JP6548240B1 - Hairspring, governor, watch movement and watch - Google Patents

Abstract

There is provided a hairspring capable of easily and accurately performing isochronous adjustment without using a slow and steep needle. A hairspring 30 includes a hairspring main body 31 in which an inner end portion 31a side is fixed to a first member 20 and an outer end portion 31b side is held by a second member 40. The hairspring main body 31 is wound. The outer end portion is held by the second member 40 so that the outer end side rotates in the plane while the insertion angle θ is within the first angle range, or the outer end portion is within the second angle range. The balance spring body 31 is held by the second member 40 so that the side moves in the radial direction, and the mainspring main body 31 changes isochronously due to in-plane rotation when the winding angle is within the first angle range. The amount of isochronous changes due to movement in the radial direction when the amount is larger than the amount of isochronous change that changes due to movement in the radial direction and the entrainment angle is within the second angle range. When the amount of change changes due to in-plane rotation Larger than the amount of change. [Selection] Figure 5

Description

  The present invention relates to a balance spring, a governor, a watch movement and a watch.

In a mechanical watch, it is important that the balance with the balance is set within a predetermined specified value. This is because when the vibration period deviates from the specified value, the rate (degree of delay of the watch, the degree of advance) of the mechanical watch changes.
As a method for adjusting the rate, in general, the length (effective length) of a balance spring in which the inner end is fixed to the balance of the balance of the balance and the outer end is fixed to the balance with a loose needle The way to do it is known.

The needle is mainly rotatable about a central axis of the balance, and mainly includes a whisker holder disposed radially outward of the balance spring and a whisker disposed radially inward of the balance spring. Thereby, the balance spring is located between the support and the beard and is configured to vibrate radially therebetween.
When adjusting the rate using this kind of slow needle, generally, after adjusting the position of the beard holding fixing the outer end of the balance spring, turn the slow needle around the center axis of the balance. Adjust the position of the beard holder and the beard in the lengthwise direction of the balance spring. Thereby, when the balance spring vibrates, it is possible to adjust the effective length between the contact point when contacting the beard holder or the beard bar and the inner end of the balance spring, and it is possible to adjust the rate. It is assumed.

Furthermore, when performing rate adjustment, by adjusting the gap amount (swing width) which is the gap between the beard holder and the beard bar, it is also known that the speed and speed needle can perform isochronous adjustment (swing adjustment) of the rate. It is done.
The balance spring repeats contact movement with the beard holder, separation from the beard holder, contact with the beard bar, separation from the beard bar during one reciprocation of the balance so that the effective length is alternately short and long. repeat. In addition, since the strength of the vibration of the hairspring changes in accordance with the amount of winding, the time for which the hairspring contacts the beard or the beard changes. Therefore, for example, the time during which the effective length is short may be long, which may affect the isochronism of the rate.

  Therefore, it is performed to adjust the isochronism by changing the strength of the spring constant in one cycle according to the swing angle by performing the up-and-down adjustment with the slow and fast needle. It is considered important to perform isochronous adjustment particularly when assembling a high precision mechanical watch.

  However, when the slow hand is not provided, for example, when time adjustment of the speed governor is performed by a variable inertia balance wheel or the like, isochronous adjustment using the slow hand can not be performed. Therefore, the isochronism of the assembled governor is dependent on the accuracy, the assembly position, etc. of each component part, and the isochronous variation occurs.

  In addition, when isochronous adjustment is performed without using the slow and fast hands, for example, there is a method of manually correcting the position, the shape, etc. of the outer end side of the hairspring mainly using tweezers or the like. Are known. Furthermore, as a balance spring for use in this type of correction, a stiffening at least partially compensates for movement speed variation of the movement depending on the vibration amplitude of the balance generated by the escapement on the outermost peripheral portion of the balance spring. There is known a hairspring which forms a part (see, for example, Patent Document 1).

JP-A-2014-525591

  However, in the conventional method of correcting the outer end side of the hairspring, the amount of adjustment is not quantitative, and very delicate work is required. Therefore, the degree of difficulty of isochronous adjustment is high, and it takes a lot of time and effort for isochronous adjustment, and there is room for improvement.

  The present invention has been made in consideration of such circumstances, and an object thereof is to provide a balance spring, a speed governor, and the like capable of performing isochronous adjustment easily and accurately without using a slow speed needle. A watch movement and a watch.

(1) The hairspring according to the present invention is fixed to the first member whose inner end side is rotated about the axis, and the outer end side is held by the second member, and from the inner end to the outer end And a spiral spring main body formed in a spiral shape with a predetermined number of turns in a plane intersecting the axis, and viewed from the axial direction, the unwinding position of the mainspring and the axis And a second imaginary line connecting the axis line with the holding position of the balance main body held by the second member and the first imaginary line connecting When it is a corner, the mainspring of the hairspring is rotated by the second member such that the outer end rotates in the plane with the winding angle falling within a predetermined first angle range. Held or within a second predetermined angle range And the outer end portion is held by the second member so that the outer end moves in the radial direction of the mainspring, and the mainspring further has the winding angle within the first angle range. When it is settled, the isochronous change amount which changes due to the rotation in the plane is larger than the isochronous change amount which changes due to the movement in the radial direction, and the winding angle is larger than the isochronous change amount. When the angle is within the two angle range, the isochronous change amount which is changed by the movement in the radial direction is larger than the isochronous change amount which is changed by the rotation in the plane.

  According to the hairspring pertaining to the present invention, in the state where the winding angle falls within the first angle range, the outer end side of the hairspring main body is rotated in the plane, or the winding angle is the second angle range It is possible to perform isochronous adjustment by moving the outer end side of the mainspring in the radial direction in the state of being accommodated inside.

  In particular, when the winding angle is within the first angle range, the mainspring of the hairspring is isochronous in which the isochronous variation that changes due to in-plane rotation changes due to radial movement. Larger than the amount of change. That is, the in-plane rotation operation can change isochronism more sensitively than the movement operation in the radial direction. On the contrary, when the winding angle is within the second angle range, the mainspring of the hairspring is changed by the movement in the radial direction, and the amount of isochronous change is changed by the rotation in the plane It is larger than the isochronous change amount. That is, movement in the radial direction can change isochronism more sensitively than rotation in the plane.

Therefore, even if the outer end side of the mainspring is either rotated in the plane or moved in the radial direction, the isochronous property is changed by the amount of change caused by either operation. It is possible. That is, it is possible to change isochronism by the amount of change caused by one operation while being less susceptible to the other operation. In addition, it is possible to make the amount of change in isochronism that changes due to the rotation operation or the movement operation approximately in proportion to the rotation operation amount or the movement operation amount. Therefore, the isochronism can be changed by the change amount corresponding to the rotation operation or the movement operation on the outer end side of the hairspring main body, and the isochronous adjustment can be performed quantitatively.
From the above, it is possible to perform isochronous adjustment quantitatively and at the same time easily and accurately without using the slow and fast hands.

(2) A direction in which the second member advances in the winding direction of the mainspring with respect to when the winding angle is zero is a positive direction of the winding angle, and the opposite direction is the winding angle. When the negative direction is set, the winding angle is (−125 ° ± 5 ° to −215 ° ± 5 °) or (−35 ° ± 5 ° to + 55 ° ± 5 °) as the first angle range And the second angle range is (−125 ° ± 5 ° to −35 ° ± 5 °), or (+ 55 ° ± 5 ° to + 145 ° ± The angle range may be included within the range of 5 degrees.

In this case, when the winding angle is included in the range of (−125 ° ± 5 ° to −215 ° ± 5 °) or (−35 ° ± 5 ° to + 55 ° ± 5 °) In the mainspring of the hairspring, the isochronous change amount which is changed by the rotation in the plane is larger than the isochronous change amount which is changed by the movement in the radial direction. In addition, when the winding angle is included in the range of (−125 ° ± 5 ° to −35 ° ± 5 °) or (+ 55 ° ± 5 ° to + 145 ° ± 5 °) The amount of isochronous change that changes due to the movement of is larger than the amount of isochronous change that changes due to in-plane rotation.
Therefore, when the winding angle is included in the range of (-125 degrees ± 5 degrees to −215 degrees ± 5 degrees) or (−35 degrees ± 5 degrees to +55 degrees ± 5 degrees) Turn the outer end side of the shaft, or the winding angle is within the range of (-125 ° ± 5 ° to -35 ° ± 5 °) or (+ 55 ° ± 5 ° to + 145 ° ± 5 °) When included, by moving the outer end side of the hairspring in the radial direction, it is possible to change isochronism by the amount of change caused by each operation, and perform isochronous adjustment. it can.

