CN113267984A - Escapement speed regulator, movement for timepiece, and timepiece - Google Patents

Abstract

The invention provides an escape speed regulator with excellent duration, a clock movement and a clock. The escape governor (13) is provided with: a balance spring; a balance-spring mechanism (40) that rotates reciprocally in a first rotational direction (M1) and a second rotational direction (M2) that are opposite to each other about a first axis (O1) as the balance spring expands and contracts; an escapement (14) having an escape fork (70) that rotates about a second axis (O2) and an escape wheel (60) that can be engaged with and disengaged from the escape fork (70); and a rocker (45) that transmits torque from the escapement (14) to the balance spring mechanism (40). The escapement (14) applies torque to the balance spring mechanism (40) by two times of impact in one cycle of the balance spring mechanism (40). When the difference obtained by subtracting the torque of the balance spring from the torque applied to the balance spring mechanism (40) by the escapement (14) is defined as the balance spring mechanism torque balance, the balance (45) is formed so that the balance spring mechanism torque balance at the end of each impact of the escapement (14) becomes equal.

Description

Escapement speed regulator, movement for timepiece, and timepiece

Technical Field

The invention relates to an escape speed regulator, a movement for a timepiece, and a timepiece.

Background

In general, a mechanical timepiece includes an escapement that controls a train wheel with a constant vibration by regular reciprocating rotation of a balance spring mechanism and transmits power for the reciprocating rotation to the balance spring mechanism. Such an escapement has been developed while repeating improvement and the like, and various types of escapements have been proposed.

As an escapement occupying the mainstream of a mechanical timepiece, a crab claw/lever escapement (swiss lever escapement) is well known. The escapement mainly comprises: an escape wheel; a swing seat provided in the balance spring mechanism; and a pallet, which is rotatable by the reciprocal rotation of the balance spring mechanism, and has an entry pallet stone and an exit pallet stone which can be engaged with and disengaged from the tooth portion of the escape wheel. The entry pallet stone and the exit pallet stone can be alternately engaged and disengaged with respect to the tooth portion of the escape wheel in accordance with the rotation of the escape pallet.

According to the crab claw/lever escapement, since the entering pallet stone and the exiting pallet stone are alternately engaged and disengaged with respect to the tooth portion of the escape wheel in accordance with the rotation of the escape wheel, the rotation of the escape wheel can be controlled, and the torque transmitted to the escape wheel can be indirectly transmitted to the balance spring mechanism via the escape wheel by the impulse when the tooth portion of the escape wheel is in contact with the entering pallet stone and the impulse when the tooth portion of the escape wheel is in contact with the exiting pallet stone, and the motive power can be supplemented to the balance spring mechanism. However, it is generally known that the crab claw/lever escapement has low transmission efficiency of torque transmitted from the escape wheel side to the balance spring mechanism side via the pallet fork (escapement efficiency), and there is room for improvement.

Thus, the following crab claw/lever escapements are known: in order to improve the torque transmission efficiency, for example, the rotational operating angle of the escape wheel when the tooth of the escape wheel contacts the entry pallet and the rotational operating angle of the escape wheel when the tooth of the escape wheel contacts the exit pallet are not matched (see, for example, patent document 1 below). In this case, the supply balance change of the transmission amount of the torque transmitted from the entry pallet stone to the balance spring mechanism via the pallet and the transmission amount of the torque transmitted from the exit pallet stone to the balance spring mechanism via the pallet can be made to be an optimum balance, and the torque transmission efficiency can be improved.

In addition, as another example, the following crab claw/lever escapement is known: for example, an escape wheel having a double-layer structure in which a first escape wheel and a second escape wheel are superposed on the same axis is provided, and an entry pallet is brought into contact with a tooth portion of the first escape wheel and an exit pallet is brought into contact with a tooth portion of the second escape wheel (see, for example, patent documents 2 and 3 below). In this case, since the combinations of the entry pallet stone and the first escape pinion, and the exit pallet stone and the second escape pinion can be individually designed, the rotational operating angle of the escape wheel when the tooth portion of the first escape pinion contacts the entry pallet stone and the rotational operating angle of the escape wheel when the tooth portion of the second escape pinion contacts the exit pallet stone can be made different from each other, and the torque transmission efficiency can be improved.

