Coil spring, torque generator, clockwork and clock.

专利摘要:
A coil spring, a torque generator, a clockwork and a clock are provided, which are set up to generate a desired torque, with self-contact or contact with surrounding components being suppressed. A constant force spring 100 is a coil spring for a watch which is wound around a first axis of rotation O1 to generate torque and which has an outer end portion 101 attached to a bracket and an inner end portion 102 attached to one lower stage cylinder is attached for constant force. In a pre-wind state, in which the outer end portion 101 is attached to the carrier, the inner end portion 102 is attached to the lower step cylinder for constant force, and no torque is generated, a distance between adjacent turns of the spring changes in one radial direction orthogonal to the first axis of rotation O1, corresponding to a position in a circumferential direction about the first axis of rotation O1.
公开号:CH715176A2
申请号:CH00861/19
申请日:2019-06-28
公开日:2020-01-15
发明作者:Kawauchiya Takuma；Yuichi Mori；Fujieda Hisashi；Ito Kengo
申请人:Seiko Instr Inc；
IPC主号:

专利说明:

description
BACKGROUND OF THE INVENTION
1. Technical Field of the Invention The present invention relates to a coil spring, a torque generator, a clockwork and a clock.
2. State of the art Generally, in a mechanical watch, a torque (force) transmitted from a barrel to an escapement, corresponding to the unwinding of a main spring, fluctuates an oscillation angle of a balance spring with a spiral spring in response to the fluctuation of the torque and Change of rhythm of the watch (a degree of delay or advance of the watch). It is known here to provide a constant force mechanism in a power transmission path from the barrel to the escapement to suppress the fluctuation of the torque transmitted to the escapement.
In the constant torque mechanism, a constant force spring is provided which applies a rotating force to an escapement side gear train. A configuration is adopted in which a constant force spring is in a state to generate a constant force by winding or the like, and a loss of force lost by transmitting the force to the escapement side gear is cycled by the force filled up, which is transmitted from the barrel. Different types of the constant torque mechanism have been proposed, and, for example, in a case with a focus on cyclical control, the constant torque mechanisms are mainly classified into three types, including a cam controlled type, a train type and a satellite type.
The cam-controlled type of constant torque mechanism has, for example, a follower or an armature fork which is in engagement with a cam which is connected to the escapement side gear train and which swings in accordance with a rotation of the cam and upon cyclical engagement and disengagement - / Separation gripper, which is arranged on the idler or the anchor fork, with or by an escapement wheel which is connected to a power source side gear train, an engagement and separation cycle is controlled. As a result, it is possible to wind the constant force spring between the power source side gear train and the escapement side gear train.
The constant torque gear mechanism type connects the power source side gear train and the escapement side gear train with a differential mechanism, and when moving in and out, the engaging / disengaging gripper engages with and disengages from a stop wheel , it is possible to control a phase difference cyclically.
For example, as described in CH-A-707 938 (patent reference 1), a satellite type has a constant torque mechanism, a satellite mechanism using a stop wheel as a satellite wheel, and wherein it is possible to cyclically control the phase shift between the power source side gear train and the escapement side gear train by the satellite mechanism. The satellite wheel rotates during rotation so that the engagement / separation gripper follows, which is provided on the driven wheel which is connected to the escapement side gear train.
[0007] However, in a case where a coil spring is used as a constant force spring, there is a possibility that a deformation of the coil spring associated with winding will cause a fluctuation in the torque generated. For example, in a case where the coil spring is wound and fixed to generate the torque, in a portion opposite to an outer end portion of the coil spring through a center of rotation, during the time of winding and fixing, the distance between them narrows adjacent springs and there is a possibility that the springs come into contact with each other. In addition, for example, in a case where the coil spring is wound and expanded to generate force, in a portion opposite an outer end portion of the coil spring above the center of rotation while the winding and expanding is currently taking place, the distance between the adjacent springs and the outer diameter of the coil spring widens, and there is a possibility that the coil spring comes into contact with surrounding components. When there is contact in the coil spring, there is a state in which the coil spring cannot generate the desired torque due to a frictional force in the contact portion.
SUMMARY OF THE INVENTION It is an object of the present invention to provide a coil spring, a torque generator, a clockwork and a watch which are capable of generating a desired torque by suppressing self-contact or contact with surrounding components.
According to the present application, a coil spring for a watch mechanism is provided, which is wound around an axis to generate a torque, comprising: an outer end portion, which is attached to a first component, and an inner end portion, which to is attached to a second component, wherein in a pre-wind state in which the outer end portion is attached to the first component, the inner end portion is attached to the second component and no torque is generated, a distance between the adjacent springs in a radial direction orthogonal to the axis changes according to a position in a circumferential direction about the axis.
According to the application, it is possible by suitably adjusting and changing the distance between the adjacent springs, according to the position in the circumferential direction, to adjust the shape of the coil spring in a state in which it is wound in any way. Accordingly, it is possible to suppress that the distance between the adjacent springs is narrowed and the springs come into contact with each other through the deformation accompanying the winding of the coil spring, or that the distance between the springs is widened and the outermost circumferential area of the Coil spring comes into contact with surrounding components. Accordingly, it is possible to suppress that the torque generated by the coil spring is reduced by the frictional force associated with the contact of the coil spring in a wound state. Accordingly, the coil spring can generate a desired torque by suppressing self-contact or contact with surrounding components.
In the coil spring described above, it is desirable that the coil spring be shaped to generate the winding and fastening torque from the pre-wind state and in the pre-wind state when viewed from an axial direction of the axis, the distance on a first half line extending from the axis to the outer end portion is narrower than the distance on a second half line extending from the axis to one side opposite the first half line.
According to the present application, deformation takes place when the coil spring is wound up and fastened from the pre-wind state, so that the distance between the springs narrows at one section, opposite the outer end section via the axis. Thus, by setting the distance between the springs in the pre-winding state on the first half line extending from the axis to the outer end portion, is narrower than the distance between the springs on the second half line extending from the axis to the side extends opposite to the first half line, even if the distance at the portion opposite to the outer end portion across the axis is narrowed between the springs, it is possible to suppress the contact between the springs. Accordingly, it is possible to generate a desired torque in the coil spring, which generates a torque when wound and fastened from the pre-wind state.
In the coil spring described above, it is desirable that the coil spring be configured to generate the torque when being wound and expanded from the pre-wind state and in the pre-wind state when viewed in the axial direction of the axis Distance on a first half line extending from the axis to the outer end portion is wider than the distance on a second half line extending from the axis to one side opposite to the first half line.
According to the present application, the deformation takes place when the coil spring is wound up and expanded from the pre-wind state, so that the distance between the springs widens at a section opposite the outer end section above the axis. Accordingly, when setting the distance between the springs on the first half-straight line in the pre-upwind condition, which extends from the axis to the outer end portion, which is wider than the distance between the springs on the second half-straight line which extends from the Axis extends to the side, opposite to the first half line, even if the distance between the springs on the section opposite to the outer end section over the axis, to suppress that the outermost peripheral section of the coil spring is larger outward in the radial direction extends over the axis as the environment at the portion opposite the outer end portion. Accordingly, it is possible to suppress the outermost peripheral portion of the coil spring from coming into contact with surrounding components. As a result, it becomes possible to generate a desired torque in the coil spring, the torque being generated from the pre-winding state when being wound and expanded.
In the coil spring described above, it is desirable that at least a part of the coil spring extends along an Archimedean curve in a state in which no load is applied to the coil spring.
According to the present application, it is possible to manufacture the shape of the coil spring in a state to be wound in a spiral curve approximating the Archimedean curve. Consequently, in the coil spring in the state to be wound, it is possible to keep the distance between the adjacent springs substantially constant regardless of the position in the circumferential direction and in the radial direction, and it is possible to keep the contact suppress between the adjacent springs. As a result, the coil spring can generate a desired torque.
In the coil spring described above, it is desirable that at least a portion of the coil spring extends along the Archimedean curve in a state that the load is not applied to the coil spring and the center of the Archimedean curve is provided on one side, opposite to the inner end portion over the axis.
According to the present application, it is possible to manufacture the shape of the coil spring in a state to be wound in a spiral curve approximating the Archimedean curve. Here, when the coil spring is wound and fixed, since the diameter of the innermost peripheral portion of the coil spring is reduced when the coil spring is wound and fixed, the center of the spiral curve is displaced to approach the inner end portion. Thus, by providing the center of the Archimedean curve in a state where the load is not applied to the coil spring on the side opposite to the inner end portion about the axis, the center of the spiral curve approaches the axis in a state in FIG which the coil spring is wound and attached. Accordingly, it is possible to cause the entire innermost peripheral portion of the coil spring to approach the axis equally and to further widen a distance between the outermost peripheral portion and the innermost peripheral portion of the coil spring in the entire circumferential direction. As a result, it is possible to increase the distance between the adjacent springs and suppress the contact between the springs. As a result, the coil spring can generate a stable desired torque.
[0019] According to the present application, a torque generator is provided, comprising: the spiral spring described above; the first component to which the outer end portion and the inner end portion of the coil spring are attached; and a second component to which the other outer end portion and the inner end portion of the coil spring are attached.
According to the present application, since the spiral spring that generates a desired torque is provided, it is possible to suppress the insufficiency of the torque applied between the first component and the second component.
In the torque generator described above, which is a constant torque mechanism, it is desirable that there are further provided: an input rotating body comprising the first component rotated by force from a power source and filling the coil spring with force, an output rotating body which comprises the second component, rotates by the force from the coil spring and transmits the force of the coil spring to the escapement; and a cycle control mechanism that intermittently rotates the input rotating body with respect to the output rotating body based on the rotation of the output rotating body.
According to the present application, since the torque applied between the input rotating body and the output rotating body is stabilized, it is possible to suppress the fluctuation of the torque to be transmitted from the output rotating body to the escapement.
In the torque generator described above, which is a reset mechanism that reciprocates a pointer between a home position and an end position, it is desirable that a rotating portion that includes the first component and that rotates in synchronization with the pointer; and a support section is provided which includes the second component and rotatably supports the rotating section.
According to the present application, it is possible to suppress that the torque applied to the rotating component is insufficient and the repetitive movement of the pointer is disturbed.
In the torque generator described above, which is a calendar mechanism that switches a date mark, indicated on a date window of a dial, it is desirable that a date transmission is further provided, which comprises the first component and rotates in synchronization with rotation of an hour wheel ; and a date finger unit that includes the second component and a date finger that is engaged with and detached from a tooth portion of a date indicator on which the date mark is displayed and is provided to be rotatable coaxially with the date gear with respect to the date gear.
According to the present application, it is possible to suppress the insufficiency of a torque that is transmitted to the date indicator, due to the insufficiency of the torque that is applied to the date finger unit. Consequently, the calendar mechanism in which a reliable date advance operation is possible can be used.
[0027] According to the present application, a clockwork is provided, comprising: the torque generator described above.
[0028] According to the present application, a watch is provided which comprises the watch mechanism described above.
According to the present application, it is possible to provide a clockwork and a clock with stable operation and high accuracy.
According to the present application, it is possible to provide a coil spring, a torque generator, a clockwork and a clock, which are set up to generate a desired torque by suppressing self-contact or contact with surrounding components.
BRIEF DESCRIPTION OF THE FIGURES
[0031]Fig. 1 12 is an external view of a watch according to a first embodiment. Fig. 2 Fig. 12 is a block diagram of a work of the first embodiment. Fig. 3 Fig. 12 is a perspective view when the work of the first embodiment is seen from above. Fig. 4 Fig. 12 is a sectional view illustrating a portion of the work of the first embodiment. Fig. 5 Fig. 12 is a top view when a portion of the work according to the first embodiment is seen from above Fig. 6 12 is a plan view illustrating a constant force spring, a fixing piece and a fixing ring of the first embodiment. Fig. 7 Fig. 12 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the first embodiment. Fig. 8 Fig. 12 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the first embodiment. Fig. 9 12 is a plan view illustrating a constant force spring, a fixing piece and a fixing ring of a second embodiment. Fig. 10 Fig. 12 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the second embodiment. Fig. 11 Fig. 12 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the second embodiment. Fig. 12 12 is a plan view illustrating a constant force spring, a fixing piece and a fixing ring of a third embodiment. Fig. 13 Fig. 12 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the third embodiment. Fig. 14 12 is a plan view illustrating a constant force spring, a fixing piece and a fixing ring of a fourth embodiment. Fig. 15 Fig. 12 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the fourth embodiment. Fig. 16 Fig. 12 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the fourth embodiment. Fig. 17 Fig. 12 is an external view of a watch according to a fifth embodiment. Fig. 18 is a top view of a reset mechanism. Fig. 19 is a supervision of the reset mechanism. Fig. 20 Fig. 12 is an external view of a watch according to a sixth embodiment. Fig. 21 is a top view of a calendar mechanism seen from below. Fig. 22 is a top view of a date indicator drive wheel seen from below. Fig. 23 is a top view of a date indicator drive wheel seen from above. Fig. 24 FIG. 22 is a sectional view taken along line XXIV-XXIV of FIG. 22. Fig. 25 Fig. 4 is an explanatory view of the operation of the calendar mechanism and is a plan view of a part of the calendar mechanism seen from below. Fig. 26 Fig. 4 is an explanatory view of the operation of the calendar mechanism and is a plan view of a part of the calendar mechanism seen from below.
