element 42 is pressed and moved in the axial direction, and the control moving element 42 is engaged with the adjusting member 20. In this state, a hoisting amount adjusting torque is applied to the control moving element 42, and the adjusting member 20 is rotated together with the control moving element 42. While the mechanical timepiece is stopped, the second member (third gear) 10 is also stopped. However, since the second member 10 is supported simply by friction with respect to the adjusting member 20, the second member 10 and A slip occurs between the adjusting member 20 and the adjusting member 20. Therefore, the adjustment member 20 is rotated by the applied winding amount adjustment torque. Further, since the stop wheel 22 is also stopped while the mechanical timepiece is stopped, the spiral spring 18 is wound up between the adjustment member 20 and the stop wheel 22. Thereby, the load state of the spiral spring 18 is adjusted.

  On the other hand, the adjusting member 20 also rotates during the operation of the mechanical timepiece. Here, when the control mover 42 rotates together with the adjusting member 20, energy loss of the mainspring occurs. Therefore, the constant load device of the invention of Patent Document 2 includes a mechanism for releasing the engagement between the adjustment member 20 and the control moving element 42. Specifically, the control moving element 42 is movable in the axial direction, and is biased by a helical spring 48 in a direction away from meshing with the adjusting member 20. Then, after adjusting the load state of the spiral spring 18, the pressing of the control moving element 42 is released, and the meshing between the control moving element 42 and the adjusting member 20 is released. Thereby, even if the adjustment member 20 rotates during the operation of the mechanical timepiece, the control mover 42 does not rotate, and energy loss of the mainspring is avoided.

British Patent No. 573942 Special table 2012-503187 gazette

  However, in the invention of Patent Document 2, it is difficult to set the spiral spring 18 to a predetermined winding amount because the operator knows how to grasp the winding amount of the spiral spring 18 by the control moving element 42.

  In addition, since the swing angle of the balance with hairspring increases as the amount of winding of the spiral spring 18 increases, a method of setting the spiral spring 18 to a predetermined winding amount while measuring the swing angle of the balance is conceivable. On the other hand, however, if there is a problem with the train wheel or the escapement, the swing angle of the balance is reduced. Therefore, if the spiral spring 18 is wound more than a predetermined value in a state where there is a problem with the train wheel or the escapement, the balance of the balance with the balance is equivalent to the balance of the balance when the spiral spring 18 is wound up to the predetermined value. There may be cases. Therefore, even if the balance angle of the balance with hairspring is measured, it is difficult to set the spiral spring 18 to a predetermined winding amount, and it is also difficult to find defects in the train wheel and the escapement.

  In the invention of Patent Document 2, a mechanism for releasing the engagement between the adjusting member 20 and the control moving element 42 is necessary, and the arrangement space (the moving space of the control moving element 42 and the arrangement space of the helical spring 48) is ensured. Therefore, volume efficiency is inferior.

  The present invention has been made in view of the above problems, and has an object to provide a torque adjusting device that can grasp the amount of winding of the torque adjusting mainspring and is excellent in volumetric efficiency. To do.

(1) A torque adjusting device including a torque adjusting mainspring incorporated in a train wheel from a barrel complete to a escapement of a mechanical timepiece, wherein a first end of the torque adjusting mainspring is connected, An escapement-side torque adjustment vehicle connected to the escapement-side wheel train from the torque adjustment mainspring and a second end of the torque adjustment mainspring are connected, and from the torque adjustment mainspring. A barrel for adjusting the torque of the barrel for torque adjustment, which is connected to the train wheel on the side of the barrel for rotation and intermittently rotates relative to the torque adjustment vehicle for escapement, and a winding for adjusting the amount of winding of the mainspring for torque adjustment. An upper amount adjusting mechanism, and a power switching mechanism which is incorporated in the barrel wheel side wheel train or the escapement side wheel train and coupled to the hoisting amount adjusting mechanism. The torque adjustment spring The power switching mechanism in the case where it is incorporated in the barrel wheel side wheel train, and a hoisting amount holding unit for holding the hoisting amount of the torque adjusting spring and a hoisting amount display unit for displaying the hoisting amount of the torque adjusting spring. The power switching mechanism when coupled to the barrel wheel, the barrel wheel side torque adjustment vehicle, and the hoisting amount adjustment mechanism and incorporated in the escapement side wheel train includes the escapement and the escapement. A torque adjusting device coupled to the side torque adjusting vehicle and the hoisting amount adjusting mechanism.

According to this configuration, the winding amount holding unit that holds the winding amount of the torque adjustment spring and the winding amount display unit that displays the winding amount are provided, so that the winding amount of the torque adjustment spring can be objectively determined. I can grasp it. Accordingly, the torque adjusting mainspring can be set to a predetermined winding amount. Moreover, if the balance of the balance of the balance with hairspring is measured, it is possible to surely find a malfunction of the train wheel or the escapement.
In addition, since it has a hoisting amount holding portion for holding the hoisting amount of the torque adjusting mainspring and a power switching mechanism, it transmits the operating torque or the constant hoisting torque during the operation of the mechanical timepiece, and the mechanical timepiece. It is possible to automatically switch the transmission of the hoisting amount adjusting torque from the hoisting amount adjusting mechanism during the stop of the motor. Therefore, a mechanism for releasing the connection between the hoisting amount adjusting mechanism and the train wheel is unnecessary, and the volume efficiency is excellent.

(2) The hoisting amount adjusting mechanism includes a hoisting amount adjusting wheel for adjusting the hoisting amount of the torque adjusting mainspring, and the hoisting amount holding unit applies a friction torque to the hoisting amount adjusting wheel. It is desirable to provide a braking spring.
(3) The hoisting amount adjusting mechanism includes a hoisting amount adjusting wheel that adjusts the hoisting amount of the torque adjusting mainspring, and the hoisting amount holding portion is a brake that restricts rotation of the hoisting amount adjusting wheel. It is desirable to have a jumper.
According to these hoisting amount holding portions, it is possible to reliably hold the hoisting amount of the torque adjusting spring and to reduce the manufacturing cost.

(4) The power switching mechanism is preferably a planetary gear mechanism.
(5) The power switching mechanism may be a differential device.
According to these power switching mechanisms, transmission of operating torque or regular hoisting torque during operation of the mechanical timepiece and transmission of hoisting amount adjustment torque from the hoisting amount adjustment mechanism while the mechanical timepiece is stopped. Can be switched automatically. Moreover, it is excellent in volume efficiency and can reduce manufacturing cost.