As a further example, the following crab claw/lever escapements are known: for example, an escape wheel having a first escape tooth and a second escape tooth formed offset in the thickness direction is provided, and an entry pallet is brought into contact with the first escape tooth and an exit pallet is brought into contact with the second escape tooth (see, for example, patent document 4 below). In this case, since the first escape tooth and the second escape tooth can be individually designed, the rotational operating angle of the escape wheel when the first escape tooth is in contact with the entry pallet stone and the rotational operating angle of the escape wheel when the second escape tooth is in contact with the exit pallet stone can be made different from each other, and the torque transmission efficiency can be improved.

However, all of the above-described crab claw/lever escapements are so-called indirect impulse type escapements that transmit torque from the escape wheel to the balance spring mechanism via the pallet fork, and therefore the torque transmission efficiency is insufficient, and there is still room for improvement.

As an escapement having higher torque transmission efficiency than the crab claw/lever escapement, a so-called semi-indirect-semi-direct impulse type escapement is known, which alternately performs indirect torque transmission via a pallet fork and direct torque transmission not via the pallet fork, and simultaneously transmits torque transmitted to an escape wheel to a balance spring mechanism (for example, see patent documents 5 and 6 below).

A semi-indirect-semi-direct impulse type escapement includes an escape fork having a first impulse pallet and a second impulse pallet fixed to a balance spring mechanism. The first and second impulse pallet-stones can be alternately in contact with respect to the pallet gear as the pallet rotates. According to the escapement configured as described above, since the first impulse pallet stone is in contact with the pallet gear in accordance with the rotation of the pallet, the torque transmitted to the escape wheel can be indirectly transmitted to the balance spring via the pallet by the impulse when the pallet gear is in contact with the first impulse pallet stone, and the motive power can be supplemented to the balance spring. Further, since the second impulse pallet comes into contact with the tooth tip of the pallet gear with the rotation of the balance spring, the torque transmitted to the escape wheel can be directly transmitted to the balance spring by the impulse when the pallet gear comes into contact with the second impulse pallet, and the power can be supplemented to the balance spring. Therefore, the semi-indirect-semi-direct impulse type escapement is an escapement whose torque transmission efficiency (escapement efficiency) is better than the crab claw/lever escapement.

Prior art documents

Patent document

Patent document 1: swiss patent specification No. 570644

Patent document 2: japanese patent No. 4894051

Patent document 3: european patent application publication No. 1914605

Patent document 4: japanese patent laid-open publication No. 2018-48958

Patent document 5: european patent application publication No. 0018796

Patent document 6: japanese patent No. 6558761.

Disclosure of Invention

Problems to be solved by the invention

However, in the conventional escapement, the torque transmitted from the escapement to the balance spring mechanism becomes uneven due to the difference in the impulse. Therefore, if the balance spring of the power source is loosened and the torque transmitted to the escape wheel decreases, the torque applied from the escapement to the balance spring mechanism at the end of the impact of any one impact is lower than the torque applied to the balance spring mechanism at the end of the impact of the other impact. If the torque applied to the balance spring mechanism from the escapement at the end of the impact is lower than the torque acting on the balance spring mechanism, the operation of the escapement is stopped until the end of the impact. Therefore, in the conventional escapement, there is room for improvement in that the operation of the escapement is suppressed from being stopped early due to the decrease in power of the power source, and the duration of the operation of the escapement is extended.

Thus, the invention provides an escape speed governor having excellent duration, a timepiece movement, and a timepiece.

Means for solving the problems

The escape speed regulator of the present invention includes: a balance spring; a balance spring mechanism that reciprocates in a first rotational direction and a second rotational direction opposite to each other about a first axis as a center in accordance with expansion and contraction of the balance spring; an escapement including an escape fork that rotates about a second axis and an escape wheel that can be engaged with and disengaged from the escape fork; and a torque transmission member that transmits torque from the escapement to the balance spring, wherein the escapement applies torque to the balance spring by at least two impacts in one cycle of the balance spring, and the torque transmission member is formed so that the balance spring torque balance at the end of the impact of each impact of the escapement becomes equal when a difference obtained by subtracting the torque of the balance spring from the torque applied to the balance spring by the escapement is defined as a balance spring torque balance.

According to the present invention, even if the torque applied to the balance spring mechanism from the escapement becomes smaller as the torque transmitted from the power source to the escape wheel decreases, the torque at the end of the impact can be suppressed from becoming insufficient earlier in any impact of the escapement than in other impacts. Therefore, it is possible to suppress the state in which the impact is not completed earlier than the other impacts in any of the impacts of the escapement. Therefore, the duration of the escape governor can be increased.

