Mechanical timepiece

Abstract

The mechanical clock (1) uses an electromagnetic unit for differential adjustment, which can efficiently extract electricity. The mechanical clock (1) has: a balance wheel (31); a hairspring (32); a permanent magnet (41); a soft magnetic core (42); a control circuit (44) for differential adjustment based on the back electromotive force generated in the coil (43) by the movement of the permanent magnet (41) with the forward and reverse motion of the balance wheel (31) and the reference vibration frequency of the reference signal source; a rectifier circuit (50) for rectifying the current generated in the coil (43) by the movement of the permanent magnet (41) with the forward and reverse motion of the balance wheel (31); and a power supply circuit (60) for driving the control circuit (44) based on the current rectified by the rectifier circuit (50). The permanent magnet (41) is configured such that the magnetization direction is toward the first end (421a) or the second end (422a) when the hairspring (32) is in a neutral position of elastic deformation.

Description

Technical Field

[0001] This invention relates to mechanical clocks. Background Technology

[0002] Patent Document 1 discloses a mechanical clock with the following functions: generating electricity based on the movement of a magnet mounted on a pivot (balance pivot), and adjusting the differential rate by observing the period of rotation of the balance wheel (e.g., paragraphs 0072 and 0073 of Patent Document 1). Figure 27 (etc.). In addition, Patent Document 2 discloses a structure for generating electricity by using a rectifier containing four diodes to perform full-wave rectification (for example, Figure 13 of Patent Document 2).

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent Document 1: Japanese Patent Application Publication No. 2020-38206

[0006] Patent Document 2: Japanese Patent Application Publication No. 2019-113548 Summary of the Invention

[0007] The problem that the invention aims to solve

[0008] Here, since the electricity generated by the movement of the magnet accompanying the movement of the pendulum axis is small, it is necessary to extract the electricity efficiently. However, as in Patent Document 2, when full-wave rectification is performed through a rectifier containing multiple diodes, a voltage drop corresponding to the number of diodes is generated, resulting in power loss.

[0009] The present invention was made in view of the above-mentioned problems, and its object is to efficiently obtain electricity in mechanical clocks that use electromagnetic means for differential adjustment.

[0010] Methods for solving problems

[0011] (1) A mechanical clock, comprising: a power source; a regulating mechanism including a balance wheel driven by power from the power source and a hairspring that elastically deforms to cause the balance wheel to rotate in both directions; a bipolar permanent magnet (bipolar permanent magnet) that rotates in both directions with the rotation of the balance wheel; a coil; a soft magnetic core including a first end disposed along the outer periphery of the permanent magnet and a second end disposed along the outer periphery of the permanent magnet and disposed opposite to the first end across the permanent magnet, the soft magnetic core forming a magnetic circuit together with the coil; and a control circuit that performs differential adjustment based on a detection voltage generated in the coil due to the movement of the permanent magnet accompanying the forward and reverse movements of the balance wheel and a reference vibration frequency of a reference signal source. The control circuit is configured such that, when the hairspring is in a neutral position of its elastic deformation, the magnet is magnetized toward either the first end or the second end. The control circuit is also configured to: adjust / speed; rectify the current generated in the coil due to the movement of the permanent magnet accompanying the forward and reverse movements of the balance wheel; and power supply circuit that drives the control circuit based on the current rectified by the rectifier circuit.

[0012] (2) The mechanical clock as described in (1), wherein the permanent magnet is configured such that, in the state where the hairspring is in a neutral position of its elastic deformation, the magnetization direction is the same as the relative direction of the first end and the second end.

[0013] (3) The mechanical clock as described in (1) or (2), wherein the soft magnetic core comprises: a first separation portion that separates the magnetic coupling between the first end and the second end; and a second separation portion that separates the magnetic coupling between the first end and the second end, and is disposed opposite to the first separation portion via the permanent magnet, the permanent magnet being configured such that, when the hairspring is in the neutral position, the magnetization direction is orthogonal to the relative directions of the first separation portion and the second separation portion.

[0014] (4) A mechanical clock as described in (1) or (2), wherein the soft magnetic core comprises: a first separation portion that separates the magnetic coupling between the first end and the second end; and a second separation portion that separates the magnetic coupling between the first end and the second end, and is disposed opposite to the first separation portion across the permanent magnet, the permanent magnet comprising an N pole portion and an S pole portion, and configured such that, in the state where the hairspring is in the neutral position, the boundary between the N pole portion and the S pole portion overlaps with an imaginary strip region connecting the first separation portion and the second separation portion.

[0015] (5) A mechanical clock as described in any one of (1) to (4), wherein, when the hairspring is in the neutral position, the balance wheel is in the power supply position where it is supplied with power from the power source.

[0016] (6) The mechanical clock as described in (5), wherein the permanent magnet is configured such that the detection voltage detected during a 180° rotation from the power supply position in the forward or reverse direction has the same polarity.

[0017] (7) A mechanical clock as described in any one of (1) to (6), comprising: a rotation detection circuit that detects a detection signal based on the detection voltage; and a speed regulating pulse output circuit that outputs a speed regulating pulse to control the motion of the balance wheel, wherein the control circuit controls the speed regulating pulse output circuit based on the detection time of the detection signal and the output time of a reference signal based on the reference vibration frequency.

[0018] (8) The mechanical clock as described in (7), wherein the speed regulating pulse output circuit outputs the speed regulating pulse to either the first terminal or the second terminal of the coil when the detection time of the detection signal is earlier than the output time of the reference signal, and outputs the speed regulating pulse to the other terminal when the detection time of the detection signal is later than the output time of the reference signal.

[0019] (9) A mechanical clock as described in (7) or (8), wherein the speed regulating pulse output circuit is configured to output a plurality of speed regulating pulses that are different from each other during the output period.

[0020] (10) A mechanical clock as described in any one of (7) to (9), wherein the speed regulating pulse output circuit is configured to output a plurality of speed regulating pulses with different duty cycles.

[0021] (11) A mechanical clock as described in (9) or (10), wherein the speed regulating pulse output circuit outputs a speed regulating pulse corresponding to the deviation of the detection time of the detection signal from the output time of the reference signal.

[0022] (12) The mechanical clock as described in (11), wherein the mechanical clock has a storage section that stores the deviation of the detection time of the detection signal relative to the output time of the reference signal, and the speed regulating pulse output circuit outputs the speed regulating pulse corresponding to the deviation stored in the storage section.

[0023] (13) A mechanical clock as described in any one of (1) to (12), wherein it further comprises a deceleration mechanism disposed in a predetermined direction relative to the rotation axis of the balance wheel, and acting on the balance wheel during the middle of the forward and reverse rotations of the balance wheel to decelerate the balance wheel, the balance wheel comprising an acted portion formed in a circumferential direction and acted upon by the deceleration mechanism.

[0024] (14) The mechanical clock as described in (13), wherein the control circuit performs differential adjustment in the forward and reverse rotation of the balance wheel based on the detection voltage generated in the coil due to the movement of the permanent magnet and the reference vibration frequency before the acted part reaches the position of the deceleration mechanism.

[0025] (15) A mechanical clock as described in (13) or (14), wherein the control circuit performs differential adjustment during the forward and reverse motions of the balance wheel, after the acted part reaches the position of the deceleration mechanism.

[0026] (16) A mechanical clock as described in any one of (13) to (15), wherein the control circuit is driven by supplying a back electromotive force generated in the coil by the movement of the permanent magnet during the forward and reverse rotation of the balance wheel, before the acted part reaches the position of the deceleration mechanism.

[0027] (17) A mechanical clock as described in any one of (1) to (16), wherein the rectifier circuit includes one diode.

[0028] (18) A mechanical clock as described in any one of (1) to (17), wherein the hairspring is made of resin.

[0029] (19) A mechanical clock as described in any one of (1) to (18), wherein at least one pair of opposing notches are formed at the first end and the second end to reduce the holding torque of the permanent magnet.

[0030] (20) A mechanical clock as described in any one of (1) to (19), wherein the hairspring is configured to cause the balance wheel to reciprocate once every two seconds.

[0031] (21) A mechanical clock as described in any one of (1) to (20), wherein it has a bearing structure that supports the end of the rotation axis of the balance wheel on the side near the permanent magnet, the bearing structure including an elastically deformable portion that elastically deforms in response to the displacement of the rotation axis and is made of a non-magnetic material.

[0032] (22) The mechanical clock as described in (21), wherein the elastically deformable part is a shape capable of elastically deforming in at least one direction of the radial or axial direction of the rotating shaft in response to the displacement of the rotating shaft.

[0033] (23) The mechanical watch as described in (21) or (22), wherein the bearing structure comprises: a through-hole jewel bearing having a bore through which the end of the rotating shaft is inserted; and a retaining portion that retains the through-hole jewel bearing and is connected to the elastically deformable portion and is made of a non-magnetic material.

[0034] (24) A mechanical clock as described in any one of (21) to (23), wherein it has a housing component for housing the bearing structure, the housing component comprising: a first circumferential surface surrounding the end of the rotating shaft; a second circumferential surface disposed on a side closer to the balance wheel than the first circumferential surface and having a smaller diameter than the first circumferential surface; and a step portion connecting the first circumferential surface and the second circumferential surface, the outer edge of the elastically deformable portion being fixed to the step portion.

[0035] (25) The mechanical clock as described in (24), wherein the diameter of the permanent magnet is smaller than the diameter of the second circumferential surface, and the permanent magnet and the second circumferential surface are disposed at at least partially in the same position in the axial direction of the rotation axis.

[0036] Invention Effects

[0037] According to aspects (1) to (25) of the present invention described above, in a mechanical clock that uses electromagnetic means for differential adjustment, electricity can be efficiently extracted. Attached Figure Description

[0038] Figure 1 This is a perspective view showing the base plate of this embodiment and the various components assembled on the base plate.

[0039] Figure 2 This is a perspective view showing the power transmission mechanism and its surroundings in this embodiment.

[0040] Figure 3 This is an exploded perspective view showing the speed regulating mechanism and its surrounding components disassembled from the base plate in this embodiment.

[0041] Figure 4 This is a diagram showing the cross-section of the support component and the soft magnetic core in this embodiment, as well as their surroundings.

[0042] Figure 5 These are top views showing the soft magnetic core and its surroundings in this embodiment, and enlarged top views showing a portion of it.

[0043] Figure 6 This is a top view showing the speed regulating mechanism and its surroundings in this embodiment.

[0044] Figure 7 This is a graph illustrating the holding torque of the permanent magnet in this embodiment.

[0045] Figure 8 This is a block diagram showing the overall structure of the mechanical clock of this embodiment.

[0046] Figure 9 This is an exploded perspective view showing the air resistance components separated from the base plate.

[0047] Figure 10 This is a perspective view showing the operation of the balance wheel in this embodiment.

[0048] Figure 11A This is a perspective view showing the balance wheel and air resistance components in a modified example of this embodiment.

[0049] Figure 11B This is a perspective view showing the balance wheel and air resistance components in a modified example of this embodiment.

[0050] Figure 11C This is a perspective view showing the balance wheel and air resistance components in a modified example of this embodiment.

[0051] Figure 11D This is a perspective view showing the balance wheel and air resistance components in a modified example of this embodiment.

[0052] Figure 11E This is a perspective view showing the balance wheel and air resistance components in a modified example of this embodiment.

[0053] Figure 11F This is a perspective view showing the balance wheel and air resistance components in a modified example of this embodiment.

[0054] Figure 11G This is a perspective view showing the balance wheel and air resistance components in a modified example of this embodiment.

[0055] Figure 11H This is a perspective view showing the balance wheel and air resistance components in a modified example of this embodiment.

[0056] Figure 11I This is a perspective view showing the balance wheel and air resistance components in a modified example of this embodiment.

[0057] Figure 11J This is a perspective view showing the balance wheel and elastic component in a modified example of this embodiment.

[0058] Figure 11KThis is a three-dimensional view showing the balance wheel of other examples as viewed from the side with the hairspring.

[0059] Figure 11L This indicates the view from the side opposite to the side where the hairspring is located. Figure 11K A three-dimensional diagram showing the balance wheel configuration.

[0060] Figure 11M It is a top view showing the state of the hairspring in its neutral position of elastic deformation.

[0061] Figure 11N It is a top view showing the state of elastic deformation of the hairspring from the neutral position to the expanding direction.

[0062] Figure 11O It is a top view showing the state of elastic deformation of the hairspring from the neutral position towards the shrinking direction.

[0063] Figure 12 This is a diagram illustrating the relationship between the movement of the balance wheel and the back electromotive force generated in the coil in this embodiment.

[0064] Figure 13A This is a diagram showing the back electromotive force detected by the coil in the permanent magnet configuration of this embodiment.

[0065] Figure 13B This is a diagram showing the back electromotive force detected by the coil in the permanent magnet configuration of Comparative Example 1.

[0066] Figure 13C This is a diagram showing the back electromotive force detected by the coil in the permanent magnet configuration of Comparative Example 2.

[0067] Figure 14A This is a circuit diagram illustrating an example of the circuitry in this embodiment.

[0068] Figure 14B This is a circuit diagram illustrating other examples of the circuitry in this embodiment.

[0069] Figure 15A This diagram illustrates the control of the permanent magnet's movement by the speed-regulating pulse in this embodiment.

[0070] Figure 15B This diagram illustrates the control of the permanent magnet's movement by the speed-regulating pulse in this embodiment.

[0071] Figure 16 This is a flowchart illustrating an example of differential rate adjustment control in this embodiment.

[0072] Figure 17 This is a timing diagram illustrating an example where a detection signal is detected during the output of a reference signal.

[0073] Figure 18 This is a timing diagram illustrating an example where the detection time of the detection signal is earlier than the output period of the reference signal.

[0074] Figure 19 This is a timing diagram illustrating an example where the detection of the detection signal occurs later than the output period of the reference signal.

[0075] Figure 20 This is a flowchart representing the first variation of differential rate adjustment control.

[0076] Figure 21 This is a timing diagram representing the detection signal and the reference signal in the first variation of differential adjustment control.

[0077] Figure 22 This is a flowchart representing the second variation of differential rate adjustment control.

[0078] Figure 23 This is a timing diagram of the detection signal and the reference signal in the second variation of the differential adjustment control.

[0079] Figure 24 This is a diagram representing an example of a speed-regulating pulse.

[0080] Figure 25 This is a timing diagram illustrating an example of differential adjustment control when a power supply circuit starts from a stopped state.

[0081] Figure 26 This is a timing diagram illustrating an example of differential adjustment control that takes into account the effects of disturbances.

[0082] Figure 27 This is a flowchart illustrating an example of differential adjustment control that takes into account the effects of disturbances.

[0083] Figure 28 It means in Figure 20 The flowchart of the first variation of the differential adjustment control shown considers the effect of disturbances.

[0084] Figure 29 This is a timing diagram illustrating an example of differential rate adjustment control in the case of continuous detection failures of the detection signal.

[0085] Figure 30 This is a timing diagram illustrating an example of differential rate adjustment control in the case of continuous detection failures of the detection signal.

[0086] Figure 31 This is a flowchart illustrating an example of differential rate adjustment control that assumes the detection of a detection signal will fail continuously.

[0087] Figure 32 This is a timing diagram representing an example of the output time of a reference signal.

[0088] Figure 33 This is a cross-sectional view showing the bearing structure and its surrounding area in this embodiment.

[0089] Figure 34 This is a top view showing an elastically deformable component. Detailed Implementation

[0090] Hereinafter, embodiments of the present invention (hereinafter referred to as "this embodiment") will be described in detail based on the accompanying drawings.