(6) It is desirable to include a torque adjustment escapement that interlocks with the escapement and intermittently relatively rotates the barrel wheel side torque adjustment vehicle with respect to the escapement side torque adjustment vehicle.
(7) The flywheel side torque adjustment vehicle may include a flywheel having a larger moment of inertia than the escapement side torque adjustment vehicle.
According to these configurations, the barrel wheel side torque adjustment vehicle can be intermittently relatively rotated with a fixed period with respect to the escapement side torque adjustment vehicle.

(8) A movement including the torque adjusting device described above.
(9) A mechanical timepiece including the torque adjusting device described above.
Since the torque adjusting device described above can grasp the amount of winding of the torque adjusting mainspring, it is possible to provide a highly accurate movement and mechanical timepiece set at a predetermined rate.
Moreover, since the torque adjusting device described above is excellent in volumetric efficiency, a small movement and a mechanical timepiece can be provided.

According to the torque adjusting device described above, the winding amount holding unit for holding the winding amount of the torque adjusting spring and the winding amount display unit for displaying the winding amount are provided. It can be grasped objectively. Accordingly, the torque adjusting mainspring can be set to a predetermined winding amount. Moreover, if the balance of the balance of the balance with hairspring is measured, it is possible to surely find a malfunction of the train wheel or the escapement.
In addition, since it has a hoisting amount holding portion for holding the hoisting amount of the torque adjusting mainspring and a power switching mechanism, it transmits the operating torque or the constant hoisting torque during the operation of the mechanical timepiece, and the mechanical timepiece. It is possible to automatically switch the transmission of the hoisting amount adjusting torque from the hoisting amount adjusting mechanism during the stop of the motor. Therefore, a mechanism for releasing the connection between the hoisting amount adjusting mechanism and the train wheel is unnecessary, and the volume efficiency is excellent.

2 is a plan view of the back side of the mechanical timepiece 1. FIG. It is explanatory drawing of the torque adjustment apparatus 6 in 1st Embodiment, and is a top view of the state except the wheel train receiver on the front side of the movement 5. FIG. It is explanatory drawing of the torque adjustment apparatus 6 in 1st Embodiment, and is side surface sectional drawing in the A1-OPQ-A2 line | wire of FIG. It is explanatory drawing of the torque adjustment apparatus main body 60, and is side surface sectional drawing in the B1-OQ-B2 line | wire of FIG. It is explanatory drawing of the winding amount adjustment mechanism 80, and is side surface sectional drawing in the C1-C1 line | wire of FIG. It is explanatory drawing of the planetary gear mechanism 90, and is side surface sectional drawing in the C1-C2 line | wire of FIG. It is explanatory drawing of the differential gear in the 1st modification of 1st Embodiment, and is side surface sectional drawing in the part corresponded to the C1-C1 line | wire of FIG. It is explanatory drawing of the winding amount adjustment mechanism 180 in the 2nd modification of 1st Embodiment, (a) is side surface sectional drawing in the part corresponded to the C1-C1 line | wire of FIG. (B) is a top view of winding amount holding | maintenance part 80b. It is explanatory drawing of the torque adjustment apparatus 206 in 2nd Embodiment, and is side surface sectional drawing in the part corresponded to the A1-OP-A2 line | wire of FIG. It is explanatory drawing of the torque adjustment apparatus 306 in 3rd Embodiment, and is a top view of the state which remove | excluded the wheel train receiver on the front side of the movement. It is a graph which shows the relationship between a mainspring torque and a rate.

Embodiments of the present invention will be described below with reference to the accompanying drawings.
(clock)
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 make a finished product is called “complete” of the watch. Of the two sides of the base plate constituting the watch substrate, the glass case side of the watch case, that is, the dial plate side is called the “back side” or “glass side” or “dial side” of the movement. . Of the two sides of the main plate, the side with the back cover of the watch case, that is, the side opposite to the dial is referred to as the “front side” or “back side” of the movement.

  FIG. 1 is a plan view of the complete back side of the mechanical timepiece 1. The complete of the mechanical timepiece 1 is provided with a dial 2 including a scale 3 indicating information relating to time. The complete of the mechanical timepiece 1 includes a hand 4 including an hour hand 4a indicating the hour, a minute hand 4b indicating the minute, and a second hand 4c indicating the second.

  FIG. 2 is an explanatory diagram of the torque adjustment device 6 in the first embodiment, and is a plan view of a state in which a wheel train receiver on the front side of the movement 5 is removed. 3 is a side cross-sectional view taken along line A1-OPQ-A2 in FIG. In FIG. 2 and FIG. 3, some of the timepiece components constituting the movement 5 are omitted for easy viewing of the drawings. As shown in FIG. 2, the movement 5 of the mechanical timepiece includes a mainspring (not shown) which is disposed inside the barrel wheel 10 and serves as a power source, and a wheel train (the barrel wheel 10, which transmits the power of the mainspring). (Second wheel 20, third wheel 30, fourth wheel 40), escapement 50 (gear wheel 51, ankle 56) that operates the train wheel intermittently, and escapement 50 is operated periodically. And a speed governor (the balance 58). As shown in FIG. 3, each of these members is disposed between a base plate 8 constituting the substrate and a train wheel bridge 9 disposed to face the base plate 8.

The main spring is arranged inside the barrel of the barrel 10.
As shown in FIG. 3, the barrel complete 10 includes a barrel gear 14 on the outer periphery of the barrel. The center wheel 20 includes a second pinion 22 that meshes with the barrel gear 14 and a second gear 24 that is linked to the second pinion 22. The third wheel & pinion 30 includes a third pinion 32 that meshes with the second pinion 24 and a third pinion gear 34 that interlocks with the third pinion 32. The fourth wheel & pinion 40 includes a fourth pinion 42 that meshes with the third pinion 34, and a fourth gear 44 that interlocks with the fourth pinion 42. The barrel complete wheel 10 to the fourth wheel & pinion 40 constitute a speed increasing wheel train that increases the rotational speed while transmitting the power of the mainspring. The fourth wheel & pinion 40 corresponds to the second hand 4c in FIG.

  As shown in FIG. 3, the escape wheel 51 includes an escape wheel 52 that meshes with the fourth gear 44 and an escape wheel 54 that is linked to the escape wheel 52. As shown in FIG. 2, the ankle 56 includes a pair of pallet stones 57 that engage with the teeth of the escape wheel 54. The balance with hairspring 58 includes a hairspring 59.

