CH707743A2 - Device torque adjustment, movement and mechanical timepiece. - Google Patents

Abstract

The invention relates to a torque adjusting device (6) including a secondary motor spring (65); an output wheel (66) to which the inner peripheral end of the secondary mains spring (65) is connected and which is connected to an exhaust (50); a ratchet wheel (64) to which the outer end of the secondary mains spring (65) is connected and which rotates intermittently and relatively relative to the output wheel (66); an armature amount adjusting mechanism (80) which adjusts the armature amount of the secondary motor spring (65); and a planetary gear mechanism (90) that is connected to the ratchet wheel (64), a barrel wheel (10), and the armature amount adjustment mechanism (80). The armature amount adjusting mechanism (80) includes a winding amount holding unit which maintains the armature amount of the secondary mains spring (65) and a windage amount display unit which displays the armature amount of the secondary motor spring (65). The invention also relates to a movement and a timepiece comprising such a device.

Description

BACKGROUND OF THE INVENTION

1. Field of the invention

The present invention relates to a torque adjustment device of a movement and a mechanical timepiece.

2. Description of the prior art

In a mechanical timepiece, if an actuating torque which is transmitted from the barrel drum to the exhaust varies according to the disarming of the primary motor spring of the barrel drum, the oscillation angle of the pendulum varies and the walking of the timepiece varies. Therefore, to remove fluctuations in the driving torque that is transmitted to the exhaust, a constant torque mechanism (torque adjustment device) has been proposed in which a secondary motor spring (torque adjustment spring) is arranged between the barrel drum and the exhaust. The constant torque mechanisms are roughly divided into a method of using a flywheel (for example, refer to British Patent Publication No. 573,942 (Patent Document 1)) and a periodic control method performed by a cam (for example, refer to JP-T-2012-503 187 (patent document 2)).

[0003] A constant charging device (torque adjustment device) disclosed in the patent document 2 will be described using terms and reference numbers which are used in the patent document 2. In the constant charging device disclosed in patent document 2, a third active member (third mobile) 9 includes a spiral spring (motor spring for torque adjustment) 18. An outer peripheral end of the spiral spring 18 is connected to a stop wheel 22 and an inner peripheral end of the spiral spring 18 is connected to an adjustment member 20. The stop wheel 22 is attached to a main axle (third axis) 8 of the third active member 9 and the adjustment member 20 is rotatable relative to the main axis 8 of the third active member 9. The adjustment member 20 supports a second member (third wheel) 10 using friction.

The third active member 9 is connected to a first second active member (second mobile) 13 and the first second active member 13 is connected to an escape wheel 2 and a second second active member 25. A cam 26 is fixed to a main axle of the second second active member 25 and a control pawl 31 is arranged to interpose an outer periphery of the cam 26 between them. A second fork 32 extends from the control pawl 31 towards the stop wheel 22. A tip of the second fork 32 is locked by a serration formed on the outer periphery of the stop wheel 22.

Following the disarming of the spiral spring 18, the actuating torque is applied to the second element (third wheel) 10 which is supported by the adjustment element 20 to actuate the mechanical timepiece. Following the actuation of the mechanical timepiece, the second second active member 25 and the cam 26 rotate. The rotation of the cam 26 causes the control pawl 31 and the second fork 32 to rotate in a pivotable manner so that the second fork 32 is locked several times and released by the stop wheel 22 at a predetermined cycle. During the unlocked period, the stop wheel 22 arms the spiral spring 18 by a certain amount by means of a periodic armature torque transmitted from the driving spring of a barrel drum 1. In this way, the spring spiral 18 of the constant charging device is adapted to restore a predetermined amount of arming at each predetermined cycle. Since the spiral spring 18 actuates the mechanical timepiece, the running of the mechanical timepiece is stabilized.

[0006] FIG. 11 is a graph illustrating the relationship between the mainspring torque and the step. As shown in fig. 11, since the running of the mechanical timepiece varies as a function of the driving spring torque, in the mechanical timepiece which includes the torque adjusting device, it is important to adjust the spring's arming amount secondary engine. Therefore, the constant load device disclosed in patent document 2 is adapted to adjust the state of charge (amount of arming) of the spiral spring 18. Specifically, the adjustment member 20 includes a bearing surface 41 and a tooth portion is formed on an outer periphery of the bearing surface 41. In addition, an active control member 42 is arranged adjacent the adjustment member 20, and a serrated pinion 44 meshes with the outer peripheral tooth portion of the bearing surface 41 is formed on the active control member 42.

The state of charge of the spiral spring 18 is adjusted when the mechanical timepiece is stopped. First, the active control member 42 is squeezed and moved in an axial direction, and the active control member 42 is urged to mesh with the adjustment member 20. In this state, the amount adjustment torque of arming is applied to the active control member 42 to rotate the active control member 42 and the adjustment member 20. When the mechanical timepiece is stopped, the second member (third wheel) 10 is also stopped. However, since the second member 10 is supported relative to the adjustment member simply by using friction, the second member 10 and the adjustment member 20 are in sliding contact with each other. Therefore, the adjustment member 20 rotates through the applied adjustment adjustment torque. In addition, since the stop wheel 22 is also stopped when the mechanical timepiece is stopped, the spiral spring 18 is cocked between the adjusting member 20 and the stop wheel 22. This adjusts the state of charge of the spiral spring 18.

On the other hand, when the mechanical timepiece is actuated, the adjustment member 20 is also rotatably actuated. Here, if the adjustment member 20 and the active control member 42 rotate, the mainspring experiences a loss of energy. Therefore, the constant load device disclosed in Patent Document 2 includes a mechanism for unlocking the engagement of the adjustment member 20 with the active control member 42. Specifically, the active control member 42 is movable in the axial direction and is biased in a direction away from the meshing with the adjusting member 20 by a helical spring 48. After the state of charge of the spiral spring 18 is adjusted, the pressure of the active control member 42 is released and the active control member 42 and the adjustment member 20 are unlocked from the meshing with each other. This causes the active control member 42 not to turn even if the adjustment member 20 rotates when the mechanical timepiece is actuated, thereby avoiding the energy loss of the main spring.

However, according to the invention disclosed in the patent document 2, an operator must rely on his intuition to deduce the amount of winding of the spiral spring 18 using the active control member 42. Therefore, it is difficult to adjust the spiral spring 18 to have a predetermined amount of arming.

When the armature amount of the spiral spring 18 increases further, the oscillation angle of the balance becomes larger. Accordingly, a method of adjusting the spiral spring 18 to have the predetermined amount of arming by measuring the swing angle of the pendulum has been considered. However, on the other hand, if there is a problem in the finishing gear or the escapement, the oscillation angle of the balance becomes smaller. Therefore, if the spiral spring 18 is armed more than a predetermined value, when there is a problem in the work train or the exhaust, in some cases the swing angle of the balance may be equal at the oscillation angle of the balance when the spiral spring 18 is armed so as to have the predetermined value. Consequently, even if the swing angle of the balance is measured, it is difficult to adjust the spiral spring 18 to have the predetermined amount of arming, and moreover it is also difficult to discover a problem of the work train. or exhaust.

In addition, according to the invention disclosed in the patent document 2, it is necessary to create a mechanism for unlocking the meshing of the adjustment element 20 with the active control member 42. Therefore, its space d the arrangement (movement space for the active control member 42 and the arrangement space for the coil spring 48) must be ensured, thereby causing a degraded volumetric efficiency.

