CN110658709A - Hairsprings, governors, movements for timepieces, and timepieces - Google Patents

Abstract

According to the present invention, isochronous adjustment can be easily and precisely performed without using a speed needle. The invention provides a hairspring (30) equipped with a hairspring main body (31), the inner end (31a) side of which is fixed to the first member (20), and the outer end (31b) side is held In the second member (40), the hairspring body is held by the second member so that the outer end side rotates in-plane in a state where the winding angle (θ) is limited within the first angle range, or is limited by the second member. In the state within the angular range, the outer end side is held by the second member so that the outer end side moves in the radial direction. When the winding angle of the hairspring body is limited within the first angular range, the isochronous change due to in-plane rotation In the case where the amount of change is larger than the amount of isochronous change due to the movement in the radial direction, and when the winding angle is limited to the second angle range, the amount of change due to the movement in the radial direction, etc. The temporal variation is larger than the isochronous variation due to in-plane rotation.

Description

Hairsprings, governors, movements for timepieces, and timepieces

technical field

The present invention relates to a hairspring (ひげぜんまい), a governor, a movement for a timepiece, and a timepiece.

Background technique

In a mechanical timepiece, it is important that the vibration period is set within a predetermined predetermined value for the balance wheel (てんぷ). This is because when the vibration period deviates from the predetermined value, the difference rate of the mechanical timepiece (how slow or fast the timepiece is) changes.

As a method for adjusting the differential rate, a method is generally known in which the length (effective length) of the hairspring is adjusted by the speed needle, and the inner end of the hairspring is fixed to the balance shaft of the balance wheel (てんTrue), The part is fixed on the outer pile (ひげhold).

The speed hand is mainly equipped with: an outer clip (ひげReceiver), which is rotatable around the central axis of the balance wheel, and is arranged on the outer side in the radial direction of the hairspring; . Thereby, the hairspring is located between the outer clip and the inner clip, and is configured to vibrate in the radial direction between the two.

In the case of adjusting the differential rate using such a speed hand, in general, after adjusting the position of the outer peg that fixes the outer end of the hairspring, the speed hand is rotated around the central axis of the balance wheel along the length of the hairspring. Orientation adjusts the position of the outer and inner clips. Thereby, when the hairspring vibrates, it is possible to adjust the effective length between the contact point and the inner end of the hairspring when it comes into contact with the outer clip or the inner clip, so that the differential ratio can be adjusted.

In addition, there is also known a speed needle that can adjust the differential ratio by adjusting the amount of clearance (pitch width), which is the gap between the outer clip and the inner clip, when the differential ratio is adjusted. Timely adjustment (pitch adjustment (あおり adjustment)).

While the balance wheel reciprocates once, the hairspring repeats the actions of contacting the outer clip, separating from the outer clip, contacting the inner clip, and separating from the inner clip, and thus alternately repeats the short and long effective length states. In addition, since the strength of the vibration of the hairspring varies depending on the amount of winding, the time of contact with the outer clip or the inner clip varies. Therefore, for example, the time in a state with a short effective length may become longer, which may affect the isochronism of the difference rate.

Therefore, by performing the pitch adjustment by the speed needle, the strength of the spring constant in one cycle is changed depending on the swing angle, thereby adjusting the isochronism. In particular, when assembling a high-precision mechanical timepiece, it is important to perform isochronous adjustment.

However, when the speed needle is not provided, for example, when the time adjustment of the governor is performed by a variable inertia balance wheel (variable inertia wheel) or the like, the isochronous adjustment by the speed needle cannot be performed. Therefore, the isochronism of the assembled governor depends on the accuracy of each constituent element alone, the assembly position, and the like, which causes variations in the isochronism.

In addition, when performing isochronous adjustment without using a speed needle, a method of manually correcting, for example, the position and shape of the main outer end side of the hairspring using tweezers or the like is known. Further, as a hairspring used in the case of performing such a correction, a hairspring is known in which a rigidity-enhancing portion is formed at the outermost peripheral portion of the hairspring, and the rigidity-enhancing portion at least partially compensates for fluctuations in the differential rate of the movement. (It depends on the vibration amplitude of the balance by the escapement) (for example, refer to Patent Document 1).

prior art literature

Patent Literature

Patent Document 1: Japanese Patent Publication No. 2014-525591.

SUMMARY OF THE INVENTION

The problem to be solved by the invention

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

The present invention has been made in consideration of such circumstances, and an object of the present invention is to provide a hairspring, a governor, a movement for a timepiece, and a timepiece that can easily and accurately perform isochronization without using a speed hand Sexual adjustment.

solutions to problems

(1) The hairspring according to the present invention is provided with a hairspring body, the inner end side is fixed to the first member that rotates around the axis, and the outer end side is held by the second member, and the hairspring body is The space between the inner end and the outer end is formed in a spiral shape by a predetermined number of turns in a plane intersecting with the axis, and when viewed in the direction of the axis, at the unwinding position of the hairspring main body and the axis When the angle around the axis formed between the connected first imaginary wire and the second imaginary wire that connects the holding position of the hairspring main body held by the second member and the axis is used as the winding angle, the hairspring main body is in the above-mentioned direction. The winding angle is held by the second member so that the outer end side is rotated within the plane in a state where the winding angle is limited within a predetermined first angle range, or is limited within a predetermined second angle range is held by the second member so that the outer end side moves in the radial direction of the hairspring body, and the hairspring body is further limited by the winding angle within the first angle range due to the in-plane The amount of isochronous change due to rotation is larger than the amount of isochronous change due to movement in the radial direction, and when the winding angle is limited to the second angle range, due to the The amount of isochronous change due to the movement in the radial direction is larger than the amount of isochronous change due to the rotation in the plane.

According to the hairspring of the present invention, the outer end portion side of the hairspring main body is rotated in-plane in a state where the winding angle is restricted to the first angle range, or the winding angle is restricted to the second angle range. In the inner state, the outer end portion side of the hairspring main body is moved in the radial direction, so that isochronous adjustment can be performed.

In particular, with regard to the hairspring main body, when the winding angle is limited to the first angle range, the isochronous change amount due to the rotation in the plane is larger than the isochronous change due to the movement in the radial direction. The amount of change is greater. That is, in the case of the rotation operation in the plane, the isochronism can be changed with better sensitivity than the movement operation in the radial direction. On the contrary, with regard to the hairspring body, when the winding angle is limited to the second angle range, the isochronous amount of change due to movement in the radial direction is larger than the isochronous change due to in-plane rotation. Sexual variability is greater. That is, in the case of movement in the radial direction, isochronism can be changed with better sensitivity than in-plane rotation.

Therefore, in any of the cases in which the outer end portion side of the hairspring body is rotated in-plane or moved in the radial direction, the isochronism can be caused by either of the operations. change in the amount of change. That is, in a state where it is hard to be influenced by the operation of the other side, the isochronous property can be changed by the amount of change caused by the operation of the other side. Furthermore, the isochronous change amount due to the rotation operation or the movement operation can be made to have a substantially proportional relationship to the rotation operation amount or the movement operation amount. Therefore, the isochronism can be changed by the amount of change corresponding to the rotation operation or the movement operation on the outer end portion side of the hairspring main body, and the isochronism can be adjusted quantitatively.

Due to the above, even without using the speed needle, the isochronous adjustment can be quantitatively performed, and the isochronous adjustment can be easily and accurately performed.

(2) On the basis of the case where the winding angle is zero, the direction in which the second member advances to the winding direction side of the hairspring main body may be regarded as the positive direction of the winding angle, and the opposite direction may be regarded as the positive direction of the winding angle. When the winding angle is in the negative direction, the first angle range is included in the winding angle (-125°±5° to -215°±5°), or (-35°±5° to +55° The angle range within the range of ±5 degrees), the second angle range is the wrapping angle is included in (-125 degrees ±5 degrees to -35 degrees ±5 degrees), or (+55 degrees ±5 degrees to + 145 degrees ± 5 degrees) within the range of the angle range.

In this case, 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), about The amount of isochronous change in the hairspring body due to in-plane rotation is larger than the amount of isochronous change due to movement in the radial direction. In addition, when the winding angle is included in the range of (-125 degrees ± 5 degrees to -35 degrees ± 5 degrees), or (+55 degrees ± 5 degrees to +145 degrees ± 5 degrees), since the radial direction The amount of isochronous change due to movement of the direction is larger than the amount of isochronous change due to rotation within the plane.

Therefore, by 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), the balance of the hairspring body The rotation operation is performed on the outer end side of the , or when the winding angle is included in (-125 degrees ± 5 degrees to -35 degrees ± 5 degrees), or (+55 degrees ± 5 degrees to +145 degrees ± 5 degrees) of Within the range, the outer end portion side of the hairspring body can be moved in the radial direction, so that the isochronism can be changed by the amount of change caused by each operation, and the isochronism can be adjusted.