In the escape speed regulator, the torque transmission member may rotate integrally with the balance spring mechanism.

According to the present invention, the torque from the escapement to the balance spring can be transmitted more efficiently as compared with a configuration including the engagement of gears and the like on the transmission path of the torque from the torque transmission member to the balance spring.

In the escape speed regulator, the escape wheel may contact the torque transmission member to apply torque to the balance spring when the balance spring rotates in the first rotational direction, and may contact the pallet to apply torque to the balance spring when the balance spring rotates in the second rotational direction.

According to the present invention, since the actuator can be configured as a so-called semi-indirect-semi-direct impulse type, the actuator can be an escapement governor having an excellent torque transmission efficiency as compared with a case where the actuator is configured as a so-called indirect impulse type.

In the escape speed regulator, the escape wheel may contact the pallet to apply a torque to the balance spring when the balance spring rotates in the first rotational direction and when the balance spring rotates in the second rotational direction.

According to the present invention, the duration can be improved in an escape speed regulator including a so-called indirect impulse type escapement such as a crab claw/lever escapement that transmits torque from the escape wheel to the balance spring mechanism only via the pallet.

In the escape speed regulator, the torque transmission member may include a balance weight that is engageable with and disengageable from the pallet fork, and a center of the balance weight may be disposed at a position offset around the first axis line with respect to an imaginary straight line passing through the first axis line and the second axis line in a stationary state in which the torque of the balance spring does not act on the balance spring mechanism when viewed from the axial direction of the first axis line.

In a configuration in which the center of the balance drill is arranged on a virtual straight line passing through the first axis and the second axis in a stationary state when viewed from the axial direction of the first axis, a difference in torque balance at the end of the impact occurs due to a difference in the rotational direction of the balance spring (difference in the impact). According to the present invention, the torque transmission member can be disposed so that the balance spring torque balance at the end of the impact of each impact of the escapement becomes uniform. Therefore, the above-described effects can be obtained.

In the escape governor, the center of the pendulum is disposed at a position that is offset from the imaginary straight line by more than 0 ° and 15 ° or less around the first axis in the stationary state when viewed from the axial direction.

Here, the position of the torque transmission member in the case where the balance spring mechanism is in the stationary state is defined as a stationary position. According to the present invention, the escape speed regulator can be formed such that the torque transmission member passes through the rest position in the impact after the stop of the escape wheel is released. Thus, in the case where the torque transmitted from the power source to the escape wheel decreases, the escape wheel stops at the position in the impact, and thus the restartability at the time of increasing the torque transmitted to the escape wheel can be ensured.

The escapement governor described above may further include an adjustment device that adjusts a position of the torque transmission member around the first axis.

According to the present invention, the torque transmission member can be disposed so that the balance spring torque balance at the end of the impact of each impact of the escapement becomes uniform, and therefore the above-described operational effects can be obtained.

In the escape speed regulator, the torque transmission member may be fixedly disposed with respect to the balance spring mechanism, and the adjustment device may include: a support member that rotatably supports the balance spring mechanism; an outer pile fixed to an outer peripheral portion of the hairspring; and an outer pile clamp plate which is fitted to a circumferential surface of the support member extending around the first axis and supports the outer pile.

According to the present invention, when the stud plate is assembled to the support member, the positions of the balance spring mechanism and the torque transmission member about the first axis with respect to the support member can be adjusted by adjusting the positions about the first axis with respect to the support member.

In the escape speed regulator, the torque transmission member may be fixedly disposed with respect to the balance spring mechanism, and the adjustment device may include: a shaft portion of the balance spring mechanism; and a collet fitted to the shaft portion and fixed to an inner end portion of the hairspring.

According to the present invention, when the collet is assembled to the shaft portion of the balance spring mechanism, the positions of the balance spring mechanism and the torque transmission member about the first axis line with respect to the support member can be adjusted by adjusting the positions about the first axis line with respect to the shaft portion.

In the escape speed regulator, the balance spring mechanism may include a shaft portion, the torque transmission member may include a mounting portion mounted on the shaft portion of the balance spring mechanism, and the adjustment device may include: the shaft portion of the balance spring mechanism; and the aforementioned fitting portion.

According to the present invention, when the mounting portion of the torque transmission member is assembled to the shaft portion of the balance spring mechanism, the