Fig. 27 is an explanatory view of the operation of the calendar mechanism and is a plan view of a part of the calendar mechanism seen from below.
DESCRIPTION OF THE EMBODIMENTS Hereinafter, the embodiments of the present invention will be described with reference to the drawings. In addition, the same reference numerals are assigned to configurations in the following description which have the same or similar functions. In the present embodiment, a mechanical watch is described as an example of a watch.
First Embodiment (Basic Configuration of a Watch) In general, a mechanical body comprising a driving part of a watch is referred to as a "movement". A state in which a clock face and a pointer are arranged on the movement, inserted into a watch case and completed to a finished product is referred to as the “completion” of the watch.
Of the two sides of a main plate that configures a plate of the watch, one side on which a glass of a watch case is provided (this is a side on which the dial is arranged) is called the "back" of the movement , Furthermore, from both sides, one side, on which a case bottom cover of the watch is provided (this is a side opposite the side on which the dial is arranged), is referred to as the “front” of the movement.
In the present embodiment, the description is also made such that a direction from the dial to the case bottom cover is defined as an upward direction and a direction opposite to it is defined as a downward direction. In addition, in which each axis of rotation is regarded as a center, a clockwise direction when viewed from above is referred to as a clockwise direction and a counterclockwise direction when viewed from above is referred to as a counterclockwise direction.
1 shows an exterior view of the clock according to the first embodiment.
As shown in Fig. 1, the completion of the watch 1 of the present embodiment in the watch case configured with a case bottom cover (not shown) and a glass 2 includes a movement 10 (clockwork), a dial 3, which has a scale which displays at least information about the time, and a pointer 4 which has an hour hand 5, a minute hand 6 and a second hand 7.
Fig. 2 is a block diagram of the work of the first embodiment.
As shown in Fig. 2, the movement 10 comprises a barrel 11, which is a power source, a power source side gear train 12, which is connected to the barrel 11, an escapement 14, of which a speed is regulated by a speed controller 13 an escapement side gear train 15 connected to the escapement 14, and a constant torque mechanism 30 interposed between the power source side gear train 12 and the escapement side gear train 15.
[0040] Furthermore, the constant torque mechanism 30 is generally configured as part of a front side gear train that includes a second wheel & pinion or a third wheel & pinion, a fourth wheel & pinion, and the like. The power source side gear train 12 in the present embodiment relates to a gear train further positioned on the side of the barrel 11, which is a power source, as a constant force mechanism 30 when viewed from the constant torque mechanism 30. Similarly, the escapement side gear train 15 in the present embodiment refers to a gear train that is further positioned on the escapement 14 side as a constant torque mechanism 30 when viewed from the constant torque mechanism 30.
A main spring 16 is accommodated in the interior of the barrel 11. The main spring 16 is wound by rotation of a winding circle (not shown) which is connected to a crown 17 shown in Fig. 1. The barrel 11 rotates by the force (torque) accompanying the unwinding of the main spring 16 and transmits the force to the constant torque mechanism 30 via the power source side gear train 12. Furthermore, in the present embodiment, although as an example, a case In which the power is transmitted from the barrel 11 to the constant torque mechanism 30 via the power source side gear train 12, the present application is not limited thereby. For example, the force from the barrel 11 can be transmitted directly to the constant torque mechanism 30 without passing through the power source side gear train 12.
For example, the power source side gear train 12 includes a first transmission wheel 18. The first transmission wheel 18 is e.g. a third wheel & pinion. The first transmission wheel 18 is rotatably held between a main plate 23 (see FIG. 4) and a gear train bridge (not shown). The first transmission wheel 18 rotates based on the rotation of the barrel 11. Furthermore, when the first transmission wheel 18 rotates, a minute tube (not shown) rotates based on the rotation. The minute hand 6, shown in Fig. 1, is attached to the minute tube, and the minute hand 6 indicates "the minute" by rotating the minute tube. The minute hand 6 rotates at a rotational speed which is regulated by the escapement 14 and the speed controller 13, so that one rotation takes place in one hour.
Further, a minute wheel (not shown) rotates when the first transmission wheel 18 rotates based on the rotation, and further an hour wheel (not shown) rotates based on the rotation of the minute wheel. The hour hand 5, shown in Fig. 1, is attached to the hour wheel and indicates "the hour" by the rotation of the hour wheel. The hour hand 5 rotates at a rotational speed which is regulated by the escapement 14 and the speed controller 13, so that a rotation takes place in 12 hours.
The escapement side train 15 mainly comprises a second transmission wheel 19. The second transmission wheel 19 is, for example, a fourth wheel & pinion. The second transmission wheel 19 is rotatably held between the main plate 23 and the train bridge, and rotates in the constant torque mechanism 30 based on the rotation of a lower constant force step wheel 60 (see FIG. 3), which will be described later In a case where the second transmission gear 19 is the fourth gear & pinion, the second hand 7 shown in Fig. 1 is disposed on the second transmission gear 19 and the second hand 7 indicates "the second" based on the Rotation of the second transmission wheel 19. The second hand 7 rotates at a rotational speed which is regulated by the escapement 14 and the speed controller 13, so that one rotation takes place in one hour.
The escapement 14 mainly comprises an escapement wheel & pinion and a pallet fork (neither of which is shown).
The escapement wheel & pinion is rotatably held between the main plate 23 and the gear train bridge, and meshes with, for example, the second transmission wheel 19. Accordingly, the force from the constant force spring is 100 (see FIG. 3), which will be described later in the constant torque mechanism 30, transmitted to the escapement wheel & pinion via the escapement side gear train 15. It follows that the escapement wheel & pinion rotates 100 by the force from the constant force spring.
The pallet fork is rotatably (swingably) held between the main plate 23 and the pallet bridge (not shown) and has a pair of claw stones (not shown). The pair of claw stones are alternately engaged and disengaged from the escapement gear & pinion teeth of the escapement gear & pinion by the speed controller 13 in a predetermined cycle. As a result, the jamming wheel & pinion can be jammed in a predetermined cycle.
The speed controller 13 mainly comprises a hair spring balance (not shown).
The balance spring with a hair spring comprises a balance wheel, a balance wheel and a hair spring and is rotatably held between the main plate 23 and a balance bridge (not shown). The hairspring balance rotates in opposite directions (forward and backward rotation) in a constant cycle, with the hairspring used as a power source.
(Configuration of a constant torque mechanism) The constant torque mechanism 30 is a mechanism that suppresses the fluctuation (torque fluctuation) of the force transmitted to the escapement 14.
Fig. 3 is a perspective view of a part of the work of the first embodiment viewed from above.
As shown in Fig. 3, the constant torque mechanism 30 comprises: a stationary gear 31, a first, upward and downward rotating axis O1 of which is a central axis, an upper step wheel for constant force 40 (input rotating body), which rotates about the first axis of rotation O1; a lower constant force stage wheel 60 (output rotating body) which is arranged coaxially with the upper constant force stage wheel 40 and can rotate relative to the upper constant force stage wheel 40 about the first axis of rotation O1; an engagement Z separating lever unit 80 which connects the upper constant force gear 40 and the lower constant force gear 60; a constant force spring 100 for transferring the stored force to the upper constant force gear 40 and to the lower constant force gear 60; and a torque adjusting mechanism 110 that adjusts the torque of the constant force spring 100. The first rotation axis O1 is arranged in a position which is in a plane direction of the main plate 23 (see FIG. 4) with respect to the rotation axes of the first transmission wheel 18 and the second transmission wheel 19 (see FIG. 2), which are described above , shifts.
Fig. 4 is a sectional view illustrating part of the work of the first embodiment.
As shown in Fig. 4, the stationary gear 31 is arranged between the main plate 23 and a constant force unit bridge 24. The constant force unit bridge 24 is arranged above the main plate 23. The stationary transmission 31 comprises a tubular body 32 which is arranged coaxially with the first axis of rotation O1 and a transmission main body 33 which is formed integrally with the tubular body 32.
The tubular body 32 is fixed to a lower surface of the constant force unit bridge 24 by means of a stationary gear pin 34 which projects downward from the constant force unit bridge 24. A central one
Hole 35 and a window portion 36 are formed in the tubular body 32. The central hole 35 extends upward and downward with a constant inner diameter with respect to the first axis of rotation O1 as a center and passes through the tubular body 32 from above and below. The window portion 36 is adjacent to the central hole 35 in a direction in which the first rotation axis O1 and the rotation axis of the first transmission wheel 18 are arranged, as seen in an up-down direction (see FIG. 3). The window portion 36 passes through the tubular body 32 in an up-down direction and is continuous with the central hole 35. Accordingly, the hole that penetrates the stationary gear 31 from above and below is an elongated hole as seen from an up-down direction. Direction.
The transmission main body 33 is formed coaxially with the first axis of rotation O1 and protrudes outward in the radial direction from a lower end portion of the tubular body 32. On the outer circumferential surface of the transmission main body 33, stationary teeth 33a are formed over the entire circumference. In other words, the stationary gear 31 is an external tooth type gear.
The upper step wheel for constant force 40 is rotatably held between the main plate 23 and the constant force unit bridge 24. The upper step wheel for constant force 40 comprises a rotating shaft 41 which rotates about the first axis of rotation O1, a planet wheel 43 which rotates about the first axis of rotation O1 and a carrier 47 (first component) which rotatably holds the planet gear 43.
The rotary shaft 41 extends along the first axis of rotation O1. The rotary shaft 41 is rotatably supported by the main plate 23 and the constant force unit bridge 24 via perforated stones 25A and 25B. The perforated stones 25A and 25B are made of artificial gemstones, such as ruby. Furthermore, the perforated stones 25A and 25B are not limited to a case in which the perforated stones are made of artificial gemstones and can also be formed, for example, from other brittle materials or metallic materials, such as ferrous alloys. An upper step gear for constant force 41 a is formed on an upper portion of the rotating shaft 41. The upper step gear for constant force 41a meshes with the first transmission wheel 18. Accordingly, the force is transmitted from the barrel 11 (see FIG. 2) to the rotary shaft 41 via the power source side gear train 12. The force of a torque Tb is transmitted from the barrel 11 to the rotary shaft 41. Here, the torque Tb relates to a torque Tb of the barrel 11. The rotating shaft 41 rotates in a clockwise direction by the force from the barrel 11.
The carrier 47 is held firmly by the rotary shaft 41. The torque Tb in the clockwise direction from the rotary shaft 41 is transmitted to the carrier 47. Consequently, the carrier 47 rotates together with the rotary shaft 41 in a clockwise direction about the first axis of rotation O1 by the force from the barrel 11. The carrier 47 comprises a lower seat 48 which is integrally connected to the rotary shaft 41 and an upper seat 54, which is arranged above the lower seat 48 and fixed to the lower seat 48.
The lower seat 48 is arranged below the stationary gear 31. The lower seat 48 includes a planet gear support portion 49 that supports the planet gear 43, a spring support portion 50 that supports the constant force spring 100, and a connecting portion 51 that connects the planet gear support portion 49 and the spring support portion 50 to each other.
Fig. 5 shows a plan view when a part of the work of the first embodiment is viewed from above. Furthermore, part of the stationary gear 31 is broken and shown in the drawing.
As shown in Figs. 3 and 5, the planet gear support portion 49 extends in an arcuate shape along the circumferential direction around the first rotation axis O1 when viewed in an up-down direction. The planet gear support portion 49 is formed so that an intermediate part is one step lower than both of the end portions when viewed from the up-down direction.
As shown in Fig. 4, a spring support portion 50 is provided on the side which is opposite to the planet gear support portion 49 via the first rotation axis O1. A pin insertion hole 50 a through which a constant force spring pin 103, which will be described later, is inserted is formed on the spring support portion 50. A central hole through which the rotary shaft 41 is inserted is formed on the connecting portion 51. The connecting portion 51 is fixed to a lower portion as the upper step pinion for constant force 41 a in the rotary shaft 41. As a result, the lower seat 48 rotates integrally with the rotation shaft 41. A carrier window portion 52 is formed on the side of the first rotation axis O1 with respect to the planet gear support portion 49. The carrier window portion 52 passes through the lower seat 48 from above and below. The carrier window portion 52 avoids contact between the lower seat 48 and an engaging claw 86, which will be described later.
As shown in Fig. 3, the upper seat 54 is disposed above the planet gear support portion 49 of the lower seat 48 and above the gear main body 33 of the stationary gear 31. The upper seat 54 extends in an arcuate shape along the circumferential direction around the first Rotation axis O1, viewed in an up-down direction. The upper seat 54 is stacked in a state in which an interval of the planet gear support portion 49 of the lower seat 48 has a plurality of collars 55. Both end portions of the upper seat 54 are fixed to both end portions of the planet gear support portion 49 by means of a plurality of bolts 56 which are inserted through the plurality of the collars 55.
As shown in Fig. 4, the planet gear 43 is rotatably supported by the carrier 47. Specifically, the planet gear 43 is rotatably supported by the planet gear support portion 49 of the lower seat 48 and the upper seat 54 via perforated stones 59A and 59B, so that it is rotatable about a second axis of rotation 02. The second axis of rotation 02 is arranged at a position which is displaced in a plane direction of the main plate 23 with respect to the first axis of rotation O1 and in a position which is fixed to the carrier 47. The planet gear 43 is disposed between the intermediate portion of the planet support portion 49 of the lower seat 48 when viewed in the up-down direction and the intermediate portion of the upper seat 54 when viewed in the up-down direction (see FIG. 3). The planet gear 43 includes a planet pinion 44 and a planetary gear 45.
The planet pinion 44 meshes with the fixed teeth 33 a of the stationary gear 31. Since the stationary gear 31 is of the external tooth type, meshing with the planet pinion 44 and the stationary gear 31 rotates in accordance with the rotation of the carrier 47 in the clockwise direction, the planet gear 43 in the clockwise direction about the first axis of rotation O1, while it rotates in the clockwise direction about the second axis of rotation 02.
The planetary gear 45 is formed below the planet pinion 44 and can rotate (can rotate and rotate) without being in contact with the stationary gear 31. The planetary gear 45 has a plurality of stop teeth 45 a, which can be brought into engagement with and released from the engagement claw block 86. The number of stop teeth 45a is eight. However, the present invention is not limited to this, and the number of teeth can be changed accordingly.