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

In this case, when the winding angle is included in the range of (-170 degrees ±α degrees), or (+10 degrees ±α degrees), about the balance spring body, the isochronous time that changes due to in-plane rotation The maximum change amount of the isochronism becomes the largest, and on the contrary, the maximum change amount of the isochronism changes due to the movement in the radial direction becomes the smallest. Therefore, the isochronism changes with high sensitivity in accordance with the rotation operation in the plane, but becomes insensitive to the movement operation in the radial direction, and becomes difficult to change 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 in-plane rotation operation can be performed, so that the isochronism can be caused by The amount of change caused by this operation is changed more efficiently, and the isochronous adjustment can be performed more easily and accurately.

Similarly, when the winding angle is included in the range of (-80 degrees ±α degrees), or (+100 degrees ±α degrees), the isochronism of the hairspring body due to the movement in the radial direction changes The maximum change in , becomes the largest, and on the contrary, the isochronous maximum change due to in-plane rotation becomes the smallest. Therefore, the isochronism changes with high sensitivity in accordance with the moving operation in the radial direction, but becomes insensitive to the rotation operation in the plane, and becomes difficult to change 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 movement operation in the radial direction can be performed, so that isochronism can be caused by The amount of change due to this operation is changed more efficiently, and the isochronous adjustment can be performed more easily and accurately.

In addition, within the first angle range, the smaller the α is from 30 degrees to 5 degrees, the more effectively the above-mentioned effects can be achieved. For example, compared with when the winding angle is included in the range of (-170 degrees ± 30 degrees), or (+10 degrees ± 30 degrees), is included in (-170 degrees ± 25 degrees), or (+ 10 degrees ± 25 degrees) can effectively achieve the above-mentioned effects.

Similarly, within the second angle range, the smaller the above α is from 30 degrees to 5 degrees, the more effectively the above effects can be achieved. For example, compared to when the winding angle is included in the range of (-80 degrees ± 30 degrees), or (+100 degrees ± 30 degrees), is included in (-80 degrees ± 25 degrees), or (+ 100 degrees ± 25 degrees) can effectively achieve the above-mentioned effects.

Preferably, in any case, the smaller the value of α is, the more effectively the above-mentioned effects can be achieved. Specifically, as α, it is considered to decrease every 5 degrees from 30 degrees.

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

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

(5) The first member may be a balance wheel, and the inner end portion of the hairspring main body may be fixed to a balance shaft in the balance wheel.

In this case, it can be utilized as a hairspring that can perform isochronous adjustment of the balance.

(6) With regard to the hairspring main body, the outer end portion side may rotate within the plane, or the outer end portion side may move in the radial direction of the balance shaft, whereby the balance may be adjusted to the balance angle of the balance wheel. The isochronous variation of the curve containing extreme values in the range of 200 to 250 degrees.

In this case, when isochronous adjustment is performed within the range of the swing angle of 200 degrees to 250 degrees, for example, even a small operation (rotation operation, movement operation in the radial direction) can be made isochronous. Sensitivity changes well and efficiently, and isochronous adjustment is easy and easy.

(7) The governor according to the present invention is equipped with: the hairspring; the balance wheel; the second member; The second member is movably supported, and the support member supports the second member rotatably in the plane or movably supports the second member in the radial direction of the pendulum shaft.

In this case, since the second member can be moved in the circumferential direction together with the support member by relatively rotating the support member about the axis with respect to the balance, the winding angle of the hairspring can be set to any angle. Thereby, the winding angle can be appropriately set within the first angle range or the second angle range. Also, since the support member supports the second member rotatably or movably in the radial direction, the second member can be rotated or moved in the radial direction depending on the winding angle, so that the same can be achieved as before. As a result of displacing the outer end portion side of the hairspring as described above, isochronous adjustment can be performed.

In particular, unlike the case where the isochronous adjustment is performed using tweezers or the like as in the related art, after the winding angle is properly set, it is not only possible to perform a series of flow of the rotation operation or the movement operation smoothly Since the isochronous adjustment is performed and the isochronous can be changed quantitatively, the isochronous adjustment can be easily and appropriately performed.

(8) The movement for a timepiece according to the present invention is equipped with the aforementioned governor.

(9) The timepiece according to the present invention is equipped with the aforementioned movement for timepieces.

In this case, since the above-described hairspring is provided, it is possible to use a high-performance movement for a timepiece and a timepiece with little error in the rate of difference due to high-precision isochronous adjustment.

effect of invention

According to the present invention, it is possible to easily and precisely perform isochronous adjustment without using a speed needle. Therefore, it is possible to obtain a high-performance movement for a timepiece and a timepiece with few errors in the difference rate.

Description of drawings

FIG. 1 is a diagram showing a first embodiment according to the present invention, and is an external view of a timepiece;

Fig. 2 is the top view of the movement in Fig. 1;

Figure 3 is a perspective view of the governor shown in Figure 2;

Figure 4 is a cross-sectional view of the governor shown in Figure 3 along line A-A;

Fig. 5 is a plan view of the governor shown in Fig. 3, and is a plan view showing the relationship of the outer spud ring, the hairspring, and the balance;

Figure 6 is a top view without an outer end hairspring;

FIG. 7 is a top view of the winding-up spring-type hairspring;

8 is a diagram showing isochronous curves in the case of no operation, in the case of a rotation operation, and in the case of a moving operation at a winding angle of 0 degrees;

9 is a diagram showing the relationship between the isochronous change curve at the time of the rotation operation and the isochronous change curve at the time of the moving operation;

10 is a graph showing the relationship between a change curve of the maximum change amount of isochronous change at the time of a rotation operation and a change curve of the maximum change amount of the isochronous change at the time of a moving operation;

11 is a diagram showing the relationship between the change curve of the maximum change amount of isochronous change during the rotation operation and the change curve of the maximum change amount of the isochronous change during the movement operation in the hairspring without an outer end ;

12 is a diagram showing a relationship between a change curve of the maximum change amount of isochronous change at the time of a rotating operation and a change curve of the maximum change amount of the isochronous change at the time of a moving operation in the wind-up spring type hairspring ;

Fig. 13 is a change curve showing the maximum change amount of the isochronous change at the time of the rotation operation and the change at the time of the movement operation with respect to each of the hairspring with the outer end type, the type without the outer end type, and the winding spring type. A diagram of the relationship of the change curve of the maximum change of the isochronous change;

FIG. 14 is a diagram showing the relationship of the isochronous change curve due to the rotation operation in the four winding angles;

15 is a graph showing the relationship of the isochronous change curve due to the moving operation in the four winding angles;

Fig. 16 is a diagram showing the rotation of each of the type with outer end, the type without outer end, and the spring type hairspring when the number of turns is 14 and the vibration frequency of the balance is 8 vibrations. A graph of the relationship between the change curve of the maximum change amount of the isochronous change at the time of operation and the change curve of the maximum change amount of the isochronous change at the time of the moving operation;

17 is a perspective view showing a governor of a modification of the first embodiment;

Fig. 18 is a perspective view showing the relationship of the post ring, the hairspring, and the balance shown in Fig. 17;

Fig. 19 is a plan view showing the relationship between the post ring and the hairspring shown in Fig. 18;

20 is a perspective view showing a governor according to a second embodiment of the present invention;

Figure 21 is an enlarged top view of the periphery of the outer pile shown in Figure 20;

22 is a perspective view showing a governor according to a third embodiment of the present invention;

Fig. 23 is a perspective view showing a state in which the outer pile presser is removed from the state shown in Fig. 22;

FIG. 24 is a perspective view of the post press shown in FIG. 22 .

Detailed ways

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

(Basic structure of a clock)

Generally speaking, the mechanical body containing the drive part of a timepiece is called "movement". A state in which a dial and a hand are attached to the movement and placed in a timepiece case is referred to as a "finished product" of the timepiece to be a finished product. Among both sides of the main plate constituting the substrate of the timepiece, the side where the glass of the timepiece case is present (ie, the side where the dial is present) is referred to as the "back side" of the movement. In addition, the side (ie, the side opposite to the dial) where the case back of the timepiece case exists among both sides of the main plate is referred to as the "front side" of the movement.

In addition, in the present embodiment, the direction from the dial to the case rear cover is described as the upper side, and the opposite side thereof is described as the lower side.

(first embodiment)

As shown in FIG. 1 , the finished timepiece 1 of the present embodiment is equipped with a movement (a watch for a timepiece according to the present invention) in a timepiece case composed of a case back and a glass 2 (not shown). Movement) 10; dial 3 having scales and the like showing at least time-related information; and hands including an hour hand 4 showing the hour, a minute hand 5 showing the minute, and a second hand 6 showing the second.