[0091] [Overall Structure Overview]

[0092] First, refer to Figures 1 to 8 The overall structure of the mechanical clock 1 of this embodiment will be described in general. Figure 1 This is a perspective view showing the base plate of this embodiment and the various components assembled on the base plate. Figure 2 This is a perspective view showing the power transmission mechanism and its surroundings in this embodiment. Figure 3 This is an exploded perspective view showing the speed regulating mechanism and its surrounding components disassembled from the base plate in this embodiment. Additionally, Figures 1-3 This shows the view from the back side of the mechanical clock 1. The back side refers to the side of the mechanical clock 1 along its thickness direction where the back cover of the outer casing is located.

[0093] Figure 4 This is a diagram showing the cross-section of the support component and the soft magnetic core in this embodiment, as well as their surroundings. Figure 5 These are top views showing the soft magnetic core and its surroundings in this embodiment, and enlarged top views showing a portion of it. Figure 6 This is a top view showing the speed regulating mechanism and its surroundings in this embodiment. Figure 7 This is a graph illustrating the holding torque of the permanent magnet in this embodiment. Figure 8 This is a block diagram showing the overall structure of the mechanical clock of this embodiment. Additionally, Figure 5 This shows the view from the back of mechanical clock 1. Figure 6 This indicates the view from the front side of the mechanical clock 1. Furthermore, "front side" refers to the side of the mechanical clock 1 along its thickness from which the user visually confirms the hands and dial.

[0094] In this embodiment, except Figure 6 In all other diagrams, the counterclockwise direction of the balance wheel 31 and the permanent magnet 41 is defined as positive, and the clockwise direction is defined as negative.

[0095] The mechanical clock 1 is a timepiece powered by a mainspring 11, whose movement is controlled by an escapement mechanism 20 and a regulating mechanism 30, thus driving the hands. The mechanical clock 1 is constructed by housing a base plate 10 containing the mechanisms for driving the hands within an outer casing. Furthermore, the outer casing is omitted from the illustration in this embodiment. Additionally, the crown, located on the side of the outer casing, is also omitted from the illustration. The crown is mounted on... Figure 1 The end of the shank 2 shown.

[0096] [Overall Structure Overview: Structure of the Drive Mechanism]

[0097] A general description of the drive mechanism of the mechanical clock 1 will be provided. In this embodiment, the mechanism including the mainspring 11 as a power source, the gear set 12, and the pointer shaft 13 will be referred to as the "drive mechanism". Furthermore, in Figure 2 The image only shows the second hand, number 131. Figure 2 The drive mechanism shown is an example, but it is not limited to this; it may also have gears other than those shown in the diagram.

[0098] The mainspring 11 is made of a metal strip and is housed in a barrel 110 with multiple teeth formed on its outer periphery. The barrel 110 is disc-shaped and has an internal cavity for housing the mainspring 11. The inner end of the mainspring 11 is fixed to a rotating shaft (not shown) located at the center of the barrel 110, and the outer end of the mainspring 11 is fixed to the inner side of the barrel 110. When the crown is rotated by the user, the stem 2 rotates. As the stem 2 rotates, the mainspring 11 is wound up. The wound mainspring 11 is then unwound by its elastic force. With this movement of the mainspring 11, the barrel 110 rotates.

[0099] The gear set 12 includes at least a second gear 122, a third gear 123, and a fourth gear 124. The second gear 122 includes a pinion that meshes with multiple teeth formed in the barrel 110, which functions as a first gear, a rotating shaft, and multiple teeth, transmitting rotation of the barrel 110 to the third gear 123. The rotating shaft of the second gear 122 is the pointer shaft of the minute hand (not shown). The third gear 123 includes a pinion that meshes with multiple teeth of the second gear 122, a rotating shaft, and multiple teeth, transmitting rotation of the second gear 122 to the fourth gear 124. The fourth gear 124 includes a pinion that meshes with multiple teeth of the third gear 123, a rotating shaft, and multiple teeth, transmitting rotation of the third gear 123 to the escapement mechanism 20. Figure 2 As shown, the rotation axis of the fourth gear 124 is the pointer axis 13 of the second hand 131.

[0100] [Overall Structure Overview: A summary of the structure and operation of the escapement mechanism 20 and the regulating mechanism 30]

[0101] Next, the escapement mechanism 20 and the regulating mechanism 30 will be described. Power from the mainspring 11 is transmitted to the escapement mechanism 20 and the regulating mechanism 30 via the gear set 12. The escapement mechanism 20 is configured to include an escapement gear 21 and an escape fork 22. The regulating mechanism 30 is configured to include a balance wheel 31 and a hairspring 32. The regulating mechanism 30 is sometimes also referred to as the balance wheel.

[0102] The escapement gear 21 is a component that receives the rhythmic pattern from the speed regulating mechanism 30 through engagement with the escape fork 22 and transforms it into regular reciprocating motion. The escapement gear 21 includes a pinion that meshes with multiple teeth of the fourth gear 124, a rotating shaft, and multiple teeth. For example... Figure 2 As shown, the teeth of the escapement gear 21 are formed at intervals in the circumferential direction compared to the teeth of each gear in the gear set 12.

[0103] Escapement 22 Figure 5 The escapement fork axis 221 shown is a rotating axis that rotates in both directions. The escapement fork 22 has a disc pin 315 extending from the escapement fork axis 221 toward the center of the balance wheel 31 (balance axis 311) and rotating together with the balance axis 311 (see reference). Figure 6 The colliding rod 222. Additionally, the disc nail 315 is fixed to a circular plate-shaped portion of the pendulum 311 having a predetermined width in the radial direction. Figure 6 The figure shows the case where the balance wheel 31 has rotated θ from a position of 0° rotation angle, and the position of the disc nail 315 in that state.

[0104] Furthermore, the escape fork 22 has: a first arm 223, which is fitted with an inlet pad 223a that collides with multiple teeth of the escape gear 21; and a second arm 224, which extends in the opposite direction to the first arm 223 and is fitted with an outlet pad 224a that collides with multiple teeth of the escape gear 21. Additionally, the inlet pad 223a and outlet pad 224a can be, for example, stones such as sapphire.

[0105] The balance wheel 31 rotates around the balance shaft 311 as its center of rotation, and rotates in both directions via power transmitted by the gear set 12. Furthermore, in the following description, the forward motion in the forward and reverse rotational motions will sometimes be referred to as "forward rotation," and the reverse motion as "reverse rotation." The structure of the balance wheel 31 will be described in detail later. The balance shaft 311 is formed by... Figure 3 , Figure 4 The washer component 35 shown is fixed to the bearing structure 330 described later (see reference 330). Figure 3 and Figure 33 ,exist Figure 4 (Not shown in the diagram) Support.

[0106] The hairspring 32 undergoes stretching and contraction (elastic deformation) to cause the balance wheel 31 to rotate clockwise and counterclockwise. The hairspring 32 is spiral-shaped, with its inner end fixed to the balance shaft 311 and its outer end fixed to the hairspring clamp 34. Furthermore, the hairspring clamp 34, together with the support member 33, is fixed to the base plate 10. Additionally, as... Figure 3 As shown, the hairspring clamp 34 is configured to be sandwiched between the support member 33 and the washer member 35.

[0107] The escapement gear 21 rotates along with the fourth gear 124. When the escapement gear 21 rotates, it collides with the lead shoe 223a of the escapement fork 22, causing the escapement fork 22 to rotate around the escapement fork shaft 221. The rotating lever 222 of the escapement fork 22 then collides with the disc pin 315 fixed to the balance shaft 311, thereby rotating the balance wheel 31. When the balance wheel 31 rotates, the lead shoe 224a of the escapement fork 22 collides with the escapement gear 21, stopping the escapement gear 21. When the balance wheel 31 rotates in the opposite direction due to the restoring force of the hairspring 32, the lead shoe 223a of the escapement fork 22 is released, and the escapement gear 21 rotates again. Furthermore, as described later, by designing the balance wheel 31 to perform one cycle every two seconds, the escapement gear 21 performs one step every one second.

[0108] As explained above, the regulating mechanism 30, through the extension and retraction of the hairspring 32, causes the balance wheel 31 to repeatedly rotate in both directions (reciprocating motion) at a certain period. The escapement mechanism 20 continuously applies a force to the balance wheel 31 for reciprocating motion. Through this structure and action, the hands, such as the second hand 131, are driven.

[0109] [Overall Structure Overview: Structure of Differential Adjustment Mechanism 40]

[0110] Next, the structure of the differential adjustment mechanism 40 will be described. In addition to the drive mechanism, escapement mechanism 20, and speed regulating mechanism 30, the mechanical clock 1 of this embodiment also includes the differential adjustment mechanism 40.

[0111] The differential adjustment mechanism 40 includes a permanent magnet 41, a soft magnetic core 42 (also called a stator), a coil 43, and various circuits (see reference). Figure 8 The differential adjustment mechanism 40 uses the detection signal detected by the forward and reverse rotational motion of the permanent magnet 41 and the crystal oscillator 70 (see reference) as a reference signal source. Figure 8 The reference vibration frequency is adjusted by differential rate. In addition, in this embodiment, in order to achieve higher frequency accuracy, a crystal oscillator 70 is used as the reference signal source, but it is not limited to this. For example, a CR oscillator composed of a capacitor and a resistor can also be used.

[0112] Furthermore, although the illustration is omitted, the coil 43 can be configured to overlap with the mid-frame located on the inner side of the outer housing when viewed from above. Alternatively, a notch can be formed in a portion of the circumference of the mid-frame, and the coil 43 can be disposed within this notch.

[0113] The permanent magnet 41 is a disk-shaped rotating body magnetized by two poles, which are magnetized radially into N poles and S poles. That is, the permanent magnet 41 is a magnet that includes an N pole portion 411 and an S pole portion 412.

[0114] The permanent magnet 41 is mounted on the balance shaft 311, which serves as the rotation axis of the balance wheel 31 (see below). Figure 10 The permanent magnet 41 is configured to rotate in both directions in tandem with the rotation of the balance wheel 31 (balance shaft 311). That is, the permanent magnet 41 rotates in both directions with the balance wheel 31 at the same angle as its rotation. Furthermore, the permanent magnet 41 can be fixed to the balance shaft 311 by pressing or bonding.

[0115] The permanent magnet 41 can be an isotropic magnet with its easy magnetization axis pointing in a random direction. Alternatively, the permanent magnet 41 can be magnetized by applying a magnetic field through a Helmholtz coil or similar means while mounted on the pendulum shaft 311. By employing this magnetization method, the magnetization direction of the permanent magnet 41 can be accurately aligned.

[0116] The soft magnetic core 42 is made of a soft magnetic material, such as... Figure 5 As shown, a first magnetic portion 421, including a first end portion 421a arranged along the outer periphery of a permanent magnet 41, and a second magnetic portion 422, including a second end portion 422a arranged along the outer periphery of a permanent magnet 41, together with a coil 43, form a magnetic circuit. The first end portion 421a and the second end portion 422a are both shaped with a semi-circular inner peripheral surface and are arranged opposite to each other across the permanent magnet 41.

[0117] In this embodiment, with the hairspring 32 in a neutral position of elastic deformation, the N pole 411 of the permanent magnet 41 is disposed on the side of the second magnetic part 422, and the S pole 412 is disposed on the side of the first magnetic part 421 (see reference). Figure 5 (Enlarged view). In addition, the N pole 411 and S pole 412 can be arranged in opposite directions, but in this case, the winding direction of the coil 43 needs to be opposite to that of this embodiment.

[0118] In addition, such as Figure 3 , Figure 4 As shown, the soft magnetic core 42 is fixed to the support member 33 by means of a tube 33a and a screw 33b, which serve as fasteners. With this structure, the soft magnetic core 42 and the support member 33 are assembled together on the base plate 10. In addition, the support member 33 and the soft magnetic core 42 are positioned by a locating pin 10a and a washer member 35 provided on the base plate 10.

[0119] In addition, such as Figure 4 As shown, the washer component 35 has an annular protrusion 35a. The protrusion 35a is fitted into the inner circumferential surfaces of the first end 421a and the second end 422a of the soft magnetic core 42. Furthermore, the soft magnetic core 42 is positioned at both the washer component 35 and the locating pin 10a. With this structure, the soft magnetic core 42 can be assembled to the base plate 10 with good positional accuracy. As a result, the positional accuracy of the soft magnetic core 42 relative to the permanent magnet 41 can be improved. Here, the soft magnetic core 42 is made of a magnetic material, and its magnetic properties may deteriorate if strong stress is applied. For example, when the soft magnetic core 42 is directly fastened to the base plate 10 by screws or the like, its magnetic properties may deteriorate. Therefore, in this embodiment, positioning is achieved by setting the engagement of the locating pin 10a with the washer component 35 to a clearance fit, and the soft magnetic core 42 is fixed to the support component 33 using the tube 33a and screws 33b, thereby achieving both positioning and fixation of the soft magnetic core 42. By adopting such a structure, the magnetic properties of the soft magnetic core 42 will not deteriorate, and the positional accuracy of the soft magnetic core 42 can be improved. In addition, in this embodiment, the soft magnetic core 42 is fixed to the support member 33, but it is also possible to adopt a structure in which the permanent magnet 41 corresponding to the soft magnetic core 42 is arranged between the balance wheel 31 and the base plate 10, and the soft magnetic core 42 is directly fastened to the base plate 10 by screws or the like.

[0120] Furthermore, among the components assembled on the base plate 10, the support component 33, the hairspring clamp 34, the washer component 35, the hairspring 32, and the balance wheel 31 located near the permanent magnet 41 (excluding the soft magnetic core 42) are preferably made of non-magnetic materials so as not to affect the forward and reverse rotational motion of the speed regulating mechanism 30 and the back electromotive force generated by the coil 43 described later.

[0121] In addition, such as Figure 5 As shown, the soft magnetic core 42 includes: a first welding portion (fusion portion) 423 serving as a first separation portion, which separates the magnetic coupling between the first end 421a and the second end 422a; and a second welding portion 424 serving as a second separation portion, which separates the magnetic coupling between the first end 421a and the second end 422a, and is disposed opposite to the first welding portion 423 with a permanent magnet 41 between them. The first welding portion 423 and the second welding portion 424 may be formed within the gap that physically separates the first end 421a and the second end 422a.

[0122] The permanent magnet 41 is in a magnetically balanced position when its magnetization direction is orthogonal to the relative directions of the first welded portion 423 and the second welded portion 424. In this embodiment, the magnetically balanced position of the permanent magnet 41 is set to a rotation angle of 0°. At this position, the holding torque of the permanent magnet 41 is approximately zero. Furthermore, as... Figure 5As shown, the relative direction of the first welded part 423 and the second welded part 424 refers to the direction of the straight line extending from the first welded part 423 to the second welded part 424.

[0123] When the permanent magnet 41 is rotated 90° away from 0° in the positive direction, its magnetization direction becomes the same as the relative direction of the first welded part 423 and the second welded part 424. In this position, the holding torque of the permanent magnet 41 is approximately 0. Figure 7 The thick, dashed curve represents the holding torque of the permanent magnet 41 generated by forming the first welded part 423 and the second welded part 424.

[0124] like Figure 5 As shown, in this embodiment, notches are formed on the inner circumferential surfaces of the first end 421a and the second end 422a of the soft magnetic core 42. Specifically, notches n11 and n12 are formed at the first end 421a. Furthermore, at the second end 422a, notch n21 is formed opposite to notch n11, separated from the permanent magnet 41, and notch n22 is formed opposite to notch n12, separated from the permanent magnet 41. By forming these notches, the magnetic influence of the soft magnetic core 42 on the permanent magnet 41 is reduced. Therefore, the holding torque of the permanent magnet 41 can be reduced.

[0125] Figure 7 The dashed curve on one side represents the holding torque of the permanent magnet 41 generated by forming the recesses n11 and n21 that are arranged opposite to each other, and the dashed curve on the other side represents the holding torque of the permanent magnet 41 generated by forming the recesses n12 and n22 that are arranged opposite to each other.

