CH715096B1 - Regulating organ comprising a hairspring, timepiece movement and timepiece. - Google Patents

Abstract

The invention relates to an adjusting member comprising a hairspring (30) and the achievement of easy and precise isochronous adjustment without using a racket. The hairspring (30) includes a hairspring main body (31) of which an inner end (31a) is fixed to a balance wheel (20) and an outer end (31b) is held by a pin (40), in which the main body hairspring (31) is held by the pin (40), such that the outer end (31b) can rotate in a plane in a state of the system where a winding angle (θ) of the hairspring is located in a first angle range (E1), or is retained by the eyebolt (40), such that the outer end (31b) moves in a radial direction in a state of the system where the winding angle (θ ) of the hairspring is in a second angle range (E2), and in which, in the hairspring main body (31), when the winding angle (θ) is in the first angle range ( E1), an isochronous variation due to rotation in the plane is greater than an isochronous variation due to movement in the radial direction, and when the winding angle (θ) is in the second angle range (E2), an isochronous variation due to movement in the radial direction is larger than an isochronous variation due to rotation in the plane.

Description

BACKGROUND OF THE INVENTION

1. Field of the invention

[0001] The present invention relates to a regulating member, a timepiece movement and a timepiece.

2. Description of the prior art

[0002] In a mechanical timepiece, it is important that a spiral balance is governed to correspond to a range of specific values in which a period of oscillation is predetermined. If the oscillation period deviates from this specific value range, the running deviation rate (timepiece delay and advance level) of the mechanical timepiece changes.

[0003] As a method of adjusting this rate, a method is generally known for adjusting the length (called effective length) of the hairspring, an internal end of which is fixed to a balance shaft of the balance wheel and an external end is fixed to a piton, by a regulator often referred to as a racket.

[0004] The racket mainly comprises an adjustment key rotatably mounted around a central balance axis, and arranged outside in the radial direction relative to the hairspring, and a racket pin arranged inside the hairspring in the radial direction. Therefore, the hairspring is disposed between the racket adjustment key and the racket pin, and is formed to oscillate in the radial direction therebetween.

[0005] In the case where the rate of deviation is adjusted using this type of racket, the position of the fixing pin of the external end of the hairspring is generally adjusted, and then the racket is rotated around the central axis of the balance wheel to adjust positions of the racket adjustment key and the racket pin in the direction of the length of the hairspring. Therefore, when the hairspring oscillates, it is possible to adjust the effective length between a contact point where the hairspring is brought into contact with the racket key or racket pin, and the inner end of the hairspring, and d 'perform the adjustment of the walking deviation rate.

[0006] In addition, rackets are also known capable of carrying out an isochronous adjustment (play adjustment) of the step deviation rate by adjusting a quantity of clearance (play level) which is constituted by a spacing between the key adjustment of the racket and the racket pin by performing the step deviation rate adjustment operation.

[0007] The hairspring repeatedly performs movements causing it to come into contact with the adjustment key of the racket, then to separate from this key, and to come into contact with the racket pin, then to separate of the latter when the pendulum makes a round trip, so that states where the effective length is respectively small and long are alternately repeated. Additionally, in the hairspring, since the level of oscillation changes depending on the amount of winding, the moment of contact with the racket adjustment key or racket pin changes. Therefore, for example, the time corresponding to a state where the effective length is small may be prolonged, and it may be feared that the isochronism of the walking deviation rate will be affected.

[0008] Consequently, the game adjustment is carried out by the racket, such that the intensity of the spring constant during a cycle varies according to the amplitude, thus adjusting the isochronism. More particularly, in a case where the mechanical timepiece having high precision is assembled, it is important to perform isochronous adjustment.

However, in the case where no racket is provided, for example, when adjusting the time of a regulating member by a balance wheel with variable inertia or the like, it is not possible to perform the isochronous adjustment using a snowshoe. Therefore, the isochronism of the assembled regulating member depends on the precision of each of the configuration components, an assembly position, or the like, thereby causing isochronism variations.

[0010] Furthermore, in the case where the isochronous adjustment is carried out without using a racket, we know for example a method for manually correcting essentially a position, a shape, or the like of the external end of the hairspring using pliers or similar. Furthermore, as a hairspring used in a case where this type of correction is carried out, hairsprings are known in which a stiffening portion at least partially compensating for a variation in speed of a movement depending on an amplitude of oscillation of the balance generated by an escapement is formed at an outermost peripheral part of the hairspring (for example, see JP-T-2014-525591 (patent document 1)).

However, according to this method known from the prior art correcting the external end of the hairspring, the level of adjustment is not quantitative and very delicate work is required. Therefore, it was very difficult to adjust the isochronism, the isochronous adjustment required a lot of work and time, and therefore there are opportunities for improvement.

SUMMARY OF THE INVENTION

[0012] An aim of the present patent application is to provide a regulating member, a timepiece movement and a timepiece in which an isochronous adjustment can be carried out easily and precisely without using the racket. (1) A regulating organ of the present patent application comprises a hairspring; a pendulum; a peak; and optionally a support element which is combined with the balance to be rotatable relative to the latter around the axis, and movably support the eyebolt in which the support element rotatably supports the eyebolt in the plane, or movably supports the eyebolt in a radial direction of the balance shaft. A hairspring of the present patent application comprises a main hairspring body of which an internal end is fixed to a balance wheel rotating around an axis via a ferrule, and an external end is held by a pin, and which has the shape of a hairspring with a predetermined number of turns in a intersecting plane with the axis between the inner end and the outer end. When an angle around the axis formed between a first virtual line connecting an end position of winding of the main hairspring body, corresponding to the place where the internal end is substantially fixed to the ferrule, and the axis, and a second virtual line connecting a holding position of the main hairspring body retained by the pin and the axis defines a winding angle in a plane perpendicular to the axial direction, the main hairspring body is retained by the pin, such that the outer end rotates in the plane in a state where the winding angle is within a first predetermined angular range, or is retained by the eyebolt, such that the outer end moves in one direction radial of the hairspring main body in a state where the winding angle is within a second predetermined angular range, and the winding angle of the hairspring main body is further configured such that, when it is located in the first angle range, an isochronous variation resulting from rotation in the plane is greater than an isochronous variation resulting from movement in the radial direction, and when the winding angle is in the second angle range, an isochronous variation resulting from movement in the radial direction is greater than an isochronous variation resulting from rotation in the plane.

[0013] According to the hairspring of the present patent application, in a state of the system where the winding angle is in the first angle range, a rotational adjustment of the outer end of the main body of the hairspring in the plane is carried out, or, in a state of the system where the winding angle is in the second angle range, a translational adjustment of the outer end of the main body of the hairspring is carried out in the radial direction, such that an isochronous adjustment can be made.

[0014] More particularly, the main hairspring body is constituted in such a way that the winding angle is in the first angle range, the isochronous variation generated by the rotation in the plane is greater than the isochronous variation caused by movement in the radial direction. That is, adjusting the isochronism via the in-plane rotation operation gives rise to more noticeable changes than via an adjustment operation via movement in the radial direction. On the other hand, in the balance spring main body, if the winding angle is in the second angle range, the isochronous variation caused by an adjustment movement in the radial direction is greater than the isochronous variation due to an adjustment movement in the radial direction. adjustment via rotation in the plane. That is, the adjustment of isochronism via movement in the radial direction can be carried out more sensitively than that via in-plane rotation.

[0015] Consequently, even in a case where a rotational adjustment operation in the plane of the outer end of the main hairspring body is carried out, or a translational adjustment operation in the radial direction is carried out, the isochronism can be modified with a variation caused by one or the other operation. That is to say, in a state where it is difficult to affect by one of the adjustment operations, the isochronism can be modified according to a variation caused by the other of the adjustment operations. Furthermore, it is possible to ensure that the isochronous variation generated by the rotation or translation adjustment is a relationship substantially proportional to the amplitude of the rotation or the length of the translation movement. Therefore, it is possible to change the isochronism by a variation corresponding to the amplitude of the adjustment rotation or translational adjustment level of the outer end of the hairspring main body, and quantitatively perform isochronous adjustment.

[0016] In the above, the isochronous adjustment can be carried out quantitatively and can be carried out easily and precisely without using a racket.

[0017] The eyebolt can be moved in the circumferential direction with the support element by rotating the support element around the axis relatively to the balance, such that the winding angle of the hairspring can be governed at any angle. Therefore, the winding angle can be suitably governed to be in the first angle range or the second angle range. Furthermore, since the support member supports the eyebolt rotatably or movable in the radial direction, as described above, the outer end of the hairspring can be moved by performing rotational adjustment or translational adjustment in the radial direction of the eyebolt depending on the winding angle; therefore, isochronous adjustment can be performed.

[0018] In particular, unlike the case where the isochronous adjustment is carried out using pliers or the like as according to the prior art, the isochronous adjustment can be carried out slightly and the isochronism can be changed quantitatively by a series of flow in which the adjustment of the winding angle is carried out appropriately, and then the rotational adjustment or the translational adjustment is carried out, so that the isochronous adjustment can be carried out easily and appropriately. (2) By defining a movement of the eyebolt in the direction of winding of the hairspring main body as a positive direction of winding angle, and a direction opposite thereto as a negative direction of winding angle , based on a case where the winding angle is zero, the first angle range is an angle range in which the winding angle is within a range of (-125 degrees, ± 5 degrees, to -215 degrees, ±5 degrees), or (-35 degrees, ±5 degrees, to +55 degrees, ±5 degrees), and the second angle range is an angle range in which the winding angle is within a range of (-125 degrees, ±5 degrees, to -35 degrees, ±5 degrees), or (+55 degrees, ±5 degrees, to +145 degrees, ±5 degrees).