As shown in FIGS. 2 and 3, the movement 10 is equipped with: a main plate 11; Between the main plate 11 , the gear train bridge and the balance bridge 12 are mainly arranged a watch-side gear train, an escapement (not shown) that controls the rotation of the watch-side gear train, and a speed control of the escapement. the governor 13. On the back side of the main board 11 , the dial 3 is arranged so as to be visually recognizable through the glass 2 .

In addition, the movement 10 of the present embodiment is exemplified by the movement 10 for a timepiece of the self-winding type equipped with the rotary hammer 14 . However, it is not limited to this case, and a hand-wound movement using the stem 15 may be used.

The watch-side gear train is mainly equipped with a barrel wheel, a second wheel, a third wheel, and a fourth wheel. In addition, in this embodiment, illustration of a 2nd wheel, a 3rd wheel, and a 4th wheel is abbreviate|omitted in order to make it easy to see a drawing. The second hand 6 shown in FIG. 1 rotates based on the rotation of the fourth wheel, and rotates at a rotation speed regulated by the escapement and governor 13 (ie, once in one minute). The minute hand 5 rotates based on the rotation of the second wheel or the rotation of the minute wheel that rotates in conjunction with the rotation of the second wheel, and rotates at a rotational speed regulated by the escapement and governor 13 (that is, in one hour). inner rotation). The hour hand 4 rotates based on the rotation of the hour wheel that rotates with the rotation of the second wheel via the straddle wheel (日の里车), and rotates at the rotational speed regulated by the escapement and the governor 13 (ie, , once in twelve or twenty-four hours).

The escapement is equipped with an escape wheel (not shown) that meshes with the fourth wheel, and an anchor (not shown) that makes the escape wheel escape and rotate regularly. Vibration controls the watch side gear train.

As shown in FIGS. 3 and 4 , the governor 13 is equipped with: a balance wheel (a first component of the present invention) 20 that reciprocates around a first axis (the axis of the present invention) O1 ( forward and reverse rotation); hairspring 30; pin (second member according to the present invention) 40 that holds the outer end 31b side of hairspring main body 31 described later; and pin ring (support member according to the present invention) 50, which is combined in a manner capable of relative rotation about the first axis O1 with respect to the balance wheel 20, and supports the external post 40 in a movable manner.

In addition, in this embodiment, the direction which crosses the 1st axis line O1 in plan view is called a radial direction, and the direction which surrounds the 1st axis line O1 is called a circumferential direction.

The balance wheel 20 is equipped with a balance shaft 21 rotatable around the first axis O1 and a balance wheel 22 mounted on the balance shaft 21 , and rotates forward and reverse around the first axis O1 with a constant amplitude (swing angle) using the hairspring 30 as a power source.

Regarding the swing shaft 21 , the upper tenon portion 21 a is pivotally supported by the upper bearing 60 , and the lower tenon portion 21 b is pivotally supported by a lower bearing (not shown) formed by the main plate 11 shown in FIG. 2 . In the middle portion of the swing shaft 21 in the vertical direction, a coupling arm portion 23 coupled to the balance wheel 22 is fixed, and a collet (ひげ玉) 24 and a disc (vibration seat) 25 are fixed.

The coupling arm portion 23 is a member that couples the swing shaft 21 and the balance wheel 22 in the radial direction, and the inner end portion is coupled to an annular boss portion 26 that is fixed to the swing shaft 21 by, for example, press fitting, etc. Also, the outer end portion is coupled to the inner peripheral surface of the balance wheel 22 . Thereby, the balance wheel 22 is attached to the swing shaft 21 via the link arm portion 23 , and rotates forward and reverse around the first axis O1 together with the swing shaft 21 . However, the number, arrangement or shape of the link arm portions 23 can be appropriately changed.

The collet 24 is arranged above the boss portion 26 , and is fixed to the swing shaft 21 by, for example, press fitting or the like.

The disk 25 is arranged below the boss portion 26, and is fixed to the swing shaft 21 by, for example, press fitting or the like. The disc 25 has a large flange 25a and a small flange 25b located further below than the large flange 25a. The large flange 25a is press-fitted and fixed, for example, with an impact stone (vibration stone) 27 formed of an artificial stone such as ruby and used to operate (swing) the anchor.

The upper bearing 60 is a vibration-resistant bearing equipped with the following components: a bearing frame 61, which is formed in a cylindrical shape; The upper cover jewel 63, which is arranged above the upper hole jewel 62, supports the upper tenon portion 21a of the swing shaft 21 from the axial direction; The upper cover jewel 63 is fixed to the bearing frame 61 .

However, the configuration of the upper bearing 60 is not limited to the above, and other configurations may be employed as long as the upper tenon portion 21a of the swing shaft 21 can be rotatably supported.

The bearing frame 61 is provided with an upper frame 61a and a lower frame 61b having a smaller outer diameter than the upper frame 61a, and is formed in two-stage cylindrical shapes with different outer diameters. The bearing frame 61 is attached to the inner side of the bearing cylindrical portion 71 of the base plate 70 formed on the balance bridge 12 by fixing the lower frame 61b by, for example, press fitting or the like. Further, the bearing frame 61 and the bearing cylindrical portion 71 are arranged coaxially with the first axis O1.

For example, as shown in FIG. 2 , the balance bridge 12 has a main body portion 72 extending in an arc shape in conformity with the shape of the timepiece case. An attachment hole 73 is formed in the main body portion 72 , and the base plate 70 is formed in a stepwise recessed manner in a part of the outer edge portion. As shown in FIG. 2 , the balance wheel bridge 12 is fixed to the main plate 11 by fixing screws 74 using mounting holes 73 . However, the shape of the balance bridge 12 is not limited to the above, and may be appropriately changed.

As shown in FIG. 4 , in the base plate 70 , a through hole 75 penetrating the base plate 70 up and down is formed coaxially with the first axis O1 . The bearing cylindrical portion 71 is formed so as to rise upward from the base plate 70 along the opening peripheral edge of the through hole 75 , and the inner side thereof communicates with the through hole 75 . Therefore, the lower frame 61b of the bearing frame 61 is fixed to the inner side of the bearing cylindrical portion 71 and the through hole 75 by, for example, press fitting. In addition, the upper frame 61 a of the bearing frame 61 is arranged on the opening end of the bearing cylindrical portion 71 , and is formed to be larger than the outer diameter of the bearing cylindrical portion 71 .

As shown in FIGS. 3 to 5 , the stud ring 50 is rotatably fitted in the bearing cylindrical portion 71 in the balance cock 12 , thereby being able to surround the first axis with respect to the bearing cylindrical portion 71 . O1 rotates relatively.

The outer spud ring 50 has a coupling ring 51 fitted to the outer side of the bearing cylindrical portion 71 , and an outer spud arm 52 extending radially outward from the coupling ring 51 and on the distal end portion side (outer end portion of the coupling ring 51 ). side) supports the outer pile 40 in a movable manner. Specifically, the outer pile ring 50 supports the outer pile 40 so as to be rotatable about a second axis O2 which is parallel to the first axis O1.

Further, the coupling ring 51 is formed in a C-shape in a plan view in which a part of the circumferential direction is divided, but may be formed in a ring shape.

The outer arm 52 is provided with two arms of a first outer arm 53 and a second outer arm 54 which sandwich and hold the outer post 40 from both sides in the circumferential direction. These first outer pegs 53 and second outer pegs 54 can be elastically deformed in the circumferential direction, and are biased in advance so that the tip portions are close to each other. Thereby, the shaft body 41 of the outer pile 40 can be sandwiched between the first outer pile arm 53 and the second outer pile arm 54 .

The first clamping surface 53a of the first outer arm 53 toward the second outer arm 54 and the second clamping surface 54a of the second outer arm 54 toward the first outer arm 53 40 is sandwiched therebetween to face each other in the circumferential direction. Curved surfaces 55 that correspond to the outer diameter of the shaft body 41 of the outer pile 40 in plan view are formed so as to be collapsed on the first clamping surface 53a and the second clamping surface 54a, respectively.

The first outer leg 53 and the second outer leg 54 support the outer leg 40 so as to sandwich the shaft body 41 from the circumferential direction by the curved surface 55 . Accordingly, the outer pile 40 is not displaced in the radial direction, but is supported between the first outer pile arm 53 and the second outer pile arm 54 so as to be rotatable about the second axis O2 .

The outer pile 40 is equipped with: a cylindrical shaft body 41 extending along the second axis O2; a head 42 formed at an upper end portion of the shaft body 41; and inner and outer legs 43 and 44 extending from The lower end portion of the shaft body 41 protrudes downward.

