CH715096A2 - Spiral, regulating organ, timepiece movement and timepiece. - Google Patents

Abstract

The invention relates to carrying out an easy and precise isochronous adjustment without using a racket. The hairspring (30) includes a main hairspring body (31) of which an inner end (31a) is fixed to a first element (20) and an outer end (31b) is held by a second element (40), in which the main hairspring body (31) is held by the second member (40), so that the outer end (31b) can rotate in a plane in a system state where a winding angle (θ) of the hairspring is located in a first angle range, or is retained by the second element (40), so 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, and in which, when the winding angle (θ) is in the first angle range, an isochronous variation due to a rotation in the plane is more large than an isochronous variation due to movement in the radial direction, and when if the winding angle (θ) is in the second angle range, an isochronous variation due to movement in the radial direction is greater than an isochronous variation due to rotation in the plane.

Description

Description

BACKGROUND OF THE INVENTION

1. Field of the invention The present invention relates to a hairspring, a regulating member, a movement of a timepiece and a timepiece.

2. Description of the Prior Art In a mechanical timepiece, it is important that a balance spring is adjusted to correspond to a range of specific values in which an oscillation period is predetermined. If the oscillation period deviates from this specific range of values, the rate of deviation (delay and advance level of the timepiece) of the mechanical timepiece changes.

As a method of adjusting this rate, a method is generally known for adjusting the length (called the effective length) of the balance spring, one internal end of which is fixed to a balance shaft of the balance wheel and one external end of which is fixed to a piton, by a regulator often called a racket.

The racket mainly comprises an adjustment key rotatably mounted around a central pendulum axis, and arranged outside in the radial direction relative to the hairspring, and a racket pin disposed inside the hairspring in the radial direction. Consequently, the hairspring is arranged between the racket adjustment key and the racket pin, and is made to oscillate in the radial direction between the latter.

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

In addition, snowshoes are also known which are capable of carrying out an isochronous adjustment (clearance adjustment) of the rate of gait deviation by adjusting an amount of clearance (clearance level) which is constituted by a spacing between the key. for adjusting the racket and the racket pin by performing the step deviation rate adjustment operation.

The hairspring makes repetitive movements causing it to come into contact with the racket adjustment key, then to separate from this key, and to come into contact with the racket pin, then to separate of this when the pendulum performs a round trip, so that states where the effective length is respectively small and long are alternately repeated. In addition, in the balance spring, since the oscillation level changes according to the amount of winding, the moment of contact with the racket adjusting key or the racket pin changes. Therefore, for example, the time corresponding to a state where the effective length is small may be extended, and there is concern that the isochronism of the gait deviation rate may be affected.

[0008] Consequently, the adjustment of play is carried out by the racket, so 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 a high precision is assembled, it is important to carry out an 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 racket. Therefore, the isochronism of the assembled regulating body depends on the precision of each of the configuration components, an assembly position, or the like, thus causing variations in isochronism.

In addition, in the case where the isochronous adjustment is carried out without using a racket, there is known for example a method for essentially manually correcting a position, a shape, or the like of the outer end of the hairspring using pliers or similar. Furthermore, as 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 dependent on an amplitude of oscillation of the pendulum generated by an escapement is formed at the outermost peripheral part of the balance spring (for example, see JP-T-2014-525 591 (patent document 1)).

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

CH 715 096 A2

SUMMARY OF THE INVENTION An object of the present patent application to provide a balance spring, a regulating member, a timepiece movement and a timepiece in which an isochronous adjustment can be carried out easily precisely without using racket.

(1) A hairspring of the present patent application comprises a main hairspring body, an internal end of which is fixed to a first element rotating about an axis, and an external end of which is held by a second element, and which has a spiral shape with a predetermined number of turns in a plane intersecting 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 of winding position of the main hairspring body and the axis, and a second virtual line connecting a holding position of the main hairspring body retained by the second element and the axis defines a winding angle in the axial direction, the main hairspring body is retained by the second element, so that the outer end rotates in the plane in a state where the angle of winding is in a first predetermined angular range, or is retained by the second element, so that the outer end moves in a radial direction of the main balance spring body in a state where the winding angle is in a second predetermined angular range, and the main hairspring body is further formed so that when the winding angle is within the first range of angle, an isochronous variation which results from a rotation in the plane is greater than an isochronous variation result of a movement in the radial direction, and when the angle of winding is in the second range of angle, an isochronous variation resulting from a movement in the radial direction is greater than an isochronous variation resulting from a rotation in the plane.

According to the hairspring of this patent application, in a state of the system where the winding angle is within the first angle range, a rotation adjustment of the outer end of the main hairspring body in the plane is carried out, or, in a state of the system where the winding angle is situated in the second angle range, a translation adjustment of the external end of the main hairspring body is carried out in the radial direction, so that an isochronous adjustment can be made.

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

[0016] Consequently, even in a case where an operation of adjustment in rotation in the plane of the outer end of the main balance spring body is carried out, or an operation of adjustment in translation in the radial direction is carried out, the isochronism can be changed with a variation caused by either 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. In addition, it is possible to ensure that the isochronous variation generated by the adjustment in rotation or in translation is a relationship substantially proportional to the amplitude of the rotation or the length of the movement in translation. Consequently, it is possible to change the isochronism of a variation corresponding to the amplitude of the adjustment rotation or of the adjustment level in translation of the external end of the main hairspring body, and to perform quantitatively. isochronous adjustment.

In the foregoing, the isochronous adjustment can be carried out quantitatively and can be carried out easily and precisely without using a racket.

(2) By defining a displacement of the second element in the direction of the winding of the main hairspring body as a positive direction of winding angle, and a direction opposite to it as a negative direction of wrap angle, based on a case where the wrap angle is zero, the first angle range is an angle range in which the wrap 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).

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 main balance spring, the isochronous variation resulting from the rotation in the plane is greater than the isochronous variation resulting from a movement in the radial direction. In addition, 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), the isochronous variation resulting from a movement in the radial direction is greater than the isochronous variation resulting from a rotation in the plane.

CH 715 096 A2 Consequently, when the winding angle is within the range of (- 125 degrees, ± 5 degrees, to - 215 degrees, ± 5 degrees), or (- 35 degrees, ± 5 degrees, at + 55 degrees, ± 5 degrees), an adjustment is made in rotation of the external end of the main hairspring 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), a translation adjustment is made in the radial direction of the outer end of the main body spiral, so that the isochronism can be changed by a variation caused by each setting operation, and an isochronous adjustment can be made.