(3) The first angle range is an angle range in which the winding angle is included in a range of (-170 degrees ± α degrees) or (+10 degrees ± α degrees), and the second angle range is The winding angle is in the range of (-80 degrees ± α degrees) or (+100 degrees ± α degrees), and α is an angle in the range of 5 degrees to 30 degrees It may be.

In this case, when the winding angle is included in the range of (-170 degrees ± α degrees) or (+10 degrees ± α degrees), the mainspring of the hairspring is changed by rotation in the plane, etc. The maximum amount of change in sex is maximized, and conversely, the maximum amount of change in isochronism, which changes due to radial movement, is minimized. Therefore, isochronism changes with high sensitivity according to the in-plane rotation operation, but becomes insensitive to the movement operation in the radial direction, and hardly changes for the movement operation.
Therefore, when the winding angle is included in the range of (-170 degrees ± α degrees) or (+10 degrees ± α degrees), the amount of change caused by the in-plane rotation operation The isochronism can be changed more effectively, and isochronous adjustment can be performed more easily and accurately.

Similarly, when the winding angle is included in the range of (−80 ° ± α °) or (+ 100 ° ± α °), the mainspring of the hairspring is isochronous which changes due to radial movement The maximum change amount is maximum, and conversely, the maximum isochronous change amount changing by rotation in the plane is minimum. Therefore, although isochronous changes with high sensitivity with the movement operation in the radial direction, it becomes insensitive to the rotation operation in the plane, and hardly changes for the rotation operation.
Therefore, when the winding angle is included in the range of (-80 degrees ± α degrees) or (+100 degrees ± α degrees), the amount of change caused by the operation of moving in the radial direction The isochronism can be changed more effectively, and isochronous adjustment can be performed more easily and accurately.

In the first angle range, the above-mentioned effects can be achieved more effectively as the above-mentioned α becomes smaller from 30 degrees to 5 degrees. For example, (-170 degrees ± 25 degrees) or (+ 10 degrees ± 25 degrees) than when the winding angle is included in the range of (-170 degrees ± 30 degrees) or (+ 10 degrees ± 30 degrees) If one is included in the range, the above-mentioned effects can be achieved more effectively.
Similarly, in the second angle range, as the above-described α decreases from 30 degrees to 5 degrees, the above-described effects can be achieved more effectively. For example, (−80 ° ± 25 °) or (+ 100 ° ± 25 °) than when the winding angle is included in the range of (−80 ° ± 30 °) or (+ 100 ° ± 30 °) If one is included in the range, the above-mentioned effects can be achieved more effectively.
In any case, the smaller the value of α is, the more effective the above-mentioned effects can be achieved. Specifically, it is conceivable to make α smaller by 30 degrees to 5 degrees.

(4) The first angle range is an angle range in which the winding angle is included in a range of (-170 degrees ± 5 degrees) or (+10 degrees ± 5 degrees), and the second angle range is The winding angle may be an angle range included in the range of (−80 ° ± 5 °) or (+ 100 ° ± 5 °).

  In this case, the above-described effects can be achieved more effectively.

(5) The first member may be a balance, and the inner end of the mainspring may be fixed to a balance in the balance.

  In this case, it can be used as a balance spring which can perform isochronous adjustment of the balance.

(6) The balance end of the balance spring has a swing angle of 200 degrees to 250 degrees by rotating the outer end side of the mainspring in the plane or moving the outer end side in the radial direction of the balance. An isochronous change may be made in a curve that includes extreme values within the range.

  In this case, when the swing angle performs isochronous adjustment within the range of 200 degrees to 250 degrees, for example, the sensitivity isochronous even if it is a minute operation (rotation operation, movement operation in the radial direction) It can be changed effectively and easily, and isochronous adjustment is easy to perform easily.

(7) The speed governor according to the present invention is combined with the hairspring, the balance, the second member, and the balance relative to the balance so as to be rotatable relative to the balance, and moves the second member. A support member that supports the support member, the support member rotatably supports the second member in the plane, or supports the second member movably in the radial direction of the stem.

In this case, the second member can be moved in the circumferential direction together with the support member by rotating the support member relative to the balance with respect to the balance, so that the winding angle of the hairspring is set to an arbitrary angle. can do. Thus, the winding angle can be appropriately set to fall within the first angle range or the second angle range. Furthermore, since the support member rotatably or radially movably supports the second member, the second member may be rotated first or moved in the radial direction according to the winding angle. As mentioned, the outer end of the balance spring can be displaced, as a result of which an isochronous adjustment can be made.
In particular, unlike in the conventional case where isochronous adjustment is performed using tweezers etc., after setting the winding angle appropriately, the isochronous adjustment is performed by a series of flow for rotating operation or moving operation. Since it is possible to carry out smoothly and it is possible to quantitatively change isochronism, it is possible to perform isochronous adjustment easily and appropriately.

(8) The watch movement according to the present invention includes the above-described governor.
(9) A watch according to the present invention includes the watch movement.

  In this case, since the above-described hairspring is provided, it is possible to obtain a high-performance watch movement and watch with less error in the rate by highly accurate isochronous adjustment.

  According to the present invention, isochronous adjustment can be easily and accurately performed without using a slow and fast hand. Therefore, it is possible to obtain a high performance watch movement and watch with less error in the rate.

It is a figure which shows 1st Embodiment concerning this invention, Comprising: It is an external view of a timepiece. FIG. 1 is a plan view of the movement. It is a perspective view of the governor shown in FIG. FIG. 4 is a cross-sectional view of the governor as taken along line A-A shown in FIG. 3. It is a top view of the governor shown in FIG. 3, Comprising: It is a top view which shows the relationship between a beard support, a balance spring, and a balance. It is a top view of a balance-less type balance spring. It is a top view of a hairspring of a winding mainspring type. It is a figure which shows the isochronous curve in the case where the winding angle is 0 degree, when not operating, when rotating operation, and when moving operation. It is a figure which shows the relationship between the isochronous change curve at the time of rotation operation, and the isochronous change curve at the time of movement operation. It is a figure which shows the relationship between the change curve of the largest change amount of isochronous change at the time of rotation operation, and the change curve of the largest change amount of isochronous change at the time of movement operation. FIG. 17 is a diagram showing the relationship between the change curve of the maximum change in isochronous change during rotation operation and the change curve of the maximum change in isochronal change during movement operation in an outer-end-less type balance spring . FIG. 17 is a view showing a relationship between a change curve of maximum change of isochronous change at the time of rotation operation and a change curve of maximum change of isochronous change at the time of movement operation in a winding-spring type of a winding spring type. . Change curves of maximum change of isochronous change during rotation operation and maximum change of isochronous change during movement operation for each type of outer-end, outer-end-less, and winding-type mainspring It is a figure which shows the relationship between and the change curve of. It is a figure which shows the relationship of the isochronous change curve which changes with rotation operation in four winding angles. It is a figure which shows the relationship of the isochronous change curve which changes with movement operation in four winding angles. In the case where the number of turns is 14 and the frequency of the balance is 8 vibrations, the maximum amount of change in isochronous change at the time of rotational operation for each of the outer-end type, outer-end-less type, and wound-up type spring of type It is a figure which shows the relationship between the change curve of, and the change curve of the largest change amount of the isochronous change at the time of movement operation. It is a perspective view of the governor which shows the modification of 1st Embodiment. FIG. 18 is a perspective view showing the relationship between a beard support, a balance spring and a balance as shown in FIG. 17; It is a top view which shows the relationship between the beard support and the balance spring shown in FIG. It is a perspective view of a speed governor showing a second embodiment according to the present invention. FIG. 21 is an enlarged plan view of the area around the beard shown in FIG. 20. It is a perspective view of the governor which shows 3rd Embodiment concerning this invention. It is a perspective view which shows the state which removed the whisker-hold from the state shown in FIG. It is a perspective view of the whisker-hold shown in FIG.

  Hereinafter, embodiments according to the present invention will be described with reference to the drawings. In the present embodiment, a mechanical timepiece is described as an example of the timepiece.

(Basic configuration of watch)
Generally, a mechanical body including a drive portion of a watch is referred to as a "movement". A state in which a dial and hands are attached to this movement and placed in a watch case to make it a finished product is referred to as a "complete" of the watch. Of the two sides of the main plate constituting the watch substrate, the side with the glass of the watch case (ie, the side with the dial) is referred to as the "back side" of the movement. Further, among the two sides of the main plate, the side with the case back lid of the watch case (ie, the side opposite to the dial) is referred to as the "front side" of the movement.
In the present embodiment, the direction from the dial to the case back cover will be described as the upper side, and the opposite side as the lower side.