The shaft body 41 is sandwiched between the first outer arm 53 and the second outer arm 54 in a state of being arranged inside the curved surface 55 of the first outer arm 53 and the curved surface 55 of the second outer arm 54 . The head portion 42 is formed integrally with the upper end portion of the shaft body 41 , and is disposed so as to overlap the upper surfaces of the first outer arm 53 and the second outer arm 54 .

Thereby, the outer peg 40 is sandwiched (supported) between the first outer peg 53 and the second outer peg 54 so as to be rotatable about the second axis O2 in a state where the outer peg 40 is at least prevented from falling off downward.

Moreover, the head part 42 is formed so that a part of the outer peripheral part may have mutually opposing linear parts 42a, and the adjustment tool etc. which are not shown in figure can be engaged with the head part 42 by the linear part 42a. Thereby, the outer pile 40 can be rotated around the second axis O2 by the adjustment tool.

The outermost peripheral spring portion 32 of the hairspring main body 31 described later is inserted and penetrated between the inner leg portion 43 and the outer leg portion 44 in the circumferential direction. That is, the inner leg portion 43 is arranged radially inward of the outermost spring portion 32 , and the outer leg portion 44 is arranged radially outward of the outermost spring portion 32 . Then, a portion of the outermost peripheral spring portion 32 of the hairspring body 31 inserted through the inner side of the inner leg portion 43 and the outer leg portion 44 is integrally fixed to the inner leg portion 43 and the outer leg portion 44 by, for example, welding or the like. .

As a result, the hairspring 30 is in a state in which the outermost peripheral spring portion 32 including the outer end portion 31 b is fixed (held) by the post 40 . Hereinafter, the balance spring 30 will be described in detail.

(gossamer)

As shown in FIG. 5, the hairspring 30 is equipped with a hairspring main body 31 in which the inner end portion 31a side is fixed to the swing shaft 21 via the inner post 24, and the outer end portion 31b side is held by the above-described outer post 40, Further, between the inner end portion 31a and the outer end portion 31b, the hairspring main body 31 is formed in a spiral shape by a predetermined number of turns in a plane intersecting with the first axis O1.

The hairspring body 31 is a thin plate spring made of metal such as iron or nickel, and is formed in a spiral shape along an Archimedes curve in a polar coordinate system with the first axis O1 as an origin. Thereby, the hairspring main body 31 is wound in a plurality of turns so as to be adjacent to each other at approximately equal intervals in the radial direction. In addition, the material of the hairspring main body 31 is not limited to the above-mentioned case, It can change suitably. In addition, the shape of the hairspring main body 31 is not limited to the spiral shape along the Archimedes curve described above, and may be changed to a shape in which the pitch changes (for example, a logarithmic spiral or the like).

A part of the outermost peripheral spring portion 32 that includes the outer end portion 31b and is located at the outermost side in the radial direction of the hairspring body 31 is an arc portion 34 that Separate, and the radius of curvature is formed larger than other parts. The peripheral end portion of the circular arc portion 34 becomes the outer end portion 31 b of the hairspring main body 31 . In addition, the part of the circular arc part 34 in the outermost peripheral spring part 32 is hold|maintained (fixed) to the outer pile 40 as mentioned above.

The hairspring 30 of the present embodiment formed as described above is classified into a so-called flat hairspring, and has an outer end shape in which an arc portion 34 is formed on the outermost peripheral spring portion 32 via a bent portion 33 . In the present embodiment, the hairspring 30 formed in this way may be simply referred to as "outside type spring (with outer end)" or "outside type spring (with outer end)".

However, in the present invention, the shape of the hairspring 30 is not limited to the "type with an outer end", and other shapes may be employed. For example, as shown in FIG. 6 , a simple outer-end-shaped hairspring 80 may be employed which is one of so-called flat hairsprings, but is not formed via a bent portion in the outermost peripheral spring portion 32 . Arc part. The hairspring 80 in this case is sometimes simply referred to as "without an outer end type (outer end no し)" or "without an outer end type spring (outer end no しのぜんまい)".

Furthermore, in FIG. 6 , the case where the winding direction is reversed with respect to the hairspring 30 shown in FIG. 5 is illustrated.

Also, as shown in FIG. 7 , a hairspring 90 classified as a so-called wind-up hairspring may be employed in which a part of the outermost peripheral spring portion 32 is raised (floated) in-plane, and the outer end The portion 31b is arranged on the opposite side in the radial direction from the portion where the rise starts. In some cases, the hairspring 90 in this case is simply referred to as a "winding spring (巻上ぜんまい)".

Furthermore, in FIG. 7 , the case where the winding direction is reversed 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 hairspring main body 31 and the first axis O1 is viewed from the axial direction of the pendulum shaft 21 and the outer pin is held The angle formed between the holding position P2 of the hairspring main body 31 of 40 and the second imaginary line L2 connecting the first axis O1 with the first axis O1 as the center is defined as the winding angle θ.

In addition, the unwinding position P1 refers to a position at which the innermost spring portion 35 of the hairspring main body 31 is substantially fixed to the collet 24 in the innermost circumferential spring portion 35 located at the innermost side in the radial direction including the inner end portion 31 a. Therefore, the position of the inner end portion 31 a of the hairspring main body 31 and the unwinding position P1 may not necessarily coincide in some cases. In the present embodiment, the inner end portion 31 a of the hairspring main body 31 and the unwinding position P1 are also slightly deviated in the circumferential direction.

In addition, the holding position P2 refers to a position in the hairspring main body 31 at which the outermost peripheral spring portion 32 is substantially fixed (held) to the post 40 . Therefore, the position of the outer end portion 31b of the hairspring main body 31 and the holding position P2 may not necessarily coincide in some cases. In the present embodiment, the outer end portion 31b of the hairspring main body 31 and the holding position P2 are also deviated in the circumferential direction.

Furthermore, in the present embodiment, the directions of the winding angle θ (that is, the positive (+) direction and the negative (−) direction) are defined as follows.

That is, when the winding angle θ is 0 (zero) (when the first imaginary line L1 and the second imaginary line L2 coincide) as a reference, the holding position P2 is advanced from the reference position to the winding direction side of the hairspring main body 31 The direction of θ is defined as the positive direction of the winding angle θ (represented by “+” in FIG. 5 ), and the opposite direction is defined as the negative direction of the winding angle θ (represented by “-” in FIG. 5 ). Therefore, in FIG. 5 , it is the winding angle θ in the positive direction. In contrast to this, for example, in FIG. 6 , the winding angle θ is the negative direction.

(Characteristics of hairspring)

Next, in the hairspring 30 of the present embodiment, how the isochronism changes when the outer end portion 31b side of the hairspring body 31 is rotated or moved in the radial direction is calculated in relation to the winding angle θ The results are explained.

Further, the rotational operation of rotating the outer end portion 31b side of the hairspring body 31 is to rotate the portion of the hairspring body 31 held by the post 40 in a plane intersecting the axial direction of the pendulum shaft 21 (that is, around the second axis O2 rotation). Hereinafter, it may be abbreviated as "rotation operation" in some cases.

In addition, the moving operation of moving the outer end portion 31 b side of the hairspring body 31 in the radial direction is an operation of moving the portion of the hairspring body 31 held by the post 40 in the radial direction of the balance shaft 21 . Hereinafter, it may be abbreviated as "move operation" in some cases.

In addition, the above calculation is performed by dividing the hairspring 30 into predetermined elements, applying the deformation theory of an elastic body to each element, and calculating using the geometric center of the hairspring 30 when the balance 20 vibrates as the center. to integrate the equation of motion (ordinary differential equation) of the balance 20 with time.

First, when the winding angle θ is 0 degrees, the rotation operation is performed on the case where no operation is performed on the outer end portion 31b side of the hairspring main body 31 (hereinafter, sometimes simply referred to as "before operation"). The isochronism of the three modes is calculated for the case of , and the case of moving operations on it. The respective isochronous curves based on the calculation results thereof are shown in FIG. 8 .

In FIG. 8, the isochronous curve CL1 shows the isochronous curve before the operation, the isochronous curve CL2 shows the isochronous curve after the rotation operation, and the isochronous curve CL3 shows the isochronous curve after the moving operation curve. In addition, in FIG. 8, the horizontal axis shows the swing angle of the balance wheel 20, and the vertical axis shows the difference ratio which becomes the time precision. In addition, the swing angle of the balance wheel 20 is calculated within the range of 120 degrees to 300 degrees.

In addition, the rotation operation is exemplified by the case where the portion of the hairspring main body 31 held by the post 40 is rotated 1 degree counterclockwise around the second axis O2. In addition, the moving operation is exemplified by the case where the portion of the hairspring main body 31 held by the post 40 is moved outward in the radial direction by +20 μm.