  As shown in FIG. 2, the escape wheel 51 is temporarily stopped in a state where one pallet 57 of the ankle 56 is engaged with the teeth of the escape wheel 54. From this state, when the balance with the balance spring 59 is rotated, the balance wheel fixed to the balance spring rotates the ankle 56. As a result, one pawl 57 of the ankle 56 is disengaged from the escape gear 54, and the escape gear 54 rotates to a position where it engages with the other pawl 57 of the ankle 56. Due to the intermittent rotational movement of the escape gear 54, the escapement 50 operates the train wheel intermittently. Further, since the balance with hairspring 58 periodically oscillates, the speed governor operates the escapement 50 periodically.

  As described above, when one of the pallet stones 57 of the ankle 56 is disengaged from the escape wheel 54, the escape wheel 54 pushes the pawl 57 so that the ankle 56 swings up the balance 58. As a result, an operating torque is applied from the escape wheel 54 to the balance 58, and the rotation vibration of the balance 58 is maintained.

(First embodiment, torque adjustment device 6)
As shown in FIG. 3, when the operating torque transmitted from the barrel complete 10 to the escapement 50 fluctuates in accordance with the unwinding of the mainspring, the balance angle of the balance is changed and the rate of the timepiece is changed. In order to suppress such fluctuations in the operating torque, the movement 5 includes a torque adjustment device 6 in which a sub-spring (torque for adjustment) 65 is incorporated in a train wheel from the barrel complete 10 to the escapement 50.

  The torque adjustment device 6 includes a torque adjustment device main body 60 including the auxiliary spring 65, a torque adjustment escapement 70 that controls the operation of the torque adjustment device main body 60, and a winding amount that adjusts the amount of winding of the auxiliary spring 65. An adjustment mechanism 80 and a power switching mechanism (planetary gear mechanism 90) that is incorporated in the train wheel and connected to the hoisting amount adjustment mechanism 80 are provided. In the first embodiment, the torque adjusting device main body 60 is incorporated in the fourth wheel & pinion 40 and the power switching mechanism is incorporated in the third wheel & pinion 30.

(Torque adjustment device main body 60)
FIG. 4 is an explanatory view of the torque adjusting device main body 60, and is a side sectional view taken along line B1-OQ-B2 of FIG. In FIG. 4, the same hatching is given to the member which rotates integrally. As shown in FIG. 4, the torque adjusting device main body 60 includes a sub-spring (torque adjusting mainspring) 65 and a toothed wheel (cursor wheel side torque adjustment) to which the outer peripheral end (first end) of the sub-spring 65 is connected. Vehicle) 64 and an output gear (escapement side torque adjustment vehicle) 66 to which the inner peripheral end (second end) of the auxiliary spring 65 is connected.

The claw wheel 64 is fixed to the fourth pinion 42 and is rotatable with the fourth pinion 42 relative to the true 41 of the fourth wheel 40. A pawl is formed on the outer periphery of the pawl wheel 64.
The output gear 66 is fixed to the true 41 of the fourth wheel 40 and functions as the fourth gear 44 described above.
The auxiliary spring 65 has an outer peripheral end fixed to the pinion wheel 64 via a first fixing member 64 f and an inner peripheral end fixed to the true 41 of the fourth wheel & pinion 40 via a second fixing member 61. As a result, the inner peripheral end of the auxiliary spring 65 is connected to the output gear 66.

(Torque adjustment escapement 70)
As shown in FIG. 2, the torque adjusting escapement 70 includes a cam 72 interlocked with the escape wheel 51, a cam follower 74 interlocked with the cam 72, a lever 76 coupled to the cam follower 74, and a lever 76. A pair of pawls 77 which are fixed and engage with pawls of the pawl wheel 64 are provided.
The cam 72 is fixed coaxially with the true of the escape wheel & pinion 51. The cam 72 is formed in a substantially polygonal shape in plan view. In particular, the cam 72 is formed in a substantially polygonal shape (in the present embodiment, a substantially triangular shape) having an odd number of vertices.

The cam follower 74 includes a pair of forks that sandwich the cam 72 in plan view. The ends of the pair of forks are arranged on the outer periphery of the cam 72 so as to sandwich the center of the cam 72. The distance between the pair of forks is smaller than twice the distance from the center of the cam 72 to the outer peripheral vertex. The cam follower 74 is formed to be rotatable around a shaft 75 that is spaced from the true side of the escape wheel & pinion 51.
The lever 76 is connected to the cam follower 74 and is formed to be rotatable around the shaft 75 together with the cam follower 74. The lever 76 includes a pair of arms extending radially across the shaft 75 in plan view. A pawl 77 is fixed to the tip of each of the pair of arms. The pawl 77 is formed to be engageable with the pawl of the pawl wheel 64.

Operations of the torque adjusting device main body 60 and the torque adjusting escapement 70 will be described.
The auxiliary mainspring 65 is wound up by a predetermined amount in advance. When one pawl 77 of the lever 76 is engaged with the pawl wheel 64, the rotation of the pawl wheel 64 is temporarily stopped. In this state, the output gear 66 rotates as the auxiliary spring 65 is unwound, so that operating torque is supplied from the auxiliary spring 65 to the escapement 50 via the output gear 66. As a result, the mechanical timepiece operates.

  As the escape wheel 50 of the escapement 50 rotates, the cam 72 rotates. As the cam 72 rotates, the cam follower 74 reciprocates around the shaft 75. When the lever 76 rotates around the shaft 75 in conjunction with the cam follower 74, one of the pawls 77 of the lever 76 is detached from the pawl wheel 64, and the pawl wheel 64 becomes rotatable. Since the regular winding torque is transmitted from the main spring to the pinion wheel 64, the pinion wheel 64 is rotated by the regular winding torque, and the auxiliary spring 65 is wound up with the output gear 66. Thereafter, the auxiliary mainspring 65 is wound up by a predetermined amount until the other pawl stone 77 of the lever 76 is engaged with the pawl wheel 64 and the rotation of the pawl wheel 64 is stopped. This predetermined amount is set to an amount that can be unwound before the auxiliary mainspring 65 is wound up again.

  In this way, since the auxiliary mainspring 65 is periodically wound up by a predetermined amount, the auxiliary mainspring 65 is held at a substantially constant amount of winding. Since the sub-spring 65 supplies substantially constant operating torque to the escapement 50 and the speed governor (balance 58), the speed governor can operate the escapement 50 at a constant cycle. Thereby, the accuracy of the timepiece can be improved. Moreover, since the escapement 50 operates at a constant cycle, the torque adjusting escapement 70 also operates at a constant cycle in conjunction with the escapement 50. As a result, it becomes possible to wind up the auxiliary mainspring 65 at a constant cycle, and the accuracy of the timepiece can be further improved.