First Embodiment
As shown in FIG. 1, the complete watch 1 according to the present embodiment includes a movement (the watch movement according to the present invention) 10 and at least information on time in a watch case consisting of a case back cover and a glass 2 (not shown). It has a dial 3 having a scale or the like shown, a hand including an hour hand 4 indicating the hour, a minute hand 5 indicating the minute, and a second hand 6 indicating the second.

  As shown in FIGS. 2 and 3, the movement 10 is provided with a main plate 11 and a train wheel holder and a balance holder 12 (not shown) disposed on the front side of the main plate 11. A front wheel train, an escapement (not shown) for controlling the rotation of the front wheel train, and a governor 13 for controlling the speed of the escapement are provided between the main plate 11 and the train wheel holder and the balance receiver 12. Mainly arranged. On the back side of the main plate 11, the dial 3 is disposed so as to be visible through the glass 2.

  The movement 10 of the present embodiment is an example of a movement 10 for a self-winding watch provided with a rotary weight 14. However, the movement is not limited to this case, and may be a hand-wound movement with a winding stem 15.

  The front wheel train mainly has a barrel car, a second wheel, a third wheel and a fourth wheel. In the present embodiment, the second wheel, third wheel and fourth wheel are not shown in order to make the drawing easy to see. The second hand 6 shown in FIG. 1 rotates based on the rotation of the fourth wheel and rotates at a rotational speed controlled by the escapement and speed governor 13, ie, one rotation per minute. The minute hand 5 is rotated based on the rotation of the second wheel or the rotation of the minute wheel which rotates with the rotation of the second wheel, and the rotation speed controlled by the escapement and the governor 13, ie, one hour Make one revolution. The hour hand 4 is rotated based on the rotation of an hour wheel that rotates with the rotation of the center wheel and pinion via the minute wheel, and the rotation speed controlled by the escapement and the speed governor 13, ie 12 It makes one revolution in time or 24 hours.

  The escapement includes an escape wheel (not shown) engaged with the fourth wheel, and an ankle (not shown) for causing the escape wheel to escape and rotate regularly, and the front wheel train with regular vibrations from the balance 20 described later Control.

As shown in FIG. 3 and FIG. 4, the speed governor 13 has a balance (first member according to the present invention) 20 that rotates back and forth (forward and reverse rotation) about a first axis O1 (axis according to the present invention). A pair of hairspring (second member according to the present invention) 40 for holding the hairspring 30 and the outer end 31b side of the hairspring main body 31 to be described later, and the balance 20 to be rotatable relative to the balance 20 around the first axis O1. And a whisker holder (support member according to the present invention) 50 for movably supporting the whisker holder 40.
In the present embodiment, the direction intersecting the first axis O1 in plan view is referred to as the radial direction, and the direction circling around the first axis O1 is referred to as the circumferential direction.

The balance 20 includes a balance 21 made rotatable around a first axis O1, and a balance 22 attached to the balance 21. A balance spring 30 is used as a motive power source, and a balance is steady around the first axis O1. Rotates forward and reverse with amplitude (swing angle).
An upper tenon portion 21a is pivotally supported by the upper bearing 60, and a lower tenon portion 21b is pivotally supported by a lower bearing (not shown) formed on the base plate 11 shown in FIG. A connecting arm portion 23 connected to the balance wheel 22 is fixed to an intermediate portion in the vertical direction of the balance stem 21, and a beard ball 24 and a swing seat 25 are fixed.

  The connection arm portion 23 is a member for connecting the balance 21 and the balance ring 22 in the radial direction, and the inner end is connected to the annular boss 26 fixed to the balance 21 by, for example, press fitting. The end is connected to the inner circumferential surface of the balance wheel 22. As a result, the balance wheel 22 is attached to the balance 21 via the connection arm portion 23, and rotates together with the balance 21 around the first axis O1. However, the number, the arrangement, and the shape of the connecting arms 23 may be changed as appropriate.

The beard ball 24 is disposed above the boss portion 26 and fixed to the balance 21 by, for example, press fitting.
The swing seat 25 is disposed below the boss portion 26 and fixed to the balance 21 by, for example, press fitting. The swing seat 25 has a large collar 25a and a small collar 25b located below the large collar 25a. The large collar 25a is formed of an artificial gemstone such as ruby, for example, and a rocking stone 27 for operating (swinging) an anchor is press-fitted and fixed, for example.

The upper bearing 60 is a cylindrical bearing frame 61, an upper hole stone 62 mounted in the bearing frame 61 and rotatably supporting the upper tenon portion 21a of the balance 21 and an upper side of the upper hole stone 62. And a stone holding spring 64 disposed on the upper support stone 63 supporting the upper tenon portion 21a of the stem 21 in the axial direction and further above the upper support stone 63 and fixing the upper support stone 63 to the bearing frame 61. And is considered to be a vibration resistant bearing.
However, the configuration of the upper bearing 60 is not limited to the above-described case, and any other configuration may be adopted as long as the upper tenon portion 21a of the balance 21 can be rotatably supported.

  The bearing frame 61 includes an upper frame 61a and a lower frame 61b whose outer diameter is smaller than that of the upper frame 61a, and is formed in a two-step cylindrical shape having different outer diameters. The bearing frame 61 is attached to the inside of the bearing cylinder portion 71 formed on the pedestal plate 70 of the balance 12 by fixing the lower frame 61 b by, for example, press fitting. The bearing frame 61 and the bearing cylindrical portion 71 are disposed coaxially with the first axis O1.

  For example, as shown in FIG. 2, the balance support 12 has a main body 72 extending in an arc shape in accordance with the shape of the watch case. A mounting hole 73 is formed in the main body portion 72, and the pedestal plate 70 is formed to be recessed in a step-like manner at a part of the outer edge portion. As shown in FIG. 2, the balance support 12 is fixed to the ground plate 11 by a fixing screw 74 using the mounting hole 73. However, the shape of the balance support 12 is not limited to the above case, and may be changed as appropriate.

  As shown in FIG. 4, in the pedestal plate 70, a through hole 75 penetrating the pedestal plate 70 up and down is formed coaxially with the first axis O1. The bearing cylindrical portion 71 is formed to rise upward from the pedestal plate 70 along the opening periphery of the through hole 75, and the inside thereof communicates with the through hole 75. Therefore, the lower frame 61 b of the bearing frame 61 is fixed to the inside of the bearing cylinder 71 and the through hole 75 by, for example, press fitting. The upper frame 61 a of the bearing frame 61 is disposed on the opening end of the bearing cylindrical portion 71 and is formed larger than the outer diameter of the bearing cylindrical portion 71.

As shown in FIGS. 3 to 5, the whisker holder 50 is rotatably fitted to the bearing cylindrical portion 71 of the balance support 12, whereby relative rotation about the first axis O 1 with respect to the bearing cylindrical portion 71 is possible. It is assumed.
The whisker support 50 extends radially outward from the connection ring 51 and the connection ring 51 fitted to the outside of the bearing cylinder 71, and holds the whisker 40 at the tip end side (outer end side). And movably supporting a bearding arm 52. Specifically, the beard support 50 rotatably supports the beard 40 around a second axis O2 parallel to the first axis O1.
In addition, although the connection ring 51 is formed in planar view C shape by which a part of circumferential direction was parted, you may form in cyclic | annular form.

  The beard holding arm 52 is provided with a bifurcated arm of a first beard holding arm 53 and a second beard holding arm 54 for holding the beard holding 40 from both sides in the circumferential direction. The first and second beard-holding arms 53 and 54 are elastically deformable in the circumferential direction, and are biased in advance so that their tips approach each other. Thereby, it is possible to hold the shaft body 41 of the beard 40 between the first beard holding arm 53 and the second beard holding arm 54.

The first holding surface 53a of the first beard holding arm 53 facing the second beard holding arm 54 and the second holding surface 54a of the second beard holding arm 54 facing the first beard holding arm 53 are: They face each other in the circumferential direction with the beard 40 interposed therebetween. On the first holding surface 53a and the second holding surface 54a, curved surfaces 55 having a circular arc shape in plan view corresponding to the outer diameter of the shaft body 41 of the whisker 40 are respectively recessed.
The first and second beard arms 53 and 54 support the beard 40 so as to sandwich the shaft 41 in the circumferential direction using the curved surface 55. Thus, the whisker holder 40 is rotatably supported between the first whisker holding arm 53 and the second whisker holding arm 54 about the second axis O <b> 2 without being displaced in the radial direction.