[0019] In this case, when the winding angle is within the range of (-125 degrees, ±5 degrees, to -215 degrees, ±5 degrees), or (-35 degrees, ±5 degrees, to +55 degrees, ±5 degrees), in the hairspring main body, the isochronous variation resulting from rotation in the plane is greater than the isochronous variation resulting from movement in the radial direction. Additionally, when the wrap angle is within the range of (-125 degrees, ±5 degrees, to -35 degrees, ±5 degrees), or (+55 degrees, ±5 degrees, to +145 degrees, ±5 degrees), the isochronous variation resulting from movement in the radial direction is greater than the isochronous variation resulting from rotation in the plane.

[0020] Consequently, when the winding angle is in the range of (-125 degrees, ±5 degrees, to -215 degrees, ±5 degrees), or (-35 degrees, ±5 degrees, to + 55 degrees, ±5 degrees), adjustment is made in rotation of the outer end of the hairspring main body, or when the winding angle is within the range of (-125 degrees, ±5 degrees, to - 35 degrees, ±5 degrees), or (+55 degrees, ±5 degrees, to +145 degrees, ±5 degrees), an adjustment is made in translation in the radial direction of the outer end of the main hairspring body, from so that the isochronism can be modified by a variation caused by each adjustment operation, and isochronous adjustment can be carried out. (3) The first angle range may be an angle range in which the winding angle is within a range of (-170 degrees ±α degrees), or (+10 degrees ±α degrees), and the second angle range may be an angle range in which the winding angle is within a range of (-80 degrees ±α degrees), or (+100 degrees ±α degrees), and α may be an angle in the range of 5 degrees to 30 degrees.

[0021] In this case, when the winding angle is within the range of (-170 degrees ±α degrees), or (+10 degrees ±α degrees), in the main hairspring body, a maximum variation of isochronism due to rotation in the plane is maximized, and on the other hand, maximum variation in isochronism due to movement in the radial direction is minimized. Consequently, the isochronism varies with great sensitivity following the rotational adjustment in the plane, but it becomes insensitive to the adjustment movement in the radial direction, and almost no longer changes with respect to the translational adjustment movement.

[0022] Consequently, when the winding angle is within the range of (-170 degrees ±α degrees), or (+10 degrees ±α degrees), the rotation adjustment in the plane is carried out, so that the isochronism can be modified more efficiently thanks to the level of variation resulting from this operation and the isochronous adjustment can be carried out more easily and more precisely.

[0023] Similarly, when the winding angle is within the range of (-80 degrees ±α degrees), or (+100 degrees ±α degrees), in the main hairspring body, a maximum variation of the isochronism resulting from the translational movement in the radial direction is maximized, and on the other hand, a maximum variation of the isochronism resulting from a rotational adjustment in the plane is minimized. Therefore, the isochronism varies with high sensitivity via translational adjustment in the radial direction, but it becomes insensitive to adjustment via in-plane rotation, and almost no longer changes with respect to rotational adjustment movement.

[0024] Consequently, when the winding angle is within the range of (-80 degrees ±α degrees), or (+100 degrees ±α degrees), the translation adjustment in the radial direction is carried out, such that the isochronism can be modified more effectively by the variation caused by this adjustment operation and the isochronous adjustment can be carried out more easily and more precisely.

[0025] Moreover, in the first angle range, while α decreases from 30 degrees to 5 degrees, the operational effect described above can be more effectively realized. For example, the operational effect described above can be achieved more effectively when the winding angle is within the range of (-170 degrees ±25 degrees), or (+10 degrees ±25 degrees) than when the The winding angle is within the range of (-170 degrees ±30 degrees), or (+10 degrees ±30 degrees).

[0026] Similarly, in the second angle range, while α decreases from 30 degrees to 5 degrees, the operational effect described above can be realized more effectively. For example, the operational effect described above can be achieved more effectively when the winding angle is included in the range of (-80 degrees, ±25 degrees), or (+100 degrees, ±25 degrees) than when the winding angle is within the range of (-80 degrees, ±30 degrees), or (+100 degrees, ±30 degrees).

[0027] In any case, while the value of α decreases, the operational effect described above can be achieved effectively, which is preferable. Specifically, it is conceivable that α decreases by 30 degrees per 5 degree step. (4) The first angle range may be an angle range in which the winding angle is within a range of (-170 degrees, ±5 degrees), or (+10 degrees, ±5 degrees) , and the second angle range may be an angle range in which the winding angle is within a range of (-80 degrees, ±5 degrees), or (+100 degrees, ±5 degrees).

[0028] In this case, the operational effect described above can be achieved more efficiently. (5) The outer end rotates in the plane, or the outer end moves in a radial direction of the balance shaft, such that the hairspring main body can vary isochronously along a curve including an extreme value included in a range in which the amplitude of the pendulum is 200 degrees to 250 degrees.

[0029] In this case, when the isochronous adjustment is carried out with the amplitude within the range of 200 degrees to 250 degrees, the isochronism can be modified effectively and sensitively, and the isochronous adjustment is easily carried out, for example, even in a one-minute operation (rotational adjustment and adjustment via translation movement in the radial direction). (6) A timepiece movement of the present patent application comprises the regulating member described above. (7) A timepiece of the present patent application comprises the timepiece movement described above.

[0030] In this case, since a hairspring as described above is provided, a timepiece movement and a timepiece having a lower error rate in terms of rate deviation and a High performance can be provided by precise isochronous adjustment.

[0031] According to the present patent application, the isochronous adjustment can be carried out easily and precisely without using a racket. Therefore, the timepiece movement and the timepiece having less error rate in terms of rate deviation and high performance can be obtained.

BRIEF DESCRIPTION OF THE DRAWINGS

[0032] Figure 1 is a view illustrating a first embodiment according to the present invention and an external view of a timepiece. Figure 2 is a plan view of a movement of Figure 1. Figure 3 is a perspective view of a regulating member illustrated in Figure 2. Figure 4 is a sectional view of the regulating member, which is seen along the line A-A illustrated in Figure 3. Figure 5 is a plan view of the regulating member illustrated in Figure 3 and a plan view illustrating a relationship between a eyebolt holder, a hairspring and a pendulum. Figure 6 is a plan view of a hairspring without a terminal curve. Figure 7 is a plan view of a hairspring with overwinding. Figure 8 is a view illustrating isochronous curves in the case where no adjustment operation is carried out, in the case where a rotational adjustment is carried out, and the case where the adjustment is carried out via a translation movement when a winding angle is 0 degrees. Figure 9 is a view illustrating a relationship between an isochronous variation curve at the time of the rotational adjustment operation and an isochronous variation curve at the time of the adjustment operation via a translation movement. Figure 10 is a view illustrating a relationship between a variation curve of a maximum amount of the isochronous variation at the time of adjustment in rotation, and a variation curve of a maximum amount of the isochronous variation at the time of adjustment via a translational movement. Figure 11 is a view illustrating a relationship between a variation curve of a maximum amount of the isochronous variation at the time of rotational adjustment, and a variation curve of a maximum amount of the isochronous variation at the time of adjustment via a translational movement in a spiral without terminal curve. Figure 12 is a view illustrating a relationship between a variation curve of a maximum amount of the isochronous variation at the time of rotational adjustment, and a variation curve of a maximum amount of the isochronous variation at the time of adjustment via a translational movement in a balance spring with overwinding spring. Figure 13 is a view illustrating a relationship between a variation curve of a maximum amount of the isochronous variation at the time of rotational adjustment, and a variation curve of a maximum amount of the isochronous variation at the time of adjustment via a translational movement in each of the hairsprings with terminal curve, without terminal curve and with overwinding spring. Figure 14 is a view illustrating a relationship between isochronism change curves following rotational adjustments in four winding angles. Figure 15 is a view illustrating a relationship between isochronism change curves following adjustments via translational movements in four winding angles. Figure 16 is a view illustrating a relationship between a change curve of a maximum amount of isochronous variation at the time of the rotation adjustment operation, and a change curve of a maximum amount of isochronous variation at the time of rotational adjustment. 'adjustment operation via a translation movement in each of the hairsprings with a terminal curve, without a terminal curve and with an overwinding spring, in a case where the number of turns of the hairspring is equal to 14, where and the number of oscillations of the balance is 8 oscillations. Figure 17 is a perspective view of a regulating member illustrating a variant of the first embodiment. Figure 18 is a perspective view illustrating a relationship between a eyebolt holder, a hairspring and a balance wheel illustrated in Figure 17. Figure 19 is a plan view illustrating a relationship between the eyebolt holder and the hairspring illustrated in Figure 17. Figure 18. Figure 20 is a perspective view of a regulating member illustrating a second embodiment according to the present invention. Figure 21 is an enlarged plan view of a periphery of a piton illustrated in Figure 20. Figure 22 is a perspective view of a regulating member illustrating a third embodiment according to the present invention. Figure 23 is a perspective view illustrating a state where an eyebolt cover is removed from the state shown in Figure 22. Figure 24 is a perspective view of the eyebolt cover shown in Figure 22.

DESCRIPTION OF THE EMBODIMENTS

[0033] In the following, embodiments of the present invention will be described with reference to the drawings. Additionally, in the embodiments, as an example of a timepiece, a mechanical timepiece is described.