[0126] in addition, Figure 7 The solid line curve represents the combined holding torque, formed by synthesizing the three dashed line curves mentioned above. That is, Figure 7 The solid curve represents the holding torque of the permanent magnet 41 generated by forming the first weld portion 423, the second weld portion 424, and the notches n11, n12, n21, and n22 in the soft magnetic core 42. For example... Figure 7 As shown, in the structure of this embodiment, the holding torques indicated by the dashed curves cancel each other out at each rotation angle, and the combined holding torque of the permanent magnet 41 is close to zero at any rotation angle. Therefore, as will be described later, even when using a hairspring 32 made of a material with a low Young's modulus, the permanent magnet 41 can rotate smoothly. Furthermore, Figure 5 The number, arrangement, and shape of the notches shown are an example and are not limited thereto. At least one pair of opposing notches that reduce the holding torque of the permanent magnet 41 may be formed at the first end 421a and the second end 422a.

[0127] [Overall Structure Overview: Summary of Differential Adjustment]

[0128] like Figure 8 As shown, in addition to the aforementioned mainspring 11, gear train 12, escapement 20, regulating mechanism 30, and differential adjustment mechanism 40, the mechanical clock 1 also includes a rectifier circuit 50, a power supply circuit 60, and a crystal oscillator 70. Furthermore, as... Figure 8 As shown, the differential adjustment mechanism 40, in addition to the aforementioned permanent magnet 41, soft magnetic core 42, and coil 43, also includes a control circuit 44, a rotation detection circuit 45, a speed regulation pulse output circuit 46, a frequency division circuit 47, and an oscillation circuit 48. Furthermore, Figure 8 The structure of the differential adjustment mechanism 40 shown is an example. The differential adjustment mechanism 40 does not need to have an independent differential adjustment mechanism. Figure 8 Each circuit shown can be used as long as it can perform the functions described below.

[0129] The control circuit 44 is a circuit that controls the operation of each circuit included in the differential adjustment mechanism 40.

[0130] The oscillation circuit 48 outputs a predetermined oscillation signal based on the oscillation frequency of the crystal oscillator 70. The oscillation frequency of the crystal oscillator 70 is 32768 Hz. The frequency divider circuit 47 divides the oscillation signal output from the oscillation circuit 48. By dividing the oscillation signal based on the crystal oscillator 70, the frequency divider circuit 47 generates a reference signal OS that is output approximately every 1000 ms. However, it is not limited to this; the reference signal OS can also be output every 2000 ms or 3000 ms. That is, the reference signal OS only needs to be output every positive second. Furthermore, it is not limited to this; the reference signal OS only needs to correspond to the period of the speed control mechanism 30.

[0131] The rotation detection circuit 45 detects the detection signal based on the voltage waveform generated in the coil 43 due to the movement of the permanent magnet 41. The speed regulation pulse output circuit 46 outputs a speed regulation pulse based on the reference signal generated by the frequency divider circuit 47 and the detection signal detected by the rotation detection circuit 45. Specifically, the detection time of the detection signal detected by the rotation detection circuit 45 is compared with the output time of the reference signal of approximately 1000 Hz. If a deviation occurs at these times, the speed regulation pulse output circuit 46 outputs a speed regulation pulse in a manner that makes the period of the detected signal approximately 1000 ms (= 1 second).

[0132] The speed control pulse is output by energizing coil 43. Therefore, when the speed control pulse output circuit 46 detects that the period of the detection signal is earlier than the reference signal, it energizes coil 43 in a manner that delays the movement of permanent magnet 41 by applying torque; conversely, when the period of the detection signal is detected to be later than the reference signal, it energizes coil 43 in a manner that advances the movement of permanent magnet 41 by applying torque. Furthermore, details regarding the differential adjustment control including the output timing of the speed control pulse will be described later.

[0133] [Overall Structure Overview: Speed ​​Control Mechanism 30 as a Generator]

[0134] Furthermore, the mechanical clock 1 has a power generation function that utilizes the principle of electromagnetic induction. In this embodiment, the speed regulating mechanism 30 functions as part of the generator. Specifically, as the balance wheel 31 rotates in both directions, the permanent magnet 41 rotates in both directions, and power is generated by the current produced in the coil 43 based on the change in the magnetic field generated by the movement of the permanent magnet 41. The power extracted through this operating principle is used to start the power supply circuit 60. By starting the power supply circuit 60, the control circuit 44 included in the differential adjustment mechanism 40 can be driven. Due to this structure, in this embodiment, it is not necessary to provide a separate power source such as a battery to drive the control circuit 44.

[0135] The rectifier circuit 50 rectifies the current generated in the coil 43 due to the forward and reverse motion of the permanent magnet 41 accompanying the forward and reverse rotation of the balance wheel of the speed regulating mechanism 30. The power supply circuit 60 is, for example, a circuit including a capacitor, which stores power for driving the control circuit 44 based on the current rectified by the rectifier circuit 50.

[0136] [Overall structural overview: the bearing construction of the balance shaft]

[0137] Here, refer to Figure 33 , Figure 34 The bearing structure 330 of the swing shaft 311 in this embodiment will be described. Figure 33 This is a cross-sectional view showing the bearing structure and its surrounding area in this embodiment. Figure 34 This is a top view showing an elastically deformable component.

[0138] The bearing structure 330 supports the end of the pendulum shaft (rotation shaft) 311 near the permanent magnet 41. For example... Figure 33 As shown, the balance shaft 311 has a tenon head 311a at its front end. The tenon head 311a is a portion with a smaller diameter compared to the other parts of the balance shaft 311. Figure 33 As shown, the bearing structure 330 supports the tenon head 311a of the swing shaft 311.

[0139] The bearing structure 330 includes at least a through-hole jewel bearing 331, an elastically deformable member 332, a thrust jewel bearing 333, a retaining member 334 for retaining the thrust jewel bearing 333, and a thrust jewel bearing spring 335. The bearing structure 330 is housed within a washer member 35, which serves as a housing component. Figure 33 As shown, the retaining member 334 is fixed relative to the washer member 35. That is, the bearing structure 330 is fixed to the support member 33 via the washer member 35.

[0140] The thrust jewel bearing spring 335 is configured to retain the retaining member 334 at its inner edge, and a portion of its outer edge is hooked onto the washer member 35. Additionally, the outer edge of the thrust jewel bearing spring 335 is in elastic contact with the washer member 35. The thrust jewel bearing spring 335 is one of the components that helps absorb impacts in the axial direction of the balance shaft 311. The retaining member 334 and the thrust jewel bearing spring 335 can be made of non-magnetic materials. For example, the retaining member 334 can be made of brass, with a zinc alloy as its main body.

[0141] The through-hole jewel bearing 331 is inserted into the opening 3323h (described later) formed in the elastic deformation member 332 and fixed to the elastic deformation member 332. Furthermore, a shaft hole 331h is formed at the center of the through-hole jewel bearing 331 for the tenon 311a of the pivot shaft 311 to pass through. The tenon 311a is radially positioned by the through-hole jewel bearing 331 through the shaft hole 331h.

[0142] The thrust bearing 333 abuts against the front end of the tenon head 311a. The tenon head 311a is positioned vertically by the thrust bearing 333.

[0143] The through-hole jewel bearing 331 and the thrust jewel bearing 333 can be jewel bearings that have good sliding properties with the tenon head 311a and are conducive to rotational movement and wear. Specifically, the through-hole jewel bearing 331 and the thrust jewel bearing 333 can be made of ruby ​​or sapphire, etc. However, they are not limited to this, and the through-hole jewel bearing 331 and the thrust jewel bearing 333 can be made of non-magnetic materials.

[0144] In the event of an external impact on the mechanical clock 1, the balance axis 311 may deviate in position in the vertical or radial direction. Here, the vertical direction refers to... Figure 33 The direction in which the axis ax of the pendulum shaft 311 extends (hereinafter also referred to as the axial direction) is radial, meaning the direction orthogonal to the direction in which the axis ax extends. If a positional deviation occurs in the pendulum shaft 311, it may lead to rotational disorder of the balance wheel 31 and the permanent magnet 41, reduced differential accuracy, and reduced power generation efficiency. Therefore, in this embodiment, the bearing structure 330 adopts a structure with an elastic deformation member 332.

[0145] like Figure 34 As shown, the elastic deformation member 332 has a spiral shape including an annular outer edge portion 3321 that forms its shape, an elastic deformation portion 3322, and an annular retaining portion 3323 that retains the through-hole jewel bearing 331.

[0146] like Figure 34 As shown, the elastically deformable portion 3322 has a shape comprising the following parts: a first connecting portion 3322a, which extends radially inward from a portion of the outer edge portion 3321 in the circumferential direction; a semi-circular portion 3322b, which is connected to the outer edge portion 3321 via the first connecting portion 3322a and extends along the outer edge portion 3321; and a second connecting portion 3322c, which extends radially inward from the end of the semi-circular portion 3322b on the side opposite to the first connecting portion 3322a, and connects the semi-circular portion 3322b and the retaining portion 3323. The outer edge portion 3321 is fixed to the washer member 35 by being clamped by the washer member 35 and the retaining member 334.

[0147] Here, as Figure 33 As shown, the washer component 35 comprises a first circumferential surface 351 surrounding the end of the balance shaft 311, a second circumferential surface 352 disposed on a side closer to the balance wheel 31 than the first circumferential surface 351 and with a diameter smaller than the first circumferential surface 351, and a stepped portion 353 connecting the first circumferential surface 351 and the second circumferential surface 352. Furthermore, the first circumferential surface 351 is... Figure 33 The circumferential surface with diameter R1 shown, the second circumferential surface 352 is Figure 33 The circumferential surface with a diameter R2 (<R1) is shown. The outer edge 3321 of the elastic deformation member 332 is clamped and fixed by the stepped portion 353 of the washer member 35 and the retaining member 334.

[0148] When the pendulum shaft 311 shifts radially due to external impacts, the semicircular portion 3322b elastically deforms radially with the first connecting portion 3322a as the fulcrum, and the retaining portion 3323 elastically deforms radially with the second connecting portion 3322c as the fulcrum. Here, "displacement" refers to the pendulum shaft 311 moving to a position deviating from its normal position.

[0149] Furthermore, when the pendulum shaft 311 is displaced along the axial direction due to an external impact, the semicircular arc portion 3322b elastically deforms along the axial direction with the first connecting portion 3322a as the fulcrum, and the retaining portion 3323 elastically deforms along the axial direction with the second connecting portion 3322c as the fulcrum.

[0150] Thus, by employing a bearing structure 330 including an elastic deformation section 3322, the swing shaft 311 can maintain a standard position even if a positional deviation occurs in the radial or axial direction using the elastic force of the elastic deformation section 3322. As a result, it is possible to suppress a decrease in differential accuracy or a decrease in power generation efficiency.

[0151] Furthermore, the elastic deformation portion 3322 can be made of a non-magnetic material. A non-magnetic material refers to a material other than a strongly magnetic material, that is unaffected by a magnetic field or less susceptible to its influence than a strongly magnetic material. Specifically, the elastic deformation portion 3322 can be made of metallic materials such as NiP (nickel-phosphorus), TiCu (titanium-copper), or copper-nickel alloys. The elastic deformation portion 3322 can be formed through an aging treatment (heat treatment). This ensures elastic force and results in a thin elastic deformation portion 3322. Additionally, the outer edge portion 3321 and the retaining portion 3323 can also be made of a non-magnetic material, similar to the elastic deformation portion 3322. That is, the elastic deformation component 332 is preferably entirely made of a non-magnetic material.

[0152] Thus, the elastic deformation member 332 (elastic deformation part 3322), which is one of the components located near the permanent magnet 41, is made of a non-magnetic material, thereby suppressing the magnetic influence on the permanent magnet 41. As a result, the operation of the permanent magnet 41 becomes stable. Consequently, it is possible to suppress the reduction in differential accuracy or power generation efficiency.

[0153] Furthermore, by making the elastic deformation member 332 and the retaining member 334 from non-magnetic materials, the bearing structure 330 of the balance shaft 311 can be positioned close to the permanent magnet 41. As a result, the mechanical clock 1 can be miniaturized in the thickness direction. Moreover, by making the elastic deformation member 332 from a non-magnetic material, the permanent magnet 41 can be enlarged. As a result, the electricity obtained by the movement of the permanent magnet 41 can be increased, and the power generation performance can be improved.

[0154] In addition, in this embodiment, such as Figure 33 As shown, the diameter of the permanent magnet 41 is smaller than the smallest diameter (diameter R2) of the opening diameter of the washer component 35. That is, the washer component 35 has an opening large enough to ensure sufficient space for the permanent magnet 41 to be positioned close to the bearing structure 330. The permanent magnet 41 is positioned perpendicular to the axial direction ax of the pendulum shaft 311 and passes through an imaginary plane P, which passes through the washer component 35. In other words, the permanent magnet 41 and the washer component 35 are at least partially positioned in the same location along the axial direction ax. Figure 33The diagram illustrates an example where the permanent magnet 41 and the second circumferential surface 352 of the washer component 35 are at least partially positioned in the axial direction ax. In this prior art, a washer component with an opening slightly larger than the diameter of the pendulum shaft is used; however, in such a structure, upon impact, the pendulum shaft and the washer component interfere with each other, potentially causing damage to the end of the pendulum shaft. In this embodiment, because the washer component 35 has an opening with a diameter sufficiently wider than the diameter of the pendulum shaft 311, the pendulum shaft 311 will not interfere with the washer component 35 even when an external impact is applied.

[0155] in addition, Figure 33 , Figure 34 The shape of the elastic deformation member 332 shown is an example and is not limited thereto. The elastic deformation member 332 (elastic deformation part 3322) may be a shape that can elastically deform in at least one direction of the radial or axial direction of the pendulum shaft 311 according to the displacement of the pendulum shaft 311.

[0156] Furthermore, although the illustration is omitted, the end of the pendulum shaft 311 on the side furthest from the permanent magnet 41 can also be supported by the same structure as the bearing structure 330. This allows for the sharing of components supporting one end of the pendulum shaft 311 with the other end, thus reducing manufacturing costs.

[0157] Among them, permanent magnet 41 can be like Figure 10 It can be directly mounted on the balance shaft 311 as shown, or as shown in the diagram. Figure 33 As shown, it is mounted on the swing shaft 311 via the storage component 410 that houses the permanent magnet 41.

[0158] Additionally, refer to Figure 33 , Figure 34 The bearing structure 330 of the swing shaft 311 described herein can also be applied to any structure in this embodiment, its variations and comparative examples.

[0159] [Regarding the slowdown of balance wheel 31]

[0160] In this mechanical clock 1, the faster the balance wheel 31 operates, i.e., the faster its operating cycle, the more easily the power transmission mechanisms (e.g., the escapement gear 21 or the escapement fork 22) wear out, thus reducing durability. On the other hand, since the current generated in the coil 43 is proportional to the angular velocity of the permanent magnet 41, the power required to drive the control circuit 44 cannot be obtained when the balance wheel 31 operates at a low speed.

[0161] Therefore, in this embodiment, a structure is adopted that enables the balance wheel 31 to operate at a low speed while ensuring power generation.