  When the mainspring is completely unwound, it is impossible to wind up the auxiliary mainspring 65. Even in this case, it is desirable to provide a mechanism that regulates the amount of unwinding of the mainspring 65 so that the mainspring 65 cannot be completely unwound. As an example of the mechanism, a mechanism for restricting relative rotation between the pawl wheel 64 and the output gear 66 can be considered. However, this mechanism is formed so as to allow relative rotation between the pawl wheel 64 and the output gear 66 when adjusting the amount of winding of the auxiliary mainspring 65 described later.

(Winding amount adjusting mechanism 80)
FIG. 11 is a graph showing the relationship between the mainspring torque and the rate. In general, the rate of the mechanical timepiece changes according to the mainspring torque, and there is an attitude difference in the rate of the mechanical timepiece. In the posture with the dial faced up and down (horizontal posture), the rate change with respect to the mainspring torque is moderate, but in the standing posture with the crown facing up and down (vertical posture), the rate change with respect to the mainspring torque becomes large. In FIG. 11, the rate of the horizontal posture and the vertical posture are equal when the mainspring torque is in the vicinity of the R portion, but the rate of vertical posture is greatly reduced as compared with the horizontal posture when the mainspring torque is near the S portion.

  As shown in FIG. 3, in the torque adjustment device 6 including the auxiliary mainspring 65, the operating torque (mainspring torque) becomes substantially constant because the auxiliary mainspring 65 is held at a substantially constant winding amount. Here, in order to keep the posture difference within a predetermined range, it is important to set the auxiliary mainspring 65 to a predetermined amount of winding so that a predetermined operating torque is supplied from the auxiliary mainspring 65. When the mechanical timepiece is manufactured, the auxiliary mainspring 65 is set to a predetermined winding amount at the time of manufacturing by incorporating the auxiliary mainspring 65 between the two in the state where the hour wheel 64 and the output gear 66 are arranged at a predetermined phase difference. Although it is possible, the work is difficult. Therefore, the torque adjusting device 6 includes a hoisting amount adjusting mechanism 80 that adjusts the hoisting amount of the auxiliary mainspring 65 after manufacturing the mechanical timepiece.

  FIG. 5 is an explanatory view of the hoisting amount adjusting mechanism 80, and is a side cross-sectional view taken along line C1-C1 of FIG. The winding amount adjustment mechanism 80 shown in FIG. 5 has a winding amount adjustment unit 80a (a winding amount adjustment screw 81, a first winding amount adjustment wheel 82, a second winding amount) to which a winding amount adjustment torque is input and transmitted. An amount adjusting wheel 84), a winding amount holding portion 80b (braking spring 85) for holding the winding amount of the sub-spring, and a winding amount display portion 80c (winding amount display needle 86, which displays the winding amount of the sub-spring) Winding amount display scale 87).

  The hoisting amount adjusting unit 80 a includes a hoisting amount adjusting screw 81, a first hoisting amount adjusting wheel 82, and a second hoisting amount adjusting wheel 84. On the upper surface of the winding amount adjustment screw 81, a groove portion that engages with the winding amount adjustment tool is formed. The hoisting amount adjusting screw 81 is fixed to the first hoisting amount adjusting wheel 82, and the first hoisting amount adjusting wheel 82 is engaged with the second hoisting amount adjusting wheel 84. The second winding amount adjustment wheel 84 is connected to the planetary gear mechanism 90 incorporated in the third wheel & pinion 30. The hoisting amount adjusting screw 81, the first hoisting amount adjusting wheel 82 and the second hoisting amount adjusting wheel 84 are arranged between the wheel train receiver 9 and the hoisting amount adjusting wheel train receiver 89.

  The hoisting amount holding unit 80 b includes a braking spring 85. The inner peripheral portion of the brake spring 85 is fixed coaxially with the second hoist adjustment wheel 84. The outer peripheral portion of the braking spring 85 is formed so as to be separated from the second hoist adjustment wheel 84 in the axial direction. The brake spring 85 is elastically deformed in the axial direction as the train wheel bridge 9 presses the outer periphery of the brake spring 85 in the axial direction. As a result, the friction torque acts on the second hoist adjustment wheel 84 from the train wheel bridge 9 via the brake spring 85, and the rotation of the second hoist adjustment wheel 84 is restricted, so that the mainspring is wound up. The amount is retained. If a winding amount adjustment torque that exceeds the friction torque is applied, the second winding amount adjustment wheel 84 rotates, so that the amount of winding of the sub-spring can be adjusted.

  The winding amount display portion 80c includes a winding amount display needle 86 and a winding amount display scale 87. The hoisting amount display needle 86 is fixed to the shaft of the second hoisting amount adjusting wheel 84 on the base end side, is formed in a needle shape on the distal end side, and is disposed along the surface of the train wheel bridge 9. A winding amount display scale 87 is formed on the surface of the train wheel bridge 9. As shown in FIG. 2, the winding amount display scale 87 is arranged along the trajectory at the tip of the winding amount display needle 86. The winding amount display scale 87 includes a large scale formed at a predetermined angular interval and a small scale formed between adjacent large scales. 0 is displayed on the reference large scale serving as the reference position. When viewed from the reference large scale, +1, +2,... Are sequentially displayed on the large scale on one side in the circumferential direction, and −1, −2,... Are sequentially displayed on the large scale on the other side in the circumferential direction. . The hoisting amount display unit 80c may be replaced by the hoisting amount adjusting screw 81 of the hoisting amount adjusting unit 80a. Even in this case, the amount of winding of the auxiliary spring can be displayed by the extending direction of the groove on the upper surface of the winding amount adjusting screw 81.

  Returning to FIG. 5, a method of adjusting the amount of winding of the auxiliary spring by the winding amount adjustment mechanism 80 will be described. Adjustment of the winding amount of the auxiliary spring is performed before the mechanical watch is shipped or during maintenance, while the mechanical watch is stopped. First, the hoisting amount adjusting tool is engaged with the groove of the hoisting amount adjusting screw 81, the hoisting amount adjusting torque is applied to the hoisting amount adjusting screw 81, and the hoisting amount adjusting screw 81 is rotated. The hoisting amount adjusting torque is transmitted from the hoisting amount adjusting screw 81 to the first hoisting amount adjusting wheel 82 and the second hoisting amount adjusting wheel 84 to rotate the second hoisting amount adjusting wheel 84. Further, the hoisting amount adjusting torque is transmitted from the second hoisting amount adjusting wheel 84 to the pinion wheel via the planetary gear mechanism 90, and the pinion wheel rotates to wind up the auxiliary mainspring. Then, by adjusting the number of rotations of the hoisting amount adjusting screw 81 by the hoisting amount adjusting tool, it is possible to adjust the winding amount of the auxiliary spring.