(Basic configuration of a timepiece)

[0034] In general, we refer to a mechanical body comprising a driving part of the timepiece as being a “movement”. In a state where a dial and hands are attached to the movement, put into a timepiece case, and assembled into a finished product, it is referred to as a timepiece “assembly”. Among the two sides of a plate constituting a base plate of the timepiece, we refer to the side with the crystal of the case of the timepiece, (that is to say, the side of the dial ) as the “rear side” of the movement. Furthermore, among the two sides of the plate, we refer to the side of the case back of the timepiece, (that is to say, the side opposite the dial) as being the “front side” of the timepiece. movement.

[0035] Additionally, in the embodiments, a description is given that the direction of the dial toward the bottom of the case is defined as “upward” and the opposite direction is defined as “downward.”

(First embodiment)

[0036] As illustrated in Figure 1, an assembly of a timepiece 1 of this embodiment comprises a movement (timepiece movement according to the present invention) 10, a dial 3 having indicators indicating information at least on the current time, and hands comprising an hour hand 4 indicating the time, a minute hand 5 indicating the minutes and a seconds hand 6 indicating the seconds in the timepiece housing consisting of a case back (not illustrated) and a crystal 2.

[0037] As illustrated in Figures 2 and 3, the movement 10 comprises a plate 11, a gear train bridge (not illustrated) and a cock 12, that is to say a balance bridge arranged on the front side of the plate 11. A finishing gear, an escapement (not illustrated) for controlling the rotation of the finishing gear, and a regulating member 13 regulating a speed of the escapement are mainly arranged between the plate 11, the gear bridge and the cock 12. The dial 3 is arranged visibly at the rear of the plate 11 through the glass 2.

[0038] Furthermore, the movement 10 of the embodiment described is taken as an example of a movement 10 for a timepiece of the automatic winding type, comprising an oscillating mass 14. However, the movement 10 is not limited to such a case, and could be a movement of the manual winding type by a winding rod 15.

The finishing gear mainly comprises a barrel, a second mobile, a third mobile and a fourth mobile. Furthermore, in the embodiment described, the second mobile, the third mobile and the fourth mobile are omitted for easier readability of the drawings. The seconds hand 6 illustrated in Figure 1 rotates on the basis of the rotation of the fourth mobile and rotates at a rotation speed regulated by the escapement and the regulating member 13, that is to say, one revolution in 1 minute. The minute hand 5 rotates on the basis of the rotation of the second mobile or the rotation of a rotating pinion in accordance with the rotation of the second mobile, and rotates at a rotation speed regulated by the escapement and the regulating member 13 , that is to say, a complete revolution in 1 hour. The hour hand 4 rotates on the basis of the rotation of an hour wheel rotating in accordance with the rotation of the second mobile via a minute wheel, and rotates at a rotation speed controlled by the escapement and the regulating member 13, that is to say, a complete revolution in 12 hours or 24 hours.

[0040] The escapement comprises an escapement wheel (not shown) meshing with the fourth wheel, and an anchor (not shown) escaping and rotating regularly the escapement wheel, and controls the finishing gear by a regular oscillation from a balance 20 which will be described later.

[0041] As illustrated in Figures 3 and 4, the regulating member 13 comprises the balance wheel (first element according to the present invention) 20 rotating alternately (that is to say repeating forward rotational movements then the rear) around a first axis O1 ("the axis" according to the present invention), a hairspring 30, a pin 40 (second element according to the present invention) holding an external end 31b of a main body of hairspring 31, which will be described later, and a pin holder 50 (support element according to the present invention) which is combined with the balance 20 to be rotatable relative to the latter around the first axis O1, and movably supports peak 40.

[0042] Furthermore, in the embodiment described, a direction secant with the first axis O1 in a plan view is defined as a radial direction, and a direction of revolution around the first axis O1 is defined as a circumferential direction.

The balance wheel 20 comprises a balance shaft 21 which is rotatably mounted around the first axis O1 and a balance wheel 22 attached to the balance shaft 21, and which rotates alternately forwards and backwards around of the first axis O1 according to an amplitude in steady state (amplitude) with the hairspring 30 as an energy source.

[0044] In the balance shaft 21, an upper tenon 21a is supported essentially on an upper stone plug 60, and a lower tenon 21b is essentially supported on a lower stone plug (not shown) formed in the plate 11 illustrated on the Figure 2. A connecting arm 23 connected to the balance wheel 22, a ferrule 24, and a double plate 25 are fixed at an intermediate portion in the balance shaft 21 in the vertical direction.

The connecting arm 23 is an element connecting the balance shaft 21 to the balance wheel 22 in the radial direction, and is connected to an annular hub 26, an internal end of which is fixed to the balance shaft 21 , for example, by press-fitting or the like, and an outer end is connected to an inner peripheral surface of the balance wheel 22. Therefore, the balance wheel 22 is fixed to the balance shaft 21 via the balance arm. connection 23, and rotates forward and backward about the first axis O1 with the balance shaft 21. However, the number, arrangement, and shape of the connecting arms 23 can be changed appropriately as required.

The ferrule 24 is arranged above the hub 26 and is fixed to the balance shaft 21, for example, by force fitting or the like.

The double plate 25 is arranged below the hub 26 and is fixed to the balance shaft 21, for example, by force fitting or the like. The double plate 25 includes a large flange 25a and a small flange 25b located below the large flange 25a. The large collar 25a is formed by an artificial precious stone such as a ruby, and a plate pin 27 for operating (swinging/oscillating) the anchor is, for example, force-fitted to be fixed there.

[0048] The upper stone plug 60 is a socket set in precious stone resistant to shock (anti-shock) comprising a set socket body 61 of cylindrical shape, an upper hole stone 62 being fixed inside the socket body crimped 61 and rotatably supporting the upper tenon 21a of the balance shaft 21, an upper cap 63 also made of precious stone placed above the upper hole stone 62, and supporting the upper tenon 21a of the shaft of balance 21 in the axial direction, and a fixing support 64 of the upper cap being still disposed above the upper cap 63 and fixing the upper cap 63 to the crimped socket body 61.

However, the configuration of the upper stone plug 60 is not limited to the case described above, but could adopt another configuration as long as the upper tenon 21a of the balance shaft 21 can be rotatably supported. .

The crimped socket body 61 comprises an upper body 61a and a lower body 61b whose external diameter is smaller than that of the upper body 61a, and has a cylindrical shape with two stages whose external diameters are different from one another. the other. The lower body 61b is fixed, for example, by press-fit or the like, such that the crimped socket body 61 is fixed inside a cylindrical part 71 formed in a base plate 70 of the cock 12 In addition, the crimped socket body 61 and the cylindrical crimped socket part 71 are arranged coaxially with respect to the first axis O1.

For example, as illustrated in Figure 2, the cock 12 comprises a main body 72 extending in an arcuate shape in accordance with a shape of the timepiece box. A mounting hole 73 is formed in the main body 72, and the base plate 70 is formed at an outer edge so as to have a gradual recess. As illustrated in Figure 2, the cock 12 is fixed to the plate 11 by fixing screws 74 using the mounting holes 73. However, the shape of cock 12 is not limited to such a configuration as that described below. above, and could be modified appropriately as needed.

[0052] As illustrated in Figure 4, a through hole 75 penetrating vertically into the base plate 70 is formed in the base plate 70 coaxially with the first axis O1. The cylindrical part 71 is formed so as to rise above the base plate 70 along the peripheral edge of the through hole 75, and the interior thereof communicates with the through hole 75. Therefore, the lower body 61b of the crimped socket body 61 is fixed inside the cylindrical part 71 and the inside of the through hole 75, for example, by press-fit. In addition, the upper body 61a of the crimped socket body 61 is disposed at an opening end of the cylindrical part 71, and has a shape larger than the outer diameter of the cylindrical part 71.

[0053] As illustrated in Figures 3 to 5, the eyebolt holder 50 is rotatably inserted into the cylindrical part 71 in the cock 12, therefore being capable of rotating relatively around the first axis O1 with respect to the cylindrical part 71.

The eyebolt holder 50 comprises a connection ring 51 fitted to the exterior of the cylindrical part 71, and a eyebolt arm 52 extending outwards in the radial direction from the connection ring 51, and movably supporting the peg 40 at one of its ends (its outer end). Specifically, the eyebolt holder 50 supports the eyebolt 40 rotatably around a second axis O2, parallel to the first axis O1.

[0055] Furthermore, the connection ring 51 is arranged in the form of C in a plan view, that is to say a ring of which a part in the circumferential direction has been removed; however, it could also take a ring shape.

The arm 52 of the eyebolt has the shape of a fork with two arms, a first eyebolt arm 53 and a second eyebolt arm 54 coming to pinch and hold the eyebolt 40 from the two opposite sides in the circumferential direction. The first eyebolt arm 53 and the second eyebolt arm 54 are elastically deformable in the circumferential direction, and ends of their tips are compressed in advance to approach each other. Consequently, a shaft body 41 of the eyebolt 40 can be sandwiched between the first eyebolt arm 53 and the second eyebolt arm 54.

[0057] A first sandwiched surface 53a of the first eyebolt arm 53 facing the second eyebolt arm 54, and a second sandwiched surface 54a of the second eyebolt arm 54 facing the first eyebolt arm 53 are mutually facing each other in the circumferential direction, with the piton 40 interposed between them. Curved surfaces 55 having an arcuate shape in a plan view corresponding to the external diameter of the shaft body 41 of the eyebolt 40 are respectively formed in the first sandwiched surface 53a and the second sandwiched surface 54a so as to present each a recess.