As shown in Fig. 5, the stop teeth 45a extend in the clockwise direction around the second axis of rotation O2 so that they are separated from the second axis of rotation 02 when viewed in the downward-upward direction. The tooth tip of the stop teeth 45a is configured to be a functional surface which is in engagement with and detached from the engagement claw block 86. In the following, a rotation path M, which is drawn from the tooth tip of the stop teeth 45a in accordance with the rotation of the planet gear 43, is referred to as a rotation path M of the planetary gear 45.
As shown in Fig. 4, the lower constant force stage gear 60 is rotatably supported by the rotating shaft 41 of the upper constant force stage gear 40 between the main plate 23 and the constant force unit bridge 24. The lower constant force stage gear 60 is arranged below the carrier 47 for the upper step wheel for constant force 40 and between the carrier 47 and the main plate 23. The lower constant force step gear 60 includes a lower step force cylinder 61 (second component) derived from the rotary shaft 41 and a lower constant force step 62 integrally connected to the lower constant force cylinder 61. Furthermore, the lower step wheel for constant force 60 is rotated in a clockwise direction about the first axis of rotation O1 by the force transmitted by the spring for constant force 100.
The rotary shaft 41 is inserted from above into the lower step cylinder for constant force 61 and protrudes downward over the lower step cylinder for constant force 61. Annular perforated bricks 69A and 69B are pressed into the upper end portion and the lower end portion in the lower step cylinder for constant force 61. The rotary shaft 41 is inserted into the perforated blocks 69A and 69B.
The lower constant force gear 62 is integrally connected to the lower end portion of the lower constant force cylinder 61. On the outer peripheral surface of the lower constant force gear 62, a lower constant force tooth 62a is formed over the entire circumference, with which the second transmission wheel 19 meshes. Thus, the lower constant force step gear 60 can transmit the force from the constant force spring 100 to the second transmission gear 19 connected to the escapement 14, which is the escapement side gear train 15.
Furthermore, although in the present embodiment, as an example, a case is described in which the constant force spring 100 transmits the force to the escapement 14 via the escapement side gear train 15, the present invention is not limited to this. For example, the escapement side gear train 15 cannot be provided and the force from the constant force spring 100 can be transmitted directly to the escapement 14.
The engagement Z-separating lever unit 80 comprises an engagement claw block 86 which is in engagement with and released from the stop tooth 45a of the planetary gear 45 and rotatably holds the engagement claw block 86 about the axis of rotation O1. The engaging / separating lever unit 80 comprises a lever bushing 81, which is arranged not to be able to rotate relative to the lower step cylinder for constant force 61, and an engaging-Z separating lever 84, which is arranged to rotate clockwise in accordance with the Rotation of the lever sleeve 81 to be rotatable in the clockwise direction.
The lever sleeve 81 is formed in a cylindrical shape, coaxial with the first axis of rotation O1. The lever sleeve 81 is extrapolated to the lower end portion of the lower step force cylinder 61 of the lower step force wheel 60 and integrally connected to the lower step force cylinder 61. Accordingly, the lever sleeve 81 rotates in the clockwise direction around the first rotation axis O1 in synchronization with the rotation of the lower step wheel for constant force 60.
The engaging / disconnecting lever 84 includes a lever main body 85 and an engaging claw block 86 carried by the lever main body 85.
The lever main body 85 is arranged below the planetary gear 45 of the planet gear 43. The lever main body 85 is held by the lever bush 81. An engaging claw block 86 is fixed to an end portion of the lever main body 85.
The engagement claw stone 86 is made of artificial gemstones, e.g. Ruby. In addition, the engaging claw stones 86 are not limited to a case in which the perforated stones described above are formed as artificial gemstones and can be made, for example, from other brittle materials or metallic materials such as ferrous alloys. Furthermore, the engaging claw block 86 may be integrally made with the lever main body 85 instead of being separate from the lever main body 85. The engaging claw block 86 is held by the lever main body 85 in a state that it projects on the side of the planetary gear 45 (upper side) above the lever main body 85. The engaging claw block 86 is arranged on the inside of the carrier window portion 52 of the carrier 47 of the upper step wheel for constant force 40.
As shown in Fig. 5, between the projecting parts of the engaging claw block 86, the tooth tip 45a of the planetary gear 45 can be engaged with and detached from the side surface which is directed against the side, opposite to the first axis of rotation O1. The engagement claw block 86 is in engagement with the planetary gear 45 in the rotational curve M of the planetary gear 45 and regulates the rotation of the planet gear 43. Furthermore, the engagement claw block 86 is displaced in the clockwise direction about the axis of rotation O1 with respect to the planet gear 43 and withdrawn from it Rotation curve M of the planetary gear 45, separated from the stop teeth 45a and the engagement with the planetary gear 45 is released.
As shown in Fig. 3, the constant force spring 100 is, for example, a coil spring made of a metal or alloy, e.g. Iron or nickel, or a non-metal such as silicon. The constant force spring 100 is below the engagement Z separating lever unit 80 and between the engaging Z separating lever unit 80 and the lower constant force gear 62.
Fig. 6 is a plan view showing a constant force spring, a fixing piece and a fixing ring of the first embodiment. 6 shows a state of the torque generation of the constant force spring 100, which will be described later. Furthermore, the spring for constant force 100, a fixing piece 105 and a fixing ring 104 are dashed in FIG. 6 (also in the following view) in order to make it easier to see the drawing.
As shown in Fig. 6, the constant force spring 100 includes an outer end portion 101 which is a peripheral portion and an inner end portion 102 which is the other peripheral portion. As shown in FIG. 4, the outer end portion 101 of the constant force spring 100 is fixed to the lower seat 48 of the carrier 47 of the upper constant force gear 40 via the fixing piece 105 and the constant force spring pin 103. The inner end portion 102 of the constant force spring 100 is fixed to the lower constant force step wheel 60 via the fixing ring 104 and the torque adjusting mechanism 110. Consequently, the constant force spring 100 can transmit the stored force to the upper step wheel for constant force 40 or to the lower step wheel for constant force 60. The detailed shape of the constant force spring 100 will be described later.
As shown in Fig. 6, the fixing piece 105 is connected to the outer end portion 101 of the constant force spring 100. In the example shown, the fixing piece 105 is formed integrally with the spring for constant force 100. A through opening 105a is formed in the fixing piece 105, through which the spring pin for constant force 103 (see FIG. 4) is guided.
As shown in FIG. 4, the fixing pieces 105 are arranged below the spring support section 50 of the upper step wheel for constant force 40. The constant force spring pin 103 is held by the spring support portion 50 in a state of protruding downward from the pin insertion hole 50 a formed in the spring support portion 50 of the upper constant force gear 40. The protruding part of the constant force spring pin 103 is inserted into the through hole 105a of the fixing piece 105 from above. Consequently, the spring pin for constant force 103 connects the fixing piece 105 and the upper step wheel for constant force 40 to one another.
As shown in Fig. 6, the fixing ring 104 is formed in an annular shape coaxially with the first axis of rotation O1. A portion of the outer circumferential surface of the fixation ring 104 projects outward in the radial direction and is connected to the inner end portion 102 of the constant force spring 100. In the illustrated example, the fixation ring 104 is integrally formed with the constant force spring 100. The fixation ring 104 is integrally connected to a constant force spring bushing 111, which will be described later in the torque adjustment mechanism 110 (see FIG. 4).
The constant force spring 100 is wound with a predetermined amount of turns in the clockwise direction against the outer end portion 101 with the inner end portion 102 as an unwound position. A bias is applied to the constant force spring 100 by winding. Accordingly, the force of a torque Tc is generated in the constant force spring 100 and the force is stored. In the present embodiment, the constant force spring 100 is elastically deformed so that the diameter when winding and fastening the outer end portion 101 in the clockwise direction with respect to the inner end portion 102 is reduced, and generates the torque.
The force stored in the constant force spring 100 is transmitted to the upper constant force gear 40 and the lower constant force gear 60 in accordance with the elastic return deformation of the constant force spring 100. Accordingly, the upper step gear is for constant force 40 and the lower step wheel for constant force 60 in the opposite directions about the first axis of rotation O1 by means of the constant force spring
100 transmitted power rotatable. In particular, the lower constant force step wheel 60 is rotatable in a clockwise direction and the upper constant force step wheel 40 is rotatable in a counterclockwise direction. Hereinafter, the torque Tc is referred to as a constant force spring torque Tc 100. Furthermore, in a case where the main spring 16 of the barrel 11 is wound around a predetermined winding amount, the torque Tc is set as a torque smaller than the torque Tb of the rotating shaft 41.
As shown in FIG. 4, the torque adjusting mechanism 110 biases the constant force spring 100 and adjusts the torque Tc of the constant force spring 100. The torque adjusting mechanism 110 includes: a constant force spring sleeve 111 held by the lower step force cylinder 61 of the lower step force wheel 60; a first torque adjustment gear 112 which is integrally connected to the constant force spring sleeve 111; a second torque adjustment gear 113 integrally connected to the lower step force constant cylinder 61; and a torque adjustment bridge 114 that connects the first torque adjustment gear 112 and the second torque adjustment gear 113 together.
The spring sleeve for constant force 111 is formed in a cylindrical shape coaxially with the first axis of rotation O1. The constant force spring sleeve 111 is extrapolated from the lower step force cylinder 61 between the lower step force wheel 62 and the engagement Z separator unit 80. The spring sleeve for constant force 111 is provided so as to be rotatable about the first axis of rotation O1 with respect to the lower step cylinder for constant force 61. The above-described fixing ring 104 is extrapolated in the upper and lower intermediate regions of the spring sleeve for constant force 111, and the spring sleeve for constant force 111 and the fixing ring 104 are integrally connected to one another.
The first torque adjustment gear 112 is integrally connected to the lower end portion of the constant force spring sleeve 111. On an outer circumferential surface of the first torque adjustment gear 112, a torque adjustment tooth 112a is formed over the entire circumference. A torque adjustment gear (not shown) meshes with the first torque adjustment tooth 112a.
Since the second torque setting gear 113 is arranged between the lower step wheel for constant force 62 and the spring sleeve for constant force 111 and the first torque setting gear 112. The second torque adjustment gear 113 is integrally connected to the lower step cylinder for constant force 61. The second torque adjustment gear 113 is smaller in diameter than the first torque adjustment gear 112. On the outer circumferential surface of the second torque adjustment gear 113, a second torque adjustment tooth 113a is formed over the entire circumference. The torque adjustment bridge 114 is releasably engaged with the second torque adjustment tooth 113a.
The torque adjustment bridge 114 is held by the first torque adjustment gear 112 and is configured to rotate about the first axis of rotation O1 around the second torque adjustment gear 113. The torque adjustment bridge 114 may regulate the rotation of the first torque adjustment gear 112 in a clockwise direction with respect to the second torque adjustment gear 113. Furthermore, the torque adjustment bridge 114 can enable the rotation of the first torque adjustment gear 112 in the counterclockwise direction with respect to the second torque adjustment gear 113.
Accordingly, when the constant force spring sleeve 111 and the first torque adjustment gear 112 receive the clockwise direction force from the constant force spring 100, the force is transmitted to the second torque adjustment gear 113 via the torque adjustment bridge 114. Then, the torque adjustment bridge 114 regulates the rotation of the first torque adjustment gear 112 in a clockwise direction with respect to the second torque adjustment gear 113, and the first torque adjustment gear 112 and the second torque adjustment gear 113 rotate integrally in the clockwise direction. It follows that the lower constant force gear 60 also rotates in the clockwise direction together with the second torque adjustment gear 113.
[0093] Further, when the constant force spring bias 100 is applied by causing a torque adjustment gear (not shown) to mesh with the first torque adjustment gear 112 and rotate the torque adjustment gear, the first torque adjustment gear 112 rotates in a clockwise direction -Direction. Since the torque adjustment bridge 114 enables the rotation of the first torque adjustment gear 112 in the counterclockwise direction with respect to the first torque adjustment gear 112, the spring sleeve for constant force 111 and the fixing ring 104 are rotated in the counterclockwise direction with respect to the second torque adjustment gear 113 without that the lower step wheel for constant force turns 60. Accordingly, the inner end portion 102 of the constant force spring 100 can be rotated in a counterclockwise direction. As a result, it is possible to wind the constant force spring 100 and when the preload of the constant force spring 100 is increased, the torque Tc can be adjusted to increase.
(Shape of the constant force spring) The shape of the above-described constant force spring 100 will be described below. Further, in the following description, a state is referred to as a natural state of the constant force spring 100 in which the constant force spring 100 is not attached to the upper constant force gear 40 and the lower constant force gear 60, and the Tension is not applied to the constant force spring 100. Further, a state in which the outer end portion 101 of the constant force spring 100 is fixed to the upper constant force wheel 40 and the inner end portion 102 of the constant force spring 100 is fixed to the lower constant force wheel 60 as a fixed one Condition of the spring for constant force designated 100. Further, in the fixed state of the constant force spring 100, a state in which the torque is not generated before the constant force spring 100 is wound is referred to as a pre-winding state and a state in which the constant force spring 100 is wound and a predetermined torque is generated, is referred to as a torque generation state. The same is used in other embodiments, as will be described later.
Fig. 7 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the first embodiment. Figure 7 shows the natural state of the constant force spring 100.
As shown in Fig. 7, in the natural state, the constant force spring 100 extends along an Archimedean curve with respect to a central axis X of the fixing ring 104 as a center. As a result, the distance between the adjacent springs is constant. The central axis X of the fixing ring 104 is an axis that coincides with the first rotation axis O1 in a state where the fixing ring 104 is fixed to the lower constant force gear 60 via the torque adjusting mechanism 110. In other words, the central axis X of the fixing ring 104 is the center of the rotation when the constant force spring 100 is wound up. In the natural state, the constant force spring 100 is designed such that the outer end portion 101 is counter-clockwise by 90 °. Direction about the central axis X of the fixing ring 104, with respect to the inner end portion 102, is offset.
Fig. 8 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the first embodiment. 8 shows the pre-winding state of the constant force spring 100.