  Here, with the rotation of the winding amount adjustment screw 81, the second winding amount adjustment wheel 84 rotates, and the winding amount display needle 86 fixed to the second winding amount adjustment wheel 84 rotates. Then, the winding amount of the auxiliary spring is displayed by a winding amount display scale 87 indicated by the winding amount display needle 86. Thereby, it is possible to objectively grasp the amount of winding of the mainspring without depending on the operator's intuition. As a result, the auxiliary spring can be set to a predetermined winding amount.

  Specifically, a correspondence table between the winding amount display scale 87 and the operation torque output from the secondary spring when the secondary spring is wound up to the winding amount display scale 87 is prepared in advance. Next, the mainspring torque for realizing a desired posture difference is obtained from the graph of FIG. Next, a winding amount display scale 87 for realizing the mainspring torque is obtained from the correspondence table described above. Then, the mainspring 65 is wound up so that the winding amount display scale 87 is indicated by the winding amount display needle 86. Thereby, the sub-spring can be set to a predetermined winding amount that realizes a desired posture difference.

  By the way, there is a correlation among the amount of winding of the auxiliary spring, the mainspring torque, the balance angle of the balance with the balance, and the attitude difference of the rate. Therefore, a method of adjusting the winding amount of the mainspring so as to obtain the balance angle of the balance that achieves a desired posture difference while measuring the balance angle of the balance is considered. In addition, while the amount of winding of the mainspring is larger, the swing angle of the balance is increased. On the other hand, if the train wheel or the escapement is defective, the swing angle of the balance is decreased. For this reason, the balance angle of the balance with the balance spring may be the same when the auxiliary spring is wound more than a predetermined value in a state where the train wheel or escapement is defective. . Therefore, even if the swing angle of the balance with hairspring is measured, it is difficult to set the auxiliary mainspring to a predetermined winding amount, and it is also difficult to find defects in the train wheel and the escapement.

  On the other hand, in the present embodiment, the amount of winding of the secondary spring can be objectively grasped, and therefore, the amount of secondary winding can be set to a predetermined amount of winding. Further, when the balance spring is smaller than the predetermined value even though the auxiliary spring is set to the predetermined winding amount, it can be determined that there is a problem with the train wheel or the escapement. Therefore, it is possible to reliably find defects in the train wheel and escapement.

(Power switching mechanism, planetary gear mechanism 90)
As shown in FIG. 5, the hoisting amount adjusting mechanism 80 transmits the hoisting amount adjusting torque to the sub-spring, while the main spring described above also transmits the timed hoisting torque to the sub-spring. Therefore, the torque adjustment device includes a power switching mechanism that automatically switches the torque transmitted to the auxiliary spring. The power switching mechanism (planetary gear mechanism 90) includes a first shaft (first sun wheel 92a) connected to the barrel wheel provided with the mainspring and a second shaft (second wheel) connected to the hoisting amount adjusting mechanism 80. A solar wheel 92b) and a third shaft (planetary carrier 94) connected to a pinion wheel to which the end of the sub-spring is fixed. The combination of the first shaft, the second shaft, and the third shaft of the power switching mechanism and the barrel wheel, the hoisting amount adjusting mechanism 80, and the pawl wheel, which are the connection destinations, is not limited to the above combination, and Combinations are also possible.

In the first embodiment, a planetary gear mechanism 90 is provided as a power switching mechanism.
FIG. 6 is an explanatory diagram of the planetary gear mechanism 90 and is a side cross-sectional view taken along line C1-C2 of FIG. In FIG. 6, the same hatching is given to the member which rotates integrally. As shown in FIG. 6, the planetary gear mechanism 90 includes a first sun wheel 92 a connected to the barrel wheel (via another member), and a second sun wheel 92 b connected to the hoisting amount adjusting mechanism 80. , A planetary carrier 94 connected to the pawl wheel 64 and a planetary car 93 supported by the planetary carrier 94. Note that only one of the first sun wheel 92a and the second sun wheel 92b may be a sun wheel and the other may be an internal gear.

  The first sun wheel 92 a is fixed to the third pinion 32. The second solar wheel 92b is formed to be rotatable with respect to the true 31 of the third wheel & pinion 30. The planet carrier 94 is formed to be rotatable with respect to the true 31 of the third wheel 30 and functions as the third gear 34 described above. The planet carrier 94 supports a plurality of planetary wheels 93 in a rotatable manner. In FIG. 2, only one planetary car 93 is shown for easy viewing of the drawing. As shown in FIG. 6, the planetary wheel 93 includes a first planetary wheel 93a that meshes with the first sun wheel 92a and a second planet wheel 93b that meshes with the second sun wheel 92b. The first planetary wheel 93 a and the second planetary wheel 93 b are fixed to each other via an axis that penetrates the planet carrier 94.

The operation of the planetary gear mechanism 90 will be described.
First, the operation for transmitting the constant winding torque from the main spring to the sub-spring during the operation of the mechanical timepiece will be described. During the operation of the mechanical timepiece, the braking spring 85 of the hoisting amount adjusting mechanism 80 shown in FIG. 5 regulates the rotation of the second hoisting amount adjusting wheel 84, and therefore the second sun wheel of the planetary gear mechanism 90. 92b is also restricted in rotation.
On the other hand, during the operation of the mechanical timepiece, the regular winding torque of the mainspring is supplied from the second gear 24 to the third pinion 32, and the first sun wheel 92a rotates together with the third pinion 32. As the first sun wheel 92 a rotates, the planetary wheel 93 revolves while rotating, so that the planet carrier 94 rotates together with the planetary wheel 93. As a result, as shown in FIG. 3, the constant hoisting torque is transmitted from the planetary carrier 94 (third gear 34) to the pinion wheel 64 and the auxiliary spring 65 through the fourth pinion 42.

Next, an operation of transmitting the winding amount adjustment torque from the winding amount adjustment mechanism 80 to the sub-spring while the mechanical timepiece is stopped will be described. Since the rotation of the second gear 24 shown in FIG. 5 is restricted while the mechanical timepiece is stopped, the rotation of the first sun wheel 92a of the planetary gear mechanism 90 is also restricted.
On the other hand, when the winding amount adjustment torque is supplied from the second winding amount adjustment wheel 84 of the winding amount adjustment mechanism 80 to the second sun wheel 92b of the planetary gear mechanism 90, the second sun wheel 92b rotates. As the second sun wheel 92b rotates, the planetary car 93 revolves while rotating, and the planet carrier 94 rotates. As a result, as shown in FIG. 3, the winding amount adjustment torque is transmitted from the planetary carrier 94 (third gear 34) to the pinion wheel 64 and the auxiliary mainspring 65 through the fourth pinion 42.