The first eyebolt arm 53 and the second eyebolt arm 54 support the eyebolt 40 by sandwiching the shaft body 41 in the circumferential direction using the curved surfaces 55. Consequently, the eyebolt 40 is supported by rotatably around the second axis O2 between the first eyebolt arm 53 and the second eyebolt arm 54 without alignment error in the radial direction.

The eyebolt 40 comprises a cylindrical shaft body 41 extending along the second axis O2, a head 42 formed at the upper end of the shaft body 41, and an inner leg 43 as well as an outer leg 44 projecting downwards from the lower end of the shaft body 41.

[0060] The shaft body 41 is sandwiched between the first eyebolt arm 53 and the second eyebolt arm 54, finding itself disposed inside the curved surface 55 of the first eyebolt arm 53 and the surface curved 55 of the second eyebolt arm 54. The head 42 is formed integrally with the upper end of the shaft body 41 and is arranged so as to cover the upper surfaces of the first eyebolt arm 53 and the second eyebolt arm 54.

Consequently, the eyebolt 40 is sandwiched between the first eyebolt arm 53 and the second eyebolt arm 54, and in parallel rotatably supported around the second axis O2, finding itself at least in a state of be blocked down.

[0062] In addition, the head 42 is formed so as to have linear parts 42a whose external peripheral edges face each other, and an adjustment tool (not illustrated) can be adjusted on the head 42 using parts linear 42a. Consequently, the eyebolt 40 can be rotated around the second axis O2 using the adjustment tool.

[0063] An outermost spring portion 32 of the balance spring main body 31, which is described below, is inserted between the inner leg 43 and the outer leg 44 in the circumferential direction. That is, the inner leg 43 is disposed inside the outermost spring part 32 in the radial direction, and the outer leg 44 is disposed outside the outermost spring part 32 in the radial direction. radial direction. A portion of the outermost spring portion 32 of the main hairspring body 31, which is inserted inside the inner leg 43 and the outer leg 44, is permanently fixed to the inner leg 43 and the outer leg 44, for example, by welding or the like.

Consequently, the hairspring 30 finds itself in a state where the outermost spring portion 32 including the external end 31b is fixed (held) by the pin 40. Below, the hairspring 30 will be described in detail.

(Spiral)

[0065] As illustrated in Figure 5, the hairspring 30 comprises the main hairspring body 31 in the form of a hairspring with a predetermined number of turns in a intersecting plane with the first axis O1 between an internal end 31a and the external end 31b , in which an internal end 31a is fixed to the balance shaft 21 via the ferrule 24, and an external end 31b is held by the pin 40 described above.

The main body of the hairspring 31 is a thin leaf spring made of, for example, a metal such as iron or nickel, and has a hairspring shape conforming to an Archimedes curve in a polar coordinate system. , with the first axis O1 as origin. Therefore, the hairspring main body 31 is wound in a plurality of windings such that each of the windings is adjacent to each other at substantially equal intervals in the radial direction. In addition, the material of the hairspring main body 31 is not limited to the case described above, but can be appropriately changed according to needs. In addition, the shape of the hairspring main body 31 is not limited to the shape of a hairspring according to an Archimedes Curve, but can be modified to take a shape according to which the spacing pitch changes, for example, a hairspring logarithmic or similar.

[0067] A portion of the outermost spring portion 32 of the hairspring main body 31, which includes the outer end 31b and is located in the outermost peripheral portion in the radial direction, is spaced outwardly in the radial direction via a straightened part 33 and is formed of an arcuate part 34 whose radius of curvature is larger than that of the other parts. A peripheral end of the arcuate part 34 is the outer end 31b of the main hairspring body 31. In addition, the portion of the arcuate part 34 of the outermost spring part 32 is held (fixed) by the pin 40 as described below -above.

[0068] The hairspring 30 of the embodiment formed as described above is classified as so-called flat-bearded and has a terminal curve shape in which the arcuate portion 34 is formed into the outermost spring portion 32 via the straightened part 33. In the embodiment described, we can thus refer to the hairspring 30 thus formed as simply being “with a terminal curve” or constituting a “spiral with a terminal curve”.

[0069] In the meantime, in the context of the present invention, the shape of the hairspring 30 is not limited to this type of hairspring "with a terminal curve", but can adopt another shape. For example, as illustrated in Figure 6, although it is one of the so-called flat beard, a hairspring 80, which has a simple external end shape and in which an arcuate part is not formed in the outermost spring part 32 via a straightened part, can be adopted. In this case, we simply refer to the hairspring 80 as being “without terminal curve”, or constituting a “spiral without terminal curve”.

[0070] Furthermore, in Figure 6, we illustrate a case where the winding direction is opposite to that of the hairspring 30 illustrated in Figure 5.

[0071] Furthermore, as illustrated in Figure 7, a balance spring 90 classified as an overwound balance spring (also sometimes called a “Breguet” balance spring) can be adopted, in which a portion of the outermost spring portion 32 is raised relative to the spring. plane in which the rest of the spiral spring is located, and the outer end 31b is arranged on the side opposite to the part where the lifting begins, in the radial direction. In this case, we can refer to the balance spring 90 as simply “overwound”.

[0072] Furthermore, in Figure 7, we illustrate a case where the direction of winding is opposite to that of the hairspring 30 illustrated in Figure 5.

[0073] In the embodiment described, the winding angle is defined as follows.

[0074] As illustrated in Figure 5, according to a view in the axial direction of the balance shaft 21, the angle formed between a first virtual line L1 connecting an end position of winding P1 of the main body of hairspring 31 and the first axis O1, and a second virtual line L2 connecting a holding position P2 of the main body of hairspring 31, retained by the pin 40, and the first axis O1, with the first axis O1 taken as center is defined as the winding angle θ.

[0075] Furthermore, the end of winding position P1 is a position which includes the internal end 31a of the main hairspring body 31 and is substantially fixed to the ferrule 24 in the innermost spring part 35, positioned the as inward as possible in the radial direction. Consequently, it is possible that the position of the internal end 31a of the main hairspring body 31 and the winding end position P1 do not necessarily correspond. Also in the embodiment described, the internal end 31a of the main hairspring body 31 and the winding end position P1 are slightly offset in the circumferential direction.

[0076] Furthermore, the holding position P2 is a substantially fixed position (retaining with respect to) the pin 40, in the outermost spring part 32 of the main balance spring body 31. Consequently, it is possible that the position of the outer end 31b of the main hairspring body 31 and the holding position P2 do not necessarily correspond. Also in this embodiment described, the outer end 31b of the main hairspring body 31 and the holding position P2 are offset relative to each other in the circumferential direction.

[0077] Furthermore, in this embodiment described, directions relating to the winding angle θ, that is to say, a positive direction (+) and a negative direction (-), are defined by the following way.

[0078] That is to say that there is a reference position when the winding angle θ is 0 (zero) - when the first virtual line L1 and the second virtual line L2 correspond - a direction according to which the holding position P2 advances relative to the reference position in the winding direction of the main body of hairspring 31 is defined as the positive direction (indicated “+” in Figure 5) of the winding angle θ , and a direction opposite to the latter is defined as a negative position (indicated “-“ in Figure 5) of the winding angle θ. Therefore, in Figure 5, the winding angle θ is set in the positive direction. On the other hand, in Figure 6 for example, the winding angle θ is set in the negative direction.

(Characteristics of the hairspring)

[0079] In what follows, we will give a description for calculating how the isochronism changes as a function of the winding angle θ in the hairspring 30 of the embodiment, when we carry out a rotational adjustment on the external end 31b next to the main body of the hairspring 31 or a translation adjustment in the radial direction.

[0080] Furthermore, the rotational adjustment to rotate the outer end 31b of the main hairspring body 31 is an operation to rotate a portion of the main hairspring body 31, which is retained by the pin 40, in a plane secant relative to the axial direction of the balance shaft 21, that is to say, to make it rotate around the second axis O2. Hereinafter, we will simply refer to a “rotational adjustment operation”.

[0081] Furthermore, the adjustment in translation to move the outer end 31b of the main hairspring body 31 in the radial direction is an operation to move a portion of the main hairspring body 31, which is retained by the pin 40, the along the radial direction of the balance shaft 21. Hereinafter, we will simply refer to a “translational adjustment operation”.

[0082] Furthermore, in the calculation described above, a calculation was carried out, in which the hairspring 30 was divided into predetermined elements, a theory of the deformation of an elastic body was applied to each element, a torque, which is calculated with a geometric center of the balance spring 30 as a center when the balance 20 oscillates, was used, and an equation of motion (ordinary differential equation) of the balance 20 was integrated over time.

[0083] Firstly, in a case where the winding angle θ is 0 degrees, the isochronism for 3 models corresponding to a case where no adjustment operation is carried out on the external end 31b of the main body of hairspring 31 (hereinafter, may refer to this state as corresponding to “before an adjustment operation”), a case where rotational adjustment is carried out, and a case where adjustment via translational movement is carried out has been calculated. Respective isochronous curves based on the calculation result are shown in Figure 8.

[0084] In Figure 8, an isochronous curve CL1 illustrates the isochronous curve before adjustment operation, an isochronous curve CL2 illustrates an isochronous curve after adjustment in rotation, and an isochronous curve CL3 illustrates an isochronous curve after adjustment in translation. Furthermore, in Figure 8, a horizontal axis illustrates an amplitude of the balance 20 and a vertical axis illustrates a temporal precision rate. Furthermore, as the amplitude of the balance 20, it is calculated in a range from 120 degrees to 300 degrees.