SUMMARY OF THE INVENTION

The present invention is made in view of the problem described above, and its object is to create a torque adjustment device which can deduce the amount of arming a torque adjustment spring and which has excellent volumetric efficiency.

[0013] (1) There is provided a torque adjusting device which includes a torque adjustment spring inserted into a work train from a barrel wheel to an exhaust of a mechanical timepiece; an exhaust side torque adjusting wheel to which a first end portion of the torque adjusting spring is connected and which is connected to the exhaust side finish work train rather than to the adjustment spring couple; a barrel wheel side torque adjusting wheel to which a second end portion of the torque adjusting spring is connected, which is connected to the barrel side wheel finishing gear train rather than the spring of the barrel side wheel; torque adjustment which rotates intermittently and relatively with respect to the exhaust side torque adjustment wheel; an armature amount adjusting mechanism which adjusts a winding amount of the torque adjustment spring; and an energy switching mechanism which is inserted into the barrel wheel finishing work train or the exhaust side finishing gear and which is connected to the winding amount adjustment mechanism. The armature amount adjustment mechanism includes a windage amount holding unit which holds a winding amount of the torque adjustment spring and a windage amount display unit which displays the amount of armature amount. arming the torque adjustment spring. When it is inserted into the barrel wheel side finishing gear train, the energy switching mechanism is connected to the barrel wheel, the barrel wheel side torque adjustment wheel and the adjustment mechanism. amount of arming. When it is inserted into the exhaust side finishing work train, the energy switching mechanism is connected to the exhaust, the exhaust side torque adjustment wheel and the fuel quantity adjustment mechanism. 'winding.

According to this configuration, the armature amount holding unit which holds the arming amount of the torque adjustment spring and the arming amount display unit which displays the arming amount. are planned. Therefore, it is possible to objectively deduce the arming amount of the torque adjustment spring. As a result, it is possible to adjust the torque adjustment spring so as to have a predetermined amount of arming. In addition, if the measurement of the swing angle of the balance is used in combination, it is possible to reliably discover a problem of the work train or the exhaust.

In addition, the armature amount holding unit which holds the arming amount of the torque adjustment spring and the energy switching mechanism are provided. As a result, it is possible to automatically switch from transmitting an actuating torque or a periodic arming torque when the mechanical timepiece is actuated to transmitting a torque adjustment torque. arming from the armature amount adjusting mechanism when the timepiece is stopped. Therefore, it is not necessary to provide a mechanism for disconnecting the winding amount adjusting mechanism and the finishing gear from each other, thereby providing excellent volumetric efficiency.

[0016] (2) It is preferable that the armature amount adjustment mechanism includes an armature amount adjusting wheel (82, 84) which adjusts the arming amount of the torque adjustment spring. and that the armature amount holding unit includes a brake spring that applies a friction torque to the arming amount adjusting wheel (82, 84).

(3) It is preferable that the armature amount adjustment mechanism includes an armature amount adjusting wheel (82, 84) which adjusts the arming amount of the torque adjustment spring. and that the armature amount holding unit includes a braking jumper which regulates a rotation of the armature amount adjusting wheel (82, 84).

With the armature amount holding unit, it is possible to reliably hold the armature amount of the torque adjustment spring and reduce manufacturing costs.

[0019] (4) It is preferred that the energy switching mechanism is a planetary gear mechanism.

[0020] (5) The energy switching mechanism may be a differential gear device.

Thanks to the energy switching mechanism, it is possible to automatically switch from the transmission of the actuating torque or the periodic arming torque when the mechanical timepiece is actuated to the transmission of the adjustment torque. amount of arming from the armature amount adjusting mechanism when the timepiece is stopped. In addition, the excellent volumetric efficiency is expected and it is possible to reduce manufacturing costs.

(6) It is preferable that the torque adjusting device further includes a torque adjustment exhaust which is linked to the exhaust and which rotates intermittently and relatively the torque adjustment wheel. side cylinder wheel relative to the exhaust side torque adjustment wheel.

(7) The torque adjustment device may comprise a flywheel serving as the barrel wheel side torque adjustment wheel, whose moment of inertia is greater than that of the adjustment wheel. exhaust side torque.

According to this configuration, it is possible to rotate intermittently and relatively the torque adjustment wheel of the barrel wheel side to a constant cycle with respect to the torque adjustment wheel on the exhaust side .

(8) A motion is provided which includes the torque adjustment device described above.

(9) There is provided a mechanical timepiece which includes the torque adjustment device described above.

The torque adjustment device described above can deduce the arming amount of the torque adjustment spring. Therefore, it is possible to provide a highly accurate movement and a mechanical timepiece that are set to have a predetermined step.

In addition, the torque adjustment device described above has excellent volumetric efficiency. Therefore, it is possible to create a miniaturized movement and mechanical timepiece.

According to the torque adjustment device, the armature amount holding unit which holds the arming amount of the torque adjustment spring and the arming amount display unit which displays the amount of arming are planned. Therefore, it is possible to objectively deduce the arming amount of the torque adjustment spring. As a result, it is possible to adjust the torque adjustment spring to have the predetermined amount of arming. In addition, if the measurement of the swing angle of the balance is used in combination, it is possible to reliably discover the problem of the work train or the exhaust.

In addition, the armature amount holding unit which holds the armature amount of the torque adjustment spring and the energy switching mechanism are provided. As a result, it is possible to automatically switch from the transmission of the actuating torque or the periodic arming torque when the mechanical timepiece is actuated to the transmission of the armature amount adjustment torque from the armature mechanism. armature amount adjustment when the mechanical timepiece is stopped. Therefore, it is not necessary to create the mechanism for disconnecting the winding amount adjusting mechanism and the finishing gear from each other, thereby allowing excellent volumetric efficiency.

BRIEF DESCRIPTION OF THE DRAWINGS

[0031] <tb> Fig. 1 <SEP> is a front view of a rear side of a mechanical timepiece 1. <tb> Fig. 2 <SEP> is an explanatory view of a torque adjusting device 6 according to a first embodiment and is a front view in the state without a gear train bridge on the front side of a movement 5. <tb> Fig. 3 <SEP> is an explanatory view of the torque adjusting device 6 according to the first embodiment and is a side sectional view taken along the line A1-O-P-Q-A2 in FIG. 2. <tb> Fig. 4 <SEP> is an explanatory view of a torque adjusting device main body 60 and is a side sectional view taken along the line B1-O-Q-B2 in FIG. 2. <tb> Fig. <SEP> is an explanatory view of an armature amount adjustment mechanism 80 and is a side sectional view taken along the line C1-C1 in FIG. 2. <tb> Fig. SEP is an explanatory view of a planetary gear mechanism 90 and is a side sectional view taken along the line C1-C2 in FIG. 2. <tb> Fig. 7 <SEP> is an explanatory view of a differential gear device 190 according to a first modification example of the first embodiment and is a side sectional view in a region corresponding to the line C1-C1 in FIG. 2. <tb> Fig. <SEP> is an explanatory view of an armature amount adjustment mechanism 180 according to a second modification example of the first embodiment, FIG. 8a is a side sectional view in the region corresponding to the line C1-C1 in FIG. 2, and FIG. 8b is a front view of a holding amount holding unit 80b. <tb> Fig. <SEP> is an explanatory view of a torque adjustment device 206 according to a second embodiment and is a side sectional view in a region corresponding to the line A1-O-P-A2 in FIG. 2. <tb> Fig. <SEP> is an explanatory view of a torque adjustment device 306 according to a third embodiment and is a front view in the state without a work train deck on the front side of a movement. <tb> Fig. 11 <SEP> is a graph illustrating the relationship between the mainspring torque and the gait.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0032] Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.

