Mechanical timepiece

Abstract

To improve the persistence of motions of a rate adjusting mechanism 30.SOLUTION: A mechanical timepiece 1 includes: a rotary body in a rate adjusting mechanism 30, the rotary body making forward reverse rotating motions; a permanent magnet 41 making forward reverse rotating motions in association with forward reverse rotating motions of the rotary body; and a stator 42 provided to generate magnetic torque on the permanent magnet 41 according to the angle of rotations of the permanent magnet 41. The mechanical timepiece also includes a regulation unit for regulating the range of rotations of the rotary body so that action torque including magnetic torque and affecting rotations of the permanent magnet is not generated in the same direction as the direction of rotations of the permanent magnet 41 when the permanent magnet 41 is heading to the return position of the forward reverse rotating motions.SELECTED DRAWING: Figure 8

Description

Technical Field

[0001] The present invention relates to a mechanical watch.

Background Art

[0002] The following Patent Document 1 discloses a mechanical watch that generates electricity by providing a permanent magnet that rotates integrally with a balance wheel, and controls the rotation of the balance wheel based on a back electromotive voltage generated in response to the rotation of the permanent magnet.

Prior Art Document

Patent Document

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] Here, in the mechanical watch of Patent Document 1, when a magnetic torque is generated on the permanent magnet in the direction of advancing the rotation of the balance wheel provided in the speed regulating mechanism, the balance wheel may not be able to turn back in the reverse direction, and there is a risk that its forward and reverse rotational movements may stop.

[0005] The present invention has been made in view of the above problems, and an object thereof is to provide a mechanical watch that improves the sustainability of the movement in the speed regulating mechanism.

Means for Solving the Problems

[0006] (1) A mechanical clock having a rotating body that rotates forward and backward within a speed regulating mechanism, a permanent magnet that rotates forward and backward in accordance with the forward and backward rotation of the rotating body, and a stator provided so as to generate a magnetic torque with respect to the permanent magnet according to the rotation angle of the permanent magnet, wherein a regulating portion is provided to regulate the rotation range of the rotating body so that an acting torque that includes the magnetic torque and affects the rotation of the permanent magnet does not occur in the same direction as the rotation direction of the permanent magnet when the permanent magnet moves toward the folding position of the forward and backward rotation. (2) The mechanical clock according to (1), further comprising an escapement mechanism including a pinion and an anchor that intermittently drives the pinion when a pendulum that rotates forward and backward in accordance with the forward and backward rotation of the rotating body collides therewith, wherein the regulating portion is a portion of the anchor that is collided with by the pendulum. (3) The mechanical clock according to (2), wherein the collided portion includes a shape that extends along the rotation locus of the pendulum. (4) The mechanical clock according to (2) or (3), wherein the collided portion includes a shape that extends along the circumferential surface of the rotation axis of the rotating body. (5) The mechanical clock according to any one of (2) to (4), wherein the collided portion includes a collided surface that is inclined with respect to the collision direction of the pendulum. (6) The mechanical clock according to any one of (2) to (5), wherein the collided portion includes a first collided portion that collides with the pendulum rotating in the forward direction and a second collided portion that collides with the pendulum rotating in the reverse direction, and the first collided portion and the second collided portion each include a first portion that extends parallel to each other and a second portion that extends in a direction away from each other from the first portion, and the second portion is longer than the first portion. (7) The mechanical clock according to any one of (1) to (6), wherein the rotating body includes a crown wheel and a hairspring that elastically deforms to rotate the crown wheel forward and backward, and the acting torque is a combined torque of the magnetic torque and the spring torque of the hairspring. (8) The mechanical clock according to any one of (1) to (7), wherein the rotating body includes a crown wheel, and a regulated portion that contacts the regulating portion is provided on the crown wheel. (9) In any one of (1) to (8) above, the regulating unit regulates the rotation range of the rotating body in the same direction as the rotation direction of the permanent magnet so that the maximum value in the change of the magnetic torque according to the rotation angle does not appear, a mechanical watch.

Advantages of the Invention

[0007] According to the aspects (1) to (9) of the present invention described above, it is possible to provide a mechanical watch that improves the sustainability of the movement in the speed regulating mechanism.