[0085] Furthermore, the rotational adjustment is an example of a case where a portion of the main hairspring body 31, which is retained by the pin 40, is rotated by 1 degree counterclockwise. with the second axis O2 as the center. Furthermore, the translational adjustment is an example of a case where a portion of the main hairspring body 31, which is retained by the pin 40, is moved a distance of +20 µm outward in the radial direction .

[0086] Furthermore, in this calculation, we take as an example a case where the number of winding turns of the hairspring 30 is equal to 12. Furthermore, as the number of oscillations of the balance 20, we take as an example a case where 10 oscillations, that is to say, 10 oscillations per second (36000 oscillations per hour).

[0087] In what follows, a difference between the isochronous curve CL1 before an adjustment operation and the isochronous curve CL2 after the rotation adjustment is calculated, and an isochronous variation curve CL4 during the rotation adjustment calculated on the basis of the result of the calculation is illustrated in Figure 9. Similarly, a difference between the isochronous curve CL1 before adjustment operation and the isochronous curve CL3 after the adjustment in translation is calculated, and an isochronous variation curve CL5 at the time of the adjustment. adjustment operation via a translational movement calculated on the basis of the result of the calculation is illustrated in Figure 9. In addition, in Figure 9, the horizontal axis illustrates the amplitude of the balance 20 and a vertical axis illustrates a curve of isochronous variation of a rate which corresponds to temporal precision.

[0088] In the following, in the isochronous variation curve CL4 during rotation adjustment, a calculation was carried out by subtracting a minimum value from a maximum value of the isochronous variation (maximum value-minimum value).

[0089] In the example of Figure 9, the value at the amplitude of 220 degrees is the maximum value (substantially 2.16), and the value at the amplitude of 120 degrees is the minimum value (substantially -2.05). Therefore, the result (maximum value-minimum value) is substantially equal to 4.21. Therefore, substantially 4.21 which corresponds to the value of (maximum value-minimum value) is the maximum amount of isochronous variation at the time of the rotational adjustment operation when the winding angle θ is 0 degrees.

[0090] Similarly, in the isochronous variation curve CL5 at the time of translation adjustment, a calculation was carried out by subtracting the minimum value from the maximum value of the isochronous variation (maximum value-minimum value). In the example in Figure 9, the value at the amplitude of 300 degrees is the maximum value (substantially -1.02), and the value at the amplitude of 200 degrees is the minimum value (substantially - 1.44). Therefore, the result (maximum value-minimum value) is substantially equal to 0.42. Therefore, this result of substantially 0.42 which corresponds to the value of (maximum value-minimum value) is the maximum amount of isochronous variation at the time of the adjustment operation via translational movement when the winding angle θ is of 0 degrees.

[0091] Furthermore, as illustrated in Figure 9, the isochronous variation curve CL4 at the time of rotation adjustment is a curve projecting upwards, so as to include an extreme value (maximum extreme value, that is to say i.e., the maximum value described above) in a range in which the amplitude is 200 degrees to 250 degrees. Similarly, the isochronous variation curve CL5 at the time of the adjustment operation via a translational movement is a downwardly protruding curve, so as to include an extreme value (minimum extreme value, i.e. , the minimum value described above) in a range in which the amplitude is 180 degrees to 250 degrees.

[0092] The trend of such a curve is not limited to a case where the winding angle θ is 0 degrees, but the same trend is illustrated at any winding angle θ (see the figures 14 and 15).

[0093] In what follows, the calculation described above was carried out repeatedly for each degree of winding angle (that is to say in steps of 1°) in a range where the winding angle θ is between -180 degrees and +180 degrees, the maximum amount of isochronous variation at the time of the rotational adjustment operation, and the maximum amount of isochronous variation at the time of the adjustment operation via a translational movement were respectively calculated.

[0094] The maximum amount of isochronous variation at the time of the rotational adjustment operation, and the maximum amount of isochronous variation at the time of the adjustment operation via translational movement at each winding angle θ are collectively illustrated on a single graph that is easy to see in Figure 10. In Figure 10, a horizontal axis illustrates the winding angle θ and a vertical axis illustrates the maximum amount of isochronous variation.

[0095] In Figure 10, the value of the maximum amount of isochronous variation at the time of the rotational adjustment operation at each winding angle θ is plotted with a symbol “0”. The curve formed by connecting the maximum variation values at each winding angle θ plotted with the symbol “0” is the variation curve CL6 of the maximum amount of isochronous variation at the time of the rotation adjustment operation.

[0096] Similarly, the value of the maximum amount of isochronous variation at the time of the adjustment operation via a translational movement at each winding angle θ is plotted with a symbol “◊”. The curve formed by connecting the maximum variation values at each winding angle θ plotted with the symbol „◊“ is the CL7 variation curve of the maximum amount of isochronous variation at the time of the adjustment operation via translational movement .

[0097] As illustrated in Figure 10, the variation curve CL6 and the variation curve CL7 were curves in which the maximum value and the minimum value of the maximum amount of variation appear alternately and periodically. Furthermore, the maximum value of the maximum amount of change in the change curve CL6 and the minimum value of the maximum amount of change in the change curve CL7 correspond to each other within a substantially similar range of the angle of change. winding θ, and the minimum value of the maximum amount of variation in the change curve CL6 and the maximum value of the maximum amount of variation in the change curve CL7 correspond to each other within a substantially similar range of the angle d winding θ. In other words, the variation curve CL6 and the variation curve CL7 are in a state where the winding angle θ is out of phase by substantially 90 degrees to 110 degrees.

[0098] Furthermore, in Figure 10, the curves corresponding to the variation curve CL6 and the variation curve 7 are corrected, such that a comparison between the variation curve CL6 and the variation curve CL7 is facilitated. , and each maximum value of the maximum amount of variation indicates a value substantially equal to 1.

However, also in this case, since only the inclinations of the curves corresponding to the variation curve CL6 and to the variation curve CL7 simply change, the variation with respect to the winding angle θ is the same as that before the correction. Furthermore, since the variation curves CL6 and CL7 are substantially proportional to the quantities relating to the rotational adjustment operation and the adjustment operation via translational movement, they are the same as the correction of the quantity of movement .

[0100] From the above, according to Figure 10, it is possible to understand how the isochronism varies according to the winding angle θ in the hairspring 30 with a terminal curve of the embodiment described, in a case where a rotational adjustment of the outer end 31b of the balance spring main body 31 is carried out, or translational adjustment in the radial direction is carried out.

[0101] Furthermore, for the hairspring without terminal curve 80 illustrated in Figure 6 and the hairspring with overwinding 90 illustrated in Figure 7, a series of calculations as described above was respectively carried out.

[0102] The calculation linked to the balance spring 80 (spiral without terminal curve) illustrated in Figure 6 is carried out, a variation curve CL8 of the maximum quantity of isochronous variation at the time of the rotation adjustment operation, and a curve of variation CL9 of the maximum amount of isochronous variation during translation adjustment, which are obtained from the result of this calculation, are shown in Figure 11. As shown in Figure 11, the variation curve CL8 and the variation curve CL9 were curves illustrating the same trend as that of the change curve CL6 and the change curve CL7 described above.

[0103] In addition, the calculation linked to the spiral 90 (overcoil spiral spring) illustrated in Figure 7 is carried out, a variation curve CL10 of the maximum quantity of isochronous variation at the time of the rotation adjustment operation, and a variation curve CL11 of the maximum amount of isochronous variation during translation adjustment, which are obtained thanks to the result of this calculation, are illustrated in Figure 12. As illustrated in Figure 12, the variation curve CL10 and the curve of variation CL11 were curves illustrating the same trend as that of the variation curve CL6 and the variation curve CL7 described above.

[0104] Figure 13 is a graph obtained by combining the respective variation curves of Figures 10 to 12. As illustrated in Figure 13, independently of the hairspring with a terminal curve 30, a variation curve CL12 of the maximum quantity of variation isochronous at the time of the rotational adjustment operation, and a CL13 variation curve of the maximum amount of isochronous variation at the time of the adjustment operation via translational movement illustrate the same trend.

[0105] From the above, it can be deduced that the hairspring 30 with a terminal curve of the embodiment described has the following characteristics. In addition, the following characteristics are also the same as those of the hairspring without end curve (hairspring 80) and that of the overcoil hairspring (hairspring 90) which are described above.

[0106] In other words, in the main body of the hairspring 31, when the winding angle θ is located in a first predetermined angular range E1, the isochronous variation resulting from an adjustment in rotation around the second axis O2 is greater that the isochronous variation resulting from an adjustment in translation in the radial direction, and when the winding angle θ corresponds to an angle different from the first angle range E1 and is located in a second predetermined angular range E2, the isochronous variation due to translational adjustment in the radial direction is greater than the isochronous variation resulting from rotational adjustment around the second axis O2.

[0107] For the first angle range E1, the winding angle θ is included in a range of (-125 degrees ±5 degrees to -215 degrees (that is to say, +145 degrees) ± 5 degrees), or (-35 degrees ±5 degrees to +55 degrees ±5 degrees). For the second angle range E2, the winding angle θ is in a range of (-125 degrees ±5 degrees to -35 degrees ±5 degrees), or (+55 degrees ±5 degrees to +145 degrees ±5 degrees).

[0108] Furthermore, with regard to the first angle range E1, in a case where the winding angle θ is located in an angle range between (-170 degrees ±α degrees), or ( +10 degrees ±α degrees), in the hairspring main body 31, the maximum amount of variation in isochronism resulting from rotational adjustment around the second axis O2 is maximized, but on the contrary, the maximum variation in isochronism due to movement in the radial direction is minimized.