(Timepiece)

In general, reference is made to a machine body including the driving part of a timepiece as a "movement". We refer to the state of the finished product with a dial and hands attached to the movement and with the movement placed in a timepiece case as a "complete assembly" of the timepiece. Between the two sides of a main plate which forms the base of the timepiece, reference is made to the side having a glass of the timepiece case, that is, the side having the dial as to a "back side", a "glass side" or a "dial side" of the movement. Between two sides of the main board, reference is made to the side having a back cover of the timepiece case, that is, the opposite side of the dial as a "front side" or a "side of back cover "of the movement.

FIG. 1 is a front view of the rear side of the complete assembly of a mechanical timepiece 1. The complete assembly of the mechanical timepiece 1 includes a dial 2 including a scale 3 indicating a time information . In addition, the complete assembly of the mechanical timepiece 1 is provided with the needles 4 including an hour hand 4a indicating the hours, a minute hand 4b indicating the minutes and a seconds hand 4c indicating the seconds.

FIG. 2 is an explanatory view of a torque adjusting device 6 according to a first embodiment and is a front view of the state without a work train deck on the front side of the movement 5. FIG. 3 is a side sectional view taken along the line A1-O-P-Q-A2 in FIG. 2. In figs. 2 and 3, some timepiece components that form the movement 5 are not illustrated for easy understanding of the drawings. As shown in fig. 2, the movement 5 of the mechanical timepiece includes a primary motor spring (not shown) which is arranged inside a barrel wheel 10 and serves as a source of energy; a work train (barrel wheel 10, center wheel 20, third wheel 30 and second wheel 40) which transmits the energy of the primary motor spring; an escapement 50 (escape wheel 51 and anchor 56) which intermittently activates the gear train; and a speed controller (balance 58) which periodically activates the escapement 50. As illustrated in FIG. 3, these elements are arranged between a main plate 8 which forms the base and a finishing gear deck 9 arranged facing the main plate 8.

The primary motor spring is arranged inside a barrel of the barrel wheel 10.

As illustrated in FIG. 3, the barrel wheel 10 includes a barrel wheel 14 on an outer periphery of a barrel drum. The center wheel 20 includes a center pinion 22 meshing with the barrel wheel 14 and a center wheel 24 connected to the center pinion 22. The third wheel 30 includes a third gear 32 meshing with the center wheel 24 and a third wheel. wheel 34 linked to the third pinion 32. The second mobile 40 includes a second pinion 42 meshing with the third wheel 34 and a second wheel 44 connected to the second pinion 42. The barrel wheel 10 to the second mobile 40 configures a finishing gear train the speed which increases the speed of rotation by transmitting the energy of the primary mainspring. The second mobile 40 corresponds to the second hand 4c in FIG. 1.

As illustrated in FIG. 3, the escape wheel 51 includes an escape pinion 52 meshing with the second wheel 44 and an escape wheel 54 connected to the escape gear 52. As illustrated in FIG. 2, the anchor 56 includes a pair of vanes 57 engaging a tooth of the escape wheel 54. The balance 58 includes a spiral spring 59.

As illustrated in FIG. 2, the escape wheel 51 is stopped temporarily when a pallet 57 of the anchor 56 engages with the tooth of the escape wheel 54. If the rocker 58 rotates due to an expansion and a contraction of the spiral spring 59 from this state, a plateau pin fixed to the balance shaft rotates the anchor 56. In this way, a pallet 57 of the anchor 56 is detached from the escape wheel 54 and the Exhaust 54 rotates to a position to engage the other pallet 57 of the anchor 56. This intermittent rotational movement of the escape wheel 54 causes the escapement 50 to intermittently actuate the work train. In addition, since the rocker 58 rotates periodically and oscillates, the cruise control periodically actuates the escapement 50.

As described above, when a pallet 57 of the anchor 56 is detached from the escape wheel 54, the escape wheel 54 pushes its pallet 57 so that the anchor 56 raises the rocker 58. In this way, an actuating torque is applied from the escape wheel 54 to the rocker 58, thereby maintaining a rotational oscillation of the rocker 58.

(First embodiment, torque adjustment device 6)

As illustrated in FIG. 3, if the actuating torque transmitted from the barrel wheel 10 to the escapement 50 fluctuates in response to the disarming of the primary motor spring, the oscillation angle of the pendulum varies and the walking of the timepiece varies. To suppress fluctuations in the driving torque, the motion includes the torque adjusting device 6 having a secondary motor spring (torque adjustment spring) 65 inserted in the finishing gear between the barrel wheel 10 and the exhaust 50.

The torque adjustment device 6 includes a torque adjustment device main body 60 provided with the secondary motor spring 65; a torque adjustment exhaust 70 which controls the actuation of the torque adjusting device main body 60: a winding amount adjusting mechanism 80 which adjusts the armature amount of the secondary power spring 65; and an energy switching mechanism (planetary gear mechanism 90) which is inserted into the finishing gear and which is connected to the armature amount adjustment mechanism 80. In the first embodiment, the main body torque adjusting device 60 is inserted into the second 40 and the energy switching mechanism is inserted into the third mobile 30.

(Main body of the torque adjustment device 60)

FIG. 4 is an explanatory view of the torque adjustment device main body 60 and is a side sectional view taken along the line B1-O-Q-B2 in FIG. 2. In fig. 4, elements that rotate in one piece have the same hatching. As shown in fig. 4, the main body of the torque adjusting device 60 includes the secondary motor spring (torque adjustment spring) 65; the ratchet wheel (barrel wheel side adjusting wheel) 64 to which the outer peripheral end portion (first end portion) of the secondary motor spring 65 is connected; and the output wheel (exhaust side torque adjustment wheel) 66 to which the inner peripheral end portion (second end portion) of the secondary motor spring 65 is connected.

The ratchet wheel 64 is fixed to the second pinion 42, and is rotatable relative to the axis 41 of the second mobile 40 with the second pinion 42. A ratchet is formed on an outer periphery of the ratchet wheel 64.

The output wheel 66 is fixed to the axis 41 of the second mobile 40 and functions as the second wheel described above 44.

In the secondary motor spring 65, an outer peripheral end portion is fixed to the ratchet wheel 64 by a first attachment member 64f and an inner peripheral end portion is fixed to the axis 41 of the second mobile 40 by a second fastener 61. In this manner, the inner peripheral end portion of the secondary motor spring 65 is connected to the output wheel 66.

(70 torque adjustment exhaust)

As illustrated in FIG. 2, the torque adjustment exhaust 70 includes a cam 72 connected to the escape wheel 51; a cam follower 74 connected to the cam 72; a lever 76 connected to the cam follower 74; and a pair of vanes 77 attached to the lever 76 and engaged with the ratchet wheel ratchet 64.