In addition, in this calculation, the case where the number of turns of the hairspring 30 is 12 turns is taken as an example. In addition, the vibration frequency of the balance wheel 20 is exemplified by 10 vibrations (ie, 10 vibrations per second (36,000 vibrations in 1 hour)).

Next, FIG. 9 shows an isochronous change curve CL4 at the time of the rotation operation, which is calculated based on the difference between the isochronous curve CL1 before the operation and the isochronous curve CL2 after the rotation operation and calculated based on the calculation result. . Similarly, FIG. 9 shows an isochronous change curve CL5 at the time of the moving operation, which is calculated based on the difference between the isochronous curve CL1 before the operation and the isochronous curve CL3 after the moving operation and calculated based on the calculation result. . In addition, in FIG. 9, the horizontal axis shows the swing angle of the balance 20, and the vertical axis shows the isochronous change amount which becomes the time precision.

Next, in the isochronous change curve CL4 at the time of the rotation operation, the calculation of subtracting the minimum value (maximum value-minimum value) from the maximum value of the isochronous change amount is performed.

In the example of FIG. 9 , the value at the swing angle of 220 degrees is the maximum value (about 2.16), and the value at the swing angle of 120 degrees is the minimum value (about -2.05). Therefore, (maximum value - minimum value) becomes about 4.21. Therefore, approximately 4.21, which is this value (maximum value-minimum value), becomes the maximum change amount of the isochronous change at the time of the rotation operation where the winding angle θ is 0 degrees.

Similarly, in the isochronous change curve CL5 at the time of the moving operation, the calculation of subtracting the minimum value (maximum value-minimum value) from the maximum value of the isochronous change amount is performed. In the example of FIG. 9 , the value at the swing angle of 300 degrees is the maximum value (about -1.02), and the value at the swing angle of 200 degrees is the minimum value (about -1.44). Therefore, (maximum value - minimum value) becomes about 0.42. Therefore, approximately 0.42, which is this value (maximum value-minimum value), becomes the maximum change amount of the isochronous change at the time of the moving operation where the winding angle θ is 0 degrees.

Further, as shown in FIG. 9, the isochronous change curve CL4 at the time of the rotation operation becomes such that an extreme value (maximum value, ie, the above-mentioned maximum value) is included in the range of the swing angle of 200 degrees to 250 degrees upward convex curve. Similarly, the isochronous change curve CL5 at the time of the moving operation is a downwardly convex curve that includes an extreme value (a minimum value, that is, the above-mentioned minimum value) within a range of a swing angle of 180 to 250 degrees.

The tendency of such a curve is not limited to the case where the winding angle θ is 0 degrees, and the same tendency is shown regardless of the winding angle θ (see FIGS. 14 and 15 ).

Next, within the range of the winding angle θ from (-180 degrees to +180 degrees), the above-mentioned calculation is repeated for each degree of the winding angle, and the rotation operation at each winding angle θ, etc. The maximum change amount of temporal change and the maximum change amount of isochronous change at the time of moving operation are calculated separately.

Then, the maximum change amount of the isochronous change at the time of the rotation operation and the maximum change amount of the isochronous change at the time of the moving operation at each winding angle θ are shown in FIG. chart. In FIG. 10 , the horizontal axis shows the winding angle θ, and the vertical axis shows the maximum change amount of the isochronous change.

In FIG. 10 , the value of the maximum change amount of the isochronous change at the time of the rotation operation at each winding angle θ is indicated by the symbol “□”. Then, a curve in which the values of the maximum change amount at each winding angle θ indicated by the symbol "□" are connected is a change curve CL6 of the maximum change amount of the isochronous change during the rotation operation.

Likewise, the value of the maximum change amount of the isochronous change at the time of the moving operation at each winding angle θ is indicated by the symbol "◇". Then, a curve in which the values of the maximum change amount at each winding angle θ indicated by the symbol "◇" are connected becomes the change curve CL7 of the maximum change amount of the isochronous change at the time of the moving operation.

As shown in FIG. 10 , both the change curve CL6 and the change curve CL7 become curves in which the maximum value and the minimum value of the maximum change amount alternately and periodically appear. Then, a state is established in which the maximum value of the maximum change amount in the change curve CL6 and the minimum value of the maximum change amount in the change curve CL7 correspond to approximately the same winding angle θ, and the change curve CL6 The minimum value of the maximum change amount corresponds to the maximum value of the maximum change amount in the change curve CL7 within a range of approximately the same winding angle θ. That is, the change curve CL6 and the change curve CL7 are in a state in which the phases are deviated as long as the winding angle θ is about 90 degrees to 110 degrees.

In addition, in FIG. 10 , in order to easily compare the change curve CL6 and the change curve CL7, the curves of the change curve CL6 and the change curve CL7 are modified so that the maximum value of the respective maximum change amounts shows a value of about 1.

However, even in this case, since only the inclinations of the curve CL6 and the curve CL7 change, the change with respect to the winding angle θ is the same as before the correction. Furthermore, since the change curves CL6 and CL7 are substantially proportional to the amount of the rotation operation and the movement operation, it is the same as the case of correcting the movement amount.

From the above, it can be understood from FIG. 10 that in the hairspring 30 with the outer end of the present embodiment, when the outer end portion 31b side of the hairspring main body 31 is rotated or moved in the radial direction , how the isochronity varies depending on the winding angle θ.

Also, the above-described series of calculations are performed for the hairspring 80 without an outer end shown in FIG. 6 and the hairspring 90 shown in FIG. 7 , respectively.

FIG. 11 shows the change curves CL8 and CL8 of the maximum change amount of the isochronous change at the time of the rotation operation obtained by calculating the hairspring 80 shown in FIG. 6 (without the outer spring) The change curve CL9 of the maximum change amount of the isochronous change at the time of the moving operation. As shown in FIG. 11 , the change curve CL8 and the change curve CL9 are curves showing the same tendency as the change curve CL6 and the change curve CL7 described above.

12 shows a change curve CL10 and a change curve CL10 of the maximum change amount of the isochronous change at the time of the rotation operation obtained by calculating the balance spring 90 (winding spring) shown in FIG. 7 . The change curve CL11 of the maximum change amount of the isochronous change at the time of the moving operation. As shown in FIG. 12 , the change curve CL10 and the change curve CL11 are curves showing the same tendency as the change curve CL6 and the change curve CL7 described above.

FIG. 13 is a graph in which the respective change curves of FIGS. 10 to 12 are integrated into one. As shown in FIG. 13 , even in the case where the shape of the outer end of the hairspring 30 is either, the change curve CL12 of the maximum change amount of the isochronous change at the time of the rotation operation and the isochronous change at the time of the moving operation The change curve CL13 of the maximum change amount also shows the same tendency.

Due to the above, the hairspring 30 with the outer end of the present embodiment has the following characteristics. In addition, the following characteristics are also the same even if the spring without an outer end (hairspring 80 ) and the winding spring (hairspring 90 ) are used as described above.

That is, with regard to the hairspring main body 31, when the winding angle θ is limited within the predetermined first angle range E1, the isochronous amount of change due to the rotational operation around the second axis O2 is more pronounced than that due to the change in the radial direction. The amount of isochronous change due to the moving operation is larger, and the wrapping angle θ is an angle different from the first angle range E1, and, when limited to the predetermined second angle range E2, since the radial direction The case where the isochronous change amount changed due to the moving operation of , is larger than the isochronous change amount changed due to the rotation operation about the second axis O2 .

As the first angle range E1, the winding angle θ belongs to (-125 degrees ±5 degrees to -215 degrees (ie, +145 degrees) ±5 degrees) or (-35 degrees ±5 degrees to +55 degrees ±5 degrees) within the range. As the second angle range E2, the winding angle θ falls within the range of (-125 degrees ±5 degrees to -35 degrees ±5 degrees) or (+55 degrees ±5 degrees to +145 degrees ±5 degrees).

Furthermore, as the first angle range E1, when the winding angle θ is included in the angle range within the range of (-170 degrees ±α degrees) or (+10 degrees ±α degrees), the hairspring main body 31 is due to The maximum isochronous change amount due to the rotational operation around the second axis O2 becomes the largest, and on the contrary, the isochronous maximum change amount due to the movement in the radial direction becomes the smallest.

In addition, the above-mentioned α is an angle included in the range of 5 degrees to 30 degrees. In this case, in the first angle range E1, the smaller the above-mentioned α is from 30 degrees to 5 degrees, the more effectively the above-mentioned characteristics can be achieved. For example, compared with when the winding angle θ is contained in the range of (-170 degrees ±30 degrees) or (+10 degrees ±30 degrees), is contained in (-170 degrees ±25 degrees) or (+10 degrees) The above-mentioned characteristics can be more effectively achieved when the temperature is within the range of ±25 degrees. More preferably, when the winding angle θ is included in the range of (-170 degrees ± 5 degrees) or (+10 degrees ± 5 degrees).