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

In this case, when the winding angle is within the range of (-170 degrees ± a degrees), or (+ 10 degrees ± a degrees), in the main hairspring body, a maximum variation of the isochronism due to the rotation in the plane is maximized, and on the other hand, a maximum variation of the isochronism due to the movement in the radial direction is minimized. Consequently, the isochronism varies with great sensitivity following the adjustment in rotation in the plane, but it becomes insensitive to the adjustment movement in the radial direction, and hardly changes any more compared to the adjustment movement in translation.

Therefore, when the winding angle is within the range of (-170 degrees ± a degrees), or (+ 10 degrees ± a degrees), the adjustment in rotation in the plane is performed, so that the isochronism can be changed 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.

Similarly, when the winding angle is within the range of (- 80 degrees ± a degrees), or (+ 100 degrees ± a 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 in the isochronism resulting from an adjustment in rotation in the plane is minimized. Consequently, the isochronism varies with great sensitivity via the adjustment in translation in the radial direction, but it becomes insensitive to the adjustment via a rotation in the plane, and hardly changes any more compared to the movement of adjustment in rotation.

Therefore, when the winding angle is within the range of (-80 degrees ± a degrees), or (+ 100 degrees ± a degrees), the adjustment in translation in the radial direction is made, of so that the isochronism can be changed more effectively by the variation caused by this adjustment operation and the isochronous adjustment can be performed more easily and more precisely.

In addition, in the first angle range, while a decreases from 30 degrees to 5 degrees, the operational effect described above can be more effectively achieved. 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 he winding angle is in the range of (-170 degrees ± 30 degrees), or (+ 10 degrees ± 30 degrees).

Similarly, in the second angle range, while a decreases from 30 degrees to 5 degrees, the operational effect described above can be achieved 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).

In all cases, while the value of a decreases, the operational effect described above can be achieved effectively, which is preferable. Specifically, it is conceivable that a decreases by 30 degrees in steps of 5 degrees.

(4) The first angle range can 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 can be an angle range in which the winding angle is within a range of (- 80 degrees, ± 5 degrees), or (+ 100 degrees, ± 5 degrees).

In this case, the operational effect described above can be achieved more effectively.

(5) The first element can be a balance, and the internal end of the main balance spring body can be fixed to a balance shaft in the balance.

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

(6) The outer end rotates in the plane, or the outer end moves in a radial direction of the balance shaft, so that the main hairspring body can vary isochronously along a curve comprising an extreme value included in a range in which the amplitude of the pendulum is from 200 degrees to 250 degrees.

In this case, when the isochronous adjustment is carried out with the amplitude in the range of 200 degrees to 250 degrees, the isochronism can be changed effectively and significantly, and the isochronous adjustment is easily

CH 715 096 A2 performed, for example, even in one minute operation (rotation adjustment and adjustment via translational movement in the radial direction).

(7) A regulating member of this patent application comprises the hairspring; the pendulum; the second element; and a support member which is combined with the pendulum to be rotatable relative to the latter about the axis, and movably support the second member, wherein the support member rotatably supports the second member in the plane , or movably supports the second element in a radial direction of the balance shaft.

In this case, the second element can be moved in the circumferential direction with the support element by turning the support element around the axis relatively to the balance, so that the angle The hairspring can be adjusted at any angle. Therefore, the winding angle can be adjusted appropriately to be in the first angle range or the second angle range. In addition, since the support member supports the second member in a rotatable or movable manner in the radial direction, as described above, the outer end of the hairspring can be moved by performing the rotation adjustment or the adjustment in translation in the radial direction of the second element as a function of the winding angle; therefore, isochronous adjustment can be performed.

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 slightly carried out and the isochronism can be changed quantitatively by a series flow in which the winding angle adjustment is made appropriately, and then the rotation adjustment or the translation adjustment is performed, so that the isochronous adjustment can be performed easily and appropriately.

(8) A timepiece movement of the present patent application comprises the regulating member described above.

(9) A timepiece of this patent application includes the timepiece movement described above.

In this case, since we supply a hairspring as described above, a timepiece movement and a timepiece having a high error rate month in terms of gait deviation and a high performance can be provided by precise isochronous adjustment.

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 deviation and high performance can be obtained.

BRIEF DESCRIPTION OF THE DRAWINGS

Fig. 1 is a view illustrating a first embodiment according to the present invention and an external view of a timepiece.

Fig. 2 is a plan view of a movement of FIG. 1.

Fig. 3 is a perspective view of a regulating member illustrated in FIG. 2.

Fig. 4 is a sectional view of the regulating member, which is seen along the line A-A illustrated in FIG. 3.

Fig. 5 is a plan view of the regulating member illustrated in FIG. 3 and a plan view illustrating a relationship between a piton holder, a hairspring and a pendulum.

Fig. 6 is a plan view of a hairspring without a terminal curve.

Fig. 7 is a plan view of a spiral with overwinding.

Fig. 8 is a view illustrating isochronous curves in the case where no adjustment operation is carried out, in the case where an adjustment in rotation is carried out, and in the case where the adjustment is carried out via a translational movement when an angle d winding is 0 degrees.

Fig. 9 is a view illustrating a relationship between an isochronous variation curve at the time of the rotary adjustment operation and an isochronous variation curve at the time of the adjustment operation via a translational movement.

Fig. 10 is a view illustrating a relationship between a curve of variation of a maximum amount of the isochronous variation at the time of adjustment in rotation, and a curve of variation of a maximum amount of the isochronous variation at the time of adjustment via a movement of translation.

CH 715 096 A2

Fig. 11 is a view illustrating a relationship between a curve of variation of a maximum amount of the isochronous variation at the time of adjustment in rotation, and a curve of variation of a maximum amount of the isochronous variation at the time of adjustment via a movement of translation in a hairspring without end curve.

Fig. 12 is a view illustrating a relationship between a curve of variation of a maximum amount of the isochronous variation at the time of adjustment in rotation, and a curve of variation of a maximum amount of the isochronous variation at the time of adjustment via a movement of translation in a hairspring with rewinding spring.