  The whisker holder 40 protrudes downward from the lower end portion of the shaft body 41, the head portion 42 formed at the upper end portion of the shaft body 41, and the cylindrical shaft body 41 extending along the second axis O2. An inner leg 43 and an outer leg 44 are provided.

The shaft body 41 is disposed between the curved surface 55 of the first beard holding arm 53 and the curved surface 55 of the second beard holding arm 54. It is held between. The head portion 42 is integrally formed on the upper end portion of the shaft body 41 and is disposed to overlap the upper surfaces of the first and second beard arms 53 and 54.
Thereby, the whisker holder 40 is rotatably held between the first whisker holding arm 53 and the second whisker holding arm 54 so as to be rotatable about the second axis O 2, at least in a state of being prevented from coming off downward (supporting ).

  The head portion 42 is formed to have linear portions 42 a in which parts of the outer peripheral edge mutually face each other, and an adjusting tool or the like (not shown) may be engaged with the head portion 42 using the linear portions 42 a. It is made possible. Thereby, using the adjustment tool, it is possible to rotate the beard 40 about the second axis O2.

  An outermost peripheral spring portion 32 of a hairspring main body 31 to be described later is inserted between the inner leg portion 43 and the outer leg portion 44 in the circumferential direction. That is, the inner leg portion 43 is disposed radially inward of the outermost circumferential spring portion 32, and the outer leg portion 44 is disposed radially outward of the outermost circumferential spring portion 32. And the part penetrated inside the inner side leg part 43 and the outer side leg part 44 among the outermost peripheral spring parts 32 of the mainspring 31 is integrated with the inner side leg 43 and the outer side leg 44 by welding etc., for example. It is fixed to

  Thereby, the hairspring 30 is in a state where the outermost circumferential spring portion 32 including the outer end portion 31 b is fixed (held) by the beard holding 40. Hereinafter, the hairspring 30 will be described in detail.

(Hairspring)
As shown in FIG. 5, the hairspring 30 is fixed to the balance 21 with the inner end 31a on the inner end 31a via the beard ball 24, and the outer end 31b is held by the above-mentioned hair support 40 and the inner end Between the end 31a and the outer end 31b, a mainspring 31 is formed in a spiral shape with a predetermined number of turns in a plane intersecting the first axis O1.

  The hairspring main body 31 is a thin plate spring made of metal such as iron or nickel, for example, and is formed in a spiral shape along the Archimedean curve in a polar coordinate system whose origin is the first axis O1. Thus, the mainspring 31 of the hairspring is wound with a plurality of turns so as to be adjacent to each other at substantially equal intervals in the radial direction. The material of the mainspring 31 is not limited to that described above, and may be changed as appropriate. Further, the shape of the mainspring 31 of the hairspring is not limited to the spiral shape along the above-described Archimedes curve, and may be changed to a shape in which the pitch changes, such as a logarithmic spiral.

  A part of the outermost peripheral spring portion 32 located at the outermost side in the radial direction, including the outer end portion 31b, of the mainspring 31 of the hairspring is spaced apart radially outward through the brazing portion 33, and the radius of curvature is other The arc portion 34 is formed larger than the portion of. The circumferential end of the arc portion 34 is the outer end 31 b of the mainspring 31 of the hairspring. Further, the portion of the circular arc portion 34 in the outermost circumferential spring portion 32 is held (fixed) on the beard 40 as described above.

  The mainspring 30 of the present embodiment formed as described above is classified as a so-called flat whisker and has an outer end shape in which the arc portion 34 is formed on the outermost peripheral spring portion 32 via the brazing portion 33 There is. In the present embodiment, the spring 30 formed in this manner may be simply referred to as “with outer end” or “spring with outer end”.

By the way, in the present invention, the shape of the hairspring 30 is not limited to “with the outer end”, and other shapes may be adopted. For example, as shown in FIG. 6, a so-called flat whisker is adopted, but a simple outer end-shaped hairspring 80 having no arc portion formed on the outermost peripheral spring portion 32 via a brazing portion is adopted. It does not matter. In this case, the mainspring 80 may be simply referred to as “no outer end” or “a mainspring without an outer end”.
6, the case where the winding direction is reverse with respect to the hairspring 30 shown in FIG. 5 is illustrated.

Furthermore, as shown in FIG. 7, a part of the outermost peripheral spring portion 32 is lifted (lifted) from within the surface, and the outer end portion 31 b is disposed on the opposite side in the radial direction from the lifting start portion You may adopt a hairspring 90 classified as a winding beard. In this case, the mainspring 90 may be simply referred to as a "rolling mainspring".
7, the case where the winding direction is reverse with respect to the hairspring 30 shown in FIG. 5 is illustrated.

In the present embodiment, the winding angle is defined as follows.
That is, as shown in FIG. 5, the first imaginary line L1 connecting the unwinding position P1 of the mainspring 31 and the first axis O1 and the whisker held by the whisker 40 when viewed from the axial direction of the stem 21 An angle centered on the first axis O1 formed between the holding position P2 of the mainspring 31 and the second imaginary line L2 connecting the first axis O1 is defined as a winding angle θ.

The unwinding position P1 is substantially fixed to the beard ball 24 in the innermost circumferential spring portion 35 including the inner end portion 31a of the mainspring 31 and located radially inward. Say where it is. Therefore, the position of the inner end 31a of the mainspring 31 may not necessarily coincide with the unwinding position P1. Also in this embodiment, the inner end 31a of the mainspring 31 of the hairspring and the unwinding position P1 are slightly shifted in the circumferential direction.
Further, the holding position P2 is a position at which the outermost peripheral spring portion 32 of the mainspring 31 is substantially fixed (held) to the beard 40. Therefore, the position of the outer end portion 31b of the mainspring 31 and the holding position P2 may not necessarily coincide with each other. Also in the present embodiment, the outer end 31b of the mainspring 31 of the hairspring and the holding position P2 are offset in the circumferential direction.

Furthermore, in the present embodiment, the direction of the winding angle θ, that is, the positive (+) direction and the negative (−) direction are defined as follows.
That is, based on the case where the winding angle θ is 0 (zero) (when the first virtual line L1 and the second virtual line L2 coincide), the holding position P2 is the winding direction of the mainspring 31 from this reference position. The direction of advancing to the side is defined as the positive direction of the winding angle θ (indicated as “+” in FIG. 5), and the opposite direction is defined as the negative direction of the winding angle θ (indicated as “−” in FIG. 5). Therefore, in FIG. 5, the winding angle θ is in the positive direction. On the other hand, for example, in FIG. 6, the winding angle θ is in the negative direction.

(Characteristics of hairspring)
Next, in the hairspring 30 of the present embodiment, when the outer end 31b side of the hairspring main body 31 is rotated or moved in the radial direction, how the isochronism changes is included. The result calculated in association with the angle θ will be described.
In the rotation operation for rotating the outer end 31 b side of the hairspring main body 31, a portion of the hairspring main body 31 held by the whisker holder 40 is rotated in a plane intersecting the axial direction of the balance 21. That is, an operation to rotate the second axis O2. Hereinafter, it may be simply referred to as "rotation operation".
In the moving operation for moving the outer end portion 31b side of the hairspring main body 31 in the radial direction, the portion of the hairspring main body 31 held by the hairspin 40 is moved along the radial direction of the balance 21 Operation. Hereinafter, the case may be simply referred to as "move operation".

  The above calculation uses the torque calculated by dividing the hairspring 30 into predetermined elements, applying the deformation theory of the elastic body to each element, and centering on the geometric center of the hairspring 30 when the balance 20 vibrates. The calculation was carried out by time-integrating the motion equation of the balance 20 (ordinary differential equation).

  First, when the winding angle θ is 0 degrees, the case where the outer end 31b of the mainspring 31 is not operated at all (hereinafter sometimes referred to simply as “before operation”), the case where the rotation operation is performed, and the movement The isochronism was calculated for the three cases of operation and. Respective isochronous curves based on the calculation results are shown in FIG.

  In FIG. 8, the isochronous curve CL1 shows an isochronous curve before operation, the isochronous curve CL2 shows an isochronous curve after rotational operation, and the isochronous curve CL3 is isochronous after moving operation Show a curve. In FIG. 8, the horizontal axis indicates the swing angle of the balance with hairspring 20, and the vertical axis indicates the rate at which time accuracy is obtained. The swing angle of the balance 20 is calculated within the range of 120 degrees to 300 degrees.