In addition, α is considered to decrease every 5 degrees from 30 degrees, that is, to decrease in the 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 included in the angular range within the range of (-80 degrees ±α degrees) or (+100 degrees ±α degrees), due to the radial direction The maximum isochronous change amount due to the movement operation becomes the largest, and on the contrary, the isochronous maximum change amount due to the rotation operation about the second axis O2 becomes the smallest.

In addition, the above-mentioned α is an angle included in the range of 5 degrees to 30 degrees similarly to the case demonstrated by the 1st angle range E1. In this case, within the second angle range E2, the smaller the above-mentioned α is from 30 degrees to 5 degrees, the more effectively the above-mentioned characteristics can be achieved. For example, compared with when the winding angle θ is contained in the range of (-80 degrees ±30 degrees) or (+100 degrees ±30 degrees), is contained in (-80 degrees ±25 degrees) or (+100 degrees) The above-mentioned characteristics can be more effectively achieved when the temperature is within the range of ±25 degrees. More preferably, when the winding angle θ is included in the range of (-80 degrees ± 5 degrees) or (+100 degrees ± 5 degrees).

In addition, α is considered to decrease every 5 degrees from 30 degrees, that is, to decrease in the order of 30 degrees, 25 degrees, 20 degrees, 15 degrees, 10 degrees, and 5 degrees.

Explain in more detail.

FIG. 14 is a diagram showing an isochronous change curve due to a rotational operation around the second axis O2 , and FIG. 15 is a diagram showing an isochronous change curve due to a moving operation in the radial direction .

As shown in FIGS. 14 and 15 , in the case where the winding angle θ is +167 degrees or +13 degrees, the isochronism changes with good sensitivity due to the rotation operation, but on the contrary, for the direction The movement operation in the radial direction becomes insensitive, and it becomes difficult to change the movement operation. Also, in the case where the winding angle θ is -77 degrees or +103 degrees, the isochronism changes with good sensitivity due to the moving operation, but on the contrary, it becomes insensitive to the rotating operation, and the rotation operation become difficult to change.

In addition, FIG. 13 shows the results in the case where the number of turns is 12 and the vibration frequency of the balance wheel 20 is 10 vibrations (that is, 36,000 vibrations in 1 hour) as described above, but even when the number of turns is The same result can be obtained even when the vibration frequency is changed.

For example, FIG. 16 is a diagram corresponding to FIG. 13 when the number of turns is 14 and the vibration frequency of the balance 20 is 8 vibrations (that is, 28800 vibrations in 1 hour). As is also apparent from this FIG. 16 , even when the number of turns and the vibration frequency are changed, the above-described characteristics are present.

As shown in FIG. 5 , the hairspring 30 configured as described above has the inner end portion 31 a side fixed to the balance shaft 21 via the inner post 24 , and the outer end portion 31 b side is fixed (held) to the outer post 40 . In particular, in the present embodiment, the outer pile ring 50 holds the outer pile 40 so as to be rotatable about the second axis O2 in a state where the winding angle θ is limited 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 including the governor 13 configured as described above will be described.

In addition, as an initial state, the outer pin 40 is located at the reference rotational position, and the hairspring main body 31 is not displaced around the second axis O2 by the outer pin 40 .

In such an initial state, in the case of performing isochronous adjustment, the outer peg 40 can be made together with the outer peg 50 by, for example, rotating the outer peg 50 relative to the balance 20 about the first axis O1 Since it moves in the circumferential direction, the winding angle θ of the hairspring 30 can be set to an arbitrary angle. Thereby, the winding angle θ can be appropriately set to be limited within the first angular range E1 or within the second angular range E2. That is, the winding angle θ can be set to +13 degrees within the first angle range E1.

In addition, it is not limited to the above-mentioned case, and the external post 40 may be pre-fixed to the hairspring body 31 so that, for example, the winding angle θ is limited within the first angular range E1 or the second angular range E2, that is, the winding angle θ It is set to +13 degrees within the first angle range E1.

Next, a rotation operation of rotating the outer pile 40 with the winding angle θ set to +13 degrees around the second axis O2 is performed. Thereby, isochronous changes can be made, and isochronous adjustment can be performed.

In particular, with regard to the hairspring main body 31, in the case where the winding angle θ is limited within the first angular range E1, as described above, the case of the isochronous change amount due to the rotational operation is smaller than that due to the change in the radial direction. The amount of isochronous change due to the movement operation is larger, and thus the isochronism can be changed with better sensitivity in the case of the rotation operation than in the case of the movement operation in the radial direction. Therefore, the isochronism can be changed by the amount of change caused by the rotation operation in a state where it is hardly affected by the moving operation in the radial direction, and the isochronism can be quantitatively performed without using the speed needle. In addition, the isochronous adjustment can be easily and accurately performed.

Also, since the winding angle θ is +13 degrees, as shown in FIGS. 14 and 15 , with regard to the hairspring main body 31 , the maximum amount of change in isochronism due to the rotational operation becomes the largest, on the contrary, The maximum amount of change in isochronism due to the movement operation in the radial direction becomes the smallest. Therefore, the isochronism changes with high sensitivity in accordance with the rotation operation, but becomes insensitive to the movement operation in the radial direction, and becomes difficult to change for the movement operation.

Therefore, by performing the rotation operation of the outer pile 40 in the 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 easiness and accuracy can be further improved. Well done isochronous adjustment.

In particular, the isochronous variation amount due to the rotation operation of the outer pile 40 is substantially proportional to the rotation operation amount. Therefore, the isochronous property can be changed by the amount of change corresponding to the rotation operation of the outer pile 40, and the isochronous property can be quantitatively adjusted.

In particular, with regard to the hairspring main body 31, due to the isochronous change caused by the polarity that becomes an extreme value in the range of the swing angle of the balance 20 of 200 to 250 degrees, when the swing angle of the balance 20 is 200 to 250 degrees When the isochronous adjustment is performed within the range, even if it is a minute rotation operation, the isochronous sensitivity can be changed effectively and efficiently, and the isochronous adjustment can be easily and easily performed.

As described above, according to the governor 13 including the hairspring 30 of the present embodiment, the isochronous adjustment can be easily and accurately performed without using the fast and slow needles.

In particular, unlike the case where the isochronous adjustment is performed using tweezers or the like as in the prior art, after the winding angle θ is appropriately set, it is possible not only to go through a series of procedures for rotating the outer pile 40 , but also to be smooth. It is possible to perform isochronous adjustment precisely, and to change the isochronism quantitatively. Therefore, the isochronous adjustment can be easily and appropriately performed.

Furthermore, since the movement 10 and the timepiece 1 according to the present embodiment are provided with the above-described governor 13, the movement 10 and the timepiece 1 can be used as high-performance movement with less error in the rate of difference.

(Variation of the first embodiment)

In the first embodiment, the winding angle θ is taken as +13 degrees, but it is not limited to this case as long as it falls within the first angle range E1 (ie, (-125 degrees ± 5 degrees to -215 degrees ± 5 degrees) Or (-35 degrees ± 5 degrees to +55 degrees ± 5 degrees) range).

Among them, it is particularly preferable that the winding angle θ falls within the range of (−170 degrees±α degrees) or (+10 degrees±α degrees), and that α falls within the range of 5 degrees to 30 degrees. Among them, it is more preferable to set in the following order.

・The winding angle θ falls within the range of (-170°±30°) or (+10°±30°).

・The winding angle θ is within the range of (-170°±25°) or (+10°±25°).

・The winding angle θ falls within the range of (-170°±20°) or (+10°±20°).

・The winding angle θ is within the range of (-170°±15°) or (+10°±15°).

・The winding angle θ is within the range of (-170°±10°) or (+10°±10°).

・The winding angle θ is within the range of (-170°±5°) or (+10°±5°).

Therefore, it is most preferable that the winding angle θ falls within the range of (-170 degrees±5 degrees) or (+10 degrees±5 degrees). In this case, the same effects as those of the first embodiment can be achieved.

Furthermore, in the first embodiment, the hairspring 30 with the outer end is used, but the hairspring 80 without the outer end shown in FIG. 6 or the winding spring type hairspring shown in FIG. 7 may also be used 90. Even in these cases, the same characteristics as those of the outer-end type hairspring 30 are provided as described above, so that the same functions and effects as those of the first embodiment can be achieved.

For example, as shown in FIGS. 17 to 19 , it is also possible to use the governor 100 provided with the wind-up spring-type hairspring 90 .

Regarding the hairspring 90 in this case, a part of the outermost peripheral spring portion 32 in the hairspring main body 31 is raised, and after extending to the opposite side in the radial direction from the raised starting point portion, it is fixed (held) to the outer pin 40. In addition, in the example shown in the figure, the post 40 fixes (holds) the outer end portion 31b side of the hairspring 90 so that the winding angle θ becomes -167 degrees.