  As shown in FIG. 5, the torque adjusting device includes a winding amount holding portion 80b that holds the amount of winding of the sub-spring, and a planetary gear mechanism 90. It is possible to automatically switch between the transmission of the scheduled winding torque to the mainspring and the transmission of the winding amount adjustment torque from the winding amount adjustment mechanism 80 to the auxiliary spring while the mechanical timepiece is stopped. Therefore, a mechanism for releasing the connection between the hoisting amount adjusting mechanism 80 and the train wheel is unnecessary, and the volume efficiency is excellent.

(First Modification of First Embodiment, Differential Device 190)
FIG. 7 is an explanatory diagram of the differential device 190 according to the first modification of the first embodiment, and is a side cross-sectional view taken along the line C1-C1 in FIG. In FIG. 7, the same hatching is given to the member which rotates integrally. In the first embodiment described above, the planetary gear mechanism 90 shown in FIG. 6 is provided as the power switching mechanism. However, in the first modification, the differential device 190 shown in FIG. 7 is provided as the power switching mechanism. It is different. Note that detailed description of portions having the same configuration as in the first embodiment is omitted.

  As shown in FIG. 7, the differential device 190 includes a first side gear 192a that functions as a first input shaft of the power switching mechanism, a second side gear 192b that functions as a second input shaft, and a carrier 194 that functions as an output shaft. And. That is, the differential gear 190 is supported by the first side gear 192a connected to the barrel complete, the second side gear 192b connected to the hoisting amount adjusting mechanism 80, the carrier 194 connected to the pawl wheel 64, and the carrier 194. The pinion gear 193 is provided.

  The first side gear 192 a is fixed to the third pinion 32. The second side gear 192 b is fixed to the differential pinion 191 and is rotatable with respect to the true 31 of the third wheel & pinion 30 together with the differential pinion 191. The carrier 194 is formed so as to be rotatable with respect to the true 31 of the third wheel 30 and functions as the third gear 34 described above. The carrier 194 rotatably supports one or a plurality of pinion gears 193. The pinion gear 193 meshes with both the first side gear 192a and the second side gear 192b.

The operation of the differential device 190 will be described.
First, the operation for transmitting the constant winding torque from the main spring to the sub-spring during the operation of the mechanical timepiece will be described. During the operation of the mechanical timepiece, the rotation of the second side gear 192b is restricted. On the other hand, during the operation of the mechanical timepiece, the regular winding torque of the mainspring is supplied from the second gear 24 to the third pinion 32, and the first side gear 192a rotates together with the third pinion 32. As the first side gear 192a rotates, the pinion gear 193 revolves while rotating, so the carrier 194 rotates together with the pinion gear 193. As a result, the constant hoisting torque is transmitted from the carrier 194 (third gear 34) to the pinion wheel 64 and the auxiliary spring 65 via the fourth pinion 42 shown in FIG.

  Next, an operation of transmitting the winding amount adjustment torque from the winding amount adjustment mechanism 80 to the sub-spring while the mechanical timepiece is stopped will be described. While the mechanical timepiece is stopped, the rotation of the first side gear 192a is restricted. On the other hand, when the winding amount adjustment torque is supplied from the second winding amount adjustment wheel 84 of the winding amount adjustment mechanism 80 to the second side gear 192b via the differential pinion 191 of the differential device 190, the second side gear 192b rotates. To do. As the second side gear 192b rotates, the pinion gear 193 revolves while rotating, so that the carrier 194 rotates together with the pinion gear 193. As a result, the hoisting amount adjustment torque is transmitted from the carrier 194 (third gear 34) to the pinion wheel 64 and the auxiliary mainspring 65 via the fourth pinion 42 shown in FIG.

  In the differential device 190 of the first modification shown in FIG. 7 as well as the planetary gear mechanism of the first embodiment, the transmission of the constant winding torque from the main spring to the auxiliary mainspring during the operation of the mechanical timepiece, It is possible to automatically switch the transmission of the hoisting amount adjusting torque from the hoisting amount adjusting mechanism 80 to the auxiliary spring while the type timepiece is stopped. Therefore, a mechanism for releasing the connection between the hoisting amount adjusting mechanism 80 and the train wheel is unnecessary, and the volume efficiency is excellent.

(Second Modification of First Embodiment, Winding Amount Adjustment Mechanism 180)
FIG. 8 is an explanatory diagram of the hoisting amount adjusting mechanism 180 in the second modification of the first embodiment, and FIG. 8A is a side cross-sectional view of a portion corresponding to the C1-C1 line of FIG. The hoisting amount adjusting mechanism 80 of the first embodiment shown in FIG. 5 described above includes the braking spring 85 as the hoisting amount holding portion 80b. However, the hoisting amount of the second modification shown in FIG. The adjustment mechanism 180 is different in that a braking pinion 186 and a braking jumper 185 are provided as the hoisting amount holding unit 180b. Note that detailed description of portions having the same configuration as in the first embodiment is omitted.

As shown in FIG. 8A, the hoisting amount adjusting unit 180a includes a hoisting amount adjusting screw 181, a first hoisting amount adjusting wheel 182 and a second hoisting amount adjusting wheel 184. The hoisting amount adjusting screw 181 is formed in a polygon such as a hexagon having a two-sided width, and is formed so as to be engageable with the hoisting amount adjusting tool.
The hoisting amount holding unit 180b includes a braking pinion 186 and a braking jumper 185. The brake pinion 186 is fixed coaxially with the second hoist adjustment wheel 184. The braking jumper 185 has a proximal end fixed to the train wheel bridge 9 and a distal end meshed with the braking pinion 186.
FIG.8 (b) is a top view of a winding amount holding | maintenance part. The brake jumper 185 is formed so as to be elastically deformable by a leaf spring material or the like, and its tip part meshes with a tooth part formed on the outer periphery of the brake pinion 186.

  Since the rotation of the second hoisting amount adjusting wheel 184 is restricted by engaging the tip of the braking jumper 185 with the tooth portion of the braking pinion 186, the amount of winding of the auxiliary spring is maintained. If a hoisting amount adjustment torque larger than a predetermined value is applied, the tip of the braking jumper 185 gets over the tooth of the braking pinion 186, and the braking pinion 186 rotates. Thereby, since the 2nd winding amount adjustment wheel 184 also rotates, the amount of winding of the auxiliary spring can be adjusted.