Fig. 13 is a view illustrating a relationship between a curve of variation of a maximum amount of the isochronous variation at the time of adjustment in rotation, and a curve of variation of a maximum amount of the isochronous variation at the time of adjustment via a movement of translation in each of the hairsprings with terminal curve, without terminal curve and with rewinding spring.

Fig. 14 is a view illustrating a relationship between curves of change in isochronism following rotational adjustments in four winding angles.

Fig. 15 is a view illustrating a relationship between curves of change in isochronism following adjustments via translational movements in four winding angles.

Fig. 16 is a view illustrating a relationship between a curve for changing a maximum amount of isochronous variation at the time of the rotary adjustment operation, and a curve for changing a maximum amount of isochronous variation at the time of operation adjustment via a translational movement in each of the balance springs with a terminal curve, without terminal curve and with a rewinding spring, in a case where the number of revolutions of the balance spring is equal to 14, where and the number of oscillations of the balance wheel is 8 oscillations.

Fig. 17 is a perspective view of a regulating member illustrating a variant of the first embodiment.

Fig. 18 is a perspective view illustrating a relationship between a piton holder, a hairspring and a pendulum illustrated in FIG. 17.

Fig. 19 is a plan view illustrating a relationship between the piton holder and the hairspring illustrated in FIG. 18.

Fig. 20 is a perspective view of a regulating member illustrating a second embodiment according to the present invention.

Fig. 21 is an enlarged plan view of a periphery of a peak illustrated in FIG. 20.

Fig. 22 is a perspective view of a regulating member illustrating a third embodiment according to the present invention.

Fig. 23 is a perspective view illustrating a state where a piton cover is removed from the state illustrated in FIG. 22.

Fig. 24 is a perspective view of the piton cover illustrated in FIG. 22.

DESCRIPTION OF THE EMBODIMENTS In the following, embodiments of the present invention will be described with reference to the drawings. In addition, in the embodiments, as an example of a timepiece, a mechanical timepiece is described.

(Basic configuration of a timepiece) In general, reference is made to a mechanical body comprising a drive part of the timepiece as being a "movement". In a state where a dial and hands are attached to the movement, put in a timepiece case, and assembled into a finished product, we refer to a "set" of timepiece. Among the two sides of a plate constituting a base plate of the timepiece, reference is made to the side with the crystal of the case of the timepiece, (that is to say, the side of the dial ) as the "back side" of the movement. Furthermore, among the two sides of the plate, reference is made to the side of the bottom of the case of the timepiece, (that is to say, the side opposite to the dial) as being the "front side" of the movement.

In addition, in the embodiments, a description is given according to which the direction of the dial towards the bottom of the case is defined as “upwards” and the opposite direction is defined as “downwards”.

(First embodiment)

CH 715 096 A2 As illustrated in fig. 1, a set 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 hour, a minute hand 5 indicating the minutes and a second hand 6 indicating the seconds in the timepiece case made up of a case back (not illustrated ) and an ice cream 2.

As illustrated in FIGS. 2 and 3, the movement 10 comprises a plate 11, a gear train (not shown) and a cock 12, that is to say a balance bridge arranged on the front side of the plate 11. A finishing train, an exhaust (not illustrated) for controlling the rotation of the gear train, and a regulating member 13 regulating an exhaust speed are mainly disposed between the plate 11, the gear bridge and the cockerel. The dial 3 is arranged visible behind the plate 11 through the glass 2.

In addition, 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 weight 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 gear train mainly comprises a barrel, a second mobile, a third mobile and a fourth mobile. In addition, 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 fig. 1 rotates on the basis of the rotation of the fourth mobile and rotates at a speed of rotation regulated by the exhaust and the regulating member 13, that is to say, a revolution in 1 minute. The minute hand 5 rotates on the basis of the rotation of the second mobile or the rotation of a pinion rotating in accordance with the rotation of the second mobile, and rotates at a speed of rotation 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 speed of rotation controlled by the escapement and the regulating member. 13, that is to say, a complete revolution in 12 hours or 24 hours.

The exhaust comprises an exhaust mobile (not shown) meshing with the fourth mobile, and an anchor (not shown) escaping and regularly rotating the exhaust mobile, and controls the train of finishing by a regular oscillation from a pendulum 20 which will be described later.

As illustrated in FIGS. 3 and 4, the regulating member 13 comprises the balance (first element according to the present invention) 20 rotating alternately (that is to say repeating rotational movements forwards and then backwards) around a first axis O1 (the “axis” according to the present invention), a hairspring 30, a stud 40 (second element according to the present invention) holding an external end 31b of a main hairspring body 31, which will be described later , and a piton holder 50 (support element according to the present invention) which is combined with the pendulum 20 to be rotatable relative to the latter about the first axis O1, and movably supports the piton 40.

In addition, in the embodiment described, a secant direction 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 pendulum 20 comprises a pendulum shaft 21 which is rotatably mounted around the first axis O1 and a pendulum wheel 22 attached to the pendulum 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 a source of energy.

In the balance shaft 21, an upper tenon 21a is supported essentially on a stony upper plug 60, and a lower lug 21b is essentially supported on a lower stony stopper (not illustrated) formed in the plate 11 illustrated on fig. 2. A link 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 force fitting or the like, and an outer end is connected to an inner peripheral surface of the balance wheel 22. Consequently, the balance wheel 22 is fixed to the balance shaft 21 via the arm of link 23, and rotates forward and backward around the first axis O1 with the pendulum shaft 21. However, the number, arrangement, and shape of the connection arms 23 can be changed appropriately as required.

The ferrule 24 is disposed 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 collar 25a and a small collar 25b situated below the large collar 25a. The large collar 25a is formed by an artificial precious stone such as a ruby, and a plateau pin 27 for operating (swinging / oscillating) the anchor is, for example, force-fitted to be fixed there.

The upper stony cap 60 is a socket set in impact-resistant precious stone (anti-shock) comprising a socket body set 61 with a cylindrical shape, a stone with an upper hole 62 being fixed inside the

CH 715 096 A2 crimped socket body 61 and rotatably supporting the upper lug 21 a of the balance shaft 21, an upper cap 63 also made of precious stone placed above the stone with upper hole 62, and supporting the upper tenon 21 a of the balance shaft 21 in the axial direction, and a fixing support 64 for the upper cap being disposed still above the upper cap 63 and fixing the upper cap 63 to the crimped sleeve body 61.