[0162] Figure 10This is a perspective view showing the operation of the balance wheel in this embodiment. Additionally, in Figure 10 The diagram shows the balance wheel 31, escapement fork 22, permanent magnet 41, and air resistance component 15, which will be described later. Figure 10 In the diagram, symbols are omitted except for the case where the rotation angle is 0°. Figure 12 This is a diagram illustrating the relationship between the movement of the balance wheel and the back electromotive force generated in the coil in this embodiment. Figure 12 In the upper section of the graph, the vertical axis represents the angular velocity of the balance wheel 31 [rad / s], and the horizontal axis represents the measurement time [s]. Figure 12 In the curve graph of the middle section, the vertical axis represents the rotation angle of the balance wheel 31 [deg], and the horizontal axis represents the measurement time [s]. Figure 12 In the lower section of the graph, the vertical axis represents the back electromotive force [V] generated by coil 43, and the horizontal axis represents the measurement time [s]. Additionally, in... Figure 12 The graphs shown illustrate examples of measuring the motion of the balance wheel 31 (permanent magnet 41) over 4 seconds.

[0163] In this embodiment, the balance wheel 31 is designed to reciprocate once every 2 seconds. Therefore, a resin material with a low Young's modulus is used as the material for the hairspring 32. As a result, a lower speed oscillation of the balance wheel 31 can be achieved compared to the case where it is made of a metal material. If a lower speed oscillation is to be achieved with a metal hairspring, the cross-sectional area of ​​the hairspring 32 must be reduced to a level that is difficult to manufacture, or the length of the hairspring must be extended to a level that is difficult to handle.

[0164] In this embodiment, a resin with a Young's modulus of approximately 5 [GPa] is used as the material for the hairspring 32. Specifically, polyester is used as the material for the hairspring 32. Furthermore, the hairspring 32 made of resin material can be manufactured, for example, by laser processing. Additionally, the Young's modulus of a typical metal hairspring is around 200 [GPa]. The Young's modulus shown here is an example; the Young's modulus of the hairspring 32 can be 20 [GPa] or less. That is, the Young's modulus of the hairspring 32 can be less than one-tenth of the Young's modulus of a metal hairspring. More preferably, the Young's modulus of the hairspring 32 is 10 [GPa] or less. That is, the Young's modulus of the hairspring 32 can be less than one-twentieth of the Young's modulus of a metal hairspring. Furthermore, a Young's modulus of 20 [GPa] or less is sufficient; the hairspring 32 can also be made of materials such as paper or wood. For details regarding the shape of the hairspring 32, please refer to [link to relevant documentation]. Figures 11M to 11O To be described later.

[0165] Furthermore, in this embodiment, the rotation angle [deg] of the balance wheel 31 and the permanent magnet 41, which are in a neutral position of elastic deformation of the hairspring 32, is set to 0°. In other words, the neutral position of elastic deformation of the hairspring 32 is the position where the hairspring 32 is at its natural length. Power is supplied from the power spring 11 to the balance wheel 31 in this neutral position. That is, at the 0° rotation angle, the balance wheel 31 and the permanent magnet 41 are in a power supply position where power is supplied from the power spring 11. Furthermore, as described above, in this embodiment, the permanent magnet 41 is in a magnetically balanced position at the 0° rotation angle.

[0166] Furthermore, in this embodiment, the balance wheel 31 is designed to be driven within a rotation angle range of 340° to -340°. Therefore, the permanent magnet 41 is also driven within the rotation angle range of 340° to -340°. However, this is just one example; it is also possible for the balance wheel 31 to move within a rotation angle range of 270° to -270° or more. In this way, by increasing the movement range of the balance wheel 31 to a certain extent, it is possible to achieve low-speed oscillation of the balance wheel 31.

[0167] In addition, Figure 10 In the diagram, every 45° or 90° interval indicates the rotation of the balance wheel 31 from a position of 0° rotation angle towards the forward direction. Furthermore, in... Figure 10 The diagram only shows the case where the balance wheel 31 is at a positive angle (0° to 340°), and the case where it is at a negative angle is omitted.

[0168] [Regarding the slowdown of balance wheel 31: air resistance component 15]

[0169] Furthermore, in this embodiment, an air resistance component 15, which serves as a deceleration mechanism, is assembled onto the base plate 10, and an action portion 313 that bears air resistance from the air resistance component 15 is formed in a portion of the circumference of the balance wheel 31. Figure 9 This is an exploded perspective view showing the air resistance components separated from the base plate.

[0170] The balance wheel 31 includes a circular portion 312 that rotates clockwise and counterclockwise around a balance axis 311, and an acted portion 313 that protrudes radially from a portion of the circumference of the circular portion 312. In this embodiment, the acted portion 313 is the longest radially extending part of the balance wheel 31. Furthermore, in this embodiment, as... Figure 10 As shown, the shape of the affected part 313 is fan-shaped.

[0171] The air resistance component 15 has a drag wall that forms an air resistance region AR that generates air resistance. Specifically, the air resistance component 15 includes a first wall portion 151 facing one side of the activated portion 313 of the balance wheel 31, a second wall portion 152 facing the other side of the activated portion 313 of the balance wheel 31, and a third wall portion 153 connecting the first wall portion 151 and the second wall portion 152, which together form the air resistance region AR. In addition, the air resistance component 15 has a base portion 154 that is integral with the first wall portion 151, the second wall portion 152, and the third wall portion 153 and fixed relative to the base plate 10.

[0172] The air resistance component 15 is fixed to the base plate 10. In this embodiment, as... Figure 9 As shown, an opening 10b is formed in a portion of the base plate 10, an air resistance component 15 is inserted into the opening 10b, and a base 154 is fixed to the base plate 10 by bolts or other fasteners. The air resistance component 15 can be inserted into the opening 10b from the side of the base plate 10 opposite to the side where the drive mechanism, escapement mechanism 20, speed regulating mechanism 30, etc., are assembled. That is, the base 154 can be fixed to the side of the base plate 10 opposite to the side where the drive mechanism, escapement mechanism 20, speed regulating mechanism 30, etc., are assembled. Furthermore, in Figure 9 The text indicates an example where an opening 10b is formed in a portion of the base plate 10, but it is not limited to this; any hole that extends from one side of the base plate 10 to the other is acceptable. For example, a notch for inserting an air resistance component 15 can be formed in the base plate 10 instead of an opening 10b.

[0173] In this embodiment, the air resistance component 15 is configured such that it is positioned in a predetermined direction relative to the balance axis 311, and when the rotation angle of the balance wheel 31 is between 135° and 225° (during the midpoint between forward and reverse motion), the affected portion 313 is located within the air resistance region AR. That is, when the rotation angle of the balance wheel 31 is between 135° and 225°, the affected portion 313 of the balance wheel 31 experiences air resistance, resulting in a decrease in angular velocity. Furthermore, although not shown in the figure, similarly, when the rotation angle of the balance wheel 31 is between -135° and -225° (during the midpoint between forward and reverse motion), the affected portion 313 of the balance wheel 31 experiences air resistance, resulting in a decrease in angular velocity.

[0174] The reason why the rotational speed of the balance wheel 31 decreases through the air resistance region AR is that the air discharge channel is blocked by the first wall 151, the second wall 152 and the third wall 153, and the air is trapped in the air resistance region AR. The trapped air hinders the movement of the balance wheel 31.

[0175] exist Figure 12In the upper and middle sections of the curve, as shown at the moment before the measurement time of 2.0 seconds, the angular velocity of the balance wheel 31 increases sharply from the position of 0° rotation angle, reaching its peak at the moment of measurement time of 2.0 seconds. This is because, when the rotation angle of the balance wheel 31 is 0°, the balance wheel 31 receives power from the power spring 11.

[0176] The balance wheel 31 rotates forward from a rotation angle of 0°, and its angular velocity gradually decreases. At the point where the forward and reverse rotations converge, i.e., at a rotation angle of 340°, the angular velocity becomes 0. Then, the balance wheel 31 rotates in the opposite direction from the rotation angle of 340° due to the elastic deformation of the hairspring 32.

[0177] As described above, when the rotation angle is between 135° and 225°, the balance wheel 31 experiences air resistance from the air resistance component 15, thus reducing the angular velocity between the balance wheels 31. Therefore, as Figure 12 As shown in the curve of the middle section, the displacement of the rotation angle of the balance wheel 31 becomes gradual during the period when it rotates in the opposite direction from the rotation angle of 340° to the rotation angle of 0°.

[0178] Then, the balance wheel 31 returns to the position with a rotation angle of 0°, and under the power from the mainspring 11, its reverse angular velocity increases sharply, reaching a peak. The reverse rotation angular velocity of the balance wheel 31 gradually decreases, reaching 0 at a rotation angle of -340° (measurement time 3.0 seconds). Then, the balance wheel 31 rotates forward from the position of -340° due to the elastic deformation of the hairspring 32.

[0179] Here, since the balance wheel 31 includes a radially protruding acted portion 313, the center of gravity of the balance wheel 31 is closer to the acted portion 313 than the balance axis 311 (center of rotation). In a structure where the center of gravity is deviated from the balance axis 311 located at the center of the balance wheel 31, the rotational motion of the balance wheel 31 becomes unstable. Therefore, in this embodiment, an opening 312h is formed in a portion of the circular portion 312 to make the center of gravity of the balance wheel 31 coincide with or be close to the balance axis 311 (center position). Figure 10 As shown, the opening 312h is formed to be adjacent to the activated part 313 in the circumferential direction. By adopting such a structure, the rotational motion of the balance wheel 31 is less likely to become unstable. In particular, even if the posture of the mechanical clock 1 is displaced, the balance wheel 31 can still rotate stably.

[0180] In this embodiment, the air resistance component 15 is configured such that when the rotation angle of the balance wheel 31 is between 135° and 225°, the acted part 313 is located within the air resistance region AR. Furthermore, the air resistance region AR is configured with its center position 15C in the circumferential direction (see reference). Figure 6The positions of the actuating part 313 overlap with those of the balance wheel 31 at 180° and -180° in the direction of rotation of the balance wheel 31. Therefore, the air resistance experienced by the actuating part 313 is symmetrical when the balance wheel 31 rotates forward and backward. Thus, as described later... Figure 12 As shown in the curve of the middle section, the angular velocity of the balance wheel 31 is symmetrical when rotating in the forward direction and in the reverse direction.

[0181] [Example of a modified structure that reduces the angular velocity of balance wheel 31]

[0182] Here, refer to Figures 11A to 11J A modified example of the structure for reducing the angular velocity of the balance wheel 31 will be explained. Figures 11A to 11I This is a perspective view showing the balance wheel and air resistance components in a modified example of this embodiment. Figure 11J This is a perspective view showing the balance wheel and elastic component in a modified example of this embodiment.

[0183] Figure 11A The balance wheel 31 shown is in Figure 10 The balance wheel 31 shown has three notches 313A on its actuated portion 313, forming a drag wall that intersects circumferentially. The notches 313A are formed so that they pass through the air resistance region AR as the balance wheel 31 rotates.

[0184] Figure 11B The balance wheel 31 shown is in Figure 10 The balance wheel 31 shown has three radially extending grooves 313B on its actuated portion 313 to form a drag wall that intersects circumferentially. The grooves 313B are formed to pass through the air resistance region AR as the balance wheel 31 rotates.

[0185] exist Figure 11C In the balance wheel 31 shown, in Figure 10 The balance wheel 31 shown has three through holes 313C on its activated portion 313, forming a drag wall that intersects the circumferential direction. The through holes 313C are formed to pass through the air resistance region AR as the balance wheel 31 rotates.

[0186] By adopting Figures 11A to 11C As the affected part 313 passes through the air resistance region AR, the airflow within the air resistance region AR becomes turbulent, increasing the air resistance experienced by the affected part 313. This allows the affected part 313 to travel at a lower speed through the air resistance region AR.

[0187] in addition, Figures 11A to 11C The structure of the balance wheel 31 shown is one example, and it is not limited to any shape that has a recessed part forming a resistance wall that increases air resistance. That is, the location and number of notches, etc., are not limited to the case shown in the figure.

[0188] exist Figure 11D In, it means that besides Figure 10 In the example shown, besides the third wall portion 153 of the air resistance component 15, the first wall portion 151 and the second wall portion 152 are disposed radially inward from the track of the affected portion 313. That is, the air resistance component 15 forms the air resistance region AR solely by the opposing first wall portions 151 and second wall portions 152. Furthermore, the first wall portions 151 and second wall portions 152 can be independently assembled to the base plate 10, etc.

[0189] In addition, Figure 11D In the middle, the acted part 313 protrudes radially inward. Therefore, the acted part 313 passes through the air resistance region AR along with the rotational motion of the balance wheel 31. According to Figure 11D The structure shown can suppress the radial enlargement of the balance wheel 31 and the air resistance component 15.

[0190] exist Figure 11E In this configuration, the affected part 313 is positioned at a different location along the axial direction of the pivot shaft 311 than the circular part 312. Furthermore, the air resistance component 15 is positioned along the axial direction of the pivot shaft 311 at a location where the affected part 313 can pass through the air resistance region AR.

[0191] exist Figure 11F In, with Figure 11E Similarly, in the modified example shown, the affected portion 313 is positioned at a different location along the axial direction of the balance shaft 311 than the circular portion 312. Furthermore, the air resistance component 15 is positioned along the axial direction of the balance shaft 311 at a location where the affected portion 313 can pass through the air resistance region AR. Moreover, the circular portion 312 of the balance wheel 31 is semi-circular. Therefore, the balance wheel 31 is made lighter.

[0192] exist Figure 11E and Figure 11F In the example shown, the center of gravity of the balance wheel 31 can be adjusted by setting the acting part 313 at a position different from the circular part 312 in the axial direction.

[0193] exist Figure 11G In the middle, it indicates the diameter ratio of the circular part 312. Figure 10 The example shown has a small diameter balance wheel 31 and a thicker thickness at the position opposite the balance shaft 311 and the acted part 313. That is, the weight of the circular portion 312 at the position opposite the balance shaft 311 and the acted part 313 increases. With this structure, the center of gravity of the balance wheel 31 can be aligned with the balance shaft 311 (the center position of the balance wheel 31). Furthermore, by reducing the diameter of the balance wheel 31... Figure 11G In this structure, the advantages of increased freedom in the layout of the hairspring clamp 34 that fixes the outer end of the hairspring 32 can also be obtained.

[0194] exist Figure 11H The diagram illustrates an example where the air resistance component 15 lacks the first wall portion 151 and the second wall portion 152, but only includes a structure equivalent to the third wall portion 153. That is, Figure 11H The air resistance component 15 is composed of a base 154 and a third wall portion 153 that stands from the base 154 and is shaped along the rotation trajectory of the balance wheel 31.

[0195] exist Figure 11I In, it means in Figure 11H The air resistance component 15 shown includes an example of a groove 153I forming a resistance wall that intersects the balance wheel 31 circumferentially. Multiple grooves 153I are formed along the axial direction of the balance shaft 311. This structure allows for... Figure 11H In comparison, it can increase the air resistance acting on the affected part 313 that passes through the air resistance region AR.

[0196] Figure 11J This is an example of a structure that reduces the speed of the balance wheel 31 by contact resistance (frictional resistance) rather than by air resistance. Specifically, the balance wheel 31 has a protrusion 316 formed on the circular portion 312 as the acted part. In addition, an elastic member is used as the frictional resistance part.

[0197] Specifically, a first elastic member 151J is provided that contacts the protrusion 316 when the balance wheel 31 is at a rotation angle of 135°, and a second elastic member 152J is provided that contacts the protrusion 316 when the balance wheel 31 is at a rotation angle of 225°. The ends of the first elastic member 151J and the second elastic member 152J can be fixed to the base plate 10.

[0198] The first elastic component 151J and the second elastic component 152J contact the protrusion 316 of the balance wheel 31, generating frictional resistance while elastically deforming. During contact with the protrusion 316, the speed of the balance wheel 31 decreases due to the frictional resistance. Figure 11J In the example shown, the area through which the protrusion 316 contacts the first elastic member 151J and the second elastic member 151J is called the resistance region R1.