Brief Description of the Drawings

[0008]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6A

Figure 6B

Figure 7

Figure 8

Figure 9A

Figure 9B

Figure 10

Figure 11

Figure 12

Figure 13

Figure 14

Embodiments for Carrying Out the Invention

[0009] Hereinafter, embodiments of the present invention (hereinafter, this embodiment) will be described in detail with reference to the drawings.

[0010] The mechanical clock 1 according to this embodiment includes a mainspring 11, and controls the movement of the mainspring 11 by an escapement mechanism 20 and a speed control mechanism 30, and is a clock that drives the hands 131. The power from the mainspring 11 is transmitted to the escapement mechanism 20 and the speed control mechanism 30 through the wheel train 12. These members and mechanisms are incorporated in the floor board 10. Note that the mainspring 11, the wheel train 12, and the hands 131 are shown with reference to FIG. 5, and the illustration of the specific structure is omitted.

[0011] As shown in FIG. 2, the escapement mechanism 20 includes a crown wheel 21 and an anchor 22. The escapement mechanism 20 continuously applies a force for reciprocating movement to the escape wheel 31 provided in the speed control mechanism 30, and rotates each gear in the wheel train 12 at a constant speed by the regular vibration from the escape wheel 31. In FIG. 2, for the purpose of showing the escapement mechanism 20, the illustration of the escape wheel 31 and the hairspring 32 is omitted. Also, the illustration of the hairspring 32 is omitted in FIG. 1.

[0012] The gang gear 21 meshes with the crank 22 to receive the rhythm marked by the speed regulating mechanism 30 from the crank 22 and convert it into a regular rotational motion. The crank 22 includes a crank shaft 221 which is a rotation axis, a rod portion 222 having a collision portion at its tip that collides with a swinging stone 312a (see FIGS. 3, 8, etc.) that is fixed to the swing seat 312 and rotates together with the tension shaft 311, a first arm portion 223 to which an engaging claw 223a that collides with the gang gear 21 is attached, and a second arm portion 224 that extends in the opposite direction of the first arm portion 223 and to which a protruding claw 224a that collides with the gang gear 21 is attached. For example, the tension wheel 31 is designed to perform one reciprocating motion in 2 seconds, and the gang gear 21 performs one step of operation per second.

[0013] As shown in FIGS. 3 and 4, the speed regulating mechanism 30 includes a tension wheel 31 and a hairspring 32.

[0014] The tension wheel 31 is rotatably supported in a forward and reverse direction by the power transmitted by the gear train 12 with the tension shaft 311, which is its rotation axis, as the center of rotation. The hairspring 32 is spiral, the outer end thereof is fixed to the hairspring holder 34 (see FIG. 1), and the inner end thereof is fixed to the tension shaft 311. However, the inner end of the hairspring 32 can also be non-fixed to the tension shaft 311. In this case, the hairspring 32 can be elastically deformed by being rotated by a protruding portion (not shown) that protrudes downward from the holding member 140. Due to the expansion and contraction motion (elastic deformation) of the hairspring 32, the tension wheel 31 repeatedly performs a forward and reverse rotational motion (reciprocating motion) at a constant period.

[0015] In this embodiment, the beard spring 32 is made of a resin material with a low Young's modulus. Thereby, compared with the case where it is made of a metal material, the low-speed vibration of the balance wheel 31 can be realized. Further, in this embodiment, the rotation angle [deg] of the balance wheel 31 (and the permanent magnet 41 described later) in the state where the beard spring 32 is at the neutral position of elastic deformation is set to 0°. The neutral position of the elastic deformation of the beard spring 32 is the position where the beard spring 32 is at its natural length. Further, power from the mainspring 11 is supplied to the balance wheel 31 in a state where it is near the neutral position of the elastic deformation of the beard spring 32.