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

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

For example, as illustrated in FIG. 2, the rooster 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 seat plate 70 is formed at an outer edge so as to have a progressive recess. As illustrated in fig. 2, the rooster 12 is fixed to the plate 11 by fixing screws 74 using the mounting holes 73. However, the shape of the rooster 12 is not limited to such a configuration as that described above, and could be modified as appropriate.

As illustrated in FIG. 4, a through hole 75 vertically penetrating into the seat plate 70 is formed in the seat plate 70 coaxially with the first axis O1. The cylindrical part 71 is formed so as to rise above the seat plate 70 along the peripheral edge of the through hole 75, and the interior of the latter communicates with the through hole 75. Consequently, 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 force fitting. In addition, the upper body 61 a of the crimped socket body 61 is disposed at an opening end of the cylindrical part 71, and has a shape larger than the external diameter of the cylindrical part 71.

As illustrated in FIGS. 3 to 5, the piton holder 50 is rotatably inserted into the cylindrical part 71 in the cock 12, being consequently able to rotate relatively around the first axis O1 relative to the cylindrical part 71.

The piton holder 50 comprises a connection ring 51 fitted to the outside of the cylindrical part 71, and a piton 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 piton holder 50 supports the piton 40 in a rotatable manner around a second axis O2, parallel to the first axis O1.

In addition, the connection ring 51 is arranged in the form of a C in a plan view, that is to say a ring, part of which in the circumferential direction would have been removed; however, it could also take an annular shape.

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

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

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

The peg 40 includes 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.

The shaft body 41 is sandwiched between the first piton arm 53 and the second piton arm 54 while being placed inside the curved surface 55 of the first piton arm 53 and the surface curved 55 of

CH 715 096 A2 second piton 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 piton arm 53 and the second arm of piton 54. Consequently, the piton 40 is sandwiched between the first piton arm 53 and the second piton arm 54, and parallel rotatably supported around the second axis 02, being found at least in one state of being blocked down.

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 pin 40 can be actuated in rotation around the second axis O2 using the adjustment tool.

A part of the outermost spring 32 of the main hairspring 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 is disposed inside the outermost spring portion 32 in the radial direction, and the outer leg is disposed outside the outermost spring portion 32 in the 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 definitively 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 part 32 including the outer end 31b is fixed (maintained) by the stud 40. Hereinafter, the hairspring 30 will be described in detail.

(Spiral) As illustrated in FIG. 5, the hairspring 30 comprises the main hairspring body 31 in the form of a hairspring with a predetermined number of turns in a plane intersecting 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 stud 40 described above.

The main hairspring body 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 the origin. Consequently, the main hairspring body 31 is wound in a plurality of windings so that each of the windings is adjacent to each other at substantially equal intervals in the radial direction. In addition, the material of the main hairspring body 31 is not limited to the case described above, but can be modified as appropriate. In addition, the shape of the main hairspring body 31 is not limited to the shape of the hairspring according to an Archimedes Curve, but can be modified to take a shape according to which the spacing step changes, for example, a hairspring logarithmic or similar.

A portion of the outermost spring portion 32 of the main hairspring body 31, which includes the outer end 31b and is located in the outermost portion outward in the radial direction, is spaced outward in the radial direction via a straightened part 33 and is formed by an arcuate part 34 whose radius of curvature is greater than that of the other parts. A peripheral end of the arcuate part 34 is the external 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 peg 40 as described below. -above.

The hairspring 30 of the embodiment formed as described above is classified as being so-called flat beard and has a shape of terminal curve in which the arcuate part 34 is formed in the outermost spring part 32 via the straightened part 33. In the embodiment described, reference can thus be made to hairspring 30 thus formed as simply being "with a terminal curve" or constituting a "hairspring with a terminal curve". Meanwhile, 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 take another form. For example, as illustrated in fig. 6, although it is one of the so-called flat beards, 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 hairspring 80 as being "without end curve", or constituting a "hairspring without end curve".

In addition, in FIG. 6, a case is illustrated where the winding direction is opposite to that of the hairspring 30 illustrated in FIG. 5. In addition, as illustrated in FIG. 7, a hairspring 90 classified as a rewinding hairspring (also sometimes called a “Breguet” hairspring) can be adopted, in which a portion of the outermost spring part 32 is raised relative to the plane in which the rest of the spiral spring is located, and the outer end 31b is disposed on the side opposite to the part where the lifting begins, in the radial direction. In this case, one can refer to hairspring 90 as being simply "with rewinding".

In addition, in FIG. 7, a case is illustrated where the winding direction is opposite to that of the hairspring 30 illustrated in FIG. 5.

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

CH 715 096 A2 As illustrated in fig. 5, according to a shot in the axial direction of the balance shaft 21, the angle formed between a first virtual line L1 connecting an end of winding position P1 of the main hairspring body 31 and the first axis O1, and a second virtual line L2 connecting a holding position P2 of the main hairspring body 31, retained by the stud 40, and the first axis O1, with the first axis O1 taken as the center is defined as the winding angle Θ.

In addition, 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 as far inside as possible in the radial direction. Consequently, it is possible the position of the internal end 31a of the main hairspring body 31 and the end of winding position P1 do not necessarily correspond. Also in the embodiment described, the internal end 31a of the main hairspring body 31 and the end of winding position P1 are slightly offset in the circumferential direction.

In addition, the holding position P2 is a substantially fixed position (retaining with respect to) the stud 40, in the outermost spring part 32 of the main balance spring body 31. Consequently, it is possible that the position of the external 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 from each other in the circumferential direction.

In addition, 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.

In other words, 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 with respect to the reference position in the winding direction of the main hairspring body 31 is defined as the positive direction (indicated “+” in fig. 5) of the winding angle Θ, and a direction opposite to it is defined as a negative position (indicated “-” in fig. 5) of the winding angle Θ. Therefore, in fig. 5, the winding angle θ is adjusted in the positive direction. On the other hand, in fig. 6 for example, the winding angle θ is set in the negative direction.

(Characteristics of the hairspring) In the following, a description will be given to calculate how the isochronism changes as a function of the winding angle θ in the hairspring 30 of the embodiment, when one performs a rotation adjustment on the outer end 31b on the side of the main hairspring body 31 or a translation adjustment in the radial direction.