In the rotation operation, a portion of the mainspring 31 held by the beard 40 is counterclockwise rotated about the second axis O2 as an example. The moving operation is exemplified by the case where the portion of the mainspring 31 held by the beard 40 is moved +20 μm outward in the radial direction.
Furthermore, in this calculation, the case where the number of turns of the hairspring 30 is 12 turns is taken as an example. Moreover, as a frequency of the balance 20, the case where it is 10 vibrations, ie, 10 vibrations per second (36000 vibrations in 1 hour), is taken as an example.

  Next, the difference between the isochronous curve CL1 before the operation and the isochronous curve CL2 after the rotational operation is calculated, and the isochronous change curve CL4 during the rotational operation calculated based on the calculation result is shown in FIG. Show. Similarly, the difference between the isochronous curve CL1 before the operation and the isochronous curve CL3 after the moving operation is calculated, and the isochronous change curve CL5 during the moving operation calculated based on the calculation result is shown in FIG. Show. In FIG. 9, the horizontal axis indicates the swing angle of the balance with hairspring 20, and the vertical axis indicates the isochronous change amount as the time accuracy.

Next, in the isochronous change curve CL4 at the time of the rotation operation, calculation was performed by subtracting the minimum value from the maximum value of the isochronous change amount (maximum value-minimum value).
In the example of FIG. 9, the value at the swing angle of 220 degrees is the maximum value (approximately 2.16), and the value at the swing angle of 120 degrees is the minimum value (approximately −2.05). Therefore, (maximum value-minimum value) is approximately 4.21. Therefore, the value of (maximum value-minimum value) of approximately 4.21 is the maximum change amount of isochronous change at the time of rotation operation when the winding angle θ is 0 degree.
Similarly, in the isochronous change curve C5 at the time of movement operation, calculation was performed by subtracting the minimum value from the maximum value of the isochronous change amount (maximum value-minimum value). In the example of FIG. 9, the value at a swing angle of 300 degrees is the maximum value (approximately −1.02), and the value at a swing angle of 200 degrees is a minimum value (approximately −1.44). Therefore, (maximum value-minimum value) is approximately 0.42. Accordingly, the value of (maximum value-minimum value) of approximately 0.42 is the maximum variation of isochronous change at the time of movement operation when the winding angle θ is 0 degree.

As shown in FIG. 9, the isochronous change curve CL4 at the time of rotational operation has an oscillation angle within the range of 200 degrees to 250 degrees and is located above the extreme value (maximum value, that is, the maximum value). It is considered to be a convex curve. Similarly, the isochronous change curve CL5 at the time of movement operation is convex downward so that an extreme value (minimum value, that is, the above-mentioned minimum value) is included when the swing angle is in the range of 180 degrees to 250 degrees. It is considered to be a curve.
The tendency of such a curve is not limited to the case where the winding angle θ is 0 degree, and the same tendency is shown for any winding angle θ (see FIGS. 14 and 15).

  Next, the above-mentioned calculation is repeated for each winding angle of 1 degree within the range of winding angle θ of (−180 degrees to +180 degrees), and isochronous change at the time of rotational operation at each winding angle θ The maximum change amount of the isochronous change and the maximum change amount of the isochronous change at the time of the movement operation were respectively calculated.

  Then, a graph is shown in FIG. 10 in which the maximum change amount of isochronous change at the time of rotational operation at each winding angle θ and the maximum change amount of isochronous change at the time of move operation are grouped together and easily viewed. In FIG. 10, the horizontal axis indicates the winding angle θ, and the vertical axis indicates the maximum amount of isochronous change.

In FIG. 10, the value of the maximum amount of change of isochronous change at the time of rotation operation at each winding angle θ is plotted by a symbol “□”. Then, a curve connecting the values of the maximum change at the respective winding angles θ plotted by the symbol “□” becomes a change curve CL6 of the maximum change of the isochronous change at the time of the rotation operation.
Similarly, the value of the maximum amount of change of isochronous change at the time of movement operation at each winding angle θ is plotted by a symbol “◇”. Then, a curve connecting values of maximum change amounts at respective winding angles θ plotted by the symbol “◇” becomes a change curve CL7 of the maximum change amount of isochronous change at the time of the movement operation.

  As shown in FIG. 10, both of the change curve CL6 and the change curve C7 are curves in which the maximum value and the minimum value of the maximum change amount alternately appear periodically. Moreover, the maximum value of the maximum change amount in the change curve CL6 corresponds to the minimum value of the maximum change amount in the change curve CL7 within the same range of the winding angle θ, and the maximum change amount in the change curve CL6 The minimum value and the maximum value of the maximum amount of change in the change curve CL7 correspond to each other within a range of substantially the same winding angle θ. That is, the change curve CL6 and the change curve C7 are in a state in which the winding angle θ is out of phase by about 90 degrees to about 110 degrees.

In FIG. 10, the curves of the change curve L6 and the change curve 7 are corrected so that the maximum values of the respective maximum change amounts indicate a value of approximately 1 so that the change curve CL6 and the change curve CL7 can be easily compared. ing.
However, even in this case, since the slopes of the change curve CL6 and the change curve CL7 only change, the change with respect to the winding angle θ is the same as that before the correction. Furthermore, since the change curves CL6 and CL7 are approximately proportional to the amounts of the rotation operation and the movement operation, they are similar to the correction of the movement amount.

  From the above, according to FIG. 10, in the hairspring 30 of the present embodiment with the outer end, when the outer end portion 31b side of the hairspring main body 31 is rotated or moved in the radial direction, isochronous is wound. It can be grasped how it changes according to the lead angle θ.

Furthermore, the series of calculations described above were performed for the outer-end-free type baldness 80 shown in FIG. 6 and the windup type 90 shown in FIG.
Calculation is performed for the hairspring 80 (spring with no outer end) shown in FIG. 6, and the obtained change curve CL8 of the maximum amount of change in isochronous change during rotation operation and isochronism during movement operation A change curve CL9 of the maximum change amount of change is shown in FIG. As shown in FIG. 11, the change curve CL8 and the change curve CL9 were curves showing the same tendency as the change curve CL6 and the change curve CL7 described above.

  Furthermore, calculation is performed on the hairspring 90 (wind-up spring) shown in FIG. 7, and the obtained change curve CL10 of the maximum change in isochronous change during rotation operation and isochronism during movement operation A change curve CL11 of the maximum change amount of change is shown in FIG. As shown in FIG. 12, the change curve CL10 and the change curve CL11 were curves showing the same tendency as the change curve CL6 and the change curve CL7 described above.

  FIG. 13: is the figure which put together each change curve of FIGS. 10-12 into one, and was graph-ized. As shown in FIG. 13, regardless of the shape of the outer end of the hairspring 30, the change curve CL12 of the maximum change of the isochronous change at the time of the rotation operation and the isochronous change at the time of the movement operation The change curve CL13 of the maximum change shows the same tendency.

  From the above, the balance spring 30 of the present embodiment with the outer end has the following characteristics. The following characteristics are the same as in the case of the outer-end-less mainspring (hairspring 80) and the winding mainspring (hairspring 90) as described above.

That is, in the case of the mainspring 31 of the hairspring, the isochronous variation, which is changed by the rotation operation around the second axis O2, when the winding angle θ falls within the first angle range E1 determined in advance, is Is larger than the isochronous change amount changed by the movement operation in the radial direction, and the winding angle θ is an angle different from the first angle range E1 and within a predetermined second angle range E2 When it is settled, the isochronous change amount which is changed by the movement operation in the radial direction is larger than the isochronous change amount which is changed by the rotation operation around the second axis O2.
As the first angle range E1, the winding angle θ is (−125 degrees ± 5 degrees to −215 degrees (that is, +145 degrees) ± 5 degrees) or (−35 degrees ± 5 degrees to +55 degrees ± 5 degrees) It is in the range. As the second angle range E2, the winding angle θ is in the range of (−125 ° ± 5 ° to −35 ° ± 5 °) or (+ 55 ° ± 5 ° to + 145 ° ± 5 °).

  Furthermore, in the case of an angle range in which the winding angle θ is included in the range of (-170 degrees ± α degrees) or (+10 degrees ± α degrees) as the first angle range E1, the balance spring main body 31 The maximum isochronous change that changes as a result of the rotation around the two axes O2 is maximized, and conversely, the maximum isochronous change that changes due to radial movement is minimized.