[0016] The mechanical watch 1 includes a rate adjustment means 40. The rate adjustment means 40 includes a permanent magnet 41, a stator 42, and a coil 43 shown in FIG. 2 and the like, a control circuit 44, a rotation detection circuit 45, a rate adjustment pulse output circuit 46, a frequency division circuit 47, an oscillation circuit 48, and a braking circuit 80. The rate adjustment means 40 performs rate adjustment based on a detection signal detected based on the forward and reverse rotational movements of the permanent magnet 41 and the reference oscillation frequency of a crystal oscillator 70 which is a reference signal source. Note that the rate adjustment means 40 does not necessarily need to independently include each circuit shown in FIG. 5, and any means capable of realizing each function of each circuit may be used.

[0017] The permanent magnet 41 is a disk-shaped rotating body magnetized with two poles, and as shown in FIGS. 6A and 6B, it is a magnet having an N-pole portion 411 and an S-pole portion 412 magnetized with N and S poles in the radial direction. Further, an insertion hole 41h through which the balance staff 311 is inserted is formed in the central portion of the permanent magnet 41. The permanent magnet 41 rotates forward and backward together with the balance wheel 31 so that the rotation angle becomes the same as the rotation angle of the balance wheel 31 along with the forward and reverse rotational movements of the balance wheel 31 (balance staff 311).

[0018] The stator 42 is made of a soft magnetic material, has a first magnetic portion 421 and a second magnetic portion 422, and forms a magnetic circuit together with the coil 43. The stator 42 is provided so that a magnetic torque is generated with respect to the permanent magnet 41 according to the rotation angle of the permanent magnet 41.

[0019] The control circuit 44 controls the operations of the respective circuits included in the step rate adjustment means 40. The control circuit 44 can perform braking control for controlling the braking force for braking the permanent magnet 41 by controlling the braking circuit 80. The braking force can act on the permanent magnet 41, for example, based on an electromagnetic brake. Note that the electromagnetic brake is a braking force obtained by a generated electromotive force that short-circuits the first terminal and the second terminal of the coil 43 to form a closed loop state and generates a magnetic field in a direction that obstructs the change in the magnetic flux generated in the coil 43 as the permanent magnet 41 rotates.

[0020] The rotation detection circuit 45 detects a detection signal based on the voltage waveform generated in the coil 43 due to the movement of the permanent magnet 41. The speed adjustment pulse output circuit 46 outputs a speed adjustment pulse based on the reference signal generated by the frequency division circuit 47 and the detection signal detected by the rotation detection circuit 45. Note that the step rate adjustment means 40 can also be configured such that braking control (step rate adjustment) can be performed by the braking circuit 80 without providing the speed adjustment pulse output circuit 46. The oscillation circuit 48 outputs a predetermined oscillation signal based on the oscillation frequency of the crystal oscillator 70. The frequency division circuit 47 divides the oscillation signal output from the oscillation circuit 48. The frequency division circuit 47 generates a reference signal that is output approximately every 1000 [ms] by dividing the oscillation signal based on the crystal oscillator 70. However, it is not limited to this, and the reference signal may be output at intervals corresponding to the period of the speed adjustment mechanism 30.

[0021] The mechanical clock 1 has a power generation function using the principle of electromagnetic induction. In the present embodiment, the speed adjustment mechanism 30 functions as part of the power generator. As the forward and reverse rotational movements of the crown wheel 31 occur, the permanent magnet 41 makes forward and reverse rotational movements, and power generation is performed by the current generated in the coil 43 based on the change in the magnetic field due to the movement of the permanent magnet 41. The power source circuit 60 is activated using the power extracted by such an operating principle. When the power source circuit 60 is activated, the control circuit 44 can be driven.

[0022] The rectifier circuit 50 rectifies the current generated in the coil 43 due to the movement of the permanent magnet 41 accompanying the forward and reverse rotational movements of the cam wheel 31 of the speed control mechanism 30. The power supply circuit 60 includes, for example, a capacitor, and stores electric power for driving the control circuit 44 based on the current rectified by the rectifier circuit 50.

[0023] In the following description, the attractive force due to the magnetic torque acting between the permanent magnet 41 and the stator 42 when the coil 43 is in a non-energized state is referred to as the "holding torque". The holding torque acts in a direction corresponding to the arrangement of welding parts and notches formed of non-magnetic materials in the stator 42. Further, the torque generated by the elastic deformation of the wiper 32 is referred to as the "spring torque". The spring torque depends on the above-described Young's modulus.