[0109] Furthermore, the angle α is an angle included in a range of 5 degrees to 30 degrees. In this case, in the first angle range E1, when α decreases from 30 degrees to 5 degrees, the characteristics described above can be realized more effectively. For example, the characteristics described above can be achieved more effectively when the winding angle θ is included in the range of (-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). It is even more preferable that the winding angle θ is included in the range of (-170 degrees ±5 degrees), or (+10 degrees ±5 degrees).

[0110] Furthermore, it is conceivable that α decreases by 30 degrees in increments of 5 degrees, that is to say, the angle α is reduced from 30 degrees to 25 degrees, then 20 degrees, 15 degrees, 10 degrees and finally 5 degrees.

[0111] Furthermore, with regard to the second angle range E2, in a case where the winding angle θ is in an angle range included in a range of (-80 degrees ±α degrees) , or (+100 degrees ±α degrees), the maximum variation in isochronism resulting from translational adjustment in the radial direction is maximized, but on the contrary, the maximum variation in isochronism due to rotational adjustment around of the second axis O2 is minimized.

[0112] Furthermore, as in the first angle range E1, α is an angle included in the range from 5 degrees to 30 degrees. In this case, in the second angle range E2, while α decreases from 30 degrees to 5 degrees, the characteristics described above can be effectively realized. For example, the characteristics described above can be achieved more effectively when the winding angle θ is included in the range of (-80 degrees ±25 degrees), or (+100 degrees ±25 degrees) than when the winding angle θ is included in the range of (-80 degrees ±30 degrees), or (+100 degrees ±30 degrees). It is more preferable when the winding angle θ is included in the range of (-80 degrees ±5 degrees), or (+100 degrees ±5 degrees).

[0113] Furthermore, it is conceivable that α decreases by 30 degrees in increments of 5 degrees, that is to say, that the angle α is reduced from around 30 degrees to 25 degrees, then 20 degrees, 15 degrees, 10 degrees and finally 5 degrees.

[0114] This will be described in more detail.

[0115] Figure 14 is a view illustrating an isochronism variation curve resulting from adjustment in rotation around the second axis O2, and Figure 15 is a view illustrating an isochronism variation curve resulting from an adjustment in translation in the radial direction.

[0116] As illustrated in Figures 14 and 15, in a case where the winding angle θ is +167 degrees or +13 degrees, the isochronism is modified towards a favorable state by the rotation adjustment operation , but on the contrary, for the translation adjustment operation in the radial direction, it becomes insensitive, therefore very difficult to change in this way. Furthermore, in a case where the winding angle θ is -77 degrees or +103 degrees, the isochronism is modified towards a favorable state by the translation adjustment, but on the contrary, for the rotation adjustment, it becomes insensitive therefore very difficult to change in this way.

[0117] Furthermore, Figure 13 illustrates a result of a case where the number of turns is 12 turns and the number of oscillations of the balance 20 is 10 oscillations (that is to say, 36,000 oscillations in one hour) as described above, and the same result could be obtained even in a case where the number of turns and the number of oscillations are changed.

[0118] For example, Figure 16 is a view corresponding to Figure 13, of a case where the number of revolutions is 14 revolutions and the number of oscillations of the balance 20 is 8 oscillations (i.e. (say, 28800 oscillations in one hour). As is clear from Figure 16, even in a case where the number of turns and the number of oscillations are changed, the characteristics described above are still provided.

[0119] As illustrated in Figure 5, in the balance spring 30 produced as described above, the internal end 31a is fixed to the balance shaft 21 via the ferrule 24, and the external end 31b is fixed to the pin 40 (maintained by the latter). Particularly, in the embodiment described, in a state where the winding angle θ is located in the first predetermined angular range E1, the eyebolt holder 50 rotatably supports the eyebolt 40 around the second axis O2. Specifically, the winding angle θ is +13 degrees.

(Isochronous adjustment of the hairspring)

[0120] In what follows, we will describe a case where the isochronous adjustment of the hairspring 30 is carried out in the timepiece 1 comprising the regulating member 13 constituted as described above.

[0121] Furthermore, in an initial state, the pin 40 is located in a reference rotation position, and the main body of the hairspring 31 is not moved around the second axis O2 by the pin 40.

[0122] In a case where the isochronous adjustment is carried out in such an initial state, for example, the eyebolt holder 50 is rotated around the first axis O1 relative to the balance 20, such that the eyebolt 40 can be moved in the circumferential direction with the eyebolt holder 50. Consequently, the winding angle θ of the hairspring 30 can be adjusted to any angle. Therefore, the winding angle θ can be suitably adjusted 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 in the first angle range E1.

[0123] Furthermore, the winding angle θ is not limited to the case as described above, but, for example, the pin 40 could be fixed to the main body of the hairspring 31 in advance, in such a way that the winding angle θ is located in the first angle range E1 or the second angle range E2, that is to say, with a winding angle θ set to +13 degrees within the the first angle range E1.

[0124] Then, in the eyebolt 40 whose winding angle θ is set to +13 degrees, the rotational adjustment operation is carried out around the second axis O2. Therefore, the isochronism can be modified and the isochronous adjustment can thus be carried out.

[0125] In particular, as described above, in the main hairspring body 31, in a case where the winding angle θ is located in the first angle range E1, the isochronous variation results from an adjustment in rotation is greater than the isochronous variation caused by translational adjustment in the radial direction, such that the isochronism of the rotational adjustment operation can be changed more sensitively than that obtained by the rotational adjustment operation. adjustment via translational movement in the radial direction. Therefore, in a state where it is hardly affected by translational adjustment in the radial direction, the isochronism can be changed with the variation caused by the rotational adjustment operation, so that it is possible to quantitatively perform isochronous adjustment and perform isochronous adjustment easily and precisely without using the racket.

[0126] Furthermore, since the winding angle θ is +13 degrees, as illustrated in Figures 14 and 15, in the main body of the hairspring 31, the maximum variation of the isochronism resulting from an adjustment in rotation is maximized, but on the contrary, the maximum variation in isochronism resulting from adjustment movement in the radial direction is minimized. Therefore, the isochronism is modified with great sensitivity by a rotational adjustment operation, but for translational adjustment in the radial direction, it becomes insensitive and therefore very difficult to change in this way.

[0127] Consequently, in a state where the winding angle θ is +13 degrees, an adjustment operation is carried out in rotation of the pin 40, such that the isochronism can be modified more effectively at the same time. help of the amount of variation caused by this operation and the isochronous adjustment can be carried out more easily and precisely.

[0128] More particularly, the variation in isochronism resulting from the rotational adjustment of the pin 40 is substantially proportional to the quantities involved in the context of the rotational adjustment operation. Consequently, it is possible to modify the isochronism by an amount corresponding to that of the rotational adjustment operation of the eyebolt 40, and thus to carry out the isochronous adjustment quantitatively.

[0129] More particularly, the isochronism of the main hairspring body 31 changes with the polarity at which the amplitude of the balance wheel 20 has an extreme value in a range of 200 degrees to 250 degrees, such that when the isochronous adjustment is carried out in an amplitude range of 200 degrees to 250 degrees, for example, even for a rotational adjustment operation corresponding to one minute of angle, the isochronism can be changed substantially and efficiently, and the isochronous adjustment can thus be carried out easily.

[0130] As described above, according to the regulating member 13 comprising the hairspring 30 of the reduced embodiment, the isochronous adjustment can be carried out easily and precisely without using a racket.

[0131] Particularly, unlike a case where the isochronous adjustment is carried out using pliers or the like as in the prior art, the isochronous adjustment can be carried out flexibly and the isochronism can be changed quantitatively by a series of flows in which the adjustment of the winding angle θ is carried out appropriately, and then the rotational adjustment of the eyebolt 40 is carried out. Therefore, isochronous adjustment can be carried out easily and appropriately as needed.

[0132] Furthermore, according to the movement 10 and the timepiece 1 of the embodiment described, since the regulating member 13 is provided, it is possible to provide a movement 10 and a timepiece 1 having a rate lower error and high performance.

(Variant of the first embodiment)

[0133] In the first embodiment, the winding angle θ is +13 degrees, but the embodiment of the invention is not limited to such a case, and the winding angle θ could be locate in a range corresponding to the first angle range E1, that is to say, in a range of (-125 degrees ±5 degrees to -215 degrees ±5 degrees), or (-35 degrees ±5 degrees at +55 degrees ±5 degrees).

[0134] Among these, it is preferable that the winding angle θ is in a range of (-170 degrees ±α degrees), or (+10 degrees ±α degrees), and α is included in a range of range from 5 degrees to 30 degrees. Among them, it is more preferable that the winding angle θ is set in the following order. · The winding angle θ is in the range of (-170 degrees ±30 degrees), or (+10 degrees ±30 degrees). · The winding angle θ is in the range of (-170 degrees ±25 degrees), or (+10 degrees ±25 degrees). · The winding angle θ is in the range of (-170 degrees ±20 degrees), or (+10 degrees ±20 degrees). · The winding angle θ is in the range of (-170 degrees ±15 degrees), or (+10 degrees ±15 degrees). · The winding angle θ is in the range of (-170 degrees ±10 degrees), or (+10 degrees ±10 degrees). · The winding angle θ is in the range of (-170 degrees ±5 degrees), or (+10 degrees ±5 degrees).

[0135] Therefore, the most preferable is that the winding angle θ is in the range of (-170 degrees ±5 degrees), or (+10 degrees ±5 degrees). In this case, it is possible to obtain the same advantageous effects as those achieved in the first embodiment.