As shown in Fig. 8, in the pre-winding state of the constant force spring 100, the outer end portion 101 of the constant force spring 100 is located at a position closer to the first rotation axis O1 than at a position A in the natural state. A distance between the outer end portion 101 and the inner end portion 102 is smaller in the pre-wind state than in the natural state. In the present embodiment, in the pre-winding state of the constant force spring 100, the outer end portion 101 of the constant force spring 100 is arranged between the position A in the natural state and the first rotation axis O1. Accordingly, in the constant force spring 100, a distance between the adjacent springs in the pre-wind state changes in the radial direction orthogonal to the first rotation axis O1 according to the position in the circumferential direction about the first rotation axis O1.
[0099] In particular, when viewed in the up-down direction, a distance P1 between the springs on a semi-straight line L1 which extends from the first axis of rotation O1 to the outer end portion 101 is smaller than a distance P2 between the springs on one second half line L2, which extends to the side opposite the first half line L1 from the first axis of rotation O1. The distance P1 between the springs on the first half line L1 is smaller than the distance between the springs in the natural state and becomes smaller the further away from the first axis of rotation O1. The distance P2 between the springs on the second half line L2 is greater than the distance between the springs in the natural state and becomes greater the further away from the first axis of rotation O1. Furthermore, in the pre-winding state of the constant force spring 100, the adjacent springs may be in contact with each other.
The constant force spring 100 reaches the torque generation state shown in Fig. 6 by rotating the inner end portion 102 in the counterclockwise direction by a predetermined angle (360 ° in the illustrated example) by the torque adjusting mechanism 110 from the pre-wind state and by winding and securing the constant force spring 100. In the torque generation state, the constant force spring 100 extends along a spiral curve that is related to the position of the Archimedean curve offset from the first rotation axis O1 to the side of the inner end portion 102 , approaches. In the torque generation state, the adjacent springs in the constant force spring 100 are separated from each other to avoid self-contact.
(Operation of the Constant Torque Mechanism) The operation of the constant torque mechanism 30 configured as described above will now be explained.
Furthermore, in an initial state, the main spring 16 of the barrel 11 is wound in a predetermined winding dimension and the force of the torque Tb is transmitted from the barrel 11 to the carrier 47 of the upper step wheel for constant force 40 via the power source side gear train 112. Further, the constant force spring 100 is wound in a predetermined winding amount, and the force of the torque Tc, which is smaller than the torque Tb, is from the constant force spring 100 to the carrier 47 of the upper step gear for constant force 40 and the lower one Step wheel for constant force 60 transmitted.
According to the constant torque mechanism 30 of the present embodiment, since the constant force spring 100 is provided, the force stored in the constant force spring 100 is transmitted to the lower step wheel constant force 60 and the lower step wheel constant force 60 can be rotated in the clockwise direction about the first axis of rotation O1. In particular, the force is transmitted from the constant force spring 100 to the torque adjusting mechanism 110 via the fixing ring 104. The force transmitted to the torque adjustment mechanism 110 is transmitted to the lower constant force stage gear 60. Accordingly, the constant force spring 100 transmits the force to the lower constant force stage gear 60 so as to rotate clockwise around the first axis of rotation O1 with the torque Tc. Further, the force of the constant force spring 100 may be transmitted from the lower constant force stage gear 60 to the second transmission gear 19, and the second transmission gear 19 may be rotated in accordance with the rotation of the lower constant force stage gear 60. In other words, the force can be transmitted from the constant force spring 100 to the escapement side gear 15 via the lower constant force stage gear 60, and the escapement 14 can be operated.
Furthermore, since the force from the constant force spring 100 is also transmitted to the upper constant force gear 40 via the fixing piece 105 and the constant force spring pin 103, the upper constant force gear 40 in the counterclockwise direction Direction rotated about the first axis of rotation O1 with the torque Tc.
However, the torque Tb is transmitted to the upper constant force gear 40 so that it rotates about the first rotation axis O1 through the power source side gear train 12 in the clockwise direction. Since the torque Tb is larger than the torque Tc, the upper constant force gear 40 is prevented from rotating in the counterclockwise direction about the first rotation axis O1.
Furthermore, in the upper constant force step gear 40, the force difference (torque Tb - torque Tc) acts between the torque Tb transmitted from the power source side gear train 12 and the torque Tc transmitted from the constant force spring 100. However Since the engagement claw block 86 of the engagement Z separating lever unit 80 is in engagement with the planetary gear 45 in the cam path M of the planetary gear 45 of the upper step gear for constant force 40, the rotation and rotation of the planet gear 43 is regulated. Accordingly, the upper constant force gear 40 and the lower constant force gear 60 can be connected to each other, and the upper constant force gear 40 is prevented from rotating about the first rotation axis O1 in the clockwise direction.
From above, in the phase in which the planetary gear 45 and the engaging claw block 86 are engaged with each other, the upper constant force gear 40 is prevented from rotating about the first rotation axis O1. Furthermore, since the force of the difference described above acts on the upper step wheel for constant force 40, the tooth tip of the stop teeth 45a of the planetary gear 45 is in engagement with the engagement claw block 86 in a strongly pressed state.
[0108] When the lower constant force step gear 60 rotates by the force of the constant force spring 100 in accordance with the rotation, the lever sleeve 81 and the engagement-separating lever 84 of the engagement / separation lever unit 80 rotate around the first rotation axis O1 clockwise- Direction. When the engaging / separating lever 84 rotates in the clockwise direction, the engaging claw block 86 included in the engaging / separating lever 84 is displaced in the clockwise direction about the first axis of rotation O1. Accordingly, the engagement / disconnect lever unit 80 can be gradually released from the planetary gear 45 to retract the engagement claw block 86 from the rotational cam path M of the planetary gear 45. Accordingly, the tooth tip moves in the counterclockwise direction about the first rotation axis O1 with respect to the engaging claw block 86 when the tooth tip of the stop teeth 45a slides on the engagement claw block 86 in accordance with the disengagement of the engagement claw block 86. Furthermore, at the time when the tooth tip of the stop teeth 45a leaves the claw tip of the engaging claw 86, the engagement between the stop teeth 45a and the engagement claw 86 is released. Accordingly, the connection between the upper constant force gear 40 and the lower constant force gear 60 is released via the engagement claw 86.
Accordingly, the upper constant force stepwheel 40 rotates in the clockwise direction around the first rotation axis O1 through the force difference (torque Tb - torque Tc) between the torque Tb transmitted to the power source side gear train 12 and the torque Tc transmitted from the constant force spring 100.
When the upper constant force gear 40 rotates clockwise around the first axis of rotation O1, the constant force spring 100 can be wound up via the constant force spring pin 103 fixed to the carrier 47 and the spring for constant force 100 can be filled up with the force. In other words, the loss of power lost when the power is transmitted from the lower constant force stage gear 60 can be replenished by using the force transmitted from the side of the barrel 11 which is the power source. Accordingly, the force of the spring door constant force 100 can be kept constant and the escapement 14 can be operated with a constant torque.
[0111] Furthermore, even in a case of replenishing the force with respect to the constant force spring 100, the lower step wheel for constant force 60 rotates with the force from the constant force spring 100 and the force from the constant force spring 100 is transmitted to the escapement gear train 15.
Furthermore, the planet gear 43 rotates in the clockwise direction around the first rotation axis O1 and follows the engaging claw block 86 when the force, based on the spring for constant force 100 described above, during rotation in the clockwise direction around the second rotation axis O2 of the upper step wheel for constant force 40 is filled. Furthermore, the planet gear 43 follows the engagement claw block 86 when rotating by a stop tooth 45a and the tooth tip of the stop tooth 45a is again in engagement with the engagement claw block 86.
Accordingly, since the upper constant force gear 40 and the lower constant force gear 60 are connected to each other, the rotation of the upper constant force gear 40 is prevented and the force loading of the constant force spring 100 is complemented.
When repeating the above, the engagement and the separation between the planetary gear 45 and the engagement claw 86 can be performed intermittently. In other words, the planetary gear 45 and the engaging claw 86 can intermittently rotate the upper constant force gear 40 with respect to the lower constant force gear 60 based on the rotation of the lower constant force gear 60 constant force 100 take place intermittently.
(Function of the constant force spring) The function of the constant force spring 100 configured as described above is explained below.
The coil spring, like the constant force spring 100, tends to reduce the diameter around the axis when winding and fastening when it is wound from a natural state. Accordingly, when the coil spring is wound up while the distance between the axis and the outer end portion and the inner end portion is kept constant, the coil spring is deformed by a force received in the radial direction by the outer end portion and the inner end portion. Comparable to the constant force spring 100 of the present embodiment, in a case of winding and fastening from the pre-wind state, the entire coil spring is deformed so that it is pulled through the outer end portion and a part opposite to the outer end portion over the axis , the distance between the springs adjacent to each other is reduced compared to that in the pre-wind state.
In the constant force spring 100 of the present embodiment in the pre-wind state, a distance between adjacent springs changes in the radial direction orthogonal to the first rotation axis O1, corresponding to the position in the circumferential direction about the first rotation axis O1. According to the configuration, upon carefully setting and changing the distance between the adjacent springs corresponding to the position in the circumferential direction, it is possible to arbitrarily set the shape of the constant force spring 100 in the torque generation state. Accordingly, it is possible to suppress the distance between the springs from narrowing and the springs from coming into contact with each other through the deformation accompanying the winding of the constant force spring 100. Accordingly, it is possible to suppress that the torque generated by the constant force spring 100 is reduced by the frictional force associated with the contact of the constant force spring 100 in the torque generation state. For example, the constant force spring can suppress 100 self-contact or contact with surrounding components and generate a desired torque.
Furthermore, the constant force spring 100 is configured to generate the winding and fastening torque from the pre-wind state and in the pre-wind state when viewed from an up-down direction, the distance P1 is between the springs on the first half line L1, which extends from the first axis of rotation O1 to the outer end section 101, is narrower than the distance P2 between the springs on the second half line L2, which extends from the first axis of rotation O1 to the side, opposite to the first Half line L1. According to the configuration, when the constant force spring 100 is wound and fixed from the pre-wind state, the deformation occurs, so that the distance between the springs becomes narrower at the portion opposite the outer end portion 101 via the first rotation axis O1. Accordingly, by setting the distance P1 between the springs on the first half degree L1, which extends from the first rotation axis O1 to the outer end portion 101, it is possible in the pre-wind state to be narrower than the distance P2 between the springs on the second half line L2, which extends from the first axis of rotation O1 to the side, opposite to the first half line L1, even if the distance between the springs is closer to the part, opposite to the outer end portion 101 via the first axis of rotation O1 possible to suppress contact between the springs. Accordingly, it is possible to generate a desired torque in the constant force spring 100, which generates the torque when wound and fastened from the pre-wind state.
[0119] Furthermore, the constant force spring 100 extends along the Archimedean curve in the natural state in which the tension is not applied to the constant force spring 100. According to the configuration, it becomes possible to bring the shape of the constant force spring 100 in the torque generation state into a spiral curve approximating the Archimedean curve. Accordingly, in the constant force spring 100 in the torque generation state, since it is possible to keep the distance between the adjacent springs substantially constant regardless of the position in the circumferential direction and in the radial direction, the contact between them is possible to suppress neighboring springs. Accordingly, the constant force spring 100 can generate a desired torque.
Further, since the constant torque mechanism 30 of the present embodiment includes the constant force spring 100 that generates a desired torque, it is possible to suppress the torque from being insufficient between the upper constant force stage gear 40 and the lower step wheel for constant force 60, and to suppress the fluctuation of the torque which is transmitted from the lower step wheel for constant force 60 to the escapement 14.
Further, since the watch 1 and the movement 10 of the present embodiment include the constant torque mechanism in which the fluctuation in the torque transmitted to the escapement 14 is suppressed, the movement 10 and the watch 1 can be obtained with high accuracy become.
[Second Embodiment] A second embodiment will be described below with reference to Figs. 9 to 11. The second embodiment differs from the first embodiment in that a part of the outermost peripheral portion of a constant force spring 200 via a curved one Section 206 is separated outwards in the radial direction. Furthermore, the configuration is the same as in the first embodiment except that described below.
Fig. 9 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the second embodiment. 9 shows the natural state of the constant force spring 200.
As shown in Fig. 9, the constant force spring 200 includes an outer end portion 201 to which the fixing piece 105 is connected and an inner end portion 202 to which the fixing ring 104 is connected and the curved portion 206. The curved portion Section 206 replaces a portion of the outermost peripheral section, including the outer end portion 201 of the constant force spring 200 in the radial outside direction. Accordingly, in the natural state, a part except for a part of the outermost peripheral portion in the constant force spring 200 extends radially outward along an Archimedean curve with respect to the central axis X of the fixing ring 104 as a center. Further, in an area of the outermost peripheral portion including the outer end portion 201 of the constant force spring 200, the distance between the adjacent springs is wider than in other areas.
Fig. 10 is a plan view illustrating the constant force spring, the fixing piece and the fixing ring of the second embodiment. 10 shows the pre-winding state of the constant force spring 200.
As shown in Fig. 10, in the pre-winding state of the constant force spring 200, the outer end portion 201 of the constant force spring 200 is located at a position closer to the first rotation axis O1 than a position B in the natural state , Accordingly, in the constant force spring 200 in the pre-winding state, comparable to the constant force spring 100 of the first embodiment, the distance between the adjacent springs in the radial direction orthogonal to the first rotation axis O1 changes according to the position in the circumferential direction around the first axis of rotation O1.