[0024] FIG. 7 shows the holding torque and the spring torque in the present embodiment. Although not shown, the waveforms of the holding torque and the spring torque at negative rotation angles are point-symmetrical with respect to the waveforms shown in FIG. 7 about the 0° position.

[0025] As shown in FIG. 7, when the permanent magnet 41 rotating in the positive direction (here, the direction in which the rotation angle increases positively) moves from the 0° position toward the turning-back position, the spring torque of the wiper 32 acting in the direction opposite to the rotation direction of the permanent magnet 41 increases linearly.

[0026] The holding torque acts in the direction opposite to the rotation direction of the permanent magnet 41 when the permanent magnet 41 rotating in the positive direction moves from the 0° position toward the 180° position, and acts in the same direction as the rotation direction of the permanent magnet 41 when the permanent magnet 41 rotating in the positive direction moves from the 180° position toward the turning-back position. That is, between 0° and the turning-back position, the node (the position where the holding torque becomes 0) of the waveform indicating the holding torque is only at the 180° position. The holding torque has the tendency shown in FIG. 7 to reduce the spring torque.

[0027] Note that the "folding position" is the position where the rotation direction of the tension ring 31 is reversed when a general-purpose ankle disclosed in Patent Document 1 (International Publication No. 2023 / 176378) or the like is adopted, and specifically, it is ±340°.

[0028] With reference to FIGS. 6A and 6B, an example of the arrangement of the permanent magnet 41, the stator 42, and the tension coil 311 for realizing the holding torque of the tendency shown in FIG. 7 will be described.

[0029] The planar shape of the permanent magnet 41 is a perfect circular shape in which the distance from the central position 41O to the outer peripheral surface is equal at any position in the circumferential direction.

[0030] The first magnetic portion 421 of the stator 42 has a first end portion 421a provided to face the outer peripheral surface of the permanent magnet 41, and the second magnetic portion 422 has a second end portion 422a provided to face the outer peripheral surface of the permanent magnet 41. The first end portion 421a includes a curved inner peripheral surface 421a1 along the outer peripheral surface of the permanent magnet 41 in the first magnetic portion 421. The second end portion 422a includes a curved inner peripheral surface 422a1 along the outer peripheral surface of the permanent magnet 41 in the second magnetic portion 422.

[0031] The stator 42 is provided with a first welding portion 423 that separates the magnetic coupling between the first end portion 421a and the second end portion 422a, and a second welding portion 424 that separates the magnetic coupling between the first end portion 421a and the second end portion 422a and is disposed opposite to the first welding portion 423 via the permanent magnet 41. However, if the magnetic coupling between the first end portion 421a and the second end portion 422a is separated, they may be connected via a constricted portion, for example.

[0032] Notches n11 and n12 are formed on the inner peripheral surface 421a1 of the first end portion 421a, and notches n21 and n22 are formed on the inner peripheral surface 422a1 of the second end portion 422a. Note that the number of notches, the interval between each notch, and the shape of each notch are not limited to those shown in the figures.

[0033] The first end portion 421a, the second end portion 422a, the first welding portion 423, and the second welding portion 424 are provided such that the inner peripheral surface of the opening formed by the stator 42 forms a circular opening that is a perfect circle with the distance from the central position 42O being equal at any position in the circumferential direction. The inner peripheral surface of the opening formed by the stator 42 means the inner peripheral surface excluding the portions where the notches n11, n12, n21, and n22 are formed.

[0034] In FIG. 6A, a state where the permanent magnet 41 is at the 0° position is shown. In the state where the permanent magnet 41 is at the 0° position, the N - pole portion 411 is arranged on the second end portion 422a side, and the S - pole portion 412 is arranged on the first end portion 421a side. With such a configuration, in the state at the 0° position, the permanent magnet 41 will be magnetically stable.

[0035] In the present embodiment, as shown in FIG. 6A, the platen 311, the permanent magnet 41, and the stator 42 are arranged so as to shift the central position 41O of the permanent magnet 41 at the 0° position with respect to the rotation center 311O of the platen 311, and also to shift the central position 42O of the opening of the stator 42 with respect to the rotation center 311O of the platen 311. Thereby, the central position 41O of the permanent magnet 41, the rotation center 311O of the platen 311, and the central position 42O of the opening of the stator 42 are on the same line and at different positions from each other.