The cam 72 is fixed coaxially to the axis of the escape wheel 51. The cam 72 is formed to have a substantially polygonal shape in a front view. In particular, the cam 72 is formed in a substantially polygonal shape having any number of vertices (in the present embodiment, a substantially triangular shape).

The cam follower 74 includes a pair of forks with the cam 72 interposed between them in a front view. Ends of the pair of forks are arranged on an outer periphery of the cam 72 to have the center of the cam 72 interposed therebetween. The distance between the pair of forks is formed to be smaller than twice the distance between the center of the cam 72 and an outer peripheral vertex. The cam follower 74 is formed to be rotatable about an axle 75 which is arranged separate from the axis of the escape wheel 51.

The lever 76 is connected to the cam follower 74, and is formed to be rotatable about the axle 75 with the cam follower 74. The lever 76 includes a pair of arms extending radially with the axle 75 interposed between them in a front view. The pallets 77 are fixed respectively to the tips of the pair of arms. The vanes 77 are formed to engage the ratchet wheel ratchet 64.

The actuation of the main body of the torque adjustment device 60 and the torque adjustment exhaust 70 will be described.

The secondary motor spring 65 is armed in advance by a predetermined amount. If a paddle 77 of the lever 76 engages with the ratchet wheel 64, the rotation of the ratchet wheel 64 is stopped temporarily. In this state, since the output wheel 66 rotates due to the disarming of the secondary drive spring 65, the driving torque is supplied from the secondary drive spring 65 to the exhaust 50 by the output wheel 66. This actuates the workpiece mechanical watchmaking.

Following the rotation of the escape wheel 51 of the exhaust 50, the cam 72 rotates. Following rotation of the cam 72, the cam follower 74 rotates reciprocally about the axle 75. If the lever 76 rotates about the axle 75 by being connected to the cam follower 74, a lever blade 77 76 is detached from the ratchet wheel 64, thereby allowing the ratchet wheel 64 to rotate. Since the periodic arming torque is transmitted to the ratchet wheel 64 from the primary mainspring, the periodic arming torque causes the ratchet wheel 64 to rotate, thereby arming the secondary motor spring 65 in a space with the output wheel 66. Thereafter, for a period until the other blade 77 of the lever 76 engages the ratchet wheel 64 to stop the rotation of the ratchet wheel 64, the secondary motor spring 65 is armed by a predetermined amount. The predetermined amount is set at such a quantity to allow the secondary drive spring 65 to be disarmed until the secondary drive spring 65 is re-armed.

In this way, since the secondary motor spring 65 is periodically armed by the predetermined amount, the secondary motor spring 65 is allowed to hold a substantially constant armature amount. A substantially constant actuating torque is supplied from the secondary motor spring 65 to the exhaust 50 and the speed regulator (balance 58). Therefore, the cruise control can actuate the exhaust 50 at a constant cycle. This can improve the accuracy of the timepiece. Moreover, since the exhaust 50 is actuated at constant cycle, the torque adjustment exhaust 70, being connected to the exhaust 50, is also actuated at constant cycle. This allows the secondary motor spring 65 to be armed with the constant cycle, thereby further improving the accuracy of the timepiece.

When the primary motor spring is completely disarmed, the secondary motor spring 65 can not be armed. It is preferable to create a mechanism which regulates the disarming amount of the secondary mains spring 65 so as not to cause the secondary mains spring 65 to be completely disarmed even in this case. As an example of the mechanism, one can consider a mechanism that regulates the relative rotation of the ratchet wheel 64 and the output wheel 66. However, during the adjustment of the armature amount of the secondary motor spring 65 which will be described later the mechanism is formed to allow the relative rotation of the ratchet wheel 64 and the output wheel 66.

(Weaving quantity adjustment mechanism 80)

FIG. 11 is a graph illustrating the relationship between the mainspring torque and the step. In general, the running of the mechanical timepiece varies in response to the main spring torque and moreover, a difference related to the position is present in the running of the mechanical timepiece. In the position where the dial is facing upwards or downwards (horizontal position), the step varies slightly with respect to the spring motor torque. However, in the position where the winding crown is facing upwards or downwards (vertical position), the step varies slightly with respect to the spring motor torque. In fig. 11, when the spring motor torque is located near a region R, the steps of the horizontal position and the vertical position are equal to one another. However, when the mainspring torque is located near a region S, the operation of the vertical position is greatly reduced compared to the operation of the horizontal position.

As illustrated in FIG. 3, in the torque adjusting device 6 including the secondary motor spring 65, the secondary motor spring 65 is held to have the amount of arming substantially constant. Therefore, the actuating torque (spring motor torque) is substantially constant. Therefore, to set the positional difference within a predetermined range, it is important to adjust the secondary mains spring 65 to have the predetermined armature amount for a predetermined drive torque to be powered by the secondary drive spring. 65. In the manufacture of the mechanical timepiece, it may also be considered to adjust the secondary motor spring 65 to have the predetermined amount of arming during manufacture by inserting the secondary motor spring 65 between the ratchet wheel 64 and the output wheel 66 when the ratchet wheel 64 and the output wheel 66 are arranged to have a predetermined phase difference. However, the associated work is difficult. Therefore, the torque adjusting device 6 includes the armature amount adjusting mechanism 80 which adjusts the arming amount of the secondary motor spring 65 after manufacture of the mechanical timepiece.

FIG. 5 is an explanatory view of the armature amount adjusting mechanism 80 and is a side sectional view taken along the line C1-C1 in FIG. 2. The armature amount adjustment mechanism 80 illustrated in FIG. 5 includes an armature amount adjustment unit 80a (armature amount adjustment screw 81, a first armature amount adjustment wheel 82 and a second armature amount adjustment wheel 84 ) to which a torque adjustment torque is entered and transmitted; an armature amount holding unit 80b (braking spring 85) which holds the arming amount of the secondary motor spring; and an arming amount display unit 80c (arming amount display pointer 86 and an arming amount display scale 87) which displays the arming amount of the secondary mains spring.

The arming amount adjustment unit 80a includes the armature amount adjusting screw 81, the first arming amount adjusting wheel 82 and the second arming amount adjusting wheel 82. 84. A groove portion engaging an armature amount adjusting tool is formed on an upper surface of the armature amount adjustment screw 81. The amount adjustment screw arming 81 is attached to the first armature amount adjusting wheel 82 and the first arming amount adjusting wheel 82 meshes with the second arming amount adjusting wheel 84. The second wheel The amount of armature amount adjustment 84 is connected to the planetary gear mechanism 90 inserted in the third movable member 30. The armature amount adjustment screw 81, the first armature amount adjustment wheel 82, and the second adjustment wheel of amount of arming 84 are arranged between the finishing gear deck 9 and the armature amount adjustment finishing gear wheel 89.

The arming amount holding unit 80b includes the braking spring 85. An inner peripheral portion of the braking spring 85 is attached coaxially to the second arm amounting wheel 84. A peripheral portion external of the braking spring 85 is formed to be separated from the second armature amount adjusting wheel 84 in the axial direction. The braking spring 85 is elastically deformed in the axial direction in such a manner that the finishing gear bridge 9 presses the outer peripheral portion of the braking spring 85 in the axial direction. In this manner, the friction torque is applied to the second armature amount adjusting wheel 84 from the finishing train 9 by the brake spring 85 to regulate the rotation of the second wheel of the wheel. arming 84. Therefore, the armature amount of the secondary motor spring is maintained. If the armature amount adjustment torque that exceeds the friction torque is applied, the second armature amount adjustment wheel 84 rotates. Therefore, it is possible to adjust the armature amount of the secondary motor spring.