In particular, when viewed in an up-down direction, the distance P1 between the springs on the first half line L1, which extends from the first axis of rotation O1 to the outer end portion 201, is smaller than the distance P2 between the springs on the second half line L2, which extends from the first axis of rotation O1 to the side, opposite to the first half line L1. The distance P1 between the springs on the first half line L1 is smaller than the distance between the springs in the natural state and becomes smaller the further away from the first axis of rotation O1, with the exception of the outermost peripheral section. The distance P2 between the springs on the second half line L2 is greater than the distance between the springs in the natural state and becomes greater the further away from the first axis of rotation O1.
Fig. 11 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the second embodiment. In Fig. 11, the torque generation state of the constant force spring 200 is shown. The constant force spring 200 reaches the torque generation state shown in FIG. 11 by rotating the inner end portion 202 in the counterclockwise direction by a predetermined angle (360 ° in the illustrated example) by the torque adjusting mechanism 110 (see FIG. 4) from the pre-upwind state and by winding and securing the constant force spring 200. In the torque generation state, the constant force spring 200 extends along a spiral path that approaches the Archimedean curve with respect to a position as a center that is from the first Axis of rotation O1 is shifted to the side of the inner end portion. In the torque generation state, in the constant force spring 200, the adjacent springs are spaced from each other to avoid self-contact.
As described above, the constant force spring 200 of the present embodiment includes a curved portion 206 which radially replaces a part of the outermost peripheral portion including the outer end portion 201. According to the configuration, compared to a case where the constant force spring does not include the curved portion, the outer end portion 201 of the constant force spring 200 can be provided on the outside in the radial direction in the natural state. Thus, by attaching the constant force spring 200 including the curved portion 206 to a constant torque mechanism of the comparable type in which the outer end portion of the constant force spring does not include a curved portion, in a position in the natural state, the outer end portion 201 of the constant force spring 200 is moved to the first rotation axis O1. Accordingly, comparable to the first embodiment, in the pre-wind state, seen in the up-down direction, the distance P1 between the springs on the first half-straight line L1, which extends from the first rotation axis O1 to the outer end portion 201, is narrower than the distance P2 between the springs on the second half line L2 extending from the first rotation axis O1 to the side opposite to the first half line L1. Accordingly, the constant force spring 200 can stably generate a desired torque by being fixed to the constant torque mechanism which is configured to fix the constant force spring of the comparable type.
[Third Embodiment] A third embodiment will be described below with reference to Figs. 12 to 13. In the first embodiment, in the natural state of the constant force spring 100 shown in FIG. 7, the center of the Archimedean curve along the shape of the constant force spring 100 coincides with the central axis X of the fixing ring 304. In contrast, the third embodiment differs from the first embodiment in that in the natural state of a constant force spring 300, a center Y of the Archimedean curve is shifted along the shape of the constant force spring 300 from the central axis X of the fixing ring 304 Furthermore, the configuration is the same as that in the first embodiment except for what is described below.
Fig. 12 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the third embodiment. 12 shows the natural state of the constant force spring 300.
As shown in FIG. 12, the constant force spring 300 includes an outer end portion 301 to which the fixing piece 105 is connected and an inner end portion 302 to which the fixing ring 304 is connected. In the natural state, the constant force spring 300 extends along the Archimedean curve with respect to a point considered as a center Y, which is provided on the side opposite to the inner end portion 302 via the central axis X of the fixing ring 304 from up-down direction. The fixing ring 304 is formed in an annular shape coaxial with the first rotation axis OL. The outer circumferential surface of the fixing ring 304 is formed to have a substantially constant outside diameter and is connected to the inner end portion 302 of the constant force spring 300.
Fig. 13 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the third embodiment. FIG. 13 shows the torque generation state of the constant force spring 200.
Comparable to the first embodiment, in the pre-winding state of the constant force spring 300, the outer end portion 301 of the constant force spring 300 is fixed to the upper constant force gear 40 via the fixing piece 105, the closer to the first rotation axis O1 than being positioned in position C in the natural state. The constant force spring 300 reaches the torque generation state shown in FIG. 13 by rotating the inner end portion 302 in the counterclockwise direction by a predetermined angle (360 ° in the illustrated example) by the torque adjusting mechanism 110 from the pre-wind state and by Winding and securing the constant force spring 300. In the torque generation state, the constant force spring 300 extends along the spiral path which approaches the Archimedean curve with respect to the first axis of rotation O1 as a center. In other words, the constant force spring 300 is arranged concentrically with the fixing ring 304 in the torque generation state.
As described above, the constant force spring 300 of the present embodiment extends along the Archimedean curve in a natural state in which the tension is not applied to the constant force spring 300 and the center Y of the Archimedean curve along the shape of the constant force spring 300 is provided on the side in the natural state opposite to the inner end portion 302 via the central axis X of the fixing ring 304. According to the embodiment, it is possible to shape the constant force spring 300 in the torque generating state in FIG to bring a spiral path that approaches the Archimedean curve. Here, when the constant force spring 300 is wound and fixed, by reducing the diameter of the innermost circumferential portion of the constant force spring 300, the center of the spiral path is shifted in winding and fixing the constant force spring 300 to the to approach inner end portion 302. Accordingly, when providing the center Y of the Archimedean curve in the natural state on the side opposite the inner end portion 302 via the central axis X of the fixing ring 304, the center of the spiral path approaches the first rotation axis O1 in the torque generation state. Accordingly, the entire innermost peripheral portion of the constant force spring 300 also approaches the first rotation axis O1, and while a distance between the innermost peripheral portion and the fixing ring 304 of the constant force spring 300 is reduced, it is possible to increase the distance between the outermost peripheral portion and to further widen the innermost peripheral portion of the constant force spring 300 in the entire circumferential direction. Accordingly, it is possible to widen the distance between adjacent springs and suppress the contact between the springs. Accordingly, the constant force spring 300 can generate a desired torque.
[Fourth Embodiment] A fourth embodiment will be described below with reference to Figs. 14 to 16. The constant force spring 100 of the first embodiment is elastically deformed so as to reduce the diameter when winding and fixing the outer end portion 101 in the clockwise direction with respect to the inner end portion 102 and to generate the torque. In contrast, the fourth embodiment differs from the first embodiment in that a constant force spring 400 is elastically deformed so as to reduce the diameter at
Winding and securing the outer end portion 401 in the clockwise direction with respect to the inner end portion 402 to reduce and generate the torque. Furthermore, the configuration is the same as that in the first embodiment except for that described below.
Fig. 14 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the fourth embodiment. 14 shows the natural state of the constant force spring 400.
As shown in FIG. 14, the constant force spring 400 includes an outer end portion 401 to which the fixing piece 105 is connected and an inner end portion 402 to which the fixing ring 104 is connected. The constant force spring 400 is wound with a predetermined amount of winding in the counterclockwise direction against the outer end portion 401 with the inner end portion 402 as an unwound position. In the natural state, the constant force spring 400 extends along an Archimedean curve with respect to the central axis X of the fixing ring 104 as a center. As a result, the distance between the adjacent springs is constant. The bias is applied to the constant force spring 400 by winding.
Fig. 15 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the fourth embodiment. 15 shows the pre-winding state of the constant force spring 400.
As shown in Fig. 15, in the pre-winding state of the constant force spring 400, the outer end portion 401 of the constant force spring 400 is located at a position distant from the first rotation axis O1 as a position D in the natural state. A distance between the outer end portion 401 and the inner end portion 402 is larger in the pre-wind state than in the natural state. In the present embodiment, in the pre-winding state of the constant force spring 400, the outer end portion 401 of the constant force spring 400 is arranged at the position opposite to the first rotation axis O1 through the position in the natural state. Accordingly, in the constant force spring 400 in the pre-winding state, a distance between adjacent springs changes in the radial direction orthogonal to the first rotation axis O1, corresponding to the position in the circumferential direction around the first rotation axis O1.
In particular, when viewed in the up-down direction, the distance P1 between the springs on the first half-straight line, which extends from the first axis of rotation O1 to the outer end portion 401, is larger than the distance between the springs on the second half line L2, which extends from the first axis of rotation O1 to the side, opposite the first half line L1. The distance P1 between the springs on the first half line L1 is greater than the distance between the springs in the natural state and becomes greater the further away from the first axis of rotation O1. The distance between the springs on the second half line L2 is smaller than the distance between the springs in the natural state. In the example shown, the adjacent springs come into contact with each other on the second half line L2 and the distance between the springs on the second half line L2 is zero. In addition, the adjacent springs on the second half line L2 cannot come into contact with each other.
Fig. 16 is a plan view showing the constant force spring, the fixing piece and the fixing ring of the fourth embodiment. 16 shows the torque generation state of the constant force spring 400.
The constant force spring 400 reaches the torque generation state shown in FIG. 16 by rotating the inner end portion 402 in the counterclockwise direction by a predetermined angle (360 ° in the illustrated example) by the torque adjusting mechanism 110 from the pre-wind. State and by winding and securing the constant force spring 400. In the torque generation state, the constant force spring 400 extends along a spiral path that approaches the Archimedean curve with respect to the position as a center shifted from the first axis of rotation O1 the side opposite to the side of the inner end portion 402. In the torque generation state, in the constant force spring 400, adjacent springs are separated from each other to avoid self-contact.
(Function of the constant force spring) The function of the constant force spring 400 configured as described above will now be described.
The coil spring, like the constant force spring 400, tends to reduce the diameter around the axis when wound around the axis from a natural state by winding and widening. As a result, when the coil spring is wound while keeping the distance between the axis and the outer end portion constant, the coil spring is deformed in the radial direction by a force received by the outer end portion and the inner end portion. Comparable to the constant force spring 400 of the present embodiment, in a case of winding and widening from the pre-wind state, the entire coil spring is deformed with the outer end portion and the portion opposite the outer end portion about the axis, the distance between the springs adjacent to each other expanded compared to that in the pre-winding state.
According to the present embodiment, by carefully adjusting and changing the distance between the adjacent springs according to the position in the circumferential direction, it becomes possible to arbitrarily set the shape of the constant force spring 400 in the torque generation state. Accordingly, it is possible to suppress that the distance between the springs becomes wider by the deformation which the winding of the
Constant force spring 400 accompanies, and the outermost peripheral portion of the constant force spring 400 comes into contact with surrounding components. Accordingly, it is possible to suppress that the torque generated by the constant force spring 400 is reduced by the frictional force accompanying the contact of the constant force spring 400 in the torque generation state. Accordingly, the constant force spring 400 can generate a desired torque.
[0148] Furthermore, the constant force spring 400 is configured to generate the torque when being wound and fixed from the pre-wind state and in the pre-wind state when viewed from the up-down direction Distance P1 between the springs on the first half line L1, which extends from the first axis of rotation O1 to the outer end section 401, wider than the distance between the springs on the second half line L2, which extends from the first axis of rotation O1 to the side, opposite to the first half line L1. According to the present embodiment, when the constant force spring 400 is wound and expanded from the pre-winding state, the deformation occurs so that the distance between the springs becomes wider on the part opposite to the outer end portion 401 via the first rotation axis O1. Accordingly, when setting the distance P1 between the springs on the first half-straight line L1, which extends from the first axis of rotation O1 to the outer end section 401, in the pre-wind state, it is wider than the distance between the springs on the second half-straight line L2, which extends from the first rotation axis O1 to the side opposite to the first half line L1, even if the distance between the springs is wider to the other part, opposite to the outer end portion 401 via the first rotation axis O1, it is possible to suppress that the outermost circumferential portion of the constant force spring 400 expands outward in the radial direction greater than the surroundings on the part, opposite to the outer end portion 401 via the first axis of rotation O1. As a result, it is possible to suppress the outermost peripheral portion of the constant force spring 400 from coming into contact with surrounding components. Accordingly, it is possible to generate a desired torque in the constant force spring 400, which generates the torque when being wound and expanded from the pre-wind state.
[Fifth Embodiment] The fifth embodiment will now be described with reference to Figs. 17 to 19. A watch 501 of the fifth embodiment differs from the watch 1 of the first embodiment in that a reset mechanism 511 is provided which has a date hand 8 moves. Furthermore, the configuration is the same as that in the first embodiment except for that described below.
17 shows an external view of a clock according to a fifth embodiment.
As shown in Fig. 17, the watch 501 is provided with a calendar display area 501a which displays a date. The calendar display area 501 a comprises the date pointer 8, which comprises a pointer 4 and a fan-shaped scale on the dial 3. The date hand 8 is rotatably arranged in a predetermined angular range around an axis other than that of the hour hand 5, the minute hand 6 and the second hand 7. The fan-shaped scale is configured to count “1” to “31”, which represent the date. The fan-shaped scale is arranged in accordance with the range of rotation of the date pointer 8 and is indicated by the date pointer 8.
18 and 19 are top views of the reset mechanism.
As shown in FIG. 18, the work 510 includes the reset mechanism 511 that drives the date hand 8. The reset mechanism 511 resets the date hand 8 within a predetermined angular range. The reset mechanism 511 includes a date display drive gear 512, a date transfer gear 520, a date hammer 540, a date handwheel 550, and a return spring 560.