In addition, the rotational adjustment to rotate the outer end 31b of the main balance spring 31 is an operation to rotate a portion of the main balance spring 31, which is retained by the peg 40, in a plane intersecting with respect to the axial direction of the balance shaft 21, that is to say, to rotate it around the second axis O2. Hereinafter, we will simply refer to a “rotation adjustment operation”.

In addition, the translational adjustment 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 peg 40, the along the radial direction of the balance shaft 21. Hereinafter, reference will simply be made to "an operation of adjustment in translation".

In addition, 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, has been used, and an equation of motion (ordinary differential equation) of the balance 20 has been integrated over time.

First, 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 outer end 31b of the main body of hairspring 31 (below, can refer to this state as corresponding to “before an adjustment operation”), a case where an adjustment in rotation is carried out, and a case where the adjustment via a translational movement is carried out calculated. Respective isochronous curves based on the result of the calculation are illustrated in fig. 8.

In FIG. 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. In addition, in fig. 8, a horizontal axis illustrates an amplitude of the balance 20 and a vertical axis illustrates a rate of temporal precision. In addition, as the amplitude of the pendulum 20, it is calculated in a range from 120 degrees to 300 degrees.

In addition, the rotation adjustment is an example of a case where a portion of the main hairspring body 31, which is retained by the stud 40, is rotated 1 degree counterclockwise. with the second axis O2 as the center. In addition, the adjustment in translation is an example of a case where a portion of the main hairspring body 31, which is retained by the stud 40, is displaced by a distance of + 20 μm outward in the radial direction. .

In addition, in this calculation, we take as an example a case where the number of winding turns of the balance spring 30 is equal to 12. In addition, 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 (36,000 oscillations per hour).

CH 715 096 A2 [0101] In the following, a difference between the isochronous curve CL1 before an adjustment operation and the isochronous curve CL2 after the adjustment in rotation is calculated, and an isochronous variation curve CL4 during the adjustment in calculated rotation on the basis of the calculation result is illustrated in fig. 9. Similarly, a difference between the isochronous curve CL1 before adjustment operation and the isochronous curve CL3 after adjustment in translation is calculated, and an isochronous variation curve CL5 during the adjustment operation via a movement in translation calculated on the basis of the calculation result is illustrated in fig. 9. In addition, in fig. 9, the horizontal axis illustrates the amplitude of the balance 20 and a vertical axis illustrates an isochronous variation curve of a rate which corresponds to the temporal precision.

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

In the example of FIG. 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). Consequently, the result (maximum value-minimum value) is substantially equal to 4.21. Consequently, 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 adjustment operation in rotation when the winding angle θ is 0 degrees.

Similarly, in the isochronous variation curve CL5 at the time of adjustment in translation, 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 of fig. 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). Consequently, the result (maximum value-minimum value) is substantially equal to 0.42. Consequently, 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 a translational movement when the winding angle θ is 0 degree.

In addition, as illustrated in FIG. 9, the isochronous variation curve CL4 at the time of the rotation adjustment is an upward projecting curve, so as to include an extreme value (maximum extreme value, that is to say, 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 curve projecting downward, so as to include an extreme value (minimum extreme value, i.e. , the minimum value described above) in a range where the amplitude is 180 degrees to 250 degrees.

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 Figs. 14 and 15).

In the following, 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 adjustment operation in rotation, and the maximum amount of isochronous variation at the time of the adjustment operation via a movement in translation were respectively calculated.

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

In FIG. 10, the value of the maximum amount of isochronous variation at the time of the adjustment operation in rotation at each winding angle θ is plotted with a symbol "□". The curve formed by connecting the maximum variation values to each winding angle θ plotted with the symbol "□" is the variation curve CL6 of the maximum amount of isochronous variation at the time of the rotation adjustment operation.

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 "0". The curve formed by connecting the maximum variation values to each winding angle θ plotted with the symbol "Q" is the variation curve CL7 of the maximum amount of isochronous variation at the time of the adjustment operation via a movement in translation .

As illustrated in FIG. 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. In addition, the maximum value of the maximum amount of variation in the variation curve CL6 and the minimum value of the maximum amount of variation in the variation curve CL7 correspond within a substantially similar range of the angle of 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 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 phase shifted from substantially 90 degrees to 110 degrees.

CH 715 096 A2 [0112] In addition, in FIG. 10, the curves corresponding to the variation curve CL6 and the variation curve 7 are corrected, so that a comparison between the variation curve CL6 and the variation curve CL7 is facilitated, and each maximum value of the maximum quantity of variation indicates a value substantially equal 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 correction. Furthermore, since the variation curves CL6 and CL7 are substantially proportional to the quantities relating to the adjustment operation in rotation and to the adjustment operation via a movement in translation, they are the same as the correction of the amount of movement. .

From the above, according to FIG. 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 an adjustment in rotation of the external end 31b of the body main balance spring 31 is made, or a translation adjustment in the radial direction is made.

In addition, for the hairspring without end curve 80 illustrated in FIG. 6 and the hairspring with overwinding 90 illustrated in FIG. 7, a series of calculations as described above was respectively carried out.

The calculation linked to hairspring 80 (hairspring without terminal curve) illustrated in FIG. 6 is performed, a variation curve CL8 of the maximum amount of isochronous variation at the time of the adjustment operation in rotation, and a variation curve CL9 of the maximum amount of isochronous variation during the adjustment in translation, which are obtained from result of this calculation, are illustrated in fig. 11. As illustrated in fig. 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.

In addition, the calculation linked to hairspring 90 (spiral rewinding spring) illustrated in FIG. 7 is performed, a variation curve CL10 of the maximum amount of isochronous variation at the time of the adjustment operation in rotation, and a variation curve CL11 of the maximum amount of isochronous variation during the adjustment in translation, which are obtained by as a result of this calculation, are illustrated in fig. 12. As illustrated in fig. 12, the variation curve CL10 and the variation curve CL11 were curves illustrating the same trend as that of the variation curve CL6 and of the variation curve CL7 described above.

[0118] FIG. 13 is a graph obtained by combining the respective variation curves of FIGS. 10 to 12. As illustrated in fig. 13, independently of the hairspring with a terminal curve 30, a variation curve CL12 of the maximum amount of isochronous variation at the time of the adjustment operation in rotation, and a variation curve CL13 of the maximum amount of isochronous variation at the time of the adjustment operation via a translational movement illustrates the same trend.