[0036] Also, the central position 41O of the permanent magnet 41 at the 0° position is arranged at a position symmetric to the central position 42O of the opening of the stator 42 via the rotation center 311O of the platen 311. Also, the amount of shift s1 of the central position 41O with respect to the rotation center 311O is made the same as the amount of shift s2 of the central position 42O with respect to the rotation center 311O.

[0037] The distance d2 between the outer peripheral surface of the S - pole portion 412 of the permanent magnet 41 at the 0° position and the inner peripheral surface 421a1 of the first end portion 421a is set larger than the distance d1 between the outer peripheral surface of the N - pole portion 411 of the permanent magnet 41 at the 0° position and the inner peripheral surface 422a1 of the second end portion 422a. With such an arrangement configuration, a relatively large holding torque acts on the permanent magnet 41 in the direction toward the 0° position.

[0038] Figure 6B shows a state in which the permanent magnet 41 has rotated 180° in the positive direction from the state shown in Figure 6A. As shown in Figure 6B, in the state where the permanent magnet 41 is at the 180° position, the central position 41O of the permanent magnet 41 coincides with the central position 42O of the opening of the stator 42. Therefore, the distance between the outer peripheral surface of the permanent magnet 41 and the inner peripheral surface of the stator 42 becomes uniform in the circumferential direction, the S - pole portion 412 faces the second end portion 422a with a gap d4, the N - pole portion 411 faces the first end portion 421a with a gap d3, and the gap d4 and the gap d3 are equal.

[0039] The gap d3 and the gap d4 are larger than the gap d1 and smaller than the gap d2. With such an arrangement configuration, a relatively small holding torque acts on the permanent magnet 41 in the direction toward the 180° position. Note that if the difference between the gap d3 and the gap d4 is smaller than the difference between the gap d1 and the gap d2, the gap d3 and the gap d4 do not necessarily have to be the same.

[0040] In this embodiment, the shift amounts s1 and s2 are set so that the holding torque that tends to be stable at the 0° position is sufficiently larger than the holding torque that tends to be stable at the 180° position, and the shift amounts s1 and s2 are set so that it is stable at the 0° position and unstable at the 180° position. Thereby, the waveform of the holding torque shown in Figure 7 is realized.

[0041] The permanent magnet 41 is held by the disk-shaped holding member 140 via the spacer 150. An opening 140h is formed in the holding member 140. The holding member 140 rotates integrally with the tension spring 311 that is press-fitted into the opening 140h. As the holding member 140 rotates with the tension spring 311, the permanent magnet 41 held by the holding member 140 rotates. The center position of the opening 140h of the holding member 140 is offset from the rotation center 311O of the tension spring 311 and coincides with the center position 41O of the permanent magnet 41. Due to such an eccentric structure, as shown in FIGS. 6A and 6B, the permanent magnet 41 and the like are arranged.

[0042] FIG. 8 is an enlarged view showing the ankle of the present embodiment. In FIG. 8, a portion of the ankle 22 behind the swing seat 312 is indicated by a broken line.

[0043] The ankle 22 has collision parts 2221 and 2222 that are regulation parts. The collision parts 2221 and 2222 are parts of the ankle 22 called parts such as a crab claw. In the present embodiment, the collision part 2221 and the collision part 2222 are formed in a shape that extends in a direction away from each other.

[0044] The collision parts 2221 and 2222 have a shape that extends along the rotation locus T (a belt-shaped circle indicated by a dotted line in FIG. 8) of the swing stone 312a in the posture when the swing stone 312a contacts, and also have a shape that extends along the circumferential surface of the tension spring 311.

[0045] As shown in FIG. 8, the collision parts 2221 and 2222 have first parts 2221b and 2222b that extend parallel to each other, and second parts 2221c and 2222c that extend in a direction away from each other from the first parts 2221b and 2222b, and the second parts 2221c and 2222c are longer than the first parts 2221b and 2222b.