The arming amount display unit 80c includes the weave amount display needle 86 and the weave amount display scale 87. The quantity display needle wire 86, having a base end side attached to an axle of the second armature amount adjusting wheel 84 and a vertex side formed in a needle shape, is arranged along a Finishing wheel deck surface 9. The windage amount display scale 87 is formed on the surface of the finishing train deck 9. As illustrated in FIG. 2, the arming amount display scale 87 is arranged along a trajectory of the vertex of the arming amount display needle 86. The arming amount display scale 87 includes a large scale formed at a predetermined angular interval and a small scale formed between large scales. A zero (0) is displayed on the large reference scale which is a reference position. When they are seen from the big scale of reference, the signs +1, +2, etc. are displayed sequentially on the large side scale in the circumferential direction, and the signs -1, -2, etc. are displayed sequentially on the other large side scale in the circumferential direction. The arming amount display unit 80c may be substituted with the arm amount adjustment screw 81 of the arming amount adjustment unit 80a. Even in this case, it is possible to display the armature amount of the secondary motor spring by using an extended direction of the groove portion on the upper surface of the armature amount adjusting screw 81.

Returning to FIG. 5, a method of adjusting the armature amount of the secondary motor spring using the armature amount adjustment mechanism 80 will be described. The armature amount of the secondary motor spring is adjusted when the mechanical timepiece is stopped, before delivery or during maintenance. First, the armature amount adjustment tool engages the groove of the armature amount adjustment screw 81 and the armature amount adjustment torque is applied to the adjustment screw amount of arming 81 to turn the armature amount adjustment screw 81. The armature amount adjustment torque is transmitted from the armature amount adjustment screw 81 to the first wheel of the armature adjustment screw 81. armature amount adjustment 82 and the second armature amount adjustment wheel 84 for turning the second armature amount adjusting wheel 84. Furthermore, the arming amount adjustment torque is transmitted. from the second winding amount adjustment wheel 84 to the ratchet wheel by the sun gear mechanism 90, and the ratchet wheel rotates to arm the secondary power spring. Then, it is possible to adjust the armature amount of the secondary motor spring in such a manner that the rotation speed of the armature amount adjustment screw 81 is adjusted using the adjustment tool of amount of arming.

Here, following the rotation of the armature amount adjusting screw 81, the second armature amount adjusting wheel 84 rotates and the arming amount display needle 86 set to the second winding amount adjustment wheel 84 rotates. Then, the armature amount of the secondary motor spring is displayed by the arming amount display scale 87 indicated by the arming amount display needle 86. In this way, it is possible to deduce objectively the amount of winding of the secondary motor spring without relying on the intuition of the worker. Therefore, it is possible to adjust the secondary motor spring to have the predetermined amount of arming.

More specifically, a correspondence table is prepared for the winding amount display scale 87 and the actuating torque output from the secondary mains spring when the secondary mains spring is cocked to the dash scale. the amount of windage 87 is displayed. Next, the motor spring torque which makes the difference related to the desired position is obtained from the graph of FIG. 11. Next, the windage amount display scale 87 which provides the engine spring torque is obtained by the correspondence table described above. Then, the secondary motor spring 65 is cocked so that the arming amount display needle 86 indicates the arming amount display scale 87. In this way, it is possible to adjust the secondary motor spring. to have the predetermined amount of arming that makes the difference related to the desired position.

By casualness, there is a correlation between the winding amount of the secondary motor spring, the spring motor torque, the oscillation angle of the balance and the difference related to the position of the step. Therefore, a method can be considered where the armature amount of the secondary mains spring is adjusted to have the oscillation angle of the beam that realizes the difference related to the desired position when measuring the oscillation angle of the pendulum. If the armature amount of the secondary motor spring is increased further, the oscillation angle of the pendulum becomes larger. On the other hand, if there is a problem in the finishing gear or in the escapement, the oscillation angle of the balance becomes smaller. Therefore, in some cases, the swinging angles of the balance may be equivalent to each other in the situation when the secondary mains spring is armed to have more than one predetermined value when there is a problem in the work train or in the exhaust and the situation when the secondary motor spring is armed to have the predetermined value. As a result, it is difficult to adjust the secondary motor spring to have the predetermined amount of armoring even by measuring the swing angle of the balance. In addition, it is difficult to find the problem in the finishing gear or in the exhaust.

In contrast, according to the present embodiment, it is possible to objectively deduce the armature amount of the secondary motor spring. Therefore, it is possible to adjust the secondary motor spring to have the predetermined amount of arming. In addition, when the swing angle of the balance is smaller than the predetermined value even though the secondary drive spring is set to have the predetermined amount of arming, it is possible to determine that there is a problem in the finishing gear or in the exhaust. Therefore, it is possible to reliably discover the problem in the finishing gear or in the exhaust.

(Energy switching mechanism, planetary gear mechanism 90)

As illustrated in FIG. 5, while the armature amount adjusting mechanism 80 transmits the armature amount adjustment torque to the secondary mains spring, the primary motor spring described above also transmits the periodic armature torque to the mainspring secondary. Therefore, the torque adjustment device includes the energy switching mechanism that automatically changes the torque that is transmitted to the secondary power spring. The energy switching mechanism (planetary gear mechanism 90) includes a first axle (first sun gear 92a) connected to the barrel wheel with the primary leaf spring, a second axle (second sun gear 92b) connected to the leaf mechanism. armature amount adjustment 80, and a third axle (planet carrier 94) connected to the ratchet wheel to which the end portion of the secondary mains spring is attached. The combination of the first axle, the second axle and the third axle in the energy switching mechanism with the barrel wheel, the winding amount adjustment mechanism 80 and the ratchet wheel which connect destinations is not limited to the combination described above. Any combination is acceptable.

The first embodiment includes the planetary gear mechanism 90 as well as the energy switching mechanism.

FIG. 6 is an explanatory view of the planetary gear mechanism 90 and is a side sectional view taken along the line C1-C2 in FIG. 2. In fig. 6, elements that rotate in one piece have the same hatching. As shown in fig. 6, the sun gear mechanism 90 includes a first sun gear 92a connected to the barrel wheel (by the other member), a second sun gear 92b connected to the armature amount adjustment mechanism 80, a sun gear satellite 94 connected to the ratchet wheel 64, and a sun gear 93 supported by the planet carrier 94. Either the first sun gear 92a or the second sun gear 92b can be set to represent the sun wheel and the other of the two can then be set to be the internal gear.

The first sun gear 92a is fixed to the third pinion 32. The second sun gear 92b is formed to be rotatable relative to the axis 31 of the third mobile 30. The satellite holder 94 is formed to be rotatable relative to the axis 31 of the third mobile 30 and functions as the third wheel described above 34. The planet carrier 94 supports a plurality of planetary wheels 93 in rotation. In fig. 2, only a sun gear 93 is illustrated for easy understanding of the drawing. As shown in fig. 6, the sun gear 93 includes a first sun gear 93a meshing with the first sun gear 92a and a second sun gear 93b meshing with the second sun gear 92b. The first sun wheel 93a and the second sun gear 93b are fixed to each other by an axle which penetrates the planet carrier 94.