[0136] Furthermore, in the first embodiment, a hairspring 30 with a terminal curve is adopted, but a hairspring without a terminal curve 80 illustrated in Figure 6, or a hairspring with overcoiling 90 illustrated in Figure 7 could also be adopted. Also in this case, as described above, by having the same characteristics as those of the hairspring 30 with a terminal curve, it is possible to obtain the same advantageous effects as those achieved within the framework of the first embodiment.

[0137] For example, as illustrated in Figures 17 to 19, it is possible to provide a regulating member 100 including the hairspring with overwinding 90.

[0138] A portion of the outermost spring portion 32 of the main balance spring body 31 is raised, the balance spring 90 extends in this case in a direction opposite to the starting point of the elevation in the radial direction, and then is fixed (maintained) at the pin 40. Furthermore, in the example illustrated, the pin 40 fixes (maintains) the external end 31b of the hairspring 90, such that the winding angle θ is -167 degrees.

[0139] Also in the case where the regulating member 100 is constituted as described above, the hairspring with overwinding 90 has the same characteristics as those of the hairspring 30 with a terminal curve, and the winding angle θ is -167 degrees in the range of (-170 degrees ±5 degrees), thus similar to the first embodiment, the isochronous adjustment can be carried out easily and precisely by the rotational adjustment of the eyebolt 40.

(Second embodiment)

[0140] In the following, a second embodiment according to the present invention will be described with reference to the drawings. For this second embodiment, the same reference numbers will be given to the same parts of the configuration elements as those of the first embodiment and their detailed description will not be repeated.

[0141] In the first embodiment, the eyebolt holder 50 rotatably supports the eyebolt 40 around the second axis O2, but in the second embodiment, the eyebolt holder 50 supports the eyebolt 40 so that it can move in the radial direction.

[0142] As illustrated in Figures 20 and 21, the regulating member 110 of this embodiment includes a stud (second element according to the present invention) 120 which fixes (maintains) an external end 31b of a main body of a hairspring 31, and an eyebolt holder 130 (support member according to the present invention) which movably supports the eyebolt 120 in the radial direction.

[0143] Furthermore, in Figure 20, part of the configuration components of the regulating member 110 is omitted to facilitate understanding of the drawings.

[0144] Similar to the first embodiment, the eyebolt carrier 130 includes a connecting ring 51 and a eyebolt arm 52 having a first eyebolt arm 53 and a second eyebolt arm 54, and is capable of rotating from relative manner around the first axis O1 relative to the balance 20.

[0145] The first eyebolt arm 53 and the second eyebolt arm 54 can be elastically deformed in the circumferential direction, and the ends of their points are compressed in advance to approach one another. Consequently, a shaft body 41 of the eyebolt 120 can be sandwiched between the first eyebolt arm 53 and the second eyebolt arm 54.

[0146] The curved surfaces 55 of the first embodiment are not included in the first sandwiched surface 53a of the first eyebolt arm 53 and the second sandwiched surface 54a of the second eyebolt arm 54 according to this embodiment. Therefore, the first sandwiched surface 53a and the second sandwiched surface 54a are flat surfaces here.

[0147] Similar to the first embodiment, the eyebolt 120 includes a shaft body 41, a head 42, an inner leg 43, and an outer leg 44. However, the shaft body 41 is formed so as to present a first contact surface 41a which is in flat contact with the first sandwiched surface 53a of the first eyebolt arm 53, and a second contact surface 41b which is in flat contact with the second sandwiched surface 54a of the second eyebolt arm peg 54 so that they face each other in the circumferential direction.

[0148] Consequently, the first eyebolt arm 53 and the second eyebolt arm 54 sandwich the eyebolt 120 in a state where the first sandwiched surface 53a is in flat contact with the first contact surface 41a, and the second sandwiched surface 54a is in flat contact with the second contact surface 41b. Therefore, the eyebolt 120 is movably supported in the radial direction between the first eyebolt arm 53 and the second eyebolt arm 54 in a state where any rotational movement is restricted.

[0149] Furthermore, in a case where the eyebolt 120 is moved in the radial direction for example, an adjustment tool is engaged with the head 42, and then the eyebolt 120 is capable of moving so as to resist the against a clamping force between the first eyebolt arm 53 and the second eyebolt arm 54.

[0150] Furthermore, in this embodiment, the support 130 supports the eyebolt 120 in a movable manner while the winding angle θ is -77 degrees.

(Isochronous adjustment of the hairspring)

[0151] In what follows, we will describe a case where the isochronous adjustment of the hairspring 30 is carried out using the regulating member 110 produced in accordance with the embodiment described above.

[0152] In the initial state, the pin 120 is located in a reference position and the main hairspring body 31 is not moved in the radial direction by the pin 120. The winding angle θ is set to -77 degrees, an angle which is in the second angle range E2, using the same method as that of the first embodiment.

[0153] In such an initial state, the winding angle θ is fixed at -77 degrees, and the translation adjustment to move the eyebolt 120 in the radial direction is carried out. Therefore, the isochronism can be changed and isochronous adjustment can be performed.

[0154] In particular, in the main hairspring body 31, in the case where the winding angle θ is located in the second angle range E2, as described above, the isochronous variation resulting from an adjustment in translation in the radial direction is greater than the isochronous variation caused by rotational adjustment, so that the isochronism obtained by the adjustment operation via translational movement in the radial direction can be changed more sensitively than that achieved by a rotational adjustment operation. Therefore, in a state where it is hardly affected by rotational adjustment, the isochronism can be changed by an amount resulting from the translational adjustment in the radial direction.

[0155] Furthermore, as illustrated in Figures 14 and 15, since the winding angle θ is -77 degrees, in the main body of hairspring 31, the maximum amount of variation in isochronism due to adjustment in translation in the radial direction is maximized, but on the contrary, the maximum amount of variation in isochronism resulting from rotational adjustment is minimized. Consequently, the isochronism is modified with great sensitivity by a translation adjustment, but for a rotation adjustment, it becomes insensitive and is therefore difficult to modify it in this way.

[0156] Consequently, in a state where the winding angle θ is -77 degrees, the translation adjustment is carried out, such that the isochronism can be changed more effectively following the variation caused by this operation adjustment and isochronous adjustment can be performed more easily and precisely.

[0157] In particular, similar to the case of the rotational adjustment operation in the context of the first embodiment, the variation in isochronism resulting from a rotational adjustment of the eyebolt 40 is substantially proportional to the level of adjustment via a translational movement. Consequently, the isochronism can be modified by an amount corresponding to the adjustment operation via a translational movement of the pin 40 and the isochronous adjustment can be carried out quantitatively.

[0158] In the above, it will be understood that also in the case of the embodiment presently described, the isochronous adjustment can be carried out quantitatively and the isochronous adjustment can thus be carried out easily and precisely without using the racket.

[0159] In particular, the isochronism of the main hairspring body 31 varies with the polarity at which the amplitude of the balance wheel 20 has an extreme value in a range between 200 degrees and 250 degrees, so that when the adjustment isochronous is carried out while the amplitude is in the range of 200 degrees to 250 degrees, the isochronism can be changed effectively with high sensitivity, and the isochronous adjustment is thus carried out easily for example, even with an adjustment operation via a translational movement carried out in one minute.

[0160] As described above, also in the regulating member 110 comprising the hairspring 30 of the embodiment, the isochronous adjustment can be carried out easily and precisely without using the racket.

(Variant of the second embodiment)

[0161] In the second embodiment, the winding angle θ is -77 degrees, but the embodiment of the invention is not limited to such a case, and the winding angle θ could be locate in a range corresponding to the second angle range E2, that is to say, (-125 degrees ±5 degrees to -35 degrees ±5 degrees), or (+55 degrees ±5 degrees to +145 degrees ±5 degrees).

[0162] Among these, it is preferable that the winding angle θ is in a range of (-80 degrees ±α degrees), or (+100 degrees ±α degrees), and α is in a range of 5 degrees to 30 degrees. Among them, it is even more preferable that the winding angle θ is set in the following order: · The winding angle θ is in a range of (-80 degrees ±30 degrees), or (+100 degrees ±30 degrees). · The winding angle θ is in the range of (-80 degrees ±25 degrees), or (+100 degrees ±25 degrees). · The winding angle θ is in the range of (-80 degrees ±20 degrees), or (+100 degrees ±20 degrees). · The winding angle θ is in the range of (-80 degrees ±15 degrees), or (+100 degrees ±15 degrees). · The winding angle θ is in the range of (-80 degrees ±10 degrees), or (+100 degrees ±10 degrees). · The winding angle θ is in the range of (-80 degrees ±5 degrees), or (+100 degrees ±5 degrees).

[0163] Therefore, the most preferable is that the winding angle θ is located in the range of (-80 degrees ±5 degrees), or (+100 degrees ±5 degrees). In this case, it is possible to achieve the same beneficial effects as those obtained within the framework of the second embodiment.

[0164] Furthermore, also in the second embodiment, the hairspring without terminal curve 80 illustrated in Figure 6, or the hairspring with overwinding 90 illustrated in Figure 7 could be adopted. Also in such a case, as described above, since they have the same characteristics as those of the hairspring 30 with a terminal curve, it is possible to achieve the same effects as those achieved in the second embodiment.

(Third embodiment)

[0165] In the following, a third embodiment according to the present invention will be described with reference to the drawings. In this third embodiment, the same reference numbers will be given to the same parts or pieces of the configuration elements as those already described in the second embodiment, and their detailed description will not be repeated.

[0166] In the second embodiment, the eyebolt 120 is supported so as to be able to move in the radial direction using the first eyebolt arm 53 and the second eyebolt arm 54, but in the third embodiment, the Eyebolt is movably supported using a eyebolt cover.