[0046] The collision part 2221 is provided with a collision surface 2221a that is a flat surface at the tip. The collision part 2222 is provided with a collision surface 2222a that is a flat surface at the tip.

[0047] The pendulum weight 312a stops by colliding with the collision surfaces 2221a and 2222a, and the rotation range of the tension ring 31 is restricted. In the present embodiment, the collision portions 2221 and 2222 are shaped such that the restricted positions where the rotation of the tension ring 31 is restricted are ±270°.

[0048] When the rotation of the tension ring 31 is restricted at the restricted positions of ±270°, it is possible to prevent a combined torque obtained by combining the holding torque and the spring torque from being generated in the same direction as the rotation direction of the permanent magnet 41 when the permanent magnet 41 moves toward the turning-back position of the forward and reverse rotational movements. The "combined torque (acting torque)" is a torque that affects the rotation of the permanent magnet 41, and the rotation of the permanent magnet 41 will be strengthened or weakened according to the combined torque.

[0049] Since the rotation of the tension ring 31 is restricted at the restricted position, it is possible to prevent a dotted line obtained by folding back a straight line indicating the spring torque shown in FIG. 7 via the horizontal axis from becoming smaller than the holding torque, and to suppress the stop of the rotation of the tension ring 31. By restricting the rotation of the tension ring 31 at the restricted position, it becomes possible to continuously rotate the tension ring 31 in the forward and reverse directions, and it also becomes possible to achieve low vibration of the tension ring 31.

[0050] The shape of the angle 22 shown in FIG. 8 is an example. When it is desired to narrow the rotation range of the tension ring 31, the lengths of the second portions 2221c and 2222c may be increased, and when it is desired to widen the rotation range of the tension ring 31, the lengths of the second portions 2221c and 2222c may be decreased. The collision portions 2221 and 2222 may be formed by extending the jaws in a general-purpose angle, or may be formed by attaching separate parts to the jaws.

[0051] Figures 9A and 9B show a series of operations in which the pendulum stone 312a (ten-ring 31) moves from the -90° position to the 270° position. The series of operations shown in FIG. 9A shows the state until the stop of the gang gear 21 by the engaging claw 223a is released and the gang gear 21 resumes rotation. The series of operations shown in FIG. 9B shows the state in which the gang gear 21 is stopped from rotating by the disengaging claw 224a and the pendulum stone 312a rotates until it collides with the collision portion 2221. Each angle described in FIGS. 9A and 9B indicates the rotation angle of the ten-ring 31 and shows the postures of the gang gear 21 and the crank 22 corresponding to the rotation angle. Further, the angles described in FIGS. 9A and 9B correspond to the angle of the center position of the pendulum stone 312a that has collided with the collision surface 2221a with respect to the straight line connecting the rotation center of the crank 221 and the rotation center of the pendulum base 321 (ten base 311), as described in the figure showing the 270° position in FIG. 9B. The state in which the straight line connecting the rotation center of the crank 221 and the rotation center of the pendulum base 321 overlaps the center position of the pendulum stone 312a is defined as the reference position (0° position).

[0052] As shown in FIG. 9A, as the pendulum base 312 (ten-ring 31) rotates, the pendulum stone 312a rotates and collides with the crank 22. As a result, the crank 22 rotates about the crankshaft 221 as the rotation center. When the crank 22 rotates, the stop of the gang gear 21 by the engaging claw 223a is released, and the gang gear 21 starts to rotate.

[0053] After the operation shown in FIG. 9A, as shown in FIG. 9B, the gang gear 21 contacts the disengaging claw 224a and its rotation is stopped again. Further, the pendulum stone 312a continues to rotate and collides with the collision portion 2221 of the crank 22. As a result, the rotation of the pendulum stone 312a stops and the rotation of the ten-ring 31 stops. Then, the rotation direction of the ten-ring 31 is reversed by the spring torque of the beard winch 32, and the pendulum stone 312a starts to rotate in the direction opposite to the arrow R shown in FIG. 9B.