[0199] also, Figure 10 , Figures 11A to 11J The structure shown is an example. Any structure that acts on the balance wheel 31 during the middle of the forward and reverse motions to decelerate the balance wheel 31 is acceptable, and it is not limited to the example shown.

[0200] Furthermore, referring to Figure 11K , Figure 11L Other examples of balance wheel 31 will be explained. Figure 11KThis is a three-dimensional view showing the balance wheel of other examples as viewed from the side with the hairspring. Figure 11L This indicates the view from the side opposite to the side where the hairspring is located. Figure 11K A three-dimensional diagram showing the balance wheel configuration.

[0201] Figure 11K , Figure 11L The balance wheel 31 shown is Figure 10 Similar to the balance wheel shown, it has a circular portion 312 and an acted portion 313. In addition, an opening 312h is formed in the circular portion 312 at a position in the circumferential direction that overlaps with the acted portion 313.

[0202] and, Figure 11K , Figure 11L The rim 312a of the circular portion 312 of the balance wheel 31 shown protrudes axially toward the balance shaft 311. That is, the thickness of the rim 312a is thicker than the inner portion of the rim 312a in the circular portion 312. The acted portion 313 is formed flush with the rim 312a. That is, the thickness of the acted portion 313 is the same as that of the rim 312a, and thicker than the inner portion of the rim 312a in the circular portion 312.

[0203] exist Figure 11K , Figure 11L In the balance wheel 31 shown, because the thickness of the acted portion 313 is relatively large, the surface area in the acted portion 313 that bears air resistance is relatively wide. Therefore, it is possible to increase the... Figure 10 The amount of air pushed away by the actuating part 313 within the air resistance region AR shown can easily hinder the movement of the balance wheel 31, making it easier to reduce speed. In addition, by arranging the hairspring 32 on the relatively thin part of the balance wheel 31 other than the edge 312a and the actuating part 313, the combined thickness of the hairspring 32 and the balance wheel 31 in the axial direction of the balance shaft 311 can be reduced.

[0204] And, as Figure 11L As shown, the thickness of the surface opposite to the side where the hairspring 32 is located in the circular portion 312 of the balance wheel 31 is locally increased. If the thickness of the affected portion 313 is increased, the weight of the affected portion 313 becomes heavier, thereby moving the center of gravity of the balance wheel 31 closer to the affected portion 313. However, by locally increasing the thickness of the circular portion 312, the center of gravity of the balance wheel 31 can be aligned with the balance axis 311 (the center position of the balance wheel 31).

[0205] Furthermore, referring to Figures 11M to 11O This section provides a detailed description of the hairspring 32. Figure 11M It is a top view showing the state of the hairspring in its neutral position of elastic deformation. Figure 11N It is a top view showing the state of elastic deformation of the hairspring from the neutral position to the expanding direction. Figure 11OIt is a top view showing the state of elastic deformation of the hairspring from the neutral position towards the shrinking direction.

[0206] The hairspring 32 has an outer end 321 connected to the hairspring clamp 34 and an inner end 322 connected to the balance shaft 311. The inner end 322 is annular along the circumference of the balance shaft 311. The outer end 321 and the inner end 322 are thicker than the other parts (elastically deformable parts) of the hairspring 32. Therefore, the connection strength with the hairspring clamp 34 and the balance shaft 311 is maintained.

[0207] By lengthening the overall length of the hairspring 32, the elasticity of the hairspring 32 is reduced, thereby achieving lower vibration. If the overall length of the hairspring 32 is increased, the diameter of the hairspring 32 can be increased. To miniaturize the hairspring 32 and lengthen its overall length, the distance between the inner and outer portions of the hairspring 32 can be shortened. That is, the pitch of the hairspring 32 can be narrowed.

[0208] In the hairspring 32, a logarithmic spiral shape is employed. As mentioned above, a logarithmic spiral hairspring can be easily manufactured through laser processing. By employing a logarithmic spiral shape, compared to the uniformly spaced Archimedean spiral used as a typical hairspring shape, the distance between the pitches of the hairspring 32 on the inner end 322 side can be reduced, allowing for an increase in the overall length of the hairspring and a smaller diameter. As a result, along with the reduction in the diameter of the hairspring 32, spring force can be reduced, and low vibration can also be achieved. However, when the hairspring 32 is manufactured by laser processing as described above, it is difficult to narrow the pitch. This is because the shape of the hairspring 32 may deform due to the heat from the laser.

[0209] Therefore, in order to narrow the pitch and maintain the dimensional accuracy of the hairspring 32, such as Figures 11M to 11O As shown, the inner end portion 322 includes a fixing portion 322a and a pitch enlargement portion 322b. The fixing portion 322a is the part fixed to the balance shaft 311. The pitch enlargement portion 322b is the part with a width narrower than the fixing portion 322a, and it is the part that enlarges the pitch of the portion 323 of the hairspring 32 that is radially adjacent to the inner end portion 322. The portion 323 of the hairspring 32 that is radially adjacent to the inner end portion 322 is the part other than the inner end portion 322, and it is the part disposed on the innermost side. Figures 11M to 11O The W shown represents the distance between the inner end portion 322 and the portion 323 that is radially adjacent to the inner end portion 322.

[0210] In addition, Figures 11M to 11OThe example shown illustrates an instance where the inner end portion 322 is annular, i.e., the fixing portion 322a is connected to the spacing expansion portion 322b, but it is not limited to this. For example, the inner end portion 322 may also be partially separated in the circumferential direction, with the separated portion functioning as the spacing expansion portion 322b. However, an annular inner end portion 322 more easily ensures the fixing strength relative to the swing axis 311. Furthermore, in Figures 11M to 11O The example shown is of a spiral shape using a logarithmic spiral, but it is not limited to this. The structure forming the pitch enlargement 322b is particularly effective in spirals with a shape in which the pitch inside the diameter is narrower than the pitch outside the diameter.

[0211] Furthermore, in this embodiment, an example of a structure that slows down the balance wheel 31 has been described, but it is not limited to this. If the number of reciprocating motions per second of the balance wheel 31 is increased by speeding up the balance wheel 31, the error per second, i.e., the impact on the accuracy of the differential rate, becomes smaller. A structure having the elastic deformation part 332 described above can also be used in such a structure that speeds up the balance wheel 31.

[0212] [Regarding the timing of power generation]

[0213] The amount of current generated in the coil 43 due to the movement of the permanent magnet 41 increases proportionally to the angular velocity of the permanent magnet 41. Therefore, for efficient power generation, it is preferable to use the current generated in the coil 43 when the angular velocity of the permanent magnet 41 is relatively high.

[0214] Therefore, in this embodiment, at the moment when the permanent magnet 41 (balun 31) is at 0° or immediately thereafter, power is generated based on the current corresponding to the back electromotive force (detection voltage) detected by the coil 43 due to the movement of the permanent magnet 41. That is, as... Figure 12 As shown in the lower section of the graph, power generation occurs at the moment when the back electromotive force detected by coil 43 reaches its peak.

[0215] Furthermore, the timing of power generation is not limited to the moment when the balance wheel 31 is at a rotation angle of 0° or immediately thereafter, as long as it occurs before the acted part 313 (balance wheel 31) reaches the position of the air resistance member 15 during either the forward or reverse rotation of the balance wheel 31. That is, power generation can also occur based on the current corresponding to the back electromotive force detected by the coil 43, before the angular velocity of the balance wheel 31 decreases due to the air resistance of the acted part 313 caused by the air resistance of the air resistance member 15.

[0216] In addition, such as Figure 12As shown in the lower section of the graph, in this embodiment, the voltage waveform detected during the forward and reverse motion of the balance wheel 31 is the same. Therefore, in the mechanical clock 1, it is not necessary to know which direction the balance wheel 31 moves in, either forward or reverse, while ensuring that the power generation time is consistent.

[0217] [Relationship between magnetization direction and power generation efficiency of permanent magnet 41]

[0218] Here, refer to Figure 5 , Figure 12 , Figures 13A-13C The relationship between the magnetization direction of permanent magnet 41 and power generation efficiency is explained.

[0219] In the mechanical clock 1 of this embodiment, electricity is generated by rectifying the current corresponding to the back electromotive force generated in the coil 43 through the rectifier circuit 50. Here, for the rectification of the rectifier circuit 50, full-wave rectification using a bridge circuit containing multiple diodes or half-wave rectification using a circuit containing a single diode are considered. When using multiple diodes, a voltage drop occurs depending on the number of diodes, resulting in a corresponding loss of power. Therefore, in this embodiment, a structure using half-wave rectification through the rectifier circuit 50 is adopted. Furthermore, in half-wave rectification, the shapes of the positive and negative back electromotive forces are set differently, and power generation is based on the back electromotive force with the larger absolute value, thereby achieving efficient power generation. Therefore, in this embodiment, the permanent magnet 41 is configured to detect a back electromotive force suitable for half-wave rectification.

[0220] exist Figure 13A The figure shows the back electromotive force detected by the coil 43 in the configuration of the permanent magnet 41 in this embodiment. Figure 13B The figure shows the back electromotive force detected by coil 43 in the configuration of permanent magnet 41 in Comparative Example 1. Figure 13C In the figure, the back electromotive force detected by the coil 43 is shown in the configuration of the permanent magnet 41 in Comparative Example 2.

[0221] [Relationship between magnetization direction of permanent magnet 41 and power generation efficiency: This embodiment]

[0222] In this embodiment, the permanent magnet 41 is configured such that, when the hairspring 32 is in a neutral position of its elastic deformation, the magnetization direction is orthogonal to the relative directions of the first welded portion 423 and the second welded portion 424.

[0223] Here, the back electromotive force detected by coil 43 is explained before the permanent magnet 41 rotates forward from a position with a rotation angle of 0°, rotates in the opposite direction by the elastic force of the hairspring 32, and then rotates forward again by the elastic force of the hairspring 32.

[0224] Furthermore, the back electromotive force generated in the coil 43 due to the change in the magnetic field when the N pole portion 411 of the permanent magnet 41 moves toward the first end portion 421a of the soft magnetic core 42 is defined as a "positive" back electromotive force. On the other hand, the back electromotive force generated in the coil 43 due to the change in the magnetic field when the N pole portion 411 moves away from the first end portion 421a of the soft magnetic core 42 is defined as a "negative" back electromotive force.

[0225] In this embodiment, the permanent magnet 41 is in a magnetic equilibrium position when the rotation angle is 0°. Therefore, at the rotation angle of 0°, the back electromotive force generated by the coil 43 is 0. The permanent magnet 41 is supplied with power from the power spring 11 at the rotation angle of 0°. That is, at the moment after the rotation angle of 0°, the angular velocity of the permanent magnet 41 becomes maximum. In addition, during the period when the permanent magnet 41 rotates 180° forward from the rotation angle of 0°, the N pole portion 411 moves towards the first end portion 421a. Thus, in this embodiment, the permanent magnet 41 is configured such that the back electromotive force detected by the coil 43 during the period of rotation 180° forward from the power supply position is of the same polarity.

[0226] Therefore, during the period when the permanent magnet 41 rotates from a rotation angle of 0° to 180°, the angular velocity of the permanent magnet 41 becomes the maximum, and the positive back electromotive force generated in the coil 43 becomes the peak value.

[0227] When the permanent magnet 41 is in magnetic equilibrium, i.e., at a rotation angle of 180°, the back electromotive force generated in the coil 43 is 0.

[0228] As the permanent magnet 41 rotates from a rotation angle of 180° towards the forward direction, the N pole 411 moves away from the first end 421a. Therefore, during the period when the permanent magnet 41 rotates from a rotation angle of 180° to 340°, a negative back electromotive force is generated in the coil 43. The angular velocity of the permanent magnet 41 at this time is smaller than the angular velocity before moving from a rotation angle of 0° to 180°. Therefore, the absolute value of the peak value of the negative back electromotive force is smaller than the absolute value of the peak value of the positive back electromotive force.

[0229] Furthermore, the angular velocity of the permanent magnet 41 is 0 at the reversing position of the reciprocating motion, i.e., at a rotation angle of 340°. Therefore, the back electromotive force generated in the coil 43 is 0 at a rotation angle of 340°.

[0230] The permanent magnet 41, having reached a rotation angle of 340°, begins to rotate in the opposite direction due to the elastic force of the hairspring 32. As the permanent magnet 41 rotates from a rotation angle of 340° to 180°, the N pole 411 moves towards the first end 421a. Therefore, during the period when the permanent magnet 41 rotates from a rotation angle of 340° to 180°, a positive back electromotive force is generated in the coil 43.

[0231] Furthermore, when the permanent magnet 41 is in a magnetic equilibrium position and rotates by 180°, the back electromotive force generated in the coil 43 is 0.

[0232] Furthermore, the permanent magnet 41 rotates from a rotation angle of 180° to 0°. As the permanent magnet 41 rotates from a rotation angle of 180° to 0°, the N pole portion 411 moves away from the first end portion 421a. Therefore, as the permanent magnet 41 rotates from a rotation angle of 180° to 0°, a negative back electromotive force is generated in the coil 43.

[0233] Furthermore, when the permanent magnet 41 is in magnetic equilibrium, i.e., when the rotation angle is 0°, the back electromotive force generated in the coil 43 is 0.

[0234] Power from the power spring 11 is supplied to the permanent magnet 41, which has reached a rotation angle of 0°. That is, after the rotation angle reaches 0°, the angular velocity of the permanent magnet 41 becomes maximum. Furthermore, during the rotation of the permanent magnet 41 from 0° to -180°, the N pole portion 411 moves towards the first end portion 421a. Thus, in this embodiment, the permanent magnet 41 is configured such that the back electromotive force detected by the coil 43 during the rotation -180° in the opposite direction from the power supply position becomes of the same polarity.

[0235] Therefore, during the period when the permanent magnet 41 rotates from a rotation angle of 0° to -180°, the angular velocity of the permanent magnet 41 becomes the maximum, and the positive back electromotive force generated in the coil 43 becomes the peak value.

[0236] When the permanent magnet 41 is in magnetic equilibrium, i.e., at a rotation angle of -180°, the back electromotive force generated in the coil 43 is 0.

[0237] When the permanent magnet 41 rotates in the opposite direction from a rotation angle of -180°, the N pole 411 moves away from the first end 421a. Therefore, during the rotation of the permanent magnet 41 from a rotation angle of -180° to -340°, a negative back electromotive force is generated in the coil 43. The angular velocity of the permanent magnet 41 at this time is lower than the angular velocity before moving from a rotation angle of 0° to -180°. Therefore, the absolute value of the peak value of the negative back electromotive force is smaller than the absolute value of the peak value of the positive back electromotive force.

[0238] Furthermore, the angular velocity of the permanent magnet is 0 at the reciprocating position, i.e., at a rotation angle of -340°. Therefore, at a rotation angle of -340°, the back electromotive force generated in coil 43 is 0.

[0239] The permanent magnet 41, having reached a rotation angle of -340°, begins to rotate in the forward direction due to the elastic force of the hairspring 32. As the permanent magnet 41 rotates from a rotation angle of -340° to -180°, the N pole 411 moves towards the first end 421a. Therefore, during the rotation of the permanent magnet 41 from a rotation angle of -340° to -180°, a positive back electromotive force is generated in the coil 43.

[0240] Furthermore, when the permanent magnet 41 is in magnetic equilibrium, i.e., at a rotation angle of -180°, the back electromotive force generated in the coil 43 is 0.

[0241] Furthermore, the permanent magnet 41 rotates from a rotation angle of -180° to 0°. As the permanent magnet 41 rotates from a rotation angle of -180° to 0°, the N pole portion 411 moves away from the first end portion 421a. Therefore, as the permanent magnet 41 rotates from a rotation angle of -180° to 0°, a negative back electromotive force is generated in the coil 43.