The above α is an angle included in the range of 5 degrees to 30 degrees. In this case, in the first angle range E1, as the α decreases from 30 degrees to 5 degrees, the above-described characteristics can be more effectively achieved. For example, (-170 degrees ± 25 degrees) or (+ 10 degrees ± 25 degrees) than when the winding angle θ is included in the range of (-170 degrees ± 30 degrees) or (+ 10 degrees ± 30 degrees) The above characteristics can be more effectively achieved if included within the range of. More preferably, the winding angle θ is in the range of (−170 ° ± 5 °) or (+ 10 ° ± 5 °).
In addition, it is possible to make it small at every 30 degrees to 5 degrees as (alpha), ie, make it small in order of 30 degrees, 25 degrees, 20 degrees, 15 degrees, 10 degrees, and 5 degrees.

  Furthermore, as the second angle range E2, when the winding angle θ is within the range of (−80 ° ± α °) or (+ 100 ° ± α °), the moving operation in the radial direction The maximum change amount of isochronous change by the maximum is the largest, and conversely, the maximum change amount of isochronous change by the rotation operation around the second axis O2 is the smallest.

In the same manner as described in the first angle range E1, the above-mentioned α is an angle included in the range of 5 degrees to 30 degrees. In this case, in the second angle range E2, as the α decreases from 30 degrees to 5 degrees, the above-described characteristics can be more effectively achieved. For example, (−80 ° ± 25 °) or (+ 100 ° ± 25 °) than when the winding angle θ is included in the range of (−80 ° ± 30 °) or (+ 100 ° ± 30 °) The above characteristics can be more effectively achieved if included within the range of. More preferably, the winding angle θ is within the range of (−80 ° ± 5 °) or (+ 100 ° ± 5 °).
In addition, it is possible to make it small at every 30 degrees to 5 degrees as (alpha), ie, make it small in order of 30 degrees, 25 degrees, 20 degrees, 15 degrees, 10 degrees, and 5 degrees.

It will be described in more detail.
FIG. 14 is a diagram showing an isochronous change curve which is changed by the rotation operation around the second axis O2, and FIG. 15 is a diagram showing an isochronous change curve which is changed by the movement operation in the radial direction. is there.
As shown in FIG. 14 and FIG. 15, when the winding angle θ is +167 degrees or +13 degrees, the isochronism changes favorably with rotation operation, but conversely, the movement operation in the radial direction It becomes insensitive to it, and it becomes difficult to change to movement operation. Furthermore, when the winding angle θ is −77 degrees or +103 degrees, the isochronism changes favorably by the movement operation, but on the contrary, it becomes insensitive to the rotation operation, and the rotation operation is not Is difficult to change.

FIG. 13 shows the result when the number of turns is 12 and the frequency of the balance 20 is 10 vibrations (that is, 36000 vibrations in one hour) as described above. Similar results could be obtained even when changed.
For example, FIG. 16 is a view corresponding to FIG. 13 in the case where the number of turns is 14 and the frequency of the balance 20 is 8 vibrations (ie, 28800 vibrations in one hour). As apparent from FIG. 16, even when the number of turns and the frequency are changed, the above-described characteristics are obtained.

  As shown in FIG. 5, in the hairspring 30 configured as described above, the inner end 31a side is fixed to the balance 21 via the beard ball 24, and the outer end 31b side is fixed (held) to the hair support 40 It is done. In particular, in the present embodiment, the whisker holder 50 holds the whisker holder 40 rotatably about the second axis O2 in a state where the winding angle θ falls within the predetermined first angle range E1. . Specifically, the winding angle θ is +13 degrees.

(Isochronous adjustment of hairspring)
Next, the case where the isochronous adjustment of the hairspring 30 is performed in the timepiece 1 equipped with the speed governor 13 configured as described above will be described.
In the initial state, it is assumed that the beard 40 is located at the reference rotational position, and the beard main body 31 is not displaced about the second axis O2 by the beard 40.

  When performing isochronous adjustment under such an initial state, for example, by rotating the beard holder 50 about the first axis O1 with respect to the balance 20, the beard holder 40 together with the beard holder 50. Since it can move in the circumferential direction, the winding angle θ of the balance spring 30 can be set to an arbitrary angle. Thus, the winding angle θ can be appropriately set so as to fall within the first angle range E1 or the second angle range E2. That is, the winding angle θ can be set to +13 degrees which is within the first angle range E1.

  The present invention is not limited to the above case. For example, the winding angle θ is within the first angle range E1 so that the winding angle θ falls within the first angle range E1 or the second angle range E2. The beard support 40 may be fixed in advance to the mainspring 31 so as to be set to a certain +13 degrees.

Then, a rotation operation is performed to rotate the beard 40 whose winding angle θ is set to +13 degrees around the second axis O2. Thereby, isochronism can be changed, and isochronous adjustment can be performed.
In particular, when the winding angle θ of the mainspring 31 falls within the first angle range E1, as described above, the isochronous variation, which is changed by the rotation operation, is in the radial direction. Since it is larger than the isochronous change amount changed by the moving operation, the rotational operation can change isochronism with high sensitivity more than the moving operation in the radial direction. Therefore, it is possible to change the isochronism by the amount of change caused by the rotation operation in a state in which the movement operation in the radial direction is less affected, and it is possible to quantify the isochronous adjustment without using the slow and fast hands. It can be carried out easily and accurately.

Moreover, since the winding angle θ is +13 degrees, as shown in FIG. 14 and FIG. 15, the maximum amount of isochronous change that changes with the rotation operation of the hairspring main body 31 becomes maximum, and conversely, the diameter The maximum isochronous change that changes due to the movement operation in the direction is minimized. Therefore, although isochronous changes with high sensitivity with the rotation operation, it becomes insensitive to the movement operation in the radial direction, and hardly changes for the movement operation.
Therefore, by performing the rotating operation of the whisker holder 40 in a state where the winding angle θ is +13 degrees, the isochronism can be changed more effectively by the amount of change caused by the operation, and the isochronous adjustment is performed. Further, it can be done easily and accurately.

  In particular, the isochronous change amount that changes due to the rotation operation of the beard 40 is approximately proportional to the rotation operation amount. Therefore, the isochronism can be changed by the change amount corresponding to the rotation operation of the whisker holder 40, and the isochronous adjustment can be performed quantitatively.

  In particular, since the isochronous property changes with the polarity at which the balance angle of the balance 20 has an extreme value within the range of 200 degrees to 250 degrees, the balance spring body 31 has the swing angle of 200 degrees to 250 degrees etc. When the time adjustment is performed, isochronism can be effectively changed with high sensitivity even if, for example, a minute rotation operation is performed, and the isochronous adjustment can be easily performed easily.

As described above, according to the governor 13 having the balance spring 30 of the present embodiment, isochronous adjustment can be easily and accurately performed without using the slow and fast hands.
In particular, unlike the conventional case where isochronous adjustment is performed using tweezers etc., after setting the winding angle θ properly, the isochronism is a series of flow for rotating the whisker holder 40. Adjustments can be made smoothly and isochronous can be changed quantitatively. Therefore, it is possible to perform isochronous adjustment easily and appropriately.
Furthermore, according to the movement 10 and the watch 1 of the present embodiment, since the above-described speed regulator 13 is provided, the high-performance movement 10 and the watch 1 can be provided with less error in the rate.

(Modification of the first embodiment)
In the first embodiment, the winding angle θ is +13 degrees. However, the winding angle θ is not limited to this case, and is within the first angle range E1, that is, (−125 degrees ± 5 degrees to −215 degrees ± 5 degrees) It does not matter as long as it is within the range of (−35 ° ± 5 ° to + 55 ° ± 5 °).
Among them, the winding angle θ is preferably in the range of (−170 ° ± α °) or (+ 10 ° ± α °), and α is preferably in the range of 5 ° to 30 °. Among these, the following order is more preferable.
Is within the range of (−170 ° ± 30 °) or (+ 10 ° ± 30 °).
Is within the range of (−170 ° ± 25 °) or (+ 10 ° ± 25 °).
Is within the range of (−170 ° ± 20 °) or (+ 10 ° ± 20 °).
Is within the range of (−170 ° ± 15 °) or (+ 10 ° ± 15 °).
Is within the range of (−170 ° ± 10 °) or (+ 10 ° ± 10 °).
Is within the range of (−170 ° ± 5 °) or (+ 10 ° ± 5 °).
Therefore, it is most preferable to set the winding angle θ in the range of (−170 ° ± 5 °) or (+ 10 ° ± 5 °). In this case, the same effects as those of the first embodiment can be achieved.

  Furthermore, in the first embodiment, although the hairspring 30 with the outer end is adopted, a hairspring 80 of the outer-endless type shown in FIG. 6 or a hairspring 90 of the wound-up spring type shown in FIG. I don't care. Even in these cases, as described above, since they have the same characteristics as those of the balance spring 30 with the outer end, the same effects as those of the first embodiment can be achieved.