[0054] As shown in FIG. 7, when the rotation range of the valve ring 31 is 270° or less, regardless of the rotation angle, the absolute value of the holding torque is smaller than the absolute value of the spring torque, and the magnitude of the holding torque does not exceed the magnitude of the spring torque. Therefore, when the valve ring 31 is on the way to the folded-back position, it is suppressed that the valve ring 31 stops due to the influence of the holding torque acting in the same direction as the rotation direction of the valve ring 31.

[0055] In FIG. 7, an example is shown in which the rotation range of the valve ring 31 is ±270° or less. However, the rotation range of the valve ring 31 may be regulated so that at least the maximum value (the peak of the holding torque) in the change of the holding torque does not appear. In the holding torque having the tendency shown in FIG. 7, a maximum value appears at the 315° position. Therefore, the rotation range of the valve ring 31 can also be regulated to be less than ±315°.

[0056] The collision portions 2221 and 2222 of the arm 22 may be longer than those shown in FIG. 8, for example, in the shape shown in FIG. 10. In the first modification, the collision portions 2221 and 2222 have a shape extending along the circumferential surface of the valve core 311. In the arm shown in FIG. 10, the rotation range of the valve ring 31 is regulated to ±180°. Thereby, the spring torque can be made smaller (see FIG. 7).

[0057] The collision portion 2221 of the arm 22 may have a collision surface 2221a inclined with respect to the collision direction of the pendulum 312a, for example, as shown in FIG. 11. In FIG. 11, the arrow V indicates the collision direction and the magnitude of the collision energy. Also, in FIG. 11, the straight line connecting the point Q and the point R indicates the surface direction of the collision surface 2221a.

[0058] The impact energy indicated by arrow V acts in a direction perpendicular to the straight line connecting the rotation center 311O of the swing seat 312 (the tenzhen 311) and the impact point P between the swing stone 312a and the impacted surface 2111a. Also, arrow V0 in FIG. 11 indicates the vertical component of the impact energy with respect to the impacted surface 2111a. When the angle between arrow V and arrow V0 is θ, since V0 = Vcosθ, the rebound energy V0' generated by the impact of the swing stone 312a is Vcosθ. Further, if the rotational energy of the swing stone 312a acting in the opposite direction of the impact direction among the rebound energy V0' is V1, then V1 = V0'cosθ = V(cosθ) 2 It follows that. Since V > V1, the rebound energy is smaller than the impact energy. By reducing the rebound energy, the movement of the ten ring 31 immediately after the swing stone 312a collides with the ankle 22 can be stabilized, and a decrease in the step accuracy can be suppressed. Note that the impacted surface 2222a may also have a shape that exhibits a similar function.

[0059] As shown in FIG. 12, the regulation of the rotation range of the ten ring 31 may be realized by providing a protrusion 315, which is a regulated part, on the ten ring 31 and providing a regulating part 320 that the protrusion 315 collides with on the rotation locus of the protrusion 315. The regulating part 320 is fixed to a member disposed around the speed regulating mechanism 30. In the configuration of FIG. 12, the rotation range of the ten ring 31 is less than ±180°. Therefore, the spring torque can be made smaller.

[0060] Note that the configuration for regulating the rotation range of the ten ring 31 is not limited to the example of FIG. 12, and it may also be realized by providing a part having a function similar to that of the protrusion 315 on any of the rotating bodies that rotate together with the tenzhen 311.

[0061] When the mechanical timepiece 1 does not have a beard escapement 32 and the crown wheel 31 (permanent magnet 41) rotates in a forward and reverse rotational motion only by the holding torque, the rotation range of the crown wheel 31 is preferably set to ±180° or less. As shown in FIG. 13, if the rotation range of the crown wheel 31 is ±180° or less, the holding torque always acts in a direction opposite to that of the permanent magnet 41 rotating in the forward direction. Therefore, the crown wheel 31 rotating in the forward direction can reverse from the regulated position and continue the forward and reverse rotational motion. Note that the regulation of the rotation range in the fourth modification example is realized by adopting the angle 22 having the shape shown in FIG. 10, or the protrusion 315 and the regulating portion 320 shown in FIG. 12.