The date display drive gear 512 rotates once in a day (24 hours), being connected to the power source side gear train 12 described above (see FIG. 2). A date finger 513 is provided in the date display drive gear 512. The date finger 513 has a spring section 514, which is formed in an arc shape in a top view, and an end section 515, which is provided at a distal end of the spring section 514. The date finger 513 is arranged to cover the date display drive gear 512 in plan. The date finger 513 is integrally provided with the date display drive wheel 512 and rotates in synchronization with the date display drive wheel 512. The spring portion 514 is elastically deformable in the circumferential direction and in the radial direction of the date display drive wheel 512. When rotating about the axis of rotation of the date display drive wheel 512, in accordance with the rotation of the Date display driving wheel 512, the end portion 515 engages the date transmission wheel 520 once every rotation and rotates the date transmission wheel 520.
The date transmission wheel 520 is formed in a disc shape, and a plurality of teeth 521 are formed on the outer peripheral edge. The plurality of teeth 521 are formed as teeth corresponding to 31 days, which is the number of days in a month. One of the plurality of teeth 521 is pressed once a day by the forehead portion 515 of the date finger 513, which rotates once a day. Accordingly, the date transmission wheel 520 rotates one step in a day and rotates once in a month (this is 31 days) at the same angular distance as the angular distance of the plurality of teeth 521.
A date column wheel 525 is provided in the date transmission wheel 520. The date column wheel 525 rotates once in a month in synchronization with the date transmission wheel 520. The outer circumferential surface of the date column wheel 525 is a curved surface 526, which is designed such that the radius increases in a spiral shape when oriented in the direction opposite to the direction of rotation of the date transmission wheel 520. The cam surface 526 has an outermost section 526a in which the separation distance from the axis of rotation of the date transmission wheel 520 is maximum and an innermost distance 526b in which the separation distance from the rotation axis of the date transmission wheel 520 is minimal. A date lever spring 530 abuts the date transmission wheel 520. The date lever spring 530 includes an elastically deformable date lever spring portion 531, one distal end portion of which is a free end. The distal end portion of the date lever spring portion 531 can be engaged with the teeth 521 of the date transmission wheel 520. Thus, the date transfer wheel 520 can rotate a step once in a day at the same angular distance as the angular distance of the plurality of teeth 521.
The date hammer 540 is provided so as to be arranged to be reset about the axis offset from the rotation axis of the date transmission wheel 520. The date hammer 540 includes a fan-shaped gear section 541 which meshes with the date hand wheel 550 and a cam arm section 542 which rotates integrally with the fan-shaped gear section 541. The cam arm section 542 is a cam follower, the distal end section of which abuts against the cam surface 526 of the date column wheel 525. Hereinafter, the position of the date hammer 540 when the distal end portion of the cam arm portion 542 abuts the innermost end portion 526b of the cam surface 526 of the date pillar wheel 525 is referred to as the "home position". Furthermore, the position of the date hammer 540 when the distal end portion of the cam arm portion 542 abuts the outermost end portion 526a is referred to as an "end position". As described above, the date column wheel 525 rotates once in a month. Accordingly, the date hammer 525 changes once a month between the starting position and the ending position. Furthermore, a state in which the date hammer 540 is in the starting position is shown in FIG. 18. Furthermore, a state in which the date hammer 540 is in the end position is shown in FIG. 19.
The date hand wheel 550 is connected to the date hand 8 to rotate the date hand 8. The date hand wheel 550 rotates about axis 03 in synchronization with the rotation of the date hammer 540. When the date hammer 540 is in the home position, the date hand wheel 550 is in a state to be rotated in most one direction (counterclockwise direction in the Presentation). At this time, the date hand 8 shows "1" on the scale of the calendar display section 501a (see Fig. 17). Furthermore, when the date hammer 540 is in the end position, the date hand wheel 550 is in a state to be rotated in the most other direction. At this time, the date hand 8 shows "31" on the scale of the calendar display section 501a. Consequently, the date hand 8 is gradually moved every day in accordance with the rotation of the date column wheel 525 and the movement of the date hammer 540.
The return spring 560 biases the date hammer 540 in one direction via the date pointer wheel 550, approaching the date column wheel 525. The return spring 560 is a coil spring which is formed in the same manner as the constant force spring 100 described above. An inner end portion 562 of the return spring 560 is fixed to the date hand wheel 550 and is fixedly provided on the date hand wheel 550. An outer end portion 561 of the return spring 560 is fixed to an element (e.g., the main plate 23 or the like) which is rotatably supported by the date hand wheel 550.
The bias is applied to the return spring 560 by winding. In the present embodiment, the return spring 560 is elastically deformed, so that the diameter during winding and fastening of the inner end section 562, relative to the outer end section 561, is reduced and generates the torque. The return spring 560 is wound from the pre-wind state in a state in which the date hammer 540 is in the home position. Further, the pre-winding state of the return spring 560 is a state in which the outer end portion 561 of the return spring 560 is fixed to the main plate 23 or the like, the inner end portion 562 of the return spring 560 is fixed to the date hand wheel 550, and the torque is not generated , The return spring 560 is further wound from a state in which the date hammer 540 is in the starting position to a state in which the date hammer 540 is in the end position. As a result, the return spring 560 also generates the torque in a state in which the date hammer 540 is in any position from the starting position to the end position and is tensioned in a direction in which the date hammer 540 approaches the date column wheel 525.
Comparable to the constant force spring 100 shown in FIG. 8, the outer end portion 561 of the return spring 560 is arranged in a position closer to the axis of rotation 03 of the date hand wheel 550 than the position in the natural state in the Prewind state of the return spring 560. The distance between the outer end portion 561 and the inner end portion 562 is smaller in the pre-wind state than in the natural state. Consequently, in the return spring 560, in the pre-winding state, the distance between the adjacent springs changes in the radial direction orthogonal to the rotation axis 03, corresponding to the position in the circumferential direction about the rotation axis 03.
As shown in FIG. 19, the return spring 560 extends along the spiral path that approaches the Archimedean curve with respect to a position offset from the axis of rotation 03 on the date hand wheel 550 to that
Side of the inner end portion 562 is in a state of being wound up and the torque is being generated. Even in a state in which the date hammer 540 is in any position from the starting position to the end position, the return springs 560 which are adjacent to one another are separated from one another and self-contact is avoided.
(Operation of the reset mechanism) The operation of the reset mechanism 511 configured as described above will now be described.
[0165] As described above, the date hand drive wheel 512 rotates once in a day. The date finger 513, which is provided in the date hand drive wheel 512, rotates once in a day in synchronization with the date hand drive wheel 512.
The forehead portion 515 of the date finger 513 abuts against the teeth 521 of the date transmission wheel 520 by the rotation, and then presses the teeth 521 when time passes. Furthermore, the time at which the forehead portion 515 of the date finger 513 abuts the teeth 521 of the date transmission wheel 520 is generally set to a predetermined time before midnight when the day changes (e.g., from 11:00 p.m. to midnight on that date next day). Further, when the teeth 521 of the date transfer wheel 520 are pressed through the end portion 515 of the date finger 513 and rotated at a predetermined angle, the distal end portion of the date lever spring portion 531 goes over the teeth 521 and engages with the next tooth 521. As a result, rotates the date transmission wheel 520 by one step once in a day with a predetermined angular distance and rotates once in a month.
The date column wheel 525 rotates one step at a time in a day in synchronization with the date transmission wheel 520 and rotates once in a month.
[0168] Here, the date hammer 540 moves from the home position to the end position when the cam arm portion 542 relatively moves from the innermost portion 526b of the cam surface 526 against the outermost portion 526a by the rotation of the date column wheel 525. Thus, the date hand wheel 550, which meshes with the fan-shaped gear section 541 of the date hammer 540, rotates one step once in a day. Furthermore, the date hand 8, which is attached to the date hand wheel 550, is moved by a value for a day approximately at midnight when the day changes, in accordance with the rotation of the date hand wheel 550. In this way, the date hand 8 moves by one Level from the first to the last day of the month.
As described above, in the return spring 560 of the present embodiment, in the pre-winding state, the distance between the adjacent springs in the radial direction orthogonal to the rotation axis 03 changes according to the position in the circumferential direction around the rotation axis 03 In configuration, the same function and effect can be achieved as that of the constant force spring 100 of the first embodiment.
[0170] Furthermore, since the reset mechanism 511 of the present embodiment includes the return spring 560 that generates a desired torque, it is possible to suppress the failure of the torque applied to the date hand wheel 550. As a result, it is possible to suppress that the torque applied to the date hand wheel 550 is insufficient and the repetitive movement of the date hand 8 is disturbed.
[Sixth Embodiment] A sixth embodiment will be described below with reference to FIGS. 20 to 27. A clock 601 of the sixth embodiment differs from the clock 1 of the first embodiment in that a calendar mechanism 611 that directly has a date indicator 9 drives, is provided. Furthermore, the configuration is the same as in the first embodiment except that described below.
Fig. 20 is an external view of the watch according to the sixth embodiment.
As shown in Fig. 20, the watch 601 is provided with a calendar display section 601a to display the date. The calendar display section 601 a comprises a date window 3a, designed as a dial 3 and date numbers 9a, which are displayed on the date indicator 9, which will be described later and is specified by the date window 3a.
Fig. 21 is a plan view when the calendar mechanism is viewed from below. In addition, in Fig. 21, part of a component of the configuration of the calendar mechanism is broken and shown.
As shown in FIG. 21, a work 610 includes the date indicator 9 described above and a calendar mechanism 611 which directly drives the date indicator 9. The date indicator 9 is an annular member which is rotatably attached to the main plate 23. In the date indicator 9, the date numerals (see Fig. 20) representing days 1 to 31 are sequentially displayed along the circumferential direction. A plurality of tooth portions 9 b are formed on the inner peripheral surface of the date indicator 9. The plurality of tooth portions 9b are formed so that they protrude inward in the radial direction and at a distance in the circumferential direction.
The calendar mechanism 611 mainly includes a date indicator drive wheel 612, a control spring of the date indicator drive wheel 690 and a date lever spring 695.
The date indicator drive wheel 612 rotates once in a day (24 hours) based on the rotation of an hour wheel 20. The date indicator drive wheel 612 rotates in an arrow direction A of the drawing about an axis of rotation 04 when the work 610 is running normally. Hereinafter, the direction of rotation of the date indicator drive wheel 612 during normal running is referred to as a forward direction. The rotation of the hour wheel 20 is transmitted to the date indicator drive wheel 612 via a first intermediate date wheel 613 and a second intermediate date wheel 614, which mesh with each other. The date indicator drive wheel 612 includes: a date gear 620 that rotates once in a day in synchronization with the rotation of the hour wheel 20; a date finger unit 630, which is arranged rotatably about the axis of rotation 04 with respect to the date transmission 620; and a date function spring 680 (see FIG. 23) which applies the torque between the date transmission 620 and the date finger unit 630.
Fig. 22 is a plan view when the date indicator driving wheel is viewed from below. Fig. 23 is a plan view when the date indicator driving wheel is viewed from above. Fig. 24 is a sectional view taken along the line XXIV-XXIV of Fig. 22. Furthermore, in Fig. 22, a part of the date indicator drive wheel is broken and shown in the drawing.
As shown in FIGS. 23 and 24, the date transmission 620 includes a transmission main body 621 which meshes with the second intermediate date wheel 614 (see FIG. 21) and a spring pin 622 which is held by the transmission main body 621. The transmission main body 621 is arranged rotatably about the axis of rotation 04. A through hole is formed in the center of the transmission main body 621, through which a date circle 632 is inserted, which will be described later. The spring pin 622 is held by the gear main body 621 in a position eccentric to the axis of rotation 04. As a result, the spring pin 622 rotates about the axis of rotation 04 in synchronization with the rotation of the transmission main body 621. The spring pin 622 comprises a shaft section 623 which is fixed to the transmission main body 621 and a flange section 624 which projects outward in the radial direction from the shaft section 623. The shaft portion 623 protrudes upward from the transmission main body 621. The flange portion 624 is formed in a disk shape. The flange portion 624 is provided in the intermediate area on the shaft portion 623 in the up-down direction.
As shown in FIGS. 22 and 24, the date finger unit 630 includes the date circle 631, a date finger 640, a date finger spring 650, a finger press 660 and a spring press 670.
As shown in FIG. 24, the date circle 631 includes a central tube 632 which is arranged coaxially with the transmission main body 621 of the date transmission 620 and a finger seat 633 which protrudes from the central tube 632. The central pipe 632 is relatively rotatably inserted in the through hole of the transmission main body 621. The central tube 632 protrudes on both the upper and lower sides with respect to the transmission main body 621. The finger seat 633 is arranged to overlap the lower surface of the transmission main body 621. The finger seat 633 is formed in an annular shape which protrudes outward in the radial direction from the central tube 632 and extends over the entire circumference along the circumferential direction.
As shown in Fig. 22, the date finger 640 is arranged to overlap the lower surface of the finger seat 633. The date finger 640 is located along the outer peripheral edge of the finger seat 633 when viewed in the down-up direction. The date finger 640 is rotatably held on the finger seat 633 in an intermediate area in the circumferential direction about the axis of rotation 04. In particular, the date finger 640 is rotatably held by a pin which projects downward from the finger seat 633. The date finger 640 includes a finger main body 641 that projects in the forward direction of rotation of the date indicator drive wheel 612 from the center of rotation and an arm 642 that extends in an opposite direction of rotation of the date indicator drive wheel 612 from the center of rotation. The arm 642 is configured to be configured to come into contact with the outer peripheral surface of the central tube 632 of the date circle 631. A distal end portion 641a of the finger main body 641 is formed to be configured to protrude outward in the radial direction from the finger seat 633 when viewed in the up-down direction. A state in which the distal end portion 641 a of the finger main body 641 protrudes most from the finger seat 633 is a state in which the arm 642 is in contact with the outer peripheral surface of the central tube 632 of the date circle 631. In other words, the arm 642 regulates the protruding area of the finger main body 641 from the finger seat 633.