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 spiral overwinding spring (hairspring 90) which are described above.

In other words, in the main hairspring body 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 a different angle from the first angle range E1 and is located in a second predetermined angular range E2, the isochronous variation due to an adjustment in translation in the radial direction is greater than the isochronous variation resulting from an adjustment in rotation around the second axis O2.

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 within a range of (-125 degrees ± 5 degrees to -35 degrees ± 5 degrees), or (+ 55 degrees ± 5 degrees to + 145 degrees ± 5 degrees).

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

In addition, the angle a is an angle included in the range of 5 degrees to 30 degrees. In this case, in the first angle range E1, when a decreases from 30 degrees to 5 degrees, the features described above can be achieved more effectively. For example, the features 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).

In addition, it is conceivable that a decreases by 30 degrees in 5-degree increments, that is to say, the angle a is reduced by passing from 30 degrees to 25 degrees, then 20 degrees, 15 degrees, 10 degrees and finally 5 degrees.

CH 715 096 A2 [0125] In addition, as regards the second angle range E2, in a case where the winding angle θ is within a range of angles within a range of (- 80 degrees ± a degrees), or (+ 100 degrees ± a degrees), the maximum variation in isochronism resulting from adjustment in translation in the radial direction is maximized, but on the contrary, the maximum variation in isochronism due to a adjustment in rotation around the second axis O2 is minimized.

In addition, as in the as described in the first angle range E1, a is an angle in the range of 5 degrees to 30 degrees. In this case, in the second angle range E2, while a decreases from 30 degrees to 5 degrees, the characteristics described above can be effectively achieved. For example, the features 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).

In addition, it is conceivable that a decreases by 30 degrees in increments of 5 degrees, that is to say, that the angle a is reduced by passing on the order of 30 degrees, to 25 degrees, then 20 degrees, 15 degrees, 10 degrees and finally 5 degrees.

This will be described in more detail.

[0129] FIG. 14 is a view illustrating a variation curve of the isochronism resulting from the adjustment in rotation around the second axis O2, and FIG. 15 is a view illustrating a variation curve of the isochronism resulting from an adjustment in translation in the radial direction.

As illustrated in FIGS. 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 operation of adjustment in rotation, but on the contrary, for the adjustment operation in translation in the radial direction, it becomes insensitive, therefore very difficult to change through this. In addition, in a case where the winding angle θ is - 77 degrees or + 103 degrees, the isochronism is modified towards a favorable state by the adjustment in translation, but on the contrary, for the adjustment in rotation, it becomes insensitive therefore very difficult to change in this way.

In addition, FIG. 13 illustrates a result of a case where the number of turns is 12 turns and the number of oscillations of the pendulum 20 is 10 oscillations (i.e., 36,000 oscillations in one hour) as described below. above, and the same result could be obtained even in a case where the number of turns and the number of oscillations are changed.

For example, FIG. 16 is a view corresponding to FIG. 13, of a case where the number of revolutions is 14 revolutions and the number of oscillations of the balance 20 is 8 oscillations (that is to say, 28,800 oscillations in one hour). As is clear from FIG. 16, even in a case where the number of turns and the number of oscillations are changed, the features described above are still provided.

As illustrated in FIG. 5, in the hairspring 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 stud 40 (held 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 pin holder 50 rotatably supports the pin 40 around the second axis O2. Specifically, the winding angle θ is + 13 degrees.

(Isochronous adjustment of the hairspring) In the following, a case will be described where the isochronous adjustment of the hairspring 30 is carried out in timepiece 1 comprising the regulating member 13 constituted as described above. .

In addition, in an initial state, the stud 40 is located in a reference rotational position, and the main hairspring body 31 is not moved around the second axis O2 by the stud 40.

In a case where the isochronous adjustment is carried out in such an initial state, for example, the holder 50 is turned around the first axis O1 relative to the balance 20, so that the eye 40 can be moved in the circumferential direction with the piton holder 50. Consequently, the winding angle θ of the hairspring 30 can be adjusted at any angle. Consequently, the winding angle θ can be adjusted appropriately so as to be in the first angle range E1 or the second angle range E2. In other words, the winding angle θ can be adjusted to + 13 degrees which is located in the first angle range E1.

In addition, the winding angle 0 is not limited to the case as described above, but, for example, the peg 40 could be fixed to the main hairspring body 31 in advance, so that that the winding angle θ is 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 first angle range E1.

Then, in the piton 40 whose winding angle θ is set to + 13 degrees, the operation of adjusting the rotation is carried out around the second axis O2. Therefore, the isochronism can be changed and the isochronous adjustment can be done as well.

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 resulting from an adjustment in rotation is greater than the isochronous variation caused by an adjustment in translation in the radial direction, so that the isochronism of

CH 715 096 A2 the rotation adjustment operation can be modified more significantly than that obtained by the adjustment operation via a translational movement in the radial direction. Consequently, in a state where it is hardly affected by adjustment in translation in the radial direction, the isochronism can be modified with the variation caused by the operation of adjustment in rotation, so that it is possible to perform isochronous adjustment quantitatively and perform isochronous adjustment easily and precisely without using the racket.

In addition, since the winding angle θ is + 13 degrees, as illustrated in figs. 14 and 15, in the main hairspring 31, the maximum variation in isochronism resulting from an adjustment in rotation is maximized, but on the contrary, the maximum variation in isochronism resulting from an adjustment movement in the direction radial is minimized. Consequently, the isochronism is modified with great sensitivity by an operation of adjustment in rotation, but for the adjustment in translation in the radial direction, it becomes insensitive and consequently very difficult to change through this.

Consequently, in a state where the winding angle θ is + 13 degrees, an operation for adjusting the rotation of the peak 40 is carried out, so that the isochronism can be changed more effectively at using the amount of variation caused by this operation and isochronous adjustment can be performed more easily and precisely.

More particularly, the variation in isochronism resulting from the adjustment in rotation of the stud 40 is substantially proportional to the quantities involved in the operation of adjustment in rotation. Consequently, it is possible to modify the isochronism by an amount corresponding to that of the operation for adjusting the rotation of piton 40, and thus to perform isochronous adjustment quantitatively.