(Second Embodiment)
FIG. 9 is an explanatory diagram of the torque adjustment device 206 according to the second embodiment, and is a side cross-sectional view of a portion corresponding to the A1-OPQ-A2 line of FIG. In the torque adjusting device 6 of the first embodiment shown in FIG. 3 described above, the planetary gear mechanism 90 is incorporated in the third wheel 30. However, the torque adjusting device 206 of the second embodiment shown in FIG. The mechanism 290 is different in that it is incorporated in the fourth wheel & pinion 40. Note that detailed description of portions having the same configuration as in the first embodiment is omitted.

  In the above-described first embodiment shown in FIG. 3, the torque adjusting device main body 60 including the pawl wheel 64, the auxiliary mainspring 65, and the output gear 66 is incorporated in the fourth wheel & pinion 40. The torque adjusting device main body 60 is a part other than the fourth wheel 40 and can be incorporated in the second wheel 20, the third wheel 30, the escape wheel 51, and the like. Note that, also in the second embodiment shown in FIG. 9, the torque adjusting device main body 60 is incorporated in the fourth wheel & pinion 40.

  On the other hand, in the first embodiment shown in FIG. 3 described above, a planetary gear as a power switching mechanism is provided in the third wheel 30 in the wheel train on the side of the barrel wheel 10 of the auxiliary spring 65 (wheel train from the barrel wheel 10 to the pawl wheel 64). A gear mechanism 90 is incorporated. This power switching mechanism can also be incorporated in a portion other than the third wheel 30 in the barrel wheel side wheel train. This power switching mechanism is connected (via another member) to the barrel complete 10, the pawl wheel 64, and the hoisting amount adjusting mechanism 80.

  On the other hand, in the second embodiment shown in FIG. 9, the power is switched to the fourth wheel & pinion 40 in the train wheel on the escapement 50 side of the auxiliary spring 65 (the train wheel from the output gear 66 to the escapement 50). A planetary gear mechanism 290 is incorporated as a mechanism. This power switching mechanism can also be incorporated in a portion other than the fourth wheel 40 in the escapement side wheel train. This power switching mechanism is connected to the escapement 50, the output gear 66, and the hoisting amount adjusting mechanism 80 (through other members).

  That is, the power switching mechanism (planetary gear mechanism 290) includes a first shaft (first sun wheel 292a) connected to the output gear 66 and a second shaft (second sun wheel 292b) connected to the hoisting amount adjusting mechanism 80. ) And a third shaft (planet carrier 94) connected to the escapement 50. The combination of the first shaft, the second shaft, and the third shaft of the power switching mechanism and the output gear 66, the hoisting amount adjusting mechanism 80, and the escapement 50, which are the connection destinations, is not limited to the above combination. Any combination is possible.

The torque adjustment device 206 of the second embodiment will be specifically described.
In the torque adjustment device 206 shown in FIG. 9, the first sun wheel 292 a of the planetary gear mechanism 290 functions as the output gear 66 of the torque adjustment device main body 60. The first sun wheel 292 a is fixed to the true 41 of the fourth wheel & pinion 40. The second sun wheel 292 b is formed to be rotatable with respect to the true 41 of the fourth wheel & pinion 40. The planet carrier 294 is formed to be rotatable with respect to the true 41 of the fourth wheel & pinion 40 and functions as the aforementioned fourth gear 44. The planet carrier 294 supports a plurality of planet wheels 293 in a rotatable manner. The planetary wheel 293 includes a first planetary wheel 293a that meshes with the first sun wheel 292a and a second planetary wheel 293b that meshes with the second sun wheel 292b. The first planetary wheel 293a and the second planetary wheel 293b are fixed to each other via an axis passing through the planet carrier 294.

The operation of the planetary gear mechanism 290 will be described.
First, the operation of transmitting the operating torque from the auxiliary spring 65 to the escapement 50 during the operation of the mechanical timepiece will be described. During the operation of the mechanical timepiece, the rotation of the second sun wheel 292b of the planetary gear mechanism 290 is restricted.
On the other hand, during the operation of the mechanical timepiece, the operating torque of the auxiliary mainspring 65 is supplied to the first sun wheel 292a, and the first sun wheel 292a rotates. As the first sun wheel 292a rotates, the planetary vehicle 293 revolves while rotating, so that the planet carrier 294 rotates together with the planetary vehicle 293. As a result, the operating torque is transmitted from the planet carrier 294 (the fourth gear 44) to the escapement 50.

Next, an operation for transmitting the hoisting amount adjusting torque from the hoisting amount adjusting mechanism 80 to the auxiliary mainspring 65 while the mechanical timepiece is stopped will be described. While the mechanical timepiece is stopped, the planetary carrier 294 is restricted from rotating together with the escapement 50.
On the other hand, when the winding amount adjustment torque is supplied from the winding amount adjustment mechanism 80 to the second sun wheel 292b, the second sun wheel 292b rotates. The planetary vehicle 293 rotates with the rotation of the second sun wheel 292b, but the planetary vehicle 293 does not revolve because the planet carrier 294 is stopped. Therefore, the first sun wheel 292a rotates with the rotation of the planetary wheel 293. Since the first sun wheel 292a functions as the output gear 66 of the torque adjusting device main body 60, the winding amount adjustment torque is transmitted from the first sun wheel 292a to the auxiliary mainspring 65.

The torque adjustment device 206 of the second embodiment has the same effect as that of the first embodiment.
In other words, since the planetary gear mechanism 290 is provided, the transmission of the operating torque from the auxiliary mainspring 65 to the escapement 50 during the operation of the mechanical timepiece and the hoisting amount adjusting mechanism 80 during the stoppage of the mechanical timepiece. Transmission of the winding amount adjustment torque to the mainspring 65 can be automatically switched. Therefore, a mechanism for releasing the connection between the hoisting amount adjusting mechanism 80 and the train wheel is unnecessary, and the volume efficiency is excellent.

(Third embodiment)
FIG. 10 is an explanatory diagram of the torque adjustment device 306 in the third embodiment, and is a plan view excluding the train wheel bridge on the front side of the movement. In FIG. 10, the illustration of the main plate and the train wheel bridge is omitted. In the torque adjusting device 6 of the first embodiment shown in FIG. 2 described above, the torque adjusting device main body 60 includes the pawl wheel 64. However, the torque adjusting device 306 of the third embodiment shown in FIG. The main body 360 is different in that it includes a flywheel 364. Note that detailed description of portions having the same configuration as in the first embodiment is omitted.