The finger main body 641 is provided with an engagement surface 641b which is oriented in the forward rotation direction of the date indicator drive wheel 612 and with a sliding contact surface 641c which is oriented toward the side opposite to the side of the rotation axis 04. The engaging surface 641b extends from the distal end portion 641a of the finger main body 641 to the rotation axis 04. The sliding contact surface 641c extends from the distal end portion 641a of the finger main body 641 in the reverse rotation direction of the date indicator drive wheel 612 to the rotation axis 04 side in a gentle to the circumferential direction State bent around the axis of rotation 04. The finger main body 641 is arranged in a position in which the engaging surface 641b can come into contact with the tooth portion 9b of the date indicator 9 when the date finger unit 630 rotates in the forward rotation direction (see also FIG. 21). The finger main body 641 is shifted inward in the radial direction when the sliding contact surface 641c comes into contact with the tooth portion 9b of the date indicator 9 when the date finger unit 630 rotates in the reverse rotation direction.
Date finger spring 650 tensions date finger 640. Date finger spring 650 is arranged to overlap the lower surface of finger seat 633. The date finger spring 650 includes a base portion 651 which is held firmly on the finger seat 633 and a spring main body 652 which extends from the base portion 651 in the forward direction of rotation of the date indicator drive wheel 612 and comes into contact with the arm 642 of the date finger 640. The base portion 651 is held by a pin that extends downward from the finger seat 633. The spring main body 652 comes into contact with the arm 642 of the date finger 640 from the outside in the radial direction. The spring main body 652 pushes the arm 642 inward in the radial direction by a stored force of the elastic deformation. Accordingly, the date finger 640 is stretched in a direction in which the arm 642 comes into contact with the outer peripheral surface of the central tube 632 of the date circle 631. In other words, the date finger 640 is stretched in the direction in which the distal end portion 641a of the finger main body 641 protrudes outward in the radial direction from the finger seat 633 when viewed in the up-down direction.
The finger presser 660 regulates the downward movement of the date finger 640 and the date finger spring 650. The finger presser 660 is arranged on the side, opposite the finger seat 633 via the date finger 640 of the date finger spring 650. Furthermore, there can be a gap between the finger presser 660 and the date finger 640 and the date finger spring 650 may be provided. The finger presser 660 is designed in a disk shape, having an essentially the same outside diameter as the finger seat 633, and is arranged coaxially with the finger seat 633. At the center of the finger presser 660, a through hole is formed in which the lower end portion of the central tube 632 of the date circle 631 is inserted. Furthermore, a through hole is formed in the finger presser 660, into which a pin is inserted, which protrudes from the finger seat 633. The finger presser 660 is permanently provided on the date circle 631.
As shown in FIG. 23, the spring press 670 holds a date function spring 680 between the spring press 670 and the transmission main body 621 of the date transmission 620. The spring press 670 is arranged above the transmission main body 621 of the date transmission 620. The spring press 670 is formed in a disk shape with a diameter smaller than that of the transmission main body 621 of the date transmission 620 and is arranged coaxially with the transmission main body 621 of the date transmission 620. At the center of the spring press 670, a through hole is formed into which the upper end portion of the central tube 632 of the date circle 631 is inserted. The spring press 670 is permanently provided on the date circle 631.
[0187] The spring press 670 is formed with a spring pin guide hole 671 and a control spring engagement portion 672. In the spring pin guide hole 671, the upper end portion of the shaft portion 623 of the spring pin 622 is inserted in the date gear 620. The spring pin guide hole 671 extends in an arc shape around the axis of rotation 04, so that the displacement of the spring pin 622 about the axis of rotation 04 is possible. The spring pin guide hole 671 includes a lower end 671a which is provided in the forward direction of rotation of the date indicator drive wheel 612 and an upper end 671b which is provided in the reverse direction of rotation of the date indicator drive wheel 612. The control spring engagement portion 672 is a recess formed on the outer peripheral surface of the spring press 670. The control spring engagement portion 672 is formed near the lower end 671a of the spring pin guide hole 671. The rule spring guide portion 672 includes a spring engagement surface 672a that is oriented in a forward rotation direction of the date indicator drive wheel 612. The spring engagement surface 672a is provided at a position that overlaps the flange portion 624 of the spring pin 622 when viewed in the up-down direction in a state where the upper end portion of the shaft portion 623 of the spring pin 622 at the lower end 671a of the spring pin guide hole 671 is positioned.
As shown in FIGS. 23 and 24, the date function spring 680 is arranged between the transmission main body 621 of the date transmission 620 and the spring press 670 of the date finger unit 630. The date function spring 680 is a coil spring which is constructed in the same manner as the constant force spring 100 described above. The inner end portion 682 of the date function spring 680 is attached to the date finger unit 630. In particular, the inner end portion 682 of the date function spring 680 is held firmly on the date circle 631 via an annular fixing ring 684, extrapolated from the central tube 632 of the date circle 631. The fixing ring 684 is arranged between the transmission main body 621 of the date transmission 620 and the spring press 670. The outer end portion 681 of the date function spring 680 is attached to the date transmission 620. In particular, the outer end portion 681 of the date function spring 680 is held by the spring pin 622 via an annular fixing piece 685, extrapolated from the shaft portion 623 of the spring pin 622. The fixing piece 685 is arranged between the gear main body 621 of the date gear 620 and the flange portion 624 of the spring pin 622. In the present embodiment, the date function spring 680 is elastically deformed so as to reduce the diameter when winding and fastening the inner end portion 682 with respect to the outer end portion 681 and to generate the torque.
As shown in Fig. 23, the date function spring 680 is fixed to the date gear 620 and the date finger unit 630 so that the spring pin 622 is positioned near the upper end 671b of the spring pin guide hole 671 in a state in which the relative torque is not from the outside between the date transmission 620 and the date finger unit 630. The date function spring 680 is wound when the outer end portion 681 moves in the forward direction of the date indicator drive wheel 612 with respect to the inner end portion 682 and generates the torque in the forward direction of the date indicator drive wheel 612 to the inner end portion 682. Accordingly, the date function spring 680 tensions the date finger unit 630 in the forward direction of rotation of the date indicator drive wheel 612.
Comparable to the constant force spring 100 shown in FIG. 8, the outer end portion 681 of the date function spring 680 is arranged in a position closer to the rotation axis 04 than the position in the natural state in the pre-winding state of the date function spring 680. Furthermore, the pre-winding state of the date function spring 680 is in a state in which the outer end portion 681 of the date function spring 680 is attached to the date transmission 620, the inner end portion 682 of the date function spring 680 is attached to the date finger unit 630 and the torque is not generated. The distance between the outer end portion 681 and the inner end portion 682 is smaller in the downwind state than in the natural state. Consequently, in the date function spring 680 in the pre-winding state, a distance between adjacent springs changes in the radial direction orthogonal to the rotation axis 04 according to the position in the circumferential direction about the rotation axis 04.
[0191] Although not shown, the date function spring 680 extends along a spiral path approximating the Archimedean curve with respect to a position offset from the axis of rotation 04 to the side of the inner end portion 682 in a wound and torque-generating state. Even in a state in which the spring pin 622 is in any position of the spring pin guide hole 671, the adjacent date function springs 680 are separated from one another and self-contact is avoided.
As shown in Fig. 21, the control spring of the date indicator driving wheel 690 is formed in a cantilevered lever shape. The base end portion of the rule spring of the date indicator drive wheel 690 is fixedly provided on the main plate 23 or the like. A distal end portion 690a of the control spring of the date indicator drive wheel 690 is slidably provided on the outer peripheral surface of the spring press 670. The distal end portion 690a of the control spring of the date indicator drive wheel 690 is oriented in the reverse direction of rotation of the date indicator drive wheel 612. The distal end portion 690a of the rule spring of the date indicator drive wheel 690 is engaged with the spring engagement surface 672a of the rule spring engagement portion 672 of the spring press 670. The rule spring of the date indicator drive wheel 690 is formed so that the flange portion 624 of the spring pin 622 of the date transmission 620 in contact with the distal end 620 a state in which the distal end portion 690a is engaged with the control spring engagement portion 672 of the spring press 670.
[0193] The date lever spring 695 corrects the position of the date indicator 9 in the direction of rotation. The date lever spring 695 is provided with an elastically deformable date lever spring section 696, the distal end section of which is a free end. The distal end portion of the date lever spring portion 696 can be engaged with the tooth portion 9b of the date indicator. The date lever spring 695 corrects the rotation of the date indicator 9 by the fact that the distal end portion engages in the tooth portion 9b of the date indicator 9. Accordingly, the date indicator 9 can rotate a step once a day by the same angular distance as the spacing angle of the plurality of tooth portions 9b.
(Function of the Calendar Mechanism) The following explains the function of the calendar mechanism 611 configured as described above with reference to Figs. 21 and 25-27.
25 to 27 are views for explaining the function of the calendar mechanism and are top views when a portion of the calendar mechanism is viewed from above.
[0196] As described above, the date gear 620 of the date indicator drive wheel 612 rotates once in a day in the forward direction in synchronization with the rotation of the hour wheel 20. When the date gear 620 rotates in the forward direction, the rotational force is applied to the date finger unit 630 via the date function spring 680 transmitted, and consequently the date finger unit 630 also rotates in the forward rotation direction.
As shown in Fig. 21, when the date finger unit 630 rotates, the distal end portion 690a is the rule spring of the date indicator drive wheel 690 engaged with the rule spring engagement portion 672 of the spring press 670 at one degree for each rotation. Therefore, a state in which the rotation of the date finger unit 630 in the forward rotation direction is regulated is applied. Accordingly, the date gear 620 rotates in the forward rotation direction with respect to the date finger unit 630. At this time, the date gear 620 rotates while the shaft portion 623 of the spring pin 622 rotates in the forward rotation direction from the vicinity of the upper end 671b (see FIG. 23) of the spring pin guide hole 671 the date finger unit 630 moves. The date gear 620 rotates in the forward direction while the date function spring 680 is wound. As a result, the date function spring 680 is wound as the torque increases to tension the date finger unit 630 in the forward rotation direction.
Further, as shown in Fig. 25, when the date gear 620 continues to rotate, the shaft portion of the spring pin 622 reaches the vicinity of the lower end 671a (see Fig. 23) of the spring pin guide hole 671. Then, the flange portion 624 of the spring pin comes 622 in contact with the distal end portion 690a of the rule spring of the date indicator drive wheel 690 and pushes the distal end portion 690a of the rule spring of the date indicator drive wheel 690 radially outward. Furthermore, the engagement between the control spring of the date indicator drive wheel 690 and the control spring engagement portion 672 of the spring press 670 is released. Furthermore, the date indicator drive wheel 612 is set up so that the engagement between the control spring of the date indicator drive wheel 690 and the control spring engagement portion 672 of the spring press 670 is released at midnight.
[0199] Accordingly, the coiled date function spring 680 is unwound at the same time, and the date finger unit 630 rotates rapidly in the forward rotation direction. In addition, as shown in FIG. 26, the finger main body 641 of the date finger 640 rapidly moves in the forward rotation direction of the date indicator drive wheel 612, and the engaging surface 612b can come into contact with the tooth portion 9b of the date indicator 9 and rotate the date indicator 9. Accordingly, the date indicator 9 can turn immediately while the engagement from the date lever spring portion 698 is released.
Furthermore, as shown in Fig. 27, when the date indicator 9 rotates, the distal end portion of the date lever spring portion 696 is again engaged with the next tooth portion 9b of the date indicator 9. As a result, it is possible to immediately obtain the date to switch, which is specified on the date window 3a of the dial 3 by a day number.
As described above, in the date function spring 680 of the present embodiment, in the pre-wind state, the distance between adjacent springs changes in the radial direction orthogonal to the rotation axis 04, according to the position in the circumferential direction around the rotation axis 04 Configuration, the same function and effect as that of the constant force spring 100 of the first embodiment can be obtained.
[0202] Further, since the calendar mechanism 611 of the present embodiment includes the date function spring 680 that generates a desired torque, it is possible to suppress the torque failure applied between the date transmission 620 and the date finger unit 630. Accordingly, it is possible to suppress the failure of the torque transmitted to the date indicator 9 due to the failure of the torque applied to the date finger unit 630. Accordingly, the calendar mechanism 611 can be used, in which a reliable data input function is possible.
[0203] Furthermore, in the present embodiment, the date indicator 9 displays the number corresponding to the date as a date character 9a, but the present invention is not limited to this. The day of the week can be displayed in the date indicator 9 as a date symbol.
Furthermore, the present invention is not limited to the embodiments described above with reference to the figures, and various modification examples are conceivable within the technical area.
For example, in the embodiment described above, the constant force spring 100, 200, 300 and 400 extends along the Archimedean curve in the natural state. However, the present invention is not limited to this, and the constant force spring may be formed such that the distance between adjacent springs in the natural state becomes narrower when oriented radially outward, or may be configured such that the distance between the neighboring springs in the natural state becomes wider when oriented radially outward.
[0206] Furthermore, in the second embodiment described above, a configuration is described in which the constant force spring 200 includes the curve portion 206 and the outer end portion 201 is offset outward in the radial direction. Comparably, for example, in the constant force spring 400 of the fourth embodiment, the outer end portion may be formed to be replaced with a curved portion inward in the radial direction. Thus, when attaching the constant force spring including the cam portion to the constant torque mechanism of the comparable type in which the outer end portion of the constant force spring having no cam portion is fixed in position in the natural state, the outer end portion of the constant force spring may be arranged at a position separate from the first rotation axis O1.
Furthermore, in the embodiment described above, although a case has been described as an example in which the coil spring of the present invention is used as a constant force spring of the constant torque mechanism, the present invention is not limited to this. For example, the coil spring of the present invention can be used as a hair spring.
Further, it is possible to appropriately replace the configuration element of the above-described embodiments with a known configuration element without departing from the spirit of the present invention, and each of the above-described embodiments can be combined with each other accordingly. For example, the reset mechanism 511 of the fifth embodiment or the calendar mechanism 611 of the sixth embodiment can be combined with a coil spring, comparable to the constant force spring of one of the second to fourth embodiments.