The actuation of the planetary gear mechanism 90 will be described.

First, the actuation will be described where the periodic armature torque is transmitted from the primary motor spring to the secondary motor spring during actuation of the mechanical timepiece. During operation of the mechanical timepiece, the braking spring 85 of the armature amount adjustment mechanism 80 illustrated in FIG. 5 regulates the rotation of the second winding amount adjustment wheel 84. Therefore, the rotation is also regulated in the second sun gear 92b of the sun gear mechanism 90.

On the other hand, during the actuation of the mechanical timepiece, the periodic winding torque of the primary spring is fed by the center wheel 24 to the third gear 32, and the third gear 32 and the first wheel. Solar 92a spin. Following the rotation of the first sun gear 92a, the sun gear 93 is articulated as it rotates. Thus, the planet wheel 93 and the planet carrier 94 rotate. In this way, as illustrated in FIG. 3, the periodic arming torque is transmitted from the planet carrier 94 (third wheel 34) to the ratchet wheel 64 and the secondary motor spring 65 through the second pinion 42.

Next, the actuation will be described where the armature amount adjustment torque is transmitted from the armature amount adjustment mechanism 80 to the secondary motor spring when the mechanical timepiece is stopped. When the mechanical timepiece is stopped, rotation is regulated in the center wheel 24 shown in FIG. 5. Thus, the rotation is also regulated in the first sun gear 92a of the planetary gear mechanism 90.

On the other hand, if the armature amount adjustment torque is fed from the second armature amount adjustment wheel 84 of the armature amount adjustment mechanism 80 to the second sun gear 92b of planetary gear mechanism 90, the second solar 92b rotates. Following the rotation of the second sun gear 92b, the sun gear 93 is articulated when it rotates. So, the satellite holder 94 rotates. In this way, as illustrated in FIG. 3, the armature amount adjustment torque is transmitted from the planet carrier 94 (third wheel 34) to the ratchet wheel 64 and the secondary motor spring 65 through the second pinion 42.

As illustrated in FIG. 5, the torque adjustment device includes the arming amount holding unit 80b which holds the armature amount of the secondary mains spring and the planetary gear mechanism 90. Accordingly, it is possible to switch automatically between the transmission of the periodic winding torque of the primary motor spring to the secondary motor spring when the mechanical timepiece is actuated and the transmission of the armature quantity adjustment torque of the armature amount adjustment mechanism 80 to the secondary motor spring when the mechanical timepiece is stopped. Therefore, it is not necessary to provide a mechanism for disconnecting the armature amount adjusting mechanism 80 and the finishing gear from each other, thereby providing excellent volumetric efficiency.

(First modification example of the first embodiment, differential gear device 190)

FIG. 7 is an explanatory view of a differential gear device 190 according to a first modification example of the first embodiment and is a side sectional view in a portion corresponding to the line C1-C1 in FIG. 2. In fig. 7, elements that rotate in one piece have the same hatching. The first embodiment described above includes a planetary gear mechanism 90 illustrated in FIG. 6 as energy switching mechanism. However, the first modification example is different in that the differential gear device 190 illustrated in FIG. 7 is intended as the energy switching mechanism. For elements with the same configuration as those in the first embodiment, their detailed description will be omitted.

As illustrated in FIG. 7, the differential gear device 190 includes a first side wheel 192a operating as a first input axle of the energy switching mechanism, a second side wheel 192b operating as a second input axle, and a working carrier 194b. like an output axle. That is, the differential gear device 190 includes the first side wheel 192a connected to the barrel wheel, the second side wheel 192b connected to the armature amount adjustment mechanism 80, the connected carrier 194 at the ratchet wheel 64, and a gear wheel 193 supported by the carrier 194.

The first side wheel 192a is fixed to the third pinion 32. The second side wheel 192b is fixed to the differential pinion 191 and is rotatable relative to the axis 31 of the third mobile 30 with the differential gear 191. The carrier 194 is formed to be rotatable relative to the axis 31 of the third mobile 30 and functions as the third wheel 34 described above. The carrier 194 supports one or more sprocket wheels 193 in rotation. The gear wheel 193 meshes with both the first side wheel 192a and the second side wheel 192b.

The actuation of the differential gear device 190 will be described.

First, the actuation will be described where the periodic armature torque is transmitted from the primary motor spring to the secondary motor spring during the actuation of the mechanical timepiece. During the actuation of the mechanical timepiece, the rotation is regulated in the second side wheel 192b. On the other hand, during the actuation of the mechanical timepiece, the periodic winding torque of the primary motor spring is supported from the center wheel 24 towards the third gear 32, and the third gear 32 and the first side wheel 192a. rotate. Following the rotation of the first side wheel 192a, the gear wheel 193 is articulated as it rotates. Thus, the gear wheel 193 and the carrier 194 rotate. In this way, the periodic arming torque is transmitted from the carrier 194 (third wheel 34) to the ratchet wheel 64 and the secondary motor spring 65 by the second gear 42 illustrated in FIG. 3.

Next, the actuation will be described where the armature amount adjustment torque is transmitted from the armature amount adjustment mechanism 80 to the secondary motor spring when the mechanical timepiece is stopped. When the mechanical timepiece is stopped, rotation is regulated in the first side wheel 192a. On the other hand, if the armature amount adjustment torque is sustained from the second armature amount adjustment wheel 84 of the armature amount adjustment mechanism 80 to the second side wheel 192b by the differential gear 191 of the differential gear device 190, the second side wheel 192b rotates. Following the rotation of the second side wheel 192b, the gear wheel 193 is articulated as it rotates. Thus, the gear wheel 193 and the carrier 194 rotate. In this manner, the armature amount adjustment torque is transmitted from the carrier 194 (third wheel 34) to the ratchet wheel 64 and the secondary motor spring 65 through the second gear 42 illustrated in FIG. 3.

In the differential gear device 190 of the first modification example illustrated in FIG. 7, similar to the planetary gear mechanism of the first embodiment, it is possible to automatically switch between transmission of the periodic arming torque from the primary motor spring to the secondary motor spring when the mechanical timepiece is actuated and transmitting the armature amount adjustment torque from the armature amount adjusting mechanism 80 to the secondary motor spring when the mechanical timepiece is stopped. Therefore, it is not necessary to provide a mechanism for disconnecting the armature amount adjusting mechanism 80 and the finishing gear from each other, thereby providing excellent volumetric efficiency.

(Second modification example of the first embodiment, armature amount adjustment mechanism 180)

FIG. 8 is an explanatory view of an armature amount adjustment mechanism 180 according to a second modification example of the first embodiment, and FIG. 8a is a side sectional view in the region corresponding to the line C1-C1 in FIG. 2. The armature amount adjusting mechanism 80 described above of the first embodiment illustrated in FIG. 5 includes the braking spring 85 as the arming amount holding unit 80b. However, the armature amount adjustment mechanism 180 of the second modification example illustrated in FIG. 8a is different in that a braking gear 186 and a braking jumper 185 are provided as a holding amount holding unit 180b. For elements with the same configuration as those in the first embodiment, their detailed description will be omitted.