[0167] As illustrated in Figure 22, the regulating member 140 of this embodiment comprises a pin (second element according to the present invention) 150 which fixes (maintains) an external end 31b of a main body of a hairspring 31, an eyebolt holder 160 (support member according to the present invention) which movably supports the eyebolt 150 in the radial direction, and a eyebolt cover 170 combined with the eyebolt holder 160.

[0168] Furthermore, in Figure 22, part of the configuration components of the regulating member 140 is omitted to facilitate understanding of the drawings.

[0169] As illustrated in Figures 22 and 23, the eyebolt carrier 160 includes a connecting ring 51, a first arm 161 extending outwardly in the radial direction from the connecting ring 51, and a second arm 162 formed in one piece with arm 161 and extending in the circumferential direction.

[0170] The second arm 162 is formed in one piece with a tip (external end) of the first arm 161, and has an elliptical shape in a plan view extending in the circumferential direction or an arcuate shape in a plan view. in plan. In this embodiment, a central part in the circumferential direction of the second arm 162 is connected to the tip of the arm 161, that is to say at its end.

[0171] A part of the arm 162, which is located in the center in the circumferential direction, has a first guide groove in the form of a slot 163 which penetrates vertically into the second arm 162, and is open outwards in the radial direction . The first guide groove 163 has a linear shape and extends along the radial direction.

[0172] Peripheral ends of the second arm 162, which are located on either side opposite the first guide groove 163 in the circumferential direction, respectively have screw holes 164 oriented vertically.

[0173] The eyebolt 150 comprises a cylindrical shaft body 41 extending along the second axis O2, a flange 151 which is positioned below an upper end of the shaft body 41, is formed of a integral (in one piece) with the shaft body 41, and has an enlarged diameter relative to the shaft body 41, and an inner leg 43 and an outer leg 44 projecting downward from a lower end of the body shaft 41. In addition, in Figures 22 and 23, the inner leg 43 and the outer leg 44 are hidden by the eyebolt holder 160.

[0174] The shaft body 41 has a cylindrical shape whose external diameter is smaller than the width of the first guide groove 163. The flange 151 has a circular shape in a plan view whose external diameter is larger than the width of the first guide groove 163. Consequently, the eyebolt 150 is arranged so as to be able to move in the radial direction in the first guide groove 163 in a state where the flange 151 covers the second arm 162.

[0175] As illustrated in Figures 22 and 24, the eyebolt cover 170 is a plate extending in the circumferential direction corresponding to the shape of the second arm 162, and is arranged so as to cover an upper surface of the second arm 162 In addition, the eyebolt cover 170 is formed such that its external diameter corresponds to the external shape of the second arm 162 so as to substantially cover the entire surface of the second arm 162.

[0176] A part of the eyebolt cover 170, which is centrally located in the circumferential direction, has a second slot-shaped guide groove 171 which vertically penetrates the eyebolt cover 170 and extends along the radial direction. The second guide groove 171 has the same groove width as that of the first guide groove 163, and is provided above the first guide groove 163. An upper end of the shaft body 41 of the eyebolt 150 is inserted in the second guide groove 171.

[0177] A lower surface of the eyebolt cover 170 is formed so as to have a recess 172 extending along the radial direction at a portion located centrally in the circumferential direction. The width of the recess 172 arranged to be larger than the diameter of the flange 151 of the eyebolt 150. Consequently, the eyebolt cover 170 is capable of covering the upper surface of the second arm 162 in a state where the flange 151 is housed in the recess 172. However, the depth of the recess 172 is arranged to be slightly shallower than the thickness of the flange 151. Consequently, the eyebolt cover 170 covers the upper surface of the second arm part 162 in a state where the flange 151 is compressed against the second arm 162.

[0178] Furthermore, the peripheral ends of the eyebolt cover 170, which are located on either side of the second guide groove 171 in the circumferential direction, respectively have fixing holes 175 for fixing the screws 173. The eyebolt cover 170 is combined with the second arm 162 to form a single piece, in a state where the flange 151 is pinched by the second arms 162 by fixing the fixing screws 173 to the screw holes 164 through the fixing holes 175.

(Isochronous adjustment of the hairspring)

[0179] According to the regulating member 140 of the embodiment described above, since the pin 150 can be moved in the radial direction, it is possible to achieve the same effects as those obtained in the context of the second embodiment.

[0180] Furthermore, in the case of this embodiment, the pinching of the flange 151 can be released by loosening or removing the fixing screws 173, such that the eyebolt 150 can be moved in the radial direction along the first guide groove 163 and the second guide groove 171. After the translation adjustment is carried out, the fixing screws 173 are tightened, so that the flange 151 can be pinched between the second arm part 162 and the eyebolt cover 170. Therefore, the eyebolt 150 can be fixed more stably in a given position after the translation adjustment operation.

[0181] Consequently, it is possible to effectively restrict any position shift caused by, for example, an unintentional movement of the position of the eyebolt 150 in the radial direction.

[0182] Although the above embodiments have been described for the present invention, these embodiments are presented as examples, without any intention of limiting the scope of the invention. These embodiments may also be implemented in various other forms, and various omissions, substitutions and changes may be made without departing from the scope of the invention. Embodiments and examples of modification thereof include, for example, those readily assumed by those skilled in the art, modifications resulting in substantially identical characteristics, modifications within an equivalent scope, etc.

[0183] For example, in each of the embodiments described above, the case where the internal end of the main hairspring body is fixed to the balance shaft of the balance has been described as an example, but the present invention is not limited to such a case. For example, the inner end of the hairspring main body may be attached to the first component (i.e., the timepiece component other than the balance wheel) rotating about the axis.

Claims (8)

1. Regulating body comprising – a hairspring (30), said hairspring (30) comprising: a balance spring main body (31) of which an internal end (31a) is fixed to a balance shaft (21) of a balance wheel (20) rotating around an axis (O1) via a ferrule (24) and an end external (31b) is held by a pin (40), and which has a spiral shape comprising a predetermined number of turns in a intersecting plane with the axis between the internal end (31a) and the external end (31b) , in which, when an angle around the axis (O1) formed between a first virtual line (L1) connecting an end of winding position (P1) of the main hairspring body (31) and the axis (O1) , corresponding to the place where the internal end (31a) is substantially fixed to the ferrule (24), and a second virtual line (L2) connecting a holding position of the main hairspring body retained by the pin (40) and the axis (O1) defines a winding angle (θ) in a plane perpendicular to the axial direction, the main hairspring body (31) is retained by the pin (40) so that the outer end (31b) can, during adjustment, rotate in the plane when the winding angle (θ) is located in a first predetermined angular range (E1), or is retained by the pin (40) such that the external end (31b) moves, during adjustment, in a radial direction of the main hairspring body ( 31) when the winding angle (θ) is within a second predetermined angular range (E2), and the winding angle (θ) of said hairspring main body (31) being further configured such that, when it is located in the first angle range (E1), the isochronous variation generated by a rotation in the plane of the outer end (31b) is greater than the isochronous variation caused by movement in the radial direction of the outer end (31b), and when the winding angle (θ) is in the second range angle (E2), an isochronous variation generated by movement in the radial direction of the outer end (31b) is greater than an isochronous variation generated by rotation in the plane of the outer end (31b). 2. Regulating body according to claim 1, in which, by defining a movement of the eyebolt (40) in the direction of winding of the main hairspring body (31) as a positive direction of winding angle (θ), and a direction opposite thereto as a negative direction of winding angle (θ), based on a case where the winding angle (θ) is zero, the first angle range (E1) is an angle range in which the winding angle (θ) is within a range of (-125 degrees ±5 degrees to -215 degrees ±5 degrees), or ( -35 degrees ±5 degrees to +55 degrees ±5 degrees), and the second angle range (E2) is an angle range in which the winding angle (θ) is within a range of (-125 degrees ±5 degrees to -35 degrees ±5 degrees), or ( +55 degrees ±5 degrees to +145 degrees ±5 degrees). 3. Regulating body according to claim 2, the first angle range (E1) being an angle range where the winding angle (θ) is within a range of (-170 degrees ±α degrees), or (+10 degrees ±α, degrees) , the second angle range (E2) being an angle range in which the winding angle (θ) is included in a range of (-80 degrees ±α degrees), or (+100 degrees ±α degrees) , And α being an angle between 5 degrees to 30 degrees. 4. Regulating body according to claim 3, the first angle range (E1) being an angle range in which the winding angle is within a range of (-170 degrees ±5 degrees), or (+10 degrees ±5 degrees), and the second angle range (E2) is an angle range in which the winding angle is within a range of (-80 degrees ±5 degrees), or (+100 degrees ±5 degrees). 5. Regulating body according to one of the preceding claims, wherein the outer end (31b) is arranged to rotate in the plane, or the outer end is arranged to move in a radial direction of the balance shaft (21), such that the balance spring main body (31) can vary isochronously according to a curve comprising an extreme value included in a range where the amplitude of the pendulum is from 200 degrees to 250 degrees. 6. Regulating member according to claim 5, comprising a support element (50) which is combined with the balance (20) so as to be rotatable relative to the latter around the axis (O1) and movably support the eyebolt (40), in which the support element (50) maintains the eyebolt (40) in the plane with a degree of freedom in rotation, or movably supports the eyebolt (40) in a radial direction relative to the balance shaft (21). 7. Timepiece movement (10) comprising: the regulating member according to one of the preceding claims. 8. Timepiece (1) comprising: the timepiece movement (10) according to claim 6.