For example, as shown in FIG. 17 to FIG. 19, the governor 100 may be provided with a winding mainspring 90 of a winding mainspring type.
In this case, a portion of the outermost peripheral spring portion 32 of the mainspring 31 of the hairspring 90 is lifted and extends toward the radial opposite side to the lifting start portion, and then fixed (held) to the hairspring 40 It is done. Further, in the illustrated example, the whisker holder 40 fixes (holds) the outer end 31 b side of the mainspring 90 so that the winding angle θ is −167 degrees.

Even in the case of the speed governor 100 configured in this manner, the windup spring type 90 of the windup mainspring type has the same characteristics as the balance spring 30 with the outer end, and the winding angle θ is (−170 Since it is -167 degrees, which is within the range of ± 5 degrees, isochronous adjustment can be easily and accurately performed by the rotation operation of the whisker holder 40 as in the first embodiment.

Second Embodiment
Next, a second embodiment according to the present invention will be described with reference to the drawings. In the second embodiment, the same parts as those in the first embodiment are indicated by the same reference numerals and the description thereof will be omitted.
In the first embodiment, the beard support 50 rotatably supports the beard 40 about the second axis O 2, but in the second embodiment, the beard support 50 supports the beard 40 movably in the radial direction. ing.

As shown in FIG. 20 and FIG. 21, the speed governor 110 of the present embodiment is a whisker holder (second member according to the present invention) 120 that fixes (holds) the outer end 31 b side of the mainspring 31. And a whisker support (a support member according to the present invention) 130 movably supporting the whisker support 120 in the radial direction.
In addition, in FIG. 20, in order to make a drawing legible, a part of components of the governor 110 is abbreviate | omitted.

  As in the first embodiment, the whisker holder 130 includes a connecting ring 51 and a whisker holding arm 52 having a first whisker holding arm 53 and a second whisker holding arm 54. Relative rotation is possible around the axis O1.

The first and second beard arms 53 and 54 are elastically deformable in the circumferential direction, and are biased in advance so that their tips approach each other. Thereby, it is possible to hold the shaft body 41 of the beard 120 between the first beard holding arm 53 and the second beard holding arm 54.
The curved surface 55 in the first embodiment is not formed on the first holding surface 53a of the first beard holding arm 53 and the second holding surface 54a of the second beard holding arm 54 of the present embodiment. Therefore, the first holding surface 53a and the second holding surface 54a are flat.

  The whisker holder 120 includes a shaft 41, a head 42, an inner leg 43 and an outer leg 44 as in the first embodiment. However, the shaft 41 has a first contact surface 41 a in surface contact with the first holding surface 53 a of the first beard holding arm 53 and a second surface in contact with the second holding surface 54 a of the second beard holding arm 54. The second contact surfaces 41b are formed to face each other in the circumferential direction.

As a result, the first whisker-holding arm 53 and the second whisker-holding arm 54 bring the first holding surface 53a into surface contact with the first contact surface 41a, and the second holding surface 54a with the second contact surface 41b. In the state of being in surface contact, the beard 120 is held. Thus, the whisker holder 120 is radially movably supported between the first whisker arm 53 and the second whisker arm 54 in a state in which the rotation is restricted.
In the case of moving the beard 120 in the radial direction, for example, after the adjustment tool is engaged with the head 42, the clamping force between the first and second beard holding arms 53 and 54 is resisted. As it does, it is possible to move the beard 120.
Furthermore, in the present embodiment, the beard support 130 movably supports the beard 120 at a winding angle θ of −77 degrees.

(Isochronous adjustment of hairspring)
Next, the case where the isochronous adjustment of the hairspring 30 is performed using the speed governor 110 of the present embodiment configured as described above will be described.
In the initial state, it is assumed that the beard 120 is located at the reference position, and the mainspring 31 is not displaced in the radial direction by the beard 120. Further, it is assumed that the winding angle θ is set to −77 degrees, which is within the second angle range E2, by the same method as in the first embodiment.

Under such an initial state, a moving operation of moving the beard 120 with the winding angle θ set to −77 degrees in the radial direction is performed. Thereby, isochronism can be changed, and isochronous adjustment can be performed.
In particular, when the winding angle θ of the mainspring 31 falls within the second angle range E2, as described above, the isochronous variation, which is changed by the movement operation in the radial direction, is Since it is larger than the isochronous change amount which changes due to the rotation operation, the movement operation in the radial direction can change the isochronism with high sensitivity more than the rotation operation. Therefore, it is possible to change isochronism by the amount of change resulting from the moving operation in the radial direction, in a state in which the influence by the rotating operation is less affected.

Moreover, since the winding angle θ is −77 degrees, as shown in FIG. 14 and FIG. 15, the maximum amount of change in isochronism that changes with the movement operation in the radial direction is maximum for the hairspring main body 31 On the other hand, the maximum isochronous change that changes due to the rotation operation is minimized. Therefore, although isochronous changes to high sensitivity with movement operation, it becomes insensitive to rotation operation, and it becomes difficult to change to rotation operation.
Therefore, by performing the moving operation with the winding angle θ of −77 degrees, isochronism can be changed more effectively by the amount of change caused by the operation, and isochronous adjustment is further facilitated and It can be done precisely.

In particular, as in the case of the rotation operation in the first embodiment, the isochronous change amount that changes due to the movement operation of the beard 40 is approximately proportional to the movement operation amount. Therefore, the isochronism can be changed by the change amount corresponding to the movement operation of the whisker holder 40, and the isochronous adjustment can be performed quantitatively.
From the above, even in the case of the present embodiment, it is possible to perform isochronous adjustment quantitatively and easily and accurately even without using the slow and sharp hands.

  In particular, since the isochronous property changes with the polarity at which the balance angle of the balance 20 has an extreme value within the range of 200 degrees to 250 degrees, the balance spring body 31 has the swing angle of 200 degrees to 250 degrees etc. When adjusting the time, it is possible to effectively change isochronism with high sensitivity, for example, even in the case of a minute movement operation, and it is easy to easily perform isochronous adjustment.

  As described above, even with the governor 110 equipped with the balance spring 30 of the present embodiment, isochronous adjustment can be easily and accurately performed without using the slow and fast hands.

(Modification of the second embodiment)
In the second embodiment, although the winding angle θ is −77 degrees, the present invention is not limited to this case, and the second angle range E2, that is, (−125 degrees ± 5 degrees to −35 degrees ± 5 degrees Or within the range of (+ 55 ° ± 5 ° to + 145 ° ± 5 °).
Among them, the winding angle θ is preferably in the range of (−80 ° ± α °) or (+ 100 ° ± α °), and α is preferably in the range of 5 ° to 30 °. Among these, the following order is more preferable.
Is within the range of (−80 ° ± 30 °) or (+ 100 ° ± 30 °).
In the range of (−80 ° ± 25 °) or (+ 100 ° ± 25 °).
In the range of (−80 ° ± 20 °) or (+ 100 ° ± 20 °).
Is within the range of (−80 ° ± 15 °) or (+ 100 ° ± 15 °).
In the range of (−80 ° ± 10 °) or (+ 100 ° ± 10 °).
Is within the range of (−80 ° ± 5 °) or (+ 100 ° ± 5 °).
Therefore, it is most preferable to set the winding angle θ within the range of (−80 ° ± 5 °) or (+ 100 ° ± 5 °). In this case, the same effects as those of the second embodiment can be achieved.

  Furthermore, in the second embodiment as well, an outer endless type hairspring 30 shown in FIG. 6 or a winding mainspring type hairspring 90 shown in FIG. 7 may be adopted. Even in these cases, as described above, since they have the same characteristics as those of the balance spring 30 with the outer end, the same working effects as those of the second embodiment can be achieved.

Third Embodiment
Next, a third embodiment according to the present invention will be described with reference to the drawings. In the third embodiment, the same components as those in the second embodiment are designated by the same reference numerals and the description thereof will be omitted.
In the second embodiment, although the beard 120 is movably supported in the radial direction using the first beard holding arm 53 and the second beard holding arm 54, in the third embodiment, the beard holding is used. , Movably supports beard holding.

As shown in FIG. 22, the speed governor 140 of the present embodiment includes a beard end (second member according to the present invention) 150 for fixing (holding) the outer end portion 31 b side of the balance main body 31 and the beard end 150. Are supported movably in the radial direction (support member according to the present invention) 160, and a whisker holder 170 combined with the whisker carrier 160.
In addition, in FIG. 22, in order to make a drawing legible, a part of components of the governor 140 is abbreviate | omitted.