As illustrated in FIG. 8a, the arming amount adjustment unit 180a includes a wrap amount adjusting screw 181, a first wrap amount adjusting wheel 182, and a second waving amount adjusting wheel. The armature adjustment screw 181 is formed to have a polygonal shape such as a hexagon with two plates in the width, and is formed to be able to engage the quantity adjustment tool. winding.

The arming amount holding unit 180b includes a braking pinion 186 and a braking pin 185. The braking pinion 186 is attached coaxially to the second pinch adjustment wheel 184. In the braking jumper 185, the base end portion is attached to the work train deck 9 and the vertex portion meshes with the braking pinion 186.

FIG. 8b is a front view of the arming quantity holding unit. The braking jumper 185 is formed of a leaf spring material to be elastically deformable. Its top portion meshes with a tooth portion formed on an outer periphery of the brake pinion 186.

The crown portion of the braking jumper 185 meshes with the tooth portion of the braking pinion 186, thereby regulating the rotation of the second armature amount adjustment wheel 184. Thus, the amount of braking pinion 186 is armature of the secondary motor spring is held. If the armature amount adjustment torque greater than a predetermined value is applied, the crown portion of the braking jumper 185 rides on the tooth portion of the braking pinion 186, thereby turning the braking pinion. 186. This also causes the second winding amount adjustment wheel 184 to rotate. Therefore, it is possible to adjust the armature amount of the secondary motor spring.

(Second embodiment)

FIG. 9 is an explanatory view of a torque adjustment device 206 according to a second embodiment and is a side sectional view in the portion corresponding to the line A1-0-P-Q-A2 in FIG. 2. In the torque adjusting device 6 described above of the first embodiment illustrated in FIG. 3, the planetary gear mechanism 90 is inserted into the third movable 30. However, the torque adjusting device 206 of the second embodiment illustrated in FIG. 9 is different in that the planetary gear mechanism 290 is inserted in the second mobile 40. As for the elements with the same configuration as those in the first embodiment, their detailed description will be omitted.

In the first embodiment described above illustrated in FIG. 3, the main body of the torque adjusting device 60 including the ratchet wheel 64, the secondary motor spring 65 and the output wheel 66 is inserted into the second mobile 40. The main body of the torque adjusting device 60 can also be inserted into the center mobile 20, the third mobile 30, the escape wheel 51, etc. which are parts other than the second mobile 40. In the second embodiment illustrated in FIG. 9, the main body of the torque adjustment device 60 is also inserted in the second mobile 40.

In contrast, in the first embodiment described above illustrated in FIG. 3, the planetary gear mechanism 90 as the energy switching mechanism is inserted into the third mobile 30 on the end gear side of the barrel wheel 10 of the secondary motor spring 65 (finishing gear between the barrel wheel 10 and the ratchet wheel 64). This energy switching mechanism may also be inserted into portions other than the third mobile 30 in the finishing gear of the barrel wheel side. This energy switching mechanism is connected to the barrel wheel 10, the ratchet wheel 64 and the armature amount adjustment mechanism 80 (through the other element).

In contrast, in the second embodiment illustrated in FIG. 9, the planetary gear mechanism 290 as the energy switching mechanism is inserted into the second moving wheel 40 of the end gear of the exhaust 50 of the secondary power spring 65 (work train between the output wheel 66 and the exhaust 50). This energy switching mechanism can also be inserted into parts other than the second mobile 40 in the finishing gear of the exhaust side. This energy switching mechanism is connected to the exhaust 50, the output wheel 66 and the armature amount adjustment mechanism 80 (through the other element).

That is to say, the energy switching mechanism (planetary gear mechanism 290) includes a first axle (first sun gear 292a) connected to the output wheel 66, a second axle (second wheel solar 292b) connected to the armature amount adjusting mechanism 80, and a third axle (planet carrier 294) connected to the exhaust 50. The combinations of the first axle, the second axle and the third axle in the mechanism of switching energy with the output wheel 66, the armature amount adjustment mechanism 80 and the exhaust 50 which are connected destinations are not limited to the combination described above. Any combination is acceptable.

The torque adjustment device 206 of the second embodiment will be described in detail.

In the torque adjustment device 206 illustrated in FIG. 9, the first sun gear 292a of the sun gear mechanism 290 functions as the output wheel 66 of the main body of the torque adjuster 60. The first sun gear 292a is attached to the shaft 41 of the second wheel 40. The second sun gear 292b is formed to be rotatable relative to the axis 41 of the second wheel 40. The planet carrier 294 is formed to be rotatable relative to the axis 41 of the second wheel 40, and functions as the second wheel described above 44. The planet carrier 294 supports a plurality of rotating planet wheels 293. The sun gear 293 includes a first sun gear 293a meshing with the first sun gear 292a and a second sun gear 293b meshing with the second sun gear 292b. The first sun wheel 293a and the second sun wheel 293b are fixed to each other by an axle which penetrates the planet carrier 294.

The operation of the planetary gear mechanism 290 will be described.

First, the actuation will be described where the actuating torque is transmitted from the secondary motor spring 65 to the exhaust 50 during the actuation of the mechanical timepiece. During the actuation of the mechanical timepiece, the rotation is regulated in the second sun gear 292b of the planetary gear mechanism 290.

In contrast, during the actuation of the mechanical timepiece, the actuating torque of the secondary motor spring 65 is supported towards the first sun gear 292a, and the first sun gear 292a rotates. Following the rotation of the first sun gear 292a, the sun gear 293 is articulated as it rotates. Thus, the planet wheel 293 and the planet carrier 294 rotate. In this way, the driving torque is transmitted from the planet carrier 294 (second gear 44) to the escapement 50.

Next, the actuation will be described where the armature amount adjustment torque is transmitted from the armature amount adjustment mechanism 80 to the secondary motor spring 65 when the mechanical timepiece is stopped. . When the mechanical timepiece is stopped, the rotation is regulated in the exhaust 50 and the planet carrier 294.

On the other hand, if the armature amount adjustment torque is supported from the armature amount adjustment mechanism 80 to the second sun gear 292b, the second sun gear 292b rotates. Following the rotation of the second sun gear 292b, the sun gear 293 rotates, but since the planet carrier 294 is stopped, the sun gear 293 does not articulate. Therefore, following the rotation of the sun gear 293, the first sun gear 292a rotates. The first sun gear 292a functions as the output wheel 66 of the main body of the torque adjusting device 60. Accordingly, the armature amount adjustment torque is transmitted from the first sun gear 292a to the secondary power spring. 65.

The torque adjusting device 206 of the second embodiment has the same effect as that of the first embodiment.

That is to say, since the planetary gear mechanism 290 is provided, it is possible to automatically switch between the transmission of the actuating torque from the secondary motor spring 65 to the exhaust 50 when the workpiece The mechanical time clock is actuated and the torque adjustment amount is transmitted from the armature amount adjusting mechanism 80 to the secondary motor spring 65 when the mechanical timepiece is stopped. Therefore, it is not necessary to provide a mechanism for disconnecting the armature amount adjusting mechanism 80 and the finishing gear from each other, thereby providing excellent volumetric efficiency.