As shown in FIG. 10, the torque adjusting device main body 360 of the third embodiment includes a handwheel (torque box) to which a sub-spring (torque adjusting mainspring) 365 and an outer peripheral end (first end) of the sub-spring 365 are connected. A vehicle-side torque adjusting vehicle) 364, and an output gear (escapement-side torque adjusting vehicle) 366 to which the inner peripheral end (second end) of the auxiliary spring 365 is connected.
The flywheel 364 is formed to have a larger moment of inertia than the output gear 366. For example, the area of the lightening portion of the flywheel 364 is formed smaller than the output gear 366, and the thickness of the flywheel 364 is formed thicker than the output gear 366.

  A pin 366 p is erected on the output gear 366 toward the flywheel 364. The flywheel 364 has a hole 364h through which the pin 366p is inserted. The hole 364h is formed in a size that allows movement of the pin 366p in the circumferential direction of the fourth wheel & pinion 40 within a predetermined range. By the pin 366p and the hole 364h, the relative rotation between the output gear 366 and the flywheel 364 is restricted within a predetermined range.

Operation | movement of the torque adjustment apparatus main body 360 of 3rd Embodiment is demonstrated.
In a state in which the rotation of the escape gear 54 is temporarily stopped by the engagement of the ankle 56, the pin 366 p of the output gear 366 is in contact with the end of the hole 364 h of the flywheel 364.
When the engagement of the ankle 56 is released, the output gear 366 can rotate together with the escape gear 54. As the auxiliary spring 365 is unwound, an operating torque acts on the output gear 366, and the output gear 366 rotates. Then, operating torque is supplied from the output gear 366 to the escapement 50, and the mechanical timepiece operates. The output gear 366 rotates by a predetermined angle until the ankle 56 is engaged with the escape gear 54 again.

  On the other hand, the flywheel 364 also rotates because the fixed winding torque is transmitted from the mainspring to the flywheel 364. However, since the flywheel 364 has a larger moment of inertia than the output gear 366, the flywheel 364 starts rotating after the output gear 366. That is, the flywheel 364 rotates intermittently relative to the output gear 366. Here, the pin 366p of the output gear 366 that has started rotating is away from the end of the hole 364h of the flywheel 364, and the end of the hole 364h abuts on the pin 366p of the flywheel 364 that has started rotating later. Rotate until. Since the output gear 366 rotates by a predetermined angle, the flywheel 364 also rotates by a predetermined angle. As a result, the flywheel 364 winds up the auxiliary spring 365 by a predetermined amount with the output gear 366.

  As described above, also in the torque adjusting device main body 360 of the third embodiment, the auxiliary spring 365 is periodically wound up by a predetermined amount, so that the auxiliary spring 365 is held at a substantially constant winding amount. Since a substantially constant torque is supplied from the auxiliary mainspring 365 to the escapement 50 and the speed governor (the balance 58), the speed governor can operate the escapement 50 at a constant cycle. Thereby, the accuracy of the timepiece can be improved. Moreover, since the escapement 50 operates at a constant cycle, the output gear 366 and the flywheel 364 also rotate relative to each other at a constant cycle. As a result, the sub-spring 365 can be wound up at a constant cycle, and the accuracy of the timepiece can be further improved.

It should be noted that the technical scope of the present invention is not limited to the above-described embodiments, and includes those in which various modifications are made to the above-described embodiments without departing from the spirit of the present invention. In other words, the specific materials and layer configurations described in the embodiments are merely examples, and can be changed as appropriate.
For example, the mechanism of the escapement is not limited to the above-described club tooth escapement, and various mechanisms can be employed.

  DESCRIPTION OF SYMBOLS 1 ... Mechanical type clock 5 ... Movement 6,206,306 ... Torque adjustment apparatus 10 ... Incense cart 50 ... Escapement machine 64 ... Pawl wheel (torque adjustment car side torque adjustment car) 65 ... Secondary spring (torque adjustment mainspring) 66 ... output gear (escapement side torque adjustment vehicle) 70 ... torque adjustment escapement 80 ... winding amount adjustment mechanism 80b ... winding amount holding part 80c ... winding amount display part 84 ... second winding amount adjustment Car (winding amount adjusting wheel) 85 ... braking spring 90 ... planet gear mechanism (power switching mechanism) 185 ... braking jumper 190 ... differential device 364 ... flywheel

Claims (9)

A torque adjustment device having a torque adjustment spring incorporated in a train wheel from a barrel complete to a escapement of a mechanical watch,
A first end portion of the torque adjustment mainspring and a escapement side torque adjustment vehicle connected to the escapement side wheel train from the torque adjustment mainspring;
A second end portion of the torque adjustment mainspring is connected, and is connected to a wheel train on the barrel side from the torque adjustment mainspring, and intermittently rotates relative to the escapement side torque adjustment vehicle. A barrel for torque adjustment on the barrel,
A winding amount adjusting mechanism for adjusting a winding amount of the torque adjusting spring;
A power switching mechanism incorporated into the barrel wheel side train wheel or the escapement side train wheel and coupled to the hoisting amount adjustment mechanism;
The hoisting amount adjusting mechanism includes a hoisting amount holding unit that holds the hoisting amount of the torque adjusting mainspring and a hoisting amount display unit that displays the hoisting amount of the torque adjusting mainspring. The power switching mechanism when incorporated in a train wheel is connected to the barrel wheel, the barrel wheel side torque adjustment vehicle, and the hoisting amount adjustment mechanism,
The power switching mechanism when incorporated in the escapement side train wheel is connected to the escapement, the escapement side torque adjustment vehicle, and the hoisting amount adjustment mechanism.
A torque adjusting device. The hoisting amount adjusting mechanism includes a hoisting amount adjusting wheel for adjusting the hoisting amount of the torque adjusting spring.
The torque adjustment device according to claim 1, wherein the hoisting amount holding unit includes a braking spring that applies a friction torque to the hoisting amount adjusting wheel. The hoisting amount adjusting mechanism includes a hoisting amount adjusting wheel for adjusting the hoisting amount of the torque adjusting spring.
The torque adjustment device according to claim 1, wherein the hoisting amount holding unit includes a braking jumper that restricts rotation of the hoisting amount adjusting wheel.   The torque adjustment device according to any one of claims 1 to 3, wherein the power switching mechanism is a planetary gear mechanism.   The torque adjustment device according to any one of claims 1 to 3, wherein the power switching mechanism is a differential device.   A torque adjustment escapement is provided in conjunction with the escapement to intermittently rotate the barrel complete torque adjustment vehicle relative to the escapement side torque adjustment vehicle. The torque adjusting device according to any one of claims 1 to 5.   6. The torque adjustment device according to claim 1, further comprising a flywheel having a greater moment of inertia than the escapement side torque adjustment vehicle. .   A movement comprising the torque adjusting device according to claim 1.   A mechanical timepiece comprising the torque adjusting device according to claim 1.

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