[0242] Repeating the above actions, in the configuration of the permanent magnet 41 in this embodiment, the coil 43 generates... Figure 13A The back electromotive force of the waveform shown. For example... Figure 13A As shown, the peak value of the back EMF differs under positive and negative back EMF conditions. That is, the maximum absolute value of the positive back EMF is greater than the maximum absolute value of the negative back EMF. Furthermore, the waveform of the detected back EMF is the same during both the forward and reverse motion of the permanent magnet 41.

[0243] [Relationship between magnetization direction of permanent magnet 41 and power generation efficiency: Comparative Example 1]

[0244] Next, refer to Figure 13B Comparative Example 1 will be described. In Comparative Example 1, the permanent magnet 41 is configured such that, with the hairspring 32 in its neutral position of elastic deformation, the magnetization direction is inclined at 45° toward the direction opposite to the first weld portion 423 and the second weld portion 424. That is, in Comparative Example 1, the position with a rotation angle of 0° is inclined at -45° compared to this embodiment.

[0245] In Comparative Example 1, when the permanent magnet 41 rotates from a rotation angle of 0° to the forward direction, firstly, the N pole portion 411 moves away from the first end portion 421a. Furthermore, when the permanent magnet 41 passes through a rotation angle of 45°, the N pole portion 411 moves closer to the first end portion 421a. Therefore, during the period when the permanent magnet 41 rotates from a rotation angle of 0° to 225° in the forward direction, a negative back electromotive force is generated in the coil 43 immediately after rotation, and then a positive back electromotive force is generated in the coil 43 after passing through a rotation angle of 45°.

[0246] In Comparative Example 1, the permanent magnet 41 rotates from a rotation angle of 0° to 340° in the forward direction, then rotates in the reverse direction due to the elastic force of the hairspring 32, returning to a rotation angle of 0°. During the reverse rotation from 0°, the N pole 411 moves towards the first end 421a. That is, when the permanent magnet 41 rotates from a rotation angle of 0° in the reverse direction, a positive back electromotive force is generated in the coil 43.

[0247] Thus, in Comparative Example 1, the waveforms of the positive and negative back electromotive forces are different before and after the rotation angle of 0° during forward and reverse rotation. Therefore, the peak values ​​of the back electromotive forces differ between forward and reverse rotation. Furthermore, since the peak position of the back electromotive force differs between forward and reverse rotation, it is judged that the period of the forward and reverse rotation of the balance wheel 31 is disordered, potentially leading to erroneous difference rate adjustments. Therefore, in the structure of Comparative Example 1, the difference rate adjustment mechanism 40 needs to have a unit that pre-determines which direction the balance wheel 31 moves in during forward and reverse motion.

[0248] [Relationship between magnetization direction of permanent magnet 41 and power generation efficiency: Comparative Example 2]

[0249] Next, refer to Figure 13C Comparative Example 2 will be described. In Comparative Example 2, the permanent magnet 41 is configured such that, with the hairspring 32 in its neutral position of elastic deformation, the magnetization direction is the same as the relative direction of the first welded portion 423 and the second welded portion 424. That is, in Comparative Example 2, the position with a rotation angle of 0° is tilted -90° compared to this embodiment.

[0250] In Comparative Example 2, when the permanent magnet 41 rotates from a rotation angle of 0° towards the forward direction, firstly, the N pole portion 411 moves away from the first end portion 421a. Then, when the permanent magnet 41 passes through a rotation angle of 90°, the N pole portion 411 moves towards the first end portion 421a. Therefore, during the period when the permanent magnet 41 rotates 180° from a rotation angle of 0° towards the forward direction, a negative back electromotive force is generated in the coil 43 immediately after rotation, and then a positive back electromotive force is generated in the coil 43 after passing through a rotation angle of 90°.

[0251] In Comparative Example 2, the permanent magnet 41 rotates from a rotation angle of 0° to 340° in the forward direction, then rotates in the reverse direction due to the elastic force of the hairspring 32, returning to a rotation angle of 0°. During the reverse rotation from 0°, the N pole 411 moves towards the first end 421a. That is, when the permanent magnet 41 rotates from a rotation angle of 0° in the reverse direction, a positive back electromotive force is generated in the coil 43.

[0252] Thus, in Comparative Example 2, the waveforms of the positive and negative back electromotive forces (EMFs) are different before and after the rotation angle of 0° during forward and reverse rotation. Therefore, the peak values ​​of the back EMFs are different during forward and reverse rotation. In the structure of Comparative Example 2, compared to Comparative Example 1, the peak value of the back EMF is smaller during either forward or reverse rotation, and it cannot be considered a suitable back EMF for half-wave rectification. Furthermore, since the peak values ​​of the back EMFs are different during forward and reverse rotation, the threshold Vth needs to be different depending on the situation. Therefore, similar to Comparative Example 1, the differential adjustment mechanism 40 needs to have a unit that pre-knows which direction the balance wheel 31 moves in during forward and reverse motion.

[0253] [Relationship between magnetization direction and power generation efficiency of permanent magnet 41: Summary]

[0254] As explained above, in this embodiment, the back electromotive force (EMF) of the same shape is detected regardless of whether the rotation direction of the permanent magnet 41 is forward or reverse. Therefore, in this embodiment, the peak value of the positive back EMF is detected with the same magnitude and a constant period. Furthermore, in this embodiment, the shapes of the positive and negative back EMFs are asymmetrical. Specifically, the peak value of the positive back EMF is greater than the peak value of the negative back EMF. Therefore, in the configuration of the permanent magnet 41 in this embodiment, compared to Comparative Examples 1 and 2, it can be said to be a back EMF waveform suitable for differential rate adjustment and half-wave rectification.

[0255] also, Figure 5 The configuration of the permanent magnet 41 shown is an example. The permanent magnet 41 can be configured such that, when the hairspring 32 is in its neutral position under elastic deformation, its magnetization direction is the same as the relative direction of the first end 421a and the second end 422a. Furthermore, the relative direction of the first end 421a and the second end 422a refers to... Figure 5 The directions of the first welded portion 423 and the second welded portion 424 shown are orthogonal. However, it is not limited to this, the magnetization direction of the permanent magnet 41 can be towards the first end 421a or the second end 422a, at least when the hairspring 32 is in its neutral position of elastic deformation.

[0256] Additionally, the permanent magnet 41 can be configured such that, when the hairspring 32 is in its neutral position of elastic deformation, the boundary B between the N pole portion 411 and the S pole portion 412 and the imaginary strip-shaped area connecting the first weld portion 423 and the second weld portion 424 ( Figure 5 The S shown overlaps. Furthermore, the strip region S is an imaginary region defined for convenience in representing the configuration of the permanent magnet 41, and is not a region that physically exists as part of the structure of the mechanical clock 1.

[0257] [Circuit Diagram]

[0258] Here, refer to Figure 14A The general outline of the rectifier circuit in this embodiment will be described. Figure 14A This is a circuit diagram illustrating an example of the circuitry in this embodiment.

[0259] In this embodiment, the following structure is adopted: a rectifier circuit 50 containing a diode D is used to perform half-wave rectification on the current corresponding to the back electromotive force generated in the coil 43 due to the movement of the permanent magnet 41. The rectifier circuit 50 is a circuit that eliminates the negative voltage portion of the back electromotive force generated in the coil 43 and converts it to direct current.

[0260] Transistors TP1 and TP2 are connected to terminals O1 and O2 of coil 43, respectively. The back electromotive force generated in coil 43 is input to transistors TP1 and TP2, and based on this, the rotation detection circuit 45 detects the detection signal. That is, by turning on transistor TP2 at a predetermined time, the induced voltage generated at terminals O1 and O2 corresponding to these transistors can be extracted as a voltage signal, i.e., the detection signal.

[0261] Additionally, transistors P11 and P12 are connected to the first terminal O1 of coil 43, and transistors P21 and P22 are connected to the second terminal O2 of coil 43. Transistors P11, P12, P21, and P22 are ON / OFF controlled by speed control pulses from speed control pulse output circuit 46. During power generation, the gate terminals of transistors P11, P12, P21, and P22 are turned off. In this state, rectifier circuit 50 is formed by transistors TP1 and TP2 and diode D. Current flows through coil 43 due to the forward and reverse rotation of permanent magnet 41, and capacitor C is charged. When capacitor C is charged to a certain extent, power supply circuit 60 is activated. Furthermore, the activation of power supply circuit 60 activates control circuit 44, which controls the circuits included in differential rate adjustment mechanism 40.

[0262] In this embodiment, such as Figure 14A As shown, a half-wave rectification structure is adopted using a rectifier circuit 50 containing one diode D, which simplifies the circuit structure and reduces voltage drop. Furthermore, Figure 14A The circuit shown is an example, such as Figure 14B As shown, the rectifier circuit 50 can also be a voltage multiplier rectifier circuit capable of rectifying the reverse back electromotive force. Figure 14B The diagram illustrates an example of a voltage doubler rectifier circuit comprising two diodes, D1 and D2, and two capacitors, C1 and C2. Compared to a full-wave rectifier circuit, the number of diodes can be reduced in a voltage doubler rectifier circuit. That is, voltage drop is less likely to occur.

[0263] [Details regarding differential adjustment control]

[0264] The following is for reference Figure 12 , Figures 15A to 19 The details of the differential rate adjustment control in this embodiment will be explained. Figure 15A , Figure 15B This diagram illustrates the control of the permanent magnet's movement based on speed-regulating pulses in this embodiment.

[0265] In this embodiment, the speed regulating pulse output circuit 46 outputs a speed regulating pulse, thereby controlling the movement of the permanent magnet 41, which in turn controls the movement of the balance wheel 31 to perform differential adjustment.

[0266] In this embodiment, such as Figure 15A As shown, when a speed-regulating pulse is output to the first terminal O1 of coil 43, the first end 421a is defined as having the S pole polarity, and the second end 422a is defined as having the N pole polarity. On the other hand, as... Figure 15B As shown, when a speed-regulating pulse is output to terminal O2 of coil 43, the first end 421a is defined as having the N pole polarity and the second end 422a as having the S pole polarity. Furthermore, when the winding direction of coil 43 is reversed, the polarities of the first end 421a and the second end 422a are reversed.

[0267] [Details regarding differential adjustment control: Output timing of the speed control pulse]

[0268] Here, with the permanent magnet 41 at a relatively high angular velocity, it is difficult to perform differential rate adjustment at the desired time. This is because, with the permanent magnet 41 at a relatively high angular velocity, the output timing of the speed regulation pulse is more likely to deviate.

[0269] Therefore, in this embodiment, during the forward and reverse rotation of the permanent magnet 41, speed regulating pulses are output during the period when the permanent magnet 41 rotates from a rotation angle of 180° to 0° in the reverse direction and during the period when it rotates from a rotation angle of -180° to 0° in the forward direction. That is, speed regulating pulses are output during the period before power is supplied from the power spring 11 to the balance wheel 31. Thus, speed regulating pulses can be output when the angular velocity of the permanent magnet 41 is relatively slow. In addition, in this embodiment, since the balance wheel 31 is subjected to air resistance generated by the air resistance member 15 between rotation angles of 225° and 135°, the angular velocity of the permanent magnet 41 is particularly slow during the period between rotation angles of 180° and 0°. The same is true between rotation angles of -225° and -135°. In this way, differential adjustment can be performed during the period after the acted part 313 reaches the position of the air resistance member 15 during the forward and reverse rotation of the balance wheel 31.

[0270] By employing this structure, the output timing offset of the speed control pulse can be suppressed. As a result, differential accuracy can be maintained. Furthermore, in Figure 12 In this context, a strip-shaped area represents the moment when the differential adjustment is performed. For example... Figure 12 As shown in the upper part of the graph, the differential rate adjustment is performed during the period when the angular velocity of the permanent magnet 41 is relatively slow.

[0271] [Details regarding differential adjustment control: coil terminals for output speed control pulses]

[0272] exist Figure 15A The example shown illustrates the output of a speed regulating pulse to the coil 43 at the moment when the permanent magnet 41 rotating in the forward direction is at a rotation angle of -90° and at the moment when the permanent magnet 41 rotating in the reverse direction is at a rotation angle of 90°.

[0273] like Figure 15A As shown, when the permanent magnet 41 rotates forward from a rotation angle of -90°, and a speed-regulating pulse is output to the first terminal O1 of the coil 43, the permanent magnet 41 experiences a repulsive force from the soft magnetic core 42. That is, braking is applied to the forward rotation of the permanent magnet 41. Conversely, when the permanent magnet 41 rotates backward from a rotation angle of 90°, and a speed-regulating pulse is output to the first terminal O1 of the coil 43, the permanent magnet 41 experiences a repulsive force from the soft magnetic core 42. That is, braking is applied to the reverse rotation of the permanent magnet 41.

[0274] In addition, such as Figure 15B As shown, when the permanent magnet 41 rotates forward from a rotation angle of -90°, and a speed-regulating pulse is output to the second terminal O2 of the coil 43, the permanent magnet 41 experiences an attractive force from the soft magnetic core 42. That is, an accelerator is applied to the forward rotation of the permanent magnet 41. Conversely, when the permanent magnet 41 rotates backward from a rotation angle of 90°, and a speed-regulating pulse is output to the second terminal O2 of the coil 43, the permanent magnet 41 experiences an attractive force from the soft magnetic core 42. That is, an accelerator is applied to the reverse rotation of the permanent magnet 41.

[0275] Thus, in this embodiment, regardless of whether the permanent magnet 41 rotates in the forward or reverse direction, the rotation of the permanent magnet 41 can be reduced by outputting a speed regulating pulse to the first terminal O1. On the other hand, the rotation of the permanent magnet 41 can be enhanced by outputting a speed regulating pulse to the second terminal O2.

[0276] That is, regardless of whether the permanent magnet 41 rotates in the forward or reverse direction, when the differential rate is adjusted in the direction of delay, the first terminal O1 is energized, and when the differential rate is adjusted in the direction of forward movement, the second terminal O2 is energized.

[0277] [Details about differential adjustment control: the operation flow of differential adjustment control]

[0278] Figure 16 This is a flowchart illustrating an example of the differential adjustment control in this embodiment. Furthermore, in the following description, the signal detected by the rotation detection circuit 45 by generating a back electromotive force exceeding a predetermined threshold Vth is defined as the detection signal DE. The control circuit 44 controls the speed regulation pulse output circuit 46 based on the detection signal DE detected by the rotation detection circuit 45 and the reference signal OS generated by the frequency divider circuit 47.

[0279] The detection signal DE is detected when the coil 43 generates a large back electromotive force, that is, when the angular velocity of the permanent magnet 41 is relatively high. Therefore, the control circuit 44 can perform differential adjustment based on the detection voltage and reference signal OS generated in the coil 43 due to the movement of the permanent magnet 41 before the acted part 313 reaches the position of the air resistance component 15 during the forward and reverse rotation of the balance wheel 31.

[0280] In this embodiment, after the power supply circuit 60 is started by generating electricity through the movement of the permanent magnet 41 (ST1 "Yes"), differential rate adjustment control is performed using the differential rate adjustment mechanism 40.

[0281] If the detection signal DE is detected during the output of the reference signal OS (ST2's "Yes"), that is, if no differential rate deviation occurs, the differential rate adjustment control ends. Additionally, Figure 17 This is a timing diagram illustrating an example where a detection signal is detected during the output of a reference signal. For example... Figure 17 As shown, in this embodiment, the output period of the reference signal OS is set to an output period ts with a specified width.

[0282] If the detection signal DE is not detected during the output period of the reference signal OS ("No" in ST2), that is, if a difference rate deviation occurs, the control circuit 44 determines whether the detection time of the detection signal DE is earlier than the output period of the reference signal OS (ST3).

[0283] If the detection time of the detection signal DE is earlier than the output period of the reference signal OS ("Yes" in ST3), the control circuit 44 controls the speed regulation pulse output circuit 46 to output a speed regulation pulse to the terminal O1 (ST4).