In the case of the governor 100 configured in this way, since the winding spring type hairspring 90 has the same characteristics as the outer end type hairspring 30, and the winding angle θ is within (-170°±5°) Also within the range of -167 degrees, as in the first embodiment, the isochronous adjustment can be easily and accurately performed by the rotation operation of the outer pile 40 .

(Second Embodiment)

Next, a second embodiment of the present invention will be described with reference to the drawings. In addition, in this 2nd Embodiment, the same code|symbol is attached|subjected to the part which is the same as the component in 1st Embodiment, and the description is abbreviate|omitted.

In the first embodiment, the outer pile ring 50 supports the outer pile 40 so as to be rotatable about the second axis O2, but in the second embodiment, the outer pile ring 50 supports the outer pile so as to be movable in the radial direction 40.

As shown in FIGS. 20 and 21 , the governor 110 of the present embodiment is equipped with a post (the second member according to the present invention) 120 that fixes (holds) the outer end portion 31 b of the hairspring main body 31 side; and an outer pile ring (support member according to the present invention) 130, which supports the outer pile 120 so as to be movable in the radial direction.

In addition, in FIG. 20, in order to make it easy to see a drawing, a part of the structural product of the governor 110 is abbreviate|omitted.

The outer peg 130 is equipped with the coupling ring 51 and the outer peg 52 having the first outer peg 53 and the second outer peg 54 as in the first embodiment, and can be opposed to the balance wheel 20 about the first axis O1 rotate.

The first outer peg 53 and the second outer peg 54 can be elastically deformed in the circumferential direction, and are biased in advance so that the tip portions are close to each other. Thereby, the shaft body 41 of the outer pile 120 can be sandwiched between the first outer pile arm 53 and the second outer pile arm 54 .

In addition, the curved surface 55 in the first embodiment is not formed on the first clamping surface 53a of the first outer arm 53 and the second clamping surface 54a of the second outer arm 54 in this embodiment. Therefore, the first holding surface 53a and the second holding surface 54a are flat surfaces.

The outer pile 120 is provided with the shaft 41 , the head 42 , the inner leg 43 , and the outer leg 44 as in the first embodiment. However, the shaft body 41 is formed with: a first contact surface 41a which is in surface contact with the first clamping surface 53a of the first outer peg 53; and a second contact surface 41b so as to face each other in the circumferential direction. , which is in surface contact with the second clamping surface 54 a of the second outer pile arm 54 .

Thus, in a state where the first clamping surface 53a is brought into surface contact with the first contact surface 41a and the second clamping surface 54a is brought into surface contact with the second contact surface 41b, the first outer arm 53 and the The second outer pile arm 54 clamps the outer pile 120 . Thereby, in a state where the rotation is restricted, the outer pile 120 is supported between the first outer pile arm 53 and the second outer pile arm 54 so as to be movable in the radial direction.

In addition, when the outer peg 120 is moved in the radial direction, for example, after the adjustment tool is engaged with the head 42, the outer peg 120 can be moved so as to resist the first outer peg 53 and the second outer peg 54 clamping force between.

Furthermore, in this embodiment, the outer pile ring 130 is movably supported by the winding angle θ being -77 degrees.

(Isochronous adjustment of hairspring)

Next, the case where the isochronous adjustment of the hairspring 30 is performed using the governor 110 of the present embodiment configured as described above will be described.

In addition, as the initial state, the outer pin 120 is located at the reference position, and the hairspring main body 31 is not displaced in the radial direction by the outer pin 120 . In addition, the winding angle θ is set to −77 degrees within the second angle range E2 by the same method as in the first embodiment.

In such an initial state, a moving operation of moving the outer pile 120 with the winding angle θ set to -77 degrees in the radial direction is performed. Thereby, isochronous changes can be made, and isochronous adjustment can be performed.

In particular, with regard to the hairspring main body 31, when the winding angle θ is limited within the second angular range E2, as described above, the isochronous amount of change due to the moving operation in the radial direction is less than that due to Since the amount of isochronous change due to the rotational operation is larger, the isochronous change can be changed with better sensitivity in the case of the movement operation in the radial direction than in the case of the rotational operation. Therefore, the isochronism can be changed by the amount of change caused by the moving operation in the radial direction in a state where it is hardly affected by the rotation operation.

Also, since the winding angle θ is -77 degrees, as shown in FIGS. 14 and 15 , with respect to the hairspring main body 31 , the isochronous maximum change amount due to the movement operation in the radial direction becomes the largest , on the contrary, the maximum amount of change in isochronism due to the rotation operation becomes the smallest. Therefore, the isochronism changes with high sensitivity in accordance with the movement operation, but becomes insensitive to the rotation operation, and becomes difficult to change for the rotation operation.

Therefore, by performing the moving operation in a state where the winding angle θ is -77 degrees, the isochronism can be changed more efficiently by the amount of change caused by the operation, and the operation can be performed more easily and accurately. Timely adjustment.

In particular, as in the case of the rotation operation in the first embodiment, the isochronous change amount due to the movement operation of the outer pile 40 is substantially proportional to the movement operation amount. Therefore, the isochronous property can be changed by the amount of change corresponding to the movement operation of the outer pile 40, and the isochronous property can be adjusted quantitatively.

Because of the above, in the case of the present embodiment, the isochronous adjustment can be quantitatively performed without using the speed needle, and the isochronous adjustment can be easily and accurately performed.

In particular, with regard to the hairspring main body 31, due to the isochronous change caused by the polarity that becomes an extreme value in the range of the swing angle of the balance 20 of 200 to 250 degrees, when the swing angle of the balance 20 is 200 to 250 degrees When the isochronous adjustment is performed within the range, even if it is a minute movement operation, the isochronous sensitivity can be changed effectively and efficiently, and the isochronous adjustment can be easily and easily performed.

As described above, even in the governor 110 including the hairspring 30 according to the present embodiment, the isochronous adjustment can be easily and accurately performed without using the fast and slow needles.

(Variation of the second embodiment)

In the second embodiment, the winding angle θ is taken as -77 degrees, but it is not limited to this case as long as it falls within the second angle range E2 (ie, (-125 degrees ±5 degrees to -35 degrees ±5 degrees) Or (+55°±5° to +145°±5°) range).

Among them, it is particularly preferable that the winding angle θ falls within the range of (−80 degrees±α degrees) or (+100 degrees±α degrees), and α falls within the range of 5 degrees to 30 degrees. Among them, it is more preferable to set in the following order.

・The winding angle θ is within the range of (-80°±30°) or (+100°±30°).

・The winding angle θ is within the range of (-80°±25°) or (+100°±25°).

・The winding angle θ falls within the range of (-80°±20°) or (+100°±20°).

・The winding angle θ falls within the range of (-80°±15°) or (+100°±15°).

・The winding angle θ is within the range of (-80°±10°) or (+100°±10°).

・The winding angle θ is within the range of (-80°±5°) or (+100°±5°).

Therefore, it is most preferable that the winding angle θ falls within the range of (-80 degrees±5 degrees) or (+100 degrees±5 degrees). In this case, the same effects as those of the second embodiment can be achieved.

Furthermore, in the second embodiment, the hairspring 80 without an outer end shown in FIG. 6 or the winding spring type hairspring 90 shown in FIG. 7 may be used. In these cases as well, since the same characteristics as those of the outer-end type hairspring 30 are provided as described above, the same functions and 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 addition, in the third embodiment, the same components as those in the second embodiment are denoted by the same reference numerals, and the description thereof will be omitted.

In the second embodiment, the first outer arm 53 and the second outer arm 54 are used to support the outer pile 120 so as to be movable in the radial direction, but in the third embodiment, the outer pile presser is used to support the outer pile 120 . Support the outer pile in a movable manner.

As shown in FIG. 22 , the governor 140 of the present embodiment is equipped with: a post (the second member according to the present invention) 150 that fixes (holds) the side of the outer end portion 31 b of the hairspring main body 31 ; The pile ring (support member according to the present invention) 160 supports the outer pile 150 so as to be movable in the radial direction;

In addition, in FIG. 22, in order to make it easy to see a drawing, a part of the constituent product of the governor 140 is omitted.

As shown in FIGS. 22 and 23 , the outer peg ring 160 is equipped with: a coupling ring 51 ; a first arm portion 161 extending outward in the radial direction from the coupling ring 51 ; and a second arm portion 162 with The first arm portion 161 is integrally formed and extends in the circumferential direction.

The second arm portion 162 is integrally formed with the distal end portion (outer end portion) of the first arm portion 161 , and is formed in an elliptical shape or a circular arc shape in plan view extending in the circumferential direction. In the present embodiment, the central portion in the circumferential direction in the second arm portion 162 is connected to the distal end portion of the first arm portion 161 .