[0062] In FIG. 7, an example in which the spring torque is 0 at the 0° position of the crown wheel 31 is shown, while in FIG. 14, an example in which the position where the spring torque is 0 (neutral position of the elastic deformation of the beard escapement 32) is shifted from the 0° position of the crown wheel 31 is shown. Such a spring torque can be realized by adjusting the arrangement of the beard holder 34 to which the outer end of the beard escapement 32 is attached. As a result, the tendency of the combined torque becomes asymmetric through the 0° position. The fifth modification example is preferably adopted when there is a difference in movement between the forward rotation and the reverse rotation due to individual differences of the mechanical timepiece 1 or the like.

[0063] In the present embodiment and each modification example, the rotating body that rotates in a forward and reverse rotational motion along with the forward and reverse rotational motion of the balance wheel 311 may not have the crown wheel 31, and it is preferable to have at least the balance wheel 311 and the balance weight 312a that rotates together with the balance wheel 311.

Explanation of Reference Numerals

[0064] 1 Mechanical clock, 10 Floor, 11 Mainspring, 12 Gear train, 131 Second hand, 20 Escapement mechanism, 21 Gang wheel, 22 Anchor, 221 Anchor plate, 222 Rod part, 223 First arm part, 223a Pawl, 224 Second arm part, 224a Escapement pawl, 30 Regulating mechanism, 31 Balance wheel, 311 Balance weight, 312 Oscillation stand, 312a Oscillation weight, 32 Hairspring, 34 Hairspring holder, 40 Pace adjustment means, 41 Permanent magnet, 42 Stator, 421 First magnetic part, 421a First end part, 422 Second magnetic part, 422a Second end part, 43 Coil, 44 Control circuit, 45 Detection circuit, 46 Regulating pulse output circuit, 47 Frequency division circuit, 48 Oscillation circuit, 50 Rectifier circuit, 60 Power supply circuit, 70 Crystal oscillator, 80 Braking circuit, n11, n12, n21, n22 Notch.

Claims

1. A rotating body that rotates forward and backward, included in a speed control mechanism, A permanent magnet that rotates forward and backward along with the forward and backward rotation of the rotating body, A stator provided so that a magnetic torque is generated with respect to the permanent magnet according to the rotation angle of the permanent magnet, having, When the permanent magnet moves toward the turning-back position of the forward and backward rotation, a regulating portion is provided to regulate the rotation range of the rotating body so that an acting torque that includes the magnetic torque and affects the rotation of the permanent magnet is not generated in the same direction as the rotation direction of the permanent magnet. A mechanical clock.

2. having a remontoire mechanism including an anchor escapement that intermittently drives a going-bar by a pendulum weight that rotates forward and backward along with the forward and backward rotation of the rotating body, wherein the regulating portion is a portion to be collided with by the pendulum weight among the anchor escapement, The mechanical clock according to claim 1.

3. The portion to be collided with includes a shape that extends along the rotation locus of the pendulum weight, The mechanical clock according to claim 2.

4. The portion to be collided with includes a shape that extends along the circumferential surface of the rotation axis of the rotating body, The mechanical clock according to claim 2.

5. The portion to be collided with includes a collided surface that is inclined with respect to the collision direction of the pendulum weight, The mechanical clock according to claim 2.

6. The portion to be collided with includes a first portion to be collided with by the pendulum weight rotating in the forward direction and a second portion to be collided with by the pendulum weight rotating in the reverse direction, The first portion to be collided with and the second portion to be collided with each include a first portion that extends in parallel with each other and a second portion that extends in a direction away from each other from the first portion, The second portion is longer than the first portion, The mechanical clock according to claim 2.

7. The rotating body includes a crown wheel and a hairspring that elastically deforms to rotate the crown wheel forward and backward, The acting torque is a combined torque of the magnetic torque and the spring torque of the hairspring, The mechanical clock according to any one of claims 1 to 6.

8. The rotating body includes a crown wheel, A portion to be regulated that contacts the regulating portion is provided on the crown wheel, The mechanical clock according to claim 1.

9. The regulating portion regulates the rotation range of the rotating body so that a maximum value does not appear in the change of the magnetic torque according to the rotation angle in the same direction as the rotation direction of the permanent magnet, The mechanical clock according to claim 1.

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