(Third embodiment)

[0103] FIG. 10 is an explanatory view of a torque adjustment device 306 according to a third embodiment and is a front view in the state without a work train deck on the front side of the movement. In fig. 10, the main plate and the gear wheel bridge are not illustrated. In the torque adjusting device 6 described above of the first embodiment illustrated in FIG. 2, the main body of the torque adjusting device 60 includes the ratchet wheel 64. However, the torque adjusting device 306 of the third embodiment illustrated in FIG. 10 is different in that the main body of the torque adjusting device 360 includes a flywheel 364. With respect to the elements with the same configuration as those in the first embodiment, their detailed description will be omitted.

As illustrated in FIG. 10, the main body of the torque adjusting device 360 of the third embodiment includes a secondary motor spring (torque adjustment spring) 365, a flywheel (torque adjustment wheel of the wheel side of barrel) 364 to which an outer peripheral end portion (first end portion) of the secondary motor spring 365 is connected, and an output wheel (exhaust side torque adjustment wheel) 366 to which a portion of the inner peripheral end (second end portion) of the secondary motor spring 365 is connected.

The flywheel 364 is formed to have a greater moment of inertia than that of the output wheel 366. For example, an area of a thinned portion of the flywheel 364 is formed to be larger. small as that of the output wheel 366, and the thickness of the flywheel 364 is formed to be thicker than that of the output wheel 366.

In the output wheel 366, a pin 366p is erected in the direction of the flywheel 364. The flywheel 364 has a hole 364h in which the pin 366p is inserted. The hole 364h is formed to have a size that allows the pin 366p to move in the circumferential direction of the second pin 40 within a predetermined range. The pin 366p and the hole 364h regulate the relative rotation of the output wheel 366 and the flywheel 364 within the predetermined range.

The actuation of the main body of the torque adjusting device 360 of the third embodiment will be described.

When the rotation of the escape wheel 54 is stopped temporarily by the engagement of the anchor 56, the pin 366p of the output wheel 366 is in contact with an end portion of the hole 364h of the steering wheel. 364 inertia.

If the anchor 56 is disengaged, the escape wheel 54 and the output wheel 366 can rotate. Disarming the secondary drive spring 365 causes the drive torque to be applied to the output wheel 366, thereby rotating the output wheel 366. Thereafter, the drive torque is sustained from the output wheel 366 to the output wheel 366. exhaust 50, thereby actuating the mechanical timepiece. During a period until the anchor 56 again engages with the escape wheel 54, the output wheel 366 rotates by a predetermined angle.

On the other hand, since the periodic armature torque is transmitted from the primary motor spring to the flywheel 364, the flywheel 364 rotates as well. However, since the flywheel 364 has the greater moment of inertia than the output wheel 366, the flywheel 364 begins to rotate later than the output wheel 366. That is, In other words, the flywheel 364 rotates intermittently and relatively relative to the output wheel 366. Therefore, the pin 366p of the output wheel 366 that starts rotating earlier is separated from the end portion. 364h 364h of the flywheel 364. The flywheel 364 which begins to rotate later turns until the end portion of the hole 364h comes into contact with the pin 366p. Since the output wheel 366 rotates by the predetermined angle, the flywheel 364 also rotates by the predetermined angle. This causes the flywheel 364 to arm the secondary drive spring 365 by a predetermined amount between the output wheel 366 and the flywheel 364.

In this way, in the main body of the torque adjusting device 360 of the third embodiment, the secondary motor spring 365 is periodically armed by the predetermined amount. As a result, the secondary motor spring 365 is required to have a substantially constant arming amount. A substantially constant torque is supported from the secondary motor spring 365 to the exhaust 50 and the speed controller (balance 58). As a result, the cruise control can actuate the exhaust 50 at a constant cycle. This can improve the accuracy of the timepiece. Moreover, since the exhaust 50 is actuated at constant cycle, the output wheel 366 and the flywheel 364 also rotate intermittently and relative to the constant cycle. This allows the secondary motor spring 365 to be armed with the constant cycle, thereby further improving the accuracy of the timepiece.

The technical scope of the present invention is not limited to the embodiments described above and includes those which have different modifications added to the embodiments described above without departing from the essentials of the present invention. invention. That is, specific materials and layer configurations that are described as an example in the embodiments are merely a few examples and can be modified appropriately.

For example, without being limited to the crab tooth exhaust described above, the exhaust mechanism may use various mechanisms.

Claims (9)

A torque adjusting device (6) comprising: a torque adjusting spring (65) inserted in the work train between the barrel wheel (10) and the exhaust (50) of a mechanical timepiece (1); an exhaust-side torque adjusting wheel (50) to which is connected a first end portion of the torque adjusting spring (65) and which is connected to the end-of-work gear on the exhaust side (50); ) rather than the torque adjustment spring (65); a barrel wheel side adjusting wheel (10) to which is connected a second end portion of the torque adjusting spring (65), which is connected to the finishing gear train on the side of the barrel wheel (10). barrel (10) rather than the torque adjusting spring (65) and which rotates intermittently and relative to the exhaust-side torque adjusting wheel (50); an armature amount adjusting mechanism (80) which adjusts the arming amount of the torque adjustment spring (65); and an energy switching mechanism which is inserted into the end work train of the barrel wheel side (10) or into the exhaust side finishing work train (50) and which is connected to the feed quantity adjustment mechanism arming (80), wherein the armature amount adjusting mechanism (80) includes a winding amount holding unit (80b) which holds the arming amount of the torque adjusting spring (65) and a winding amount holding unit (80b). armature amount display (80c) which displays the arming amount of the torque adjustment spring (65), wherein, when inserted into the barrelwheel side finishing gear train (10), the energy switching mechanism is connected to the barrel wheel (10), the barrel wheel (10) and the armature amount adjustment mechanism (80), and wherein, when inserted into the exhaust-side finishing work train (50), the energy switching mechanism is connected to the exhaust (50), the exhaust-side torque adjusting wheel (50) and the armature amount adjustment mechanism (80). Torque adjustment device (6) according to claim 1, wherein the armature amount adjusting mechanism (80) includes an armature amount adjusting wheel (82, 84) which adjusts the arming amount of the torque adjustment spring (65), and wherein the armature amount holding unit (80b) includes a braking spring (85) which applies frictional torque to the armature amount adjusting wheel (82, 84). Torque adjusting device (6) according to claim 1, wherein the armature amount adjusting mechanism (80) includes an armature amount adjusting wheel (82, 84) which adjusts the arming amount of the torque adjustment spring (65), and wherein the arming amount holding unit (80b) includes a braking jumper (185) which regulates the rotation of the arming amount adjusting wheel (82, 84). Torque adjusting device (6) according to one of claims 1 to 3, wherein the energy switching mechanism is a planetary gear mechanism (90). Torque adjusting device (6) according to one of claims 1 to 3, wherein the energy switching mechanism is a differential gear device (190). The torque adjusting device (6) according to any one of claims 1 to 5, further comprising: a torque adjustment exhaust (50) which is connected to the exhaust (50) and which rotates intermittently and relatively the torque adjusting wheel of the cylinder wheel side (10) with respect to the wheel torque adjustment device on the exhaust side (50). The torque adjusting device (6) according to any one of claims 1 to 5, further comprising: an inertia flywheel (364) serving as a torque adjusting wheel on the barrel wheel side (10), whose moment of inertia is greater than that of the exhaust-side torque adjusting wheel (50). 8. Movement (5) comprising: the torque adjusting device (6) according to claim 1. 9. Mechanical timepiece (1) comprising: the torque adjusting device (6) according to claim 1.