[0284] Figure 18 This is a timing diagram illustrating an example where the detection time of the detected signal is earlier than the output period of the reference signal. Figure 18The example shown illustrates that, at a time tp1 elapsed since the detection time of the detection signal DE, the speed control pulse p1 is output to the first terminal O1 of coil 43. For example... Figure 18 As shown, the periods of the detection signal DE are different before and after the output of the speed control pulse p1. That is, the detection period of the detection signal DE detected after the output speed control pulse p1 is longer than the detection period of the detection signal DE detected before the output speed control pulse p1. Therefore, the detection signal DE is detected within ts during the output period of the reference signal OS after the output speed control pulse p1.

[0285] If the detection time of the detection signal DE is later than that of the reference signal OS (No in ST3), the control circuit 44 controls the speed regulation pulse output circuit 46 to output a speed regulation pulse to the terminal O2 (ST5).

[0286] Figure 19 This is a timing diagram illustrating an example where the detection of the detection signal occurs later than the output period of the reference signal. Figure 19 The example shown illustrates that, at a time tp2 elapsed since the detection time of the detection signal DE, the speed control pulse p2 is output to the second terminal O2 of coil 43. For example... Figure 19 As shown, the periods of the detection signal DE are different before and after the output of the speed control pulse p2. That is, the detection period of the detection signal DE detected after the output speed control pulse p2 is shorter than the detection period of the detection signal DE detected before the output speed control pulse p2. Therefore, the detection signal DE is detected within ts during the output period of the reference signal OS after the output speed control pulse p2.

[0287] Furthermore, the output timing and duration of the speed-regulating pulse p1 output to terminal O1 and the speed-regulating pulse p2 output to terminal O2 can also be different. This is because the correction amount generated by the output speed-regulating pulses may sometimes differ in the direction of advancing the permanent magnet 41 and the direction of delay.

[0288] [Details about differential adjustment control: Operation flow of the first variation of differential adjustment control]

[0289] Next, refer to Figure 20 , Figure 21 The first variation of the differential rate adjustment control will be explained. Figure 20 This is a flowchart representing the first variation of differential rate adjustment control.

[0290] In this example, the differential adjustment mechanism 40 may have: a first counter that counts the number of times the detection signal DE is detected; and a second counter as a storage unit that stores the period difference between the detection signal DE and the reference signal OS (the deviation of the detection time of the detection signal DE from the output time of the reference signal OS).

[0291] In the first variation of differential rate adjustment control, after the power supply circuit 60 is started by generating electricity through the movement of the permanent magnet 41 (ST1 "Yes"), differential rate adjustment control is performed using the differential rate adjustment mechanism 40.

[0292] The control circuit 44 determines whether the forward and reverse rotation of the balance wheel 31 (permanent magnet 41) is the 8th time. Specifically, the control circuit 44 determines whether the count value of the first counter is 8 (ST21).

[0293] If the count of the first counter is not 8 (ST21), calculate the period difference between the detection signal DE and the reference signal OS, and save the period difference (ST22). Then, increment the count value of the first counter by 1 (ST23).

[0294] On the other hand, if the count of the first counter is 8 ("Yes" in ST21), the first counter is reset so that the count is 0 (ST24).

[0295] Then, the control circuit 44 determines whether the stored amount of the period difference between the detection signal DE and the reference signal OS is 0 or within a specified range (ST25). If the stored amount of the period difference between the detection signal DE and the reference signal OS is 0 or within a specified range, no difference adjustment is performed, and the count of the first counter is incremented by 1 (ST23).

[0296] When the retention amount of the period difference between the detection signal DE and the reference signal OS is positive ("No" in ST25, "Yes" in ST26), the control circuit 44 controls the speed regulation pulse output circuit 46 to output a speed regulation pulse (ST4) to the first terminal O1.

[0297] On the other hand, when the amount of time difference between the detection signal DE and the reference signal OS is negative ("No" in ST25, "No" in ST26), the control circuit 44 controls the speed regulation pulse output circuit 46 to output a speed regulation pulse (ST5) to the second terminal O2.

[0298] exist Figure 21The preceding section illustrates examples where, when the first counter is 2, the detection time of the detection signal DE is t earlier than the output period of the reference signal OS; when the first counter is 3, the detection time of the detection signal DE is 2t earlier than the output period of the reference signal OS; and when the first counter is 6, the detection time of the detection signal DE is t later than the output period of the reference signal OS. In this example, the retention amount of the period difference until the first counter becomes 8 is +2t. That is, the detection time of the detection signal DE is a total of 2t earlier than the reference signal OS. Therefore, the control circuit 44 outputs a speed adjustment pulse to the first terminal O1 to slow down the difference rate.

[0299] exist Figure 21 The following section illustrates examples where, when the first counter is 2, the detection time of the detection signal DE is 3t earlier than the output period of the reference signal OS; when the first counter is 3, the detection time of the detection signal DE is 2t earlier than the output period of the reference signal OS; and when the first counter is 6, the detection time of the detection signal DE is t later than the output period of the reference signal OS. In this example, the retention amount of the period difference until the first counter becomes 8 is +4t. That is, the detection time of the detection signal DE is a total of 4t earlier than the reference signal OS. Therefore, a speed adjustment pulse is output to the first terminal O1 to slow down the difference rate.

[0300] In addition, Figure 21 In the example below, with Figure 21 Compared to the example above, the retention of the time difference is larger, thus extending the output period of the speed control pulse. Specifically, it makes... Figure 22 The lower part shows the output period of the speed regulating pulse p112 compared to Figure 22 The output period of the speed control pulse shown at the top is p111 long. Additionally, in Figure 22 In either the upper or lower segment, the speed control pulse is output at a time tp111 after the reference signal OS is output when the first output counter is 8. That is, the output time of the speed control pulse is the same regardless of the output period of the speed control pulse.

[0301] In the first variation of the differential rate adjustment control described above, by not performing differential rate adjustment every second, the number of output speed control pulses can be reduced. As a result, power consumption can be reduced.

[0302] [Details about differential rate adjustment control: Operation flow of the second variation of differential rate adjustment control]

[0303] Next, refer to Figure 22 , Figure 23 The second variation of the differential rate adjustment control will be explained. Figure 22 This is a flowchart representing the second variation of differential rate adjustment control.

[0304] In this example, the differential adjustment mechanism 40 may include: a first counter that counts the number of times the detection signal DE is detected; and a second counter as a storage unit that stores the period difference between the detection signal DE and the reference signal OS (the deviation of the detection time of the detection signal DE from the output time of the reference signal OS). Furthermore, in a second variation of the differential adjustment control, when the second counter is reset, the count becomes 7.

[0305] In the second variation of differential rate adjustment control, after the power supply circuit 60 is started by generating electricity through the movement of the permanent magnet 41 (ST1 "Yes"), differential rate adjustment control is performed using the differential rate adjustment mechanism 40.

[0306] The control circuit 44 determines whether the forward and reverse rotation of the balance wheel 31 (permanent magnet 41) is the 8th time. Specifically, the control circuit 44 determines whether the count value of the first counter is 8 (ST21).

[0307] If the count of the first counter is not 8 ("No" in ST21), the control circuit 44 calculates the period difference between the detection signal DE and the reference signal OS (ST31).

[0308] Then, if the detection time of the detection signal DE is within the output period of the reference signal OS ("Yes" in ST32), the control circuit 44 does not perform differential adjustment and increments the count of the first counter by 1 (ST23).

[0309] If the detection time of the detection signal DE is not within the output period of the reference signal OS (ST32 "No"), the control circuit 44 determines whether the detection time of the detection signal DE is earlier than the output period of the reference signal OS (ST33).

[0310] If the detection time of the detection signal DE is earlier than the output period of the reference signal OS (ST33 "Yes"), subtract the second count based on the period difference (ST34). If the detection time of the detection signal DE is later than the output period of the reference signal OS (ST33 "No"), add the second count based on the period difference (ST35). Then, increment the count value of the first counter by 1 (ST23).

[0311] If the count of the first counter is 8 (ST21 is), the first counter is reset so that the count is 0 (ST24).

[0312] Then, the control circuit 44 determines whether the count value of the second counter is 7 (ST36). If the count value of the second counter is 7 ("Yes" in ST36), no differential adjustment is performed, and the count value of the first counter is incremented by 1 (ST23).

[0313] If the count of the second counter is not 7 (ST36 "No"), the control circuit 44 determines whether the count of the second counter is less than 7 (ST37). If the count of the second counter is less than 7 (ST37 "Yes"), the control circuit 44 controls the speed regulation pulse output circuit 46 to output a speed regulation pulse to the first terminal O1 (ST4). If the count of the second counter is greater than 7 (ST37 "No"), the control circuit 44 controls the speed regulation pulse output circuit 46 to output a speed regulation pulse to the second terminal O2 (ST5). Then, the count value of the second counter is reset to 7 (ST38).

[0314] In the second variation of the differential adjustment control described above, by not performing differential adjustment every second, the number of output speed control pulses can be reduced. As a result, power consumption can be reduced.

[0315] exist Figure 23 The example illustrates how, when the first counter is 2, the detection time of the detection signal DE is t earlier than the output period of the reference signal OS; when the first counter is 3, the detection time of the detection signal DE is 2t earlier than the output period of the reference signal OS; and when the first counter is 6, the detection time of the detection signal DE is t later than the output period of the reference signal OS. In this example, the second counter becomes 5 before the first counter becomes 8. That is, the detection time of the detection signal DE is a total of 2t earlier than the reference signal OS. Therefore, the control circuit 44 outputs a speed adjustment pulse to the first terminal O1 to slow down the differential rate.

[0316] Furthermore, the speed control pulse is not limited to a single pulse, such as... Figure 24 As shown, it can also be composed of pulse groups containing multiple single pulses. By making the speed regulating pulses consist of pulse groups, manufacturing deviations and drive deviations of the speed regulating mechanism 30 can be absorbed. In this case, it is also possible that it is not as shown... Figure 21 Instead of changing the output period of the speed-regulating pulse as shown, the attractive or repulsive force acting on the permanent magnet 41 is controlled by changing the duty cycle of the speed-regulating pulse. Furthermore, the duty cycle represents the proportion of output pulses within a specified period. Figure 24 The example shown is a speed-regulating pulse with a duty cycle of 3 / 5.

[0317] [Details regarding differential adjustment control: Differential adjustment control when the power supply circuit starts from a stopped state]

[0318] Figure 25 This is a timing diagram illustrating an example of differential adjustment control when a power supply circuit starts from a stopped state.

[0319] As described above, after the power supply circuit 60 is started by generating electricity using the movement of the permanent magnet 41, differential rate adjustment control is performed using the differential rate adjustment mechanism 40. Therefore, the output of the reference signal OS for differential rate adjustment control can begin after the power supply circuit 60 is started. For example, as Figure 25 As shown, the output of the reference signal OS can begin from the moment the detection signal DE is first detected. Figure 25 The diagram illustrates the scenario where the peak value of the back electromotive force gradually increases, and the output of the reference signal OS begins at the moment it initially exceeds the threshold Vth. Specifically, it represents the scenario where the output of the reference signal OS begins one second after the moment it initially exceeds the threshold Vth. However, this is not the only possibility; the unstable rotating state of the power supply circuit 60 immediately after startup can also be considered, with the output of the reference signal OS beginning at the moment when multiple (predetermined) detection signals DE are detected.

[0320] [Details about differential adjustment control: Differential adjustment control considering the effects of disturbances]

[0321] Figure 26 This is a timing diagram illustrating an example of differential adjustment control that takes into account the effects of disturbances. Figure 27 This is a flowchart illustrating an example of differential adjustment control that takes into account the effects of disturbances. Figure 28 It means in Figure 20 The flowchart of the first variation of the differential adjustment control shown considers the effect of disturbances.

[0322] When an external magnet approaches or impacts the mechanical clock 1, the back electromotive force may become disordered due to the instantaneous interference, making it impossible to detect the detection signal DE. In this case, the control circuit 44 makes a misjudgment due to a significant delay in the differential rate.

[0323] Therefore, as Figure 26 As shown, if no detection signal DE is detected within a specified period before and after the output period containing the reference signal OS, differential adjustment may not be performed. Figure 26 The upper section describes the case where the detection signal DE was not detected near the measurement time of 2.0 [s] due to interference. Specifically, it describes the case where the detection signal was not detected during the output period ts of the reference signal OS, the period dt1 immediately before the output period ts, and the period dt2 immediately after the output period ts. Furthermore, in Figure 26The example shown illustrates that periods dt1 and dt2 are of the same length, but they can also be of different lengths. Furthermore, the speed control pulse can be output without considering periods dt1 and dt2. This is because when a speed control pulse is output, the coil waveform (the waveform of the back electromotive force) becomes disordered, potentially reducing the detection accuracy of the detection signal DE.

[0324] exist Figure 27 The flowchart shown illustrates an example where, after the power supply circuit 60 is activated by generating electricity through the movement of the permanent magnet 41 (ST1 "Yes"), differential rate adjustment is performed when a detection signal DE is output (detected) during a predetermined detection period (dt1~ts~dt2) (step ST11 "Yes"). Conversely, an example is shown where differential rate adjustment is not performed when no detection signal DE is output (detected) during the predetermined detection period (dt1~ts~dt2) (step ST11 "No"). Furthermore, Figure 27 Except for ST11, the steps shown are the same as... Figure 16 The steps shown are the same, so detailed instructions are omitted.

[0325] exist Figure 28 The flowchart shown illustrates an example where, after the power supply circuit 60 is activated by generating electricity through the movement of the permanent magnet 41 ("Yes" in ST1), a differential rate adjustment is performed when a detection signal DE is output (detected) during a predetermined detection period (dt1~ts~dt2) ("Yes" in step ST11). On the other hand, it illustrates an example where, if the detection signal DE is not output (detected) during the predetermined detection period (dt1~ts~dt2) ("No" in step ST11), the first counter is reset without differential rate adjustment (ST12). Thus, in the event of interference or other disturbances, resetting the first counter restarts the counting of the number of detections of the detection signal DE.

[0326] also, Figure 28 Except for ST11 and ST12, the steps shown are the same as... Figure 20 The steps shown are the same, and the function of the first counter is also the same, so its detailed description is omitted.

[0327] By adopting Figures 26-28 The structure shown enables high-precision differential rate adjustment even under interference. Furthermore, it can suppress unnecessary output speed control pulses, thus reducing power consumption.

[0328] [Details regarding differential adjustment control: Differential adjustment control in the case of continuous detection signal failures]

[0329] Figure 29 , Figure 30This is a timing diagram illustrating an example of differential rate adjustment control in the case of continuous detection failures of the detection signal. Figure 31 This is a flowchart illustrating an example of differential rate adjustment control that assumes the detection of a detection signal will fail continuously.

[0330] When the winding of the power spring 11 is released, the rotational force of the rotor 41 decreases, and sometimes the back electromotive force (back electromotive force / back electromotive force voltage) does not exceed the threshold Vth. In this case, the power generation decreases, and the charge stored in the capacitor C also decreases. That is, the mechanical clock 1 is in a state where it is easy to stop, and the power supply circuit 60 is in a state where it is easy to stop. In such a case, in order to save power, it is preferable not to output speed regulating pulses. That is, it is preferable not to perform differential rate adjustment.

[0331] Therefore, in Figure 29 , Figure 30 In the example shown, the following structure is used: a third counter that counts the number of consecutive failures in detecting the detection signal DE and a fourth counter that counts the number of consecutive successes in detecting the detection signal DE, and a "speed control pulse output setting" that switches the output speed control pulse and a "speed control pulse stop setting" that stops the output of the speed control pulse.