A slit-shaped first guide groove 163 is formed in a central portion of the second arm portion 162 in the circumferential direction. The first guide groove 163 penetrates the second arm portion 162 up and down and extends outward in the radial direction. Open your mouth. The first guide groove 163 is formed in a linear shape extending in the radial direction.

In the peripheral end portions of the second arm portion 162 located on both sides in the circumferential direction with the first guide groove 163 interposed therebetween, screw holes 164 extending up and down are respectively formed.

The outer pile 150 is provided with: a cylindrical shaft body 41 extending along the second axis O2; a flange portion 151 which is positioned further below the upper end portion of the shaft body 41 and is integrally formed with the shaft body 41, Furthermore, the diameter is enlarged compared to the shaft body 41 ; and the inner leg portion 43 and the outer leg portion 44 protrude downward from the lower end portion of the shaft body 41 . In addition, in FIGS. 22 and 23 , the inner leg portion 43 and the outer leg portion 44 are blocked by the outer peg ring 160 .

The shaft body 41 is formed in a columnar shape with an outer diameter smaller than the groove width of the first guide groove 163 . The outer diameter of the flange portion 151 is larger than the groove width of the first guide groove 163 and is formed in a circular shape in a plan view. Thereby, the outer pile 150 is arranged in the first guide groove 163 so as to be movable in the radial direction in a state where the flange portion 151 and the second arm portion 162 are overlapped.

As shown in FIGS. 22 and 24 , the outer pile presser 170 is a plate extending in the circumferential direction corresponding to the shape of the second arm portion 162 , and is arranged so as to overlap the upper surface of the second arm portion 162 . . In addition, the outer pile presser 170 is formed so that the outer diameter thereof corresponds to the outer shape of the second arm portion 162 so that the pile presser 170 covers approximately the entire surface of the second arm portion 162 .

A slit-shaped second guide groove 171 is formed in a portion of the outer pile presser 170 located at the center in the circumferential direction. The second guide groove 171 penetrates the outer pile presser 170 up and down and extends in the radial direction. . The second guide groove 171 has the same groove width as the first guide groove 163 and is arranged above the first guide groove 163 . The upper end portion of the shaft body 41 in the outer pile 150 is inserted through the second guide groove 171 .

A groove 172 extending in the radial direction is formed in a portion located at the center in the circumferential direction on the lower surface of the outer pile presser 170 . The width of the groove 172 is formed to be larger than the diameter of the flange portion 151 of the outer pile 150 . Thereby, in the state where the flange part 151 is accommodated in the groove|channel 172, the pile press 170 can overlap with the upper surface of the 2nd arm part 162. However, the depth of the groove 172 is formed to be slightly shallower than the thickness of the flange portion 151 . Thereby, in the state which pressed the flange part 151 to the 2nd arm part 162, the pile press 170 overlaps with the upper surface of the 2nd arm part 162.

Further, in peripheral end portions of the outer pile presser 170 located on both sides in the circumferential direction with the second guide groove 171 interposed therebetween, mounting holes 175 for fixing the screws 173 are formed. The outer pile presser 170 attaches the fixing screw 173 to the threaded hole 164 through the attachment hole 175 , and thereby, in a state where the flange portion 151 is sandwiched between the second arm portion 162 and the second arm portion 162 , relative to the second arm portion 162 and combined together.

(Isochronous adjustment of hairspring)

According to the governor 140 of the present embodiment configured as described above, since the outer pile 150 can be moved in the radial direction, the same functions and effects as those of the second embodiment can be achieved.

In addition, in the case of the present embodiment, since the clamping of the flange portion 151 can be released by loosening or removing the fixing screw 173, the outer post 150 can be caused to follow the first guide groove 163 and the second guide groove. 171 moves in the radial direction. Then, after the moving operation, by tightening the fixing screws 173, the flange portion 151 can be sandwiched between the second arm portion 162 and the outer pile presser 170, so that the outer pile 150 can be more stably fixed to the moving position after the operation.

Therefore, the position of the outer pile 150 can be effectively prevented from being displaced by, for example, unintentionally moving in the radial direction.

The embodiments of the present invention have been described above, but these embodiments are presented as examples and are not intended to limit the scope of the invention. The embodiments can be implemented in various other forms, and various omissions, substitutions, and changes can be made without departing from the gist of the invention. In the embodiment or its modifications, for example, examples that can be easily conceived by those skilled in the art, examples that are substantially the same, examples of equivalent ranges, and the like are included.

For example, in each of the above-described embodiments, the case where the inner end portion side of the hairspring main body is fixed to the balance shaft of the balance has been described as an example, but the present invention is not limited to this case. For example, the inner end side of the hairspring main body may be fixed to a first component (ie, a component for a timepiece other than the balance) that rotates around the axis.

Symbol Description

θ winding angle

E1 first angle range

E2 Second angle range

L1 first imaginary line

L2 second imaginary line

O1 first axis (the axis of the balance wheel)

P1 Unwind position

P2 hold position

1 clock

10 Movements (movements for timepieces)

13, 100, 110, 140 governor

20 balance wheel (first part)

21 Swing axis

30, 80, 90 hairspring

31 Hairspring body

31a Inner end of hairspring body

31b Outer end of hairspring body

40, 120, 150 outer pile (second part)

50, 130, 160 outer pile ring (support part).

Claims (9)

1. A balance spring comprises a balance spring main body, an inner end part side of the balance spring main body is fixed on a first component rotating around an axis, an outer end part side is held on a second component, and the balance spring main body is formed in a vortex shape according to a preset number of turns in a plane crossed with the axis between the inner end part and the outer end part,

when an angle around the axis formed between a first imaginary line joining the unwinding position of the spring main body and the axis and a second imaginary line joining the holding position of the spring main body held by the second member and the axis is taken as a winding angle as viewed from the axis direction,

the outer end side is held by the second member so as to rotate in the plane in a state where the winding angle is limited within a predetermined first angular range, or is held by the second member so as to move in a radial direction of the balance spring main body in a state where the winding angle is limited within a predetermined second angular range,

the balance spring main body further has a case where an amount of isochronous change that changes due to rotation in the plane is larger than an amount of isochronous change that changes due to movement in the radial direction when the winding angle is limited within the first angle range, and has a case where the amount of isochronous change that changes due to movement in the radial direction is larger than the amount of isochronous change that changes due to rotation in the plane when the winding angle is limited within the second angle range.

2. Balance spring according to claim 1,

when the direction in which the second member advances to the winding direction side of the balance spring main body is taken as the positive direction of the winding angle and the opposite direction thereof is taken as the negative direction of the winding angle, with reference to when the winding angle is zero,

the first angle range becomes an angle range in which the winding angle is included in a range of (-125 degrees + -5 degrees to-215 degrees + -5 degrees), or (-35 degrees + -5 degrees to +55 degrees + -5 degrees),

the second angle range becomes an angle range in which the winding angle is included in a range of (-125 degrees + -5 degrees to-35 degrees + -5 degrees), or (+55 degrees + -5 degrees to +145 degrees + -5 degrees).

3. Balance spring according to claim 2,

the first angle range becomes an angle range in which the winding angle is included in a range of (-170 degrees + -alpha degrees), or (+10 degrees + -alpha degrees),

the second angle range becomes an angle range in which the winding angle is included in a range of (-80 degrees + -alpha degrees), or (+100 degrees + -alpha degrees),

the α is an angle included in a range of 5 degrees to 30 degrees.

4. Balance spring according to claim 3,

the first angle range becomes an angle range in which the winding angle is included in a range of (-170 degrees + -5 degrees), or (+10 degrees + -5 degrees),

the second angle range becomes an angle range in which the winding angle is included in a range of (-80 degrees ± 5 degrees), or (+100 degrees ± 5 degrees).

5. Balance spring according to any of claims 1 to 4,

said first component becomes a balance wheel,

the inner end portion of the balance spring main body is fixed to a balance staff in the balance.

6. Balance spring according to claim 5,

in the balance spring main body, the outer end portion side rotates in the plane, or the outer end portion side moves in a radial direction of the balance staff, and thereby, a curve including an extremum in a range where a balance angle of the balance is 200 degrees to 250 degrees changes isochronously.

7. A governor equipped with:

a balance spring according to claim 5 or 6;

the balance wheel;

the second component; and

a support member that is combined so as to be rotatable about the axis relative to the balance and that movably supports the second member,

the support member supports the second member so as to be rotatable in the plane, or movably in a radial direction of the pendulum shaft.

8. Movement for a timepiece, equipped with a speed regulator according to claim 7.

9. A timepiece equipped with the movement for a timepiece according to claim 8.

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