More particularly, the isochronism of the main hairspring body 31 changes with the polarity at which the amplitude of the balance 20 has an extreme value in a range of 200 degrees to 250 degrees, so that when the isochronous adjustment is performed in an amplitude range of 200 degrees to 250 degrees, for example, even for a rotation adjustment operation corresponding to one minute of angle, the isochronism can be changed significantly and effectively, and the isochronous adjustment can thus be carried out easily.

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

In particular, 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 in a flexible manner and the isochronism can be changed quantitatively by a series of flows in which the adjustment of the winding angle θ is carried out in an appropriate manner, and then the adjustment in rotation of the peg 40 is carried out. Therefore, isochronous adjustment can be carried out easily and appropriately as required.

In addition, 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) [0149] 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 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 to + 55 degrees ± 5 degrees).

Among these, it is preferable that the winding angle θ is within a range of (- 170 degrees ± a degrees), or (+ 10 degrees ± a degrees), and a is included in a range from 5 degrees to 30 degrees. Among these, it is more preferable that the winding angle θ be adjusted in the following order.

- The winding angle θ is within a range of (- 170 degrees ± 30 degrees), or (+ 10 degrees ± 30 degrees).

- The winding angle θ is within a range of (- 170 degrees ± 25 degrees), or (+ 10 degrees ± 25 degrees).

- The winding angle θ is within a range of (- 170 degrees ± 20 degrees), or (+ 10 degrees ± 20 degrees).

- The winding angle θ is within a range of (- 170 degrees ± 15 degrees), or (+ 10 degrees ± 15 degrees).

- The winding angle θ is within a range of (- 170 degrees ± 10 degrees), or (+ 10 degrees ± 10 degrees).

- The winding angle θ is within a range of (- 170 degrees ± 5 degrees), or (+ 10 degrees ± 5 degrees).

[0151] Consequently, 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 carried out in the context of the first embodiment.

In addition, in the first embodiment, a hairspring 30 with a terminal curve is adopted, but a hairspring without end curve 80 illustrated in FIG. 6, or a hairspring with overwinding 90 illustrated in FIG. 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 produced in the context of the first embodiment.

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

CH 715 096 A2 [0154] A portion of the outermost spring part 32 of the main hairspring body 31 is raised, the hairspring 90 in this case extends in a direction opposite to the starting point of the elevation in the radial direction, and then is fixed (maintained) to the peak 40. In addition, in the example illustrated, the peak 40 fixes (maintains) the outer end 31 b of the hairspring 90, so that the winding angle θ is - 167 degrees.

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 adjusting the rotation of the peak 40.

(Second embodiment) [0157] 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.

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

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

In addition, in FIG. 20, part of the configuration components of the regulating member 110 is omitted to facilitate understanding of the drawings.

Similarly to the first embodiment, the piton holder 130 includes a link ring 51 and a piton arm 52 having a first piton arm 53 and a second piton arm 54, and is capable of rotating by relative way around the first axis O1 relative to the balance 20.

The first piton arm 53 and the second piton arm 54 can be elastically deformed in the circumferential direction, and the ends of their tips are compressed in advance to approach each other. Consequently, a shaft body 41 of the piton 120 can be sandwiched between the first piton arm 53 and the second piton arm 54.

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

Similar to the first embodiment, the peg 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 peg arm 53, and a second contact surface 41b which is in flat contact with the second sandwiched surface 54a of the second arm of 53 pin 54 so that they face each other in the circumferential direction.

[0165] Consequently, the first piton arm 53 and the second piton arm 54 sandwich the piton 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 piton 120 is movably supported in the radial direction between the first piton arm 53 and the second piton arm 54 in a state where all rotational movement is restricted.

In addition, in a case where the peg 120 is moved in the radial direction for example, an adjustment tool is engaged with the head 42, and then the peg 120 is able to move so as to resist encountering a clamping force between the first piton arm 53 and the second piton arm 54.

In addition, in this embodiment, the support 130 releasably supports the stud 120 while the winding angle θ is - 77 degrees.

In the following, a case will be described where the isochronous adjustment of the balance spring 30 is carried out using the regulating member 110 produced in accordance with the embodiment described above.

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

CH 715 096 A2 [0171] In such an initial state, the winding angle θ is fixed at - 77 degrees, and the adjustment in translation to move the stud 120 in the radial direction is carried out. Therefore, the isochronism can be changed and the isochronous adjustment can be performed.

In particular, in the main hairspring body 31, in the case where the winding angle Ose 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 an adjustment in rotation, so that the isochronism obtained by the adjustment operation via a movement in translation in the radial direction can be modified to handle more sensitive than that performed by a rotation adjustment operation. Consequently, in a state where it is difficult to affect by an adjustment in rotation, the isochronism can be modified by an amount resulting from the adjustment in translation in the radial direction.

In addition, as illustrated in FIGS. 14 and 15, since the winding angle θ is - 77 degrees, in the main 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 isochronism variation resulting from rotation adjustment is minimized. Consequently, the isochronism is modified with great sensitivity by an adjustment in translation, but for an adjustment in rotation, it becomes insensitive it is thus difficult to modify it through this.

Therefore, in a state where the winding angle θ is - 77 degrees, the translation adjustment is made, so 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.

In particular, similarly to the case of the rotation adjustment operation in the context of the first embodiment, the variation in isochronism resulting from a rotation adjustment of the stud 40 is substantially proportional to the level of adjustment via a movement in translation. Consequently, the isochronism can be modified by an amount corresponding to the adjustment operation via a translational movement of the peak 40 and the isochronous adjustment can be carried out quantitatively.

In the above, it will be understood that also in the case of the embodiment now 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.

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

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) [0180] 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 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).

Among these, it is preferable that the winding angle θ is in a range of (- 80 degrees ± a degrees), or (+ 100 degrees ± a degrees), and a is in a range of 5 degrees to 30 degrees. Among these, it is even more preferable that the winding angle θ be adjusted in the following order:

- The winding angle θ is within a range of (- 80 degrees ± 30 degrees), or (+ 100 degrees ± 30 degrees).

- The winding angle θ is within a range of (- 80 degrees ± 25 degrees), or (+ 100 degrees ± 25 degrees).

- The winding angle θ is within a range of (- 80 degrees ± 20 degrees), or (+ 100 degrees ± 20 degrees).

- The winding angle θ is within a range of (- 80 degrees ± 15 degrees), or (+ 100 degrees ± 15 degrees).

- The winding angle θ is within a range of (- 80 degrees ± 10 degrees), or (+ 100 degrees ± 10 degrees).