[0332] Specifically, when the third counter reaches 10, that is, when the detection signal DE fails to be detected 10 times consecutively, the setting switches to speed control pulse stop. Furthermore, when the fourth counter reaches 20, that is, when the detection signal DE is detected successfully 20 times consecutively, the setting switches to speed control pulse output. The counter value that triggers the setting switch is just one example, and is not limited to the example shown here.

[0333] exist Figure 29 The example in the image shows a small peak value of the back electromotive force, and the detection signal DE fails to detect 10 times consecutively, thus switching to the speed control pulse stop setting.

[0334] exist Figure 30 The example illustrates a scenario where the speed control pulse is stopped after 10 consecutive failures in detecting the DE signal, and then switched to a speed control pulse output setting after 20 consecutive successful detections of the DE signal, thus outputting a speed control pulse p1. Additionally, regarding... Figures 26-28 Similarly, in the example shown, the success of the detection of the detection signal DE is determined by whether the detection signal DE was output (detected) within the specified detection period (dt1~ts~dt2).

[0335] exist Figure 31In the flowchart shown, after the power supply circuit 60 is started by generating electricity using the movement of the permanent magnet 41 (ST1 "Yes"), it is determined whether the speed control pulse stop setting is in progress (ST41). Furthermore, whether the speed control pulse stop setting is in progress can be determined, for example, by whether the speed control pulse stop flag is on.

[0336] If the speed control pulse is not set to stop (ST41 "No"), the control circuit 44 determines whether the third counter is 10 (ST42). That is, the control circuit 44 determines whether the detection signal DE has failed 10 times consecutively. If the third counter is not 10 (ST42 "No"), the control circuit 44 determines whether the first counter is 8 (ST21). That is, the control circuit 44 determines whether the detection count of the detection signal DE is 8.

[0337] If the first counter is 8 (ST21 indicates "Yes"), proceed. Figure 20 The processing after ST24 is shown. On the other hand, if the first counter is not 8 (ST21 "No"), the control circuit 44 determines whether the detection signal DE is output (detected) during the specified detection period (dt1~ts~dt2) (ST43). If the detection signal DE is not output (detected) during the specified detection period (dt1~ts~dt2) (ST43 "No"), the count value of the third counter is incremented by 1 (ST44), and the count value of the first counter is incremented by 1 (ST23). On the other hand, if the detection signal DE is output (detected) during the specified detection period (dt1~ts~dt2) (ST43 "Yes"), the third counter is reset (ST45), and the period difference between the detection signal DE and the reference signal OS is calculated and stored (ST22).

[0338] Furthermore, when the speed control pulse is set to stop in ST41 (ST41 is "Yes"), the control circuit 44 determines whether the count value of the fourth counter is 20 (ST51). That is, the control circuit 44 determines whether the detection signal DE has been successfully detected 20 times consecutively. If the fourth counter is not 20 (ST51 is "No"), the control circuit 44 determines whether the detection signal DE is output (detected) during the specified detection period (dt1~ts~dt2) (ST52). If the detection signal DE is not output (detected) during the specified detection period (dt1~ts~dt2) (ST52 is "No"), the fourth counter is reset (ST53). If the detection signal DE is output (detected) during the specified detection period (dt1~ts~dt2) (ST52 is "Yes"), the count value of the fourth counter is incremented by 1 (ST54).

[0339] If the count value of the fourth counter in ST51 is 20 (ST51 is "Yes"), the fourth counter is reset (ST55) and the speed control pulse output setting is switched (ST56).

[0340] Furthermore, when the count of the third counter in ST42 is 10 (ST42 is set to "Yes"), the third counter is reset (ST61), and the speed control pulse stop setting is switched (ST62). Additionally, when the operation of the power supply circuit 60 resumes after it has stopped, since the charge stored in capacitor C is low, the power supply circuit 60 is in a state where it is easy to stop again. Therefore, when the operation of the power supply circuit 60 resumes after it has stopped, the number of consecutive successful detection signals DE required to start differential adjustment can be increased. For example, in... Figure 31 In the ST51, when the fourth counter counts to 60, that is, when the detection signal DE is successfully detected 60 times consecutively, the speed control pulse output setting can be switched.

[0341] In the above explanation Figures 29-31 In the example, by limiting differential rate adjustment, power consumption can be reduced, and it is easier to immediately switch to differential rate adjustment when the power spring 11 is wound up.

[0342] In addition, Figures 29-31 In the example, it could also have the following function: if no back electromotive force exceeding the threshold Vth is detected for a specified number of consecutive seconds, it notifies the user that the mechanical clock 1 is in a state where it is easily stopped. As a means of notification, for example, the position indicated by the hands could be used. This would prompt the user to wind the mainspring 11.

[0343] In addition, Figures 29-31 In the example, the threshold voltage can be lowered if no back electromotive force exceeding the threshold Vth is detected for a specified number of seconds. Specifically, for example, if the threshold Vth is 0.5V, and the detection signal DE fails to detect 10 times consecutively, the threshold voltage can be set to 0.25V. This way, although the power supply circuit 60 is prone to stopping, the accuracy of the differential rate can be maintained. Then, after lowering the threshold Vth, if a back electromotive force exceeding the lowered threshold is detected for a specified number of seconds, the original threshold Vth can be returned to. Alternatively, the threshold can be lowered in stages if no back electromotive force exceeding the threshold Vth is detected for a specified number of seconds.

[0344] [Details regarding the differential adjustment control: Differential adjustment control taking into account the rotation direction of the balance wheel]

[0345] Figure 32This is a timing diagram showing an example of the output time of the reference signal. Due to manufacturing deviations during the assembly of the mechanical clock 1, or the position adjustment of the balance wheel 31 performed by the support component 33 during factory inspection, the rotation angle of the balance wheel 31 may differ in the forward and reverse directions. When the rotation angle is different, the time for detecting the detection signal DE differs in the forward and reverse directions. Therefore, even if there is no overall rate deviation, it is possible to unnecessarily output a speed regulating pulse.

[0346] Therefore, in Figure 32 In the example shown, a structure is used to set the reference signal OS based on two steps (2 seconds). Figure 32 The upper section represents an example of the waveform of the back electromotive force when the detection signal DE is detected in the forward and reverse directions, respectively. Figure 32 The lower section represents an example of a timing diagram when the reference signal OS is set based on a 2-step (2-second) timeframe. For example... Figure 32 As shown in the lower section, the output interval of the odd-numbered reference signal OS from the left is set to tr1, and the output interval of the even-numbered reference signal OS from the left is set to tr2 (=tr1). This example can be implemented by two-system control in two-step units (two-second units) using control circuit 44. Moreover, if a differential rate anomaly is detected in either of the control systems, differential rate adjustment can be performed. Alternatively, to simplify the circuit structure, it can also be configured as a single-system control system that outputs only one of the intervals tr1 or tr2.

[0347] according to Figure 32 In the example shown, by setting the reference signal OS with two-step references (tr1 and tr2) and performing differential adjustments corresponding to the reference signal OS and the reference signal OS respectively, even if there is a difference in the forward and reverse rotation angles of the balance wheel 31, the circuit can perform high-precision differential adjustments relative to interference that is difficult to stop.

[0348] in addition, Figure 32 The middle section indicates the case where the reference signal OS is set based on 1 step (1 second), i.e., the above. Figure 17 The timing diagrams shown in the examples are as follows. Figure 32 In the example shown in the middle section, the peak position of the back electromotive force differs in the forward and reverse directions. Therefore, although there is no overall rate deviation, the output time of the even-numbered detection signal DE from the left is always off. In this case, a speed control pulse is unnecessarily output.

[0349] [Summarize]

[0350] In this embodiment, by employing a structure that sets the angular velocity of the balance wheel 31 to a low speed, wear on the various mechanisms transmitting power (e.g., the escapement gear 21 or the escapement fork 22) can be suppressed. As a result, the durability of the mechanical clock 1 is improved. Furthermore, by using the air resistance component 15, a structure is adopted that reduces the angular velocity of the balance wheel 31 during the forward and reverse motions. This delays the rotation period of the balance wheel 31 and allows power generation during the period when the balance wheel 31 is not subject to air resistance from the air resistance component 15, thereby ensuring sufficient power generation. Additionally, by performing differential rate adjustment during or after the period when the balance wheel 31 is subject to air resistance from the air resistance component 15, the accuracy of differential rate adjustment can be maintained. Moreover, by employing a structure that configures the permanent magnet 41 to obtain a back electromotive force suitable for half-wave rectification, power can be efficiently extracted using half-wave rectification.

[0351] [other]

[0352] The differential adjustment mechanism 40 obtains a detection signal based on the movement of the permanent magnet 41, which is magnetized by two poles. If there are components around the permanent magnet 41 that cause magnetic influence, the detection accuracy may be reduced. Therefore, the material of the components around the permanent magnet 41 can be a material with less magnetic influence.

[0353] For example, resin can be used as the material for the support member 33 and the hairspring clamp 34. Additionally, phosphor bronze can be used as the material for the fixing member 33a used to secure the support member 33 to the base plate 10. Furthermore, resin or aluminum can be used as the material for the balance wheel 31. Additionally, acrylic resin can be used as the air resistance component 15. However, the materials listed here are examples and are not limited to these.

[0354] Furthermore, as mentioned above, the hairspring 32 is made of resin to reduce Young's modulus, thereby reducing the magnetic influence on the permanent magnet 41 compared to a metal hairspring. Additionally, if the hairspring 32 is made of a magnetic metal, its shape and orientation may shift due to the magnetic influence of the permanent magnet 41. In this embodiment, by making the hairspring 32 of resin, its shape and orientation can be stabilized. Furthermore, a non-magnetic plate made of magnetic material can be additionally provided on the mechanical clock 1. Therefore, even when an external magnet approaches the mechanical clock 1, the disordered forward and reverse rotation of the permanent magnet 41 (balance wheel 31) can be suppressed, enabling stable differential adjustment.

[0355] In addition, in this embodiment, such as Figure 5The illustration shows an example where the first end 421a and the second end 422a of the soft magnetic core 42 are integrated via the first weld portion 423 and the second weld portion 424, but this is not a limitation. For example, the first weld portion 423 and the second weld portion 424 may not be present, and the first end 421a and the second end 422a may be magnetically separated via a gap. Furthermore, complete separation of magnetic coupling is not limited. For example, the first end 421a and the second end 422a may also be physically connected via a narrow portion that serves as a separation portion.

[0356] Furthermore, although the illustration is omitted, the mechanical watch 1 may also have an opening or transparent part on the dial or back cover that allows the balance wheel 31 to be visually confirmed from the outside.

[0357] Furthermore, this embodiment describes an example with the air resistance component 15, but it is not limited to this; the air resistance component 15 may not be present. Additionally, without the air resistance component 15, the balance wheel 31 may not have the action part 313.

[0358] As in this embodiment, if an air resistance component 15 is used to apply air resistance to the balance wheel 31, energy is consumed due to the air resistance, and the duration of the power spring 11 is correspondingly shortened. On the other hand, in this embodiment, by using a resin material with a low Young's modulus as the material for the hairspring 32, the movement of the balance wheel 31 is slowed down, resulting in a longer duration compared to conventional mechanical clocks with 6 to 8 oscillations. That is, by slowing down the movement of the balance wheel 31, the reduction in duration caused by air resistance can be compensated for. Therefore, a sufficient duration can be achieved as a mechanical clock.

Claims

1. A mechanical clock, characterized in that, include: A hairspring that undergoes elastic deformation to enable the balance wheel to rotate in both directions; The permanent magnet, which is polarized by two magnets, rotates in opposite directions along with the counter-rotation of the balance wheel. A coil that generates a back electromotive force through the forward and reverse rotational motion of the permanent magnet; A soft magnetic core includes a first end disposed along the outer periphery of the permanent magnet and a second end disposed along the outer periphery of the permanent magnet and disposed opposite to the first end across the permanent magnet, the soft magnetic core forming a magnetic circuit together with the coil; and The control circuit is driven by the power generated by the back electromotive force and performs differential adjustment based on the back electromotive force and the reference vibration frequency of the reference signal source. The permanent magnet is configured such that, when the hairspring is at its natural length, the magnetization direction is toward either the first end or the second end.

2. The mechanical clock as described in claim 1, characterized in that: The permanent magnet is configured such that, when the hairspring is at its natural length, the magnetization direction is the same as the relative direction of the first end and the second end.

3. The mechanical clock as described in claim 1, characterized in that: The soft magnetic core includes: a first separating portion that separates the magnetic coupling between the first end and the second end; and a second separating portion that separates the magnetic coupling between the first end and the second end, and is disposed opposite to the first separating portion across the permanent magnet. The permanent magnet is configured such that, when the hairspring is at its natural length, the magnetization direction is orthogonal to the relative directions of the first separation section and the second separation section.

4. The mechanical clock as described in claim 1, characterized in that: The soft magnetic core includes: a first separating portion that separates the magnetic coupling between the first end and the second end; and a second separating portion that separates the magnetic coupling between the first end and the second end, and is disposed opposite to the first separating portion across the permanent magnet. The permanent magnet includes an N pole portion and an S pole portion, and is configured such that, when the hairspring is at its natural length, the boundary between the N pole portion and the S pole portion overlaps with the strip-shaped region connecting the first separation portion and the second separation portion.

5. The mechanical clock as described in claim 1, characterized in that: It has a power source that drives the balance wheel. With the hairspring at its natural length, the balance wheel is in a power supply position where it is supplied with power from the power source.

6. The mechanical clock as described in claim 5, characterized in that: The permanent magnet is configured such that the back electromotive force detected during a 180° rotation from the power supply position in either the forward or reverse direction has the same polarity.

7. The mechanical clock as described in claim 1, characterized in that, have: A rotation detection circuit detects the detection signal based on the back electromotive force; and The speed-regulating pulse output circuit outputs speed-regulating pulses to control the motion of the balance wheel. The control circuit controls the speed regulation pulse output circuit based on the detection time of the detection signal and the output time of the reference signal based on the reference vibration frequency.

8. The mechanical clock as described in claim 7, characterized in that: The speed regulation pulse output circuit If the detection time of the detection signal is earlier than the output time of the reference signal, the speed regulating pulse is output to either the first terminal or the second terminal of the coil. If the detection time of the detection signal is later than the output time of the reference signal, the speed adjustment pulse is output to the other of the first terminal and the second terminal.

9. The mechanical clock as described in claim 7, characterized in that: The speed-regulating pulse output circuit is configured to output multiple speed-regulating pulses that are different from each other during the output period.

10. The mechanical clock as described in claim 7, characterized in that: The speed-regulating pulse output circuit is configured to output multiple speed-regulating pulses with different duty cycles.

11. The mechanical clock as described in claim 9, characterized in that: The speed control pulse output circuit outputs a speed control pulse corresponding to the deviation of the detection time of the detection signal from the output time of the reference signal.

12. The mechanical clock as described in claim 11, characterized in that: It has a storage unit that stores the deviation of the detection time of the detection signal relative to the output time of the reference signal. The speed control pulse output circuit outputs a speed control pulse corresponding to the deviation amount stored in the storage unit.

13. The mechanical clock as described in claim 1, characterized in that: It has a rectifier circuit to rectify the current generated in the coil corresponding to the back electromotive force. The rectifier circuit contains one diode.

14. The mechanical clock as described in claim 1, characterized in that: At least one pair of opposing notches are formed at the first end and the second end to reduce the holding torque of the permanent magnet.

15. The mechanical clock as described in any one of claims 1 to 14, characterized in that: It has a bearing structure that supports the end of the rotation axis of the balance wheel on the side closest to the permanent magnet. The bearing structure includes an elastically deformable portion that elastically deforms in response to the displacement of the rotating shaft and is made of a non-magnetic material.

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