权利要求:
Claims (11)
[1]
claims
1. A coil spring for a watch wound about an axis to generate torque, comprising: an outer end portion attached to a first component; and an inner end portion attached to a second component, wherein in the pre-wind state in which the outer end portion is attached to the first component, the inner end portion is attached to the second component and the torque is not generated Distance between adjacent springs changes in a radial direction orthogonal to the axis, corresponding to a position in a circumferential direction around the axis.
[2]
2. The coil spring of claim 1, wherein the coil spring is configured to generate the winding and fastening torque from the pre-wind state, and wherein in the pre-wind state, when viewed in an axial direction of the axis, the distance at a first Half line extending from the axis to the outer end portion is narrower than the distance on a second half line extending from the axis to one side opposite to the first half line.
[3]
3. The coil spring of claim 1, wherein the coil spring is configured to generate the winding and expanding torque from the pre-wind state, and wherein, in the pre-wind state, when viewed in an axial direction of the axis, the distance at one first half line extending from the axis to the outer end portion is wider than the distance on a second half line extending from the axis to the side opposite the first half line.
[4]
4. A coil spring according to any one of claims 1 to 3, wherein at least a portion of the coil spring extends along an Archimedean curve in a state in which no tension is applied to the coil spring.
[5]
5. A coil spring according to claim 2, wherein at least a part of the coil spring extends along an Archimedean curve in a state in which no tension is applied to the coil spring, and wherein the center of the Archimedean curve is provided on one side opposite to the inner one End section over the axis.
[6]
6. A torque generator comprising:
the coil spring according to one of claims 1 to 5;
the first component to which at least one of the outer end portion and the inner end portion of the coil spring is attached; and the second component to which the other of the outer end portion and the inner end portion is attached.
[7]
7. The torque generator according to claim 6, which is a constant torque mechanism, further comprising: an input rotating body, which includes the first component, rotates by the force of a power source and fills the coil spring with the force;
an output rotating body that includes the second component, rotates by the force from the coil spring, and transmits the force of the coil spring to an escapement; and a cycle control mechanism that intermittently rotates the input rotating body with respect to the output rotating body based on the rotation of the output rotating body.
[8]
8. The torque generator of claim 6, which is a reset mechanism that resets a pointer between a home position and an end position, further comprising:
a rotating section comprising the first component and rotating in synchronization with the pointer; and a support portion that includes the second component and rotatably supports the rotation portion.
[9]
9. The torque generator of claim 6, which is a calendar mechanism that switches a date number displayed on a date window of a date dial, further comprising:
a date transmission which includes the first component and rotates in synchronization with rotation of an hour wheel; and a date finger that includes the second component and the date finger is provided to be engageable and detachable from a tooth portion of a date indicator on which the date number is displayed and is provided to be rotatable coaxially with the date transmission with respect to the date transmission to be.
[10]
10. A movement comprising:
the torque generator according to one of claims 6 to 9.
[11]
11. A watch comprising:
the clockwork according to claim 10.

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同族专利:

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公开号 | 公开日

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JP2020008560A|2020-01-16|

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JP6626594B1|2019-12-25|

引用文献:

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法律状态:

优先权:

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申请号 | 申请日 | 专利标题

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JP2018126190|2018-07-02|

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JP2019060567A|JP6626594B1|2018-07-02|2019-03-27|Spiral spring, torque generator, watch movement and watch|

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