- The winding angle θ is within a range of (- 80 degrees ± 5 degrees), or (+ 100 degrees ± 5 degrees).

Therefore, the most preferable is that the winding angle θ is 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 in the context of the second embodiment.

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

[0184] (Third embodiment)

CH 715 096 A2 [0185] 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.

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

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

[0188] In addition, in FIG. 22, part of the configuration components of the regulating member 140 is omitted to facilitate understanding of the drawings.

As illustrated in FIGS. 22 and 23, the pin holder 160 includes a link ring 51, a first arm 161 extending outward in the radial direction from the link ring 51, and a second arm 162 formed in one piece with arm 161 and extending in the circumferential direction.

The second arm 162 is formed integrally 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 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.

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 in the second arm 162, and is open towards the outside in the radial direction . The first guide groove 163 has a linear shape and extends along the radial direction.

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

The stud 150 includes 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 with respect 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 FIGS. 22 and 23, the inner leg 43 and the outer leg 44 are hidden by the piton holder 160.

The shaft body 41 has a cylindrical shape whose outer diameter is smaller than the width of the first guide groove 163. The flange 151 has a circular shape according to a plan view whose outer diameter is larger than the width of the first guide groove 163. Consequently, the peg 150 is arranged so that it can move in the radial direction in the first guide groove 163 in a state where the flange 151 covers the second arm 162.

As illustrated in FIGS. 22 and 24, the piton 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 piton cover 170 is formed in such a way 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.

Part of the piton cover 170, which is located centrally in the circumferential direction, has a second slot-shaped guide groove 171 which penetrates vertically into the piton 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 disposed above the first guide groove 163. An upper end of the shaft body 41 of the stud 150 is inserted in the second guide groove 171.

A lower surface of the piton cover 170 is formed so as to have a recess 172 extending along the radial direction at a part located in the center in the circumferential direction. The width of the recess 172 arranged to be greater than the diameter of the flange 151 of the piton 150. Consequently, the piton 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 less deep than the thickness of the flange 151. Consequently, the eyelet cover 170 covers the upper surface of the second arm portion 162 in a state where the flange 151 is pressed against the second arm 162.

In addition, the peripheral ends of the piton 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 piton cover 170 is combined with the second arm 162 to form a single piece

CH 715 096 A2 holding, 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) [0200] According to the regulating member 140 of the embodiment described above, since the peg 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.

In addition, in the case of this embodiment, the clamping of the flange 151 can be released by loosening or removing the fixing screws 173, so that the peg 150 can be moved in the radial direction along the first guide groove 163 and the second guide groove 171. After the adjustment in translation 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 piton cover 170. Consequently, the piton 150 can be more stably fixed in a given position after the translational adjustment operation.

[0202] Consequently, it is possible to effectively restrict any position shift caused by, for example, an unintentional movement of the position of the peg 150 in the radial direction.

[0203] 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 can also be implemented in various other forms, and various omissions, substitutions and changes can be made without departing from the scope of the invention. The embodiments and their examples of modifications include, for example, those which are easily presumed by those skilled in the art who are competent in the field, modifications resulting in substantially identical characteristics, modifications in an equivalent field of application, etc.

[0204] For example, in each of the embodiments described above, the case where the internal end of the main balance spring body is fixed to the balance shaft of the balance wheel has been described as an example, but the present invention is not limited to such a case. For example, the inner end of the main hairspring body can be attached to the first component (that is, the timepiece component other than the pendulum) rotating around the axis.

Claims (9)

claims 1. Spiral (30) comprising: a main hairspring body (31) of which an internal end (31a) is fixed to a first element (20) rotating about an axis (O1) and an external end (31b) is held by a second element (40), and which has a spiral shape comprising a predetermined number of turns in a plane intersecting 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), and a second virtual line (L2) connecting a position holding the main hairspring body retained by the second element (40) and the axis (O2) defines a winding angle (Θ) in the axial direction, the main hairspring body (31) is retained by the second element (40) so that the outer end (31b) can rotate in the plane when the angle d winding (Θ) is located in a first predetermined angular range (E1), or is retained by the second element (40) so that the outer end (31 b) moves 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 main hairspring body (31) is further constituted so that when the winding angle (Θ) 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 generated by a movement in the radial direction of the outer end (31b), and when the winding angle (Θ) is within the second angle range (E2), an isochronous variation generated by the movement in the radial direction of the outer end (31 b) is greater than an isoc variation hrone generated by a rotation in the plane of the outer end (31b). 2. hairspring (30) according to claim 1, in which, by defining a displacement of the second element (40) in the direction of winding of the main hairspring body (31) as a positive direction of winding angle ( Θ), and a direction opposite to it as a negative winding angle direction (Θ), based on a case where the winding angle (Θ) is zero, the first range of angle (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 at - 35 degrees ± 5 degrees), or (+ 55 degrees ± 5 degrees at + 145 degrees ± 5 degrees). 3. Spiral (30) 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 ± a degrees) , or (+ 10 degrees ± a degrees), CH 715 096 A2 the second angle range (E2) being an angle range in which the winding angle (Θ) is included in a range of (- 80 degrees ± a degrees), or (+ 100 degrees ± a degrees), and a being an angle between 5 degrees to 30 degrees. 4. Spiral (30) 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. hairspring (30) according to one of claims 1 to 4, in which the first element (20) is a pendulum, and in which the internal end (31a) of the main hairspring body (31) is fixed to a pendulum shaft (21) in the pendulum. 6. Spiral according to claim 5, wherein the outer end (31b) rotates in the plane, or the outer end moves in a radial direction of the balance shaft (21), so that the main body hairspring (31) can vary isochronously along a curve comprising an extreme value included in a range where the amplitude of the pendulum is from 200 degrees to 250 degrees. 7. Regulating body including: the hairspring (30) according to claim 5 or 6; the pendulum (20); the second element (40); and a support element (50) which is combined with the balance (20) so as to be rotatable relative thereto about the axis (O1), and movably support the second element (40), in which the support element (50) maintains the second element (20) in the plane with a degree of freedom in rotation, or movably supports the second element (40) in a radial direction relative to the balance shaft ( 21). 8. Timepiece movement (10) comprising: the regulating member according to claim 7. 9. Timepiece (1) comprising: the timepiece movement (10) according to claim 8. CH 715 096 A2