  As shown in FIGS. 22 and 23, the whisker holder 160 is integrally formed with the connection ring 51, the first arm portion 161 extending radially outward from the connection ring 51, and the first arm portion 161. And a second arm portion 162 extending in the circumferential direction.

The second arm portion 162 is integrally formed at the distal end portion (outer end portion) of the first arm portion 161, and is formed in an elliptical shape in plan view or in an arc shape in plan view extending in the circumferential direction. In the present embodiment, the circumferential center portion of the second arm portion 162 is connected to the tip end portion of the first arm portion 161.
In a portion of the second arm portion 162 located at the center in the circumferential direction, a slit-shaped first guide groove 163 which penetrates the second arm portion 162 up and down and opens outward in the radial direction is formed ing. The first guide groove 163 is formed in a linear shape extending in the radial direction.
Screw holes 164 extending in the vertical direction are respectively formed at circumferential end portions of the second arm portion 162 positioned on both sides in the circumferential direction across the first guide groove 163.

  The whisker holder 150 is a cylindrical shaft 41 extending along the second axis O 2, is positioned lower than the upper end of the shaft 41, is integrally formed with the shaft 41, and is more than the shaft 41. The flange portion 151 is expanded in diameter, and an inner leg portion 43 and an outer leg portion 44 which project downward from the lower end portion of the shaft body 41 are provided. In FIGS. 22 and 23, the inner leg 43 and the outer leg 44 are hidden by the beard holder 160.

  The shaft body 41 is formed in a cylindrical shape having an outer diameter smaller than the groove width of the first guide groove 163. The flange portion 151 is formed in a circular shape in a plan view, the outer diameter of which is larger than the groove width of the first guide groove 163. Thus, the whisker holder 150 is radially movably disposed in the first guide groove 163 in a state where the flange portion 151 overlaps the second arm portion 162.

  As shown in FIG. 22 and FIG. 24, the whisker holder 170 is a circumferentially extending plate corresponding to the shape of the second arm portion 162, and is disposed to overlap the upper surface of the second arm portion 162. . Note that the outer diameter of the beard holding member 170 is formed to correspond to the outer shape of the second arm portion 162 so as to cover substantially the entire surface of the second arm portion 162.

  A slit-like second guide groove 171 extending in the radial direction is formed in a portion of the beard-holder presser 170 which is located at the center in the circumferential direction. The second guide groove 171 has a groove width equivalent to that of the first guide groove 163 and is disposed above the first guide groove 163. The upper end portion of the shaft body 41 in the whisker holder 150 is inserted into the second guide groove 171.

  A concave groove 172 extending in the radial direction is formed on the lower surface of the whisker holder 170 at a portion positioned in the circumferential direction. The width of the recessed groove 172 is formed larger than the diameter of the flange portion 151 of the whisker holder 150. As a result, the whisker holder 170 can overlap the upper surface of the second arm portion 162 in a state in which the flange portion 151 is accommodated in the recessed groove 172. However, the depth of the recessed groove 172 is formed slightly shallower than the thickness of the flange portion 151. As a result, the whisker holder 170 overlaps the upper surface of the second arm 162 while the flange 151 is pressed against the second arm 162.

  Further, mounting holes 175 for fixing screws 173 are formed at circumferential end portions of the hair holder 170 located on both sides in the circumferential direction across the second guide groove 171. By attaching the fixing screw 173 to the screw hole 164 through the mounting hole 175, the whisker holder 170 is integral with the second arm 162 while the flange 151 is sandwiched between the second arm 162 and the second arm 162. Combined with

(Isochronous adjustment of hairspring)
According to the speed governor 140 of the present embodiment configured as described above, since the whisker holder 150 can be moved in the radial direction, the same effects as those of the second embodiment can be achieved.

In addition, in the case of the present embodiment, since the pinching of the flange portion 151 can be released by loosening or removing the fixing screw 173, the diameter of the whiskers 150 along the first guide groove 163 and the second guide groove 171. It can be moved in the direction. Then, after the moving operation is performed, the flange portion 151 can be sandwiched between the second arm portion 162 and the beard holding member 170 by tightening the fixing screw 173. Therefore, the beard holding at the position after the moving operation 150 can be fixed more stably.
Therefore, it is possible to effectively suppress the position shift of the beard holding 150, for example, when it is unexpectedly moved in the radial direction.

  While the embodiments of the present invention have been described above, these embodiments are presented as examples and are not intended to limit the scope of the invention. The embodiment can be implemented in various other forms, and various omissions, replacements, and modifications can be made without departing from the scope of the invention. The embodiments and the modifications thereof include, for example, those which can be easily conceived by those skilled in the art, substantially the same ones, and equivalent ranges.

  For example, although the case where the inner-end part side of the mainspring was fixed to the balance of the balance was mentioned as an example and said each embodiment demonstrated, it is not limited to this case. For example, the inner end side of the mainspring may be fixed to a first part (i.e., a watch part other than a balance) rotating about an axis.

θ: Winding angle E1: First angle range E2: Second angle range L1: First virtual line L2: Second virtual line O1: First axis (axis of balance)
P1: Unwinding position P2: Holding position 1: Clock 10: Movement (movement for clock)
13, 100, 110, 140 ... speed governor 20 ... temp (first member)
21: Tenshin 30, 80, 90: Hairspring 31: Hairspring main body 31a: Inner end of hairspring main body 31b: Outer end of hairspring main body 40, 120, 150: Beard holding (second member)
50, 130, 160 ... Beard support (supporting member)

Claims (9)

The inner end side is fixed to a first member rotating about an axis, and the outer end side is held by the second member, and intersects with the axis between the inner end and the outer end The main body of the spiral spring formed in a predetermined number of turns in the plane
When viewed from the axial direction, a first virtual line connecting the unwinding position of the balance spring main body and the axis line, and a second connection connecting the support position of the balance spring body held by the second member and the axis When an angle around the axis formed between the virtual line and
The hairspring main body is
The second member is held by the second member so that the outer end rotates in the plane with the winding angle falling within a predetermined first angle range, or a predetermined second angle The outer end portion is held by the second member so as to move in the radial direction of the mainspring in the state of being contained within a range;
The hairspring main body is
Furthermore, when the winding angle is within the first angle range, the isochronous variation that changes due to rotation in the plane is isochronous that changes due to the radial movement. When the winding angle is larger than the variation and the winding angle is within the second angle range, the isochronous variation that changes due to the radial movement changes due to the rotation in the plane. Hairspring greater than the isochronous change amount. In the hairspring according to claim 1,
The direction in which the second member advances toward the winding direction of the mainspring with respect to when the winding angle is zero is defined as the positive direction of the winding angle, and the opposite direction is the negative direction of the winding angle. When you
The first angle range is an angle in which the winding angle is included in a range of (−125 ° ± 5 ° to −215 ° ± 5 °) or (−35 ° ± 5 ° to + 55 ° ± 5 °) Range and
The second angle range is an angle range in which the winding angle is included in a range of (−125 ° ± 5 ° to −35 ° ± 5 °) or (+ 55 ° ± 5 ° to + 145 ° ± 5 °) It is supposed to be a mustache. In the hairspring according to claim 2,
The first angle range is an angle range in which the winding angle is included in a range of (-170 degrees ± α degrees) or (+10 degrees ± α degrees),
The second angle range is an angle range in which the winding angle is included in a range of (-80 degrees ± α degrees) or (+100 degrees ± α degrees),
The above-mentioned a is an angle included in the range of 5 degrees to 30 degrees. In the hairspring according to claim 3,
The first angle range is an angle range in which the winding angle is included in a range of (−170 degrees ± 5 degrees) or (+10 degrees ± 5 degrees),
A balance spring, wherein the second angle range is an angle range in which the winding angle is in a range of (−80 ° ± 5 °) or (+ 100 ° ± 5 °). In the hairspring according to any one of claims 1 to 4,
The first member is a balance,
The balance spring, wherein the inner end of the balance spring body is fixed to a balance in the balance. In the hairspring according to claim 5,
The swing angle of the balance is within the range of 200 degrees to 250 degrees when the outer end portion side rotates in the plane, or the outer end portion side moves in the radial direction of the balance after the balance spring main body moves. An isochronous change in a curve that includes extreme values, a hairspring. The balance spring according to claim 5 or 6;
The above-mentioned balance,
The second member;
And a support member that is combined with the balance so as to be relatively rotatable about the axis, and supports the second member so as to be movable.
The governor according to claim 1, wherein the support member rotatably supports the second member in the plane, or supports the second member movably in the radial direction of the stem.   A watch movement comprising the governor according to claim 7.   A watch comprising the watch movement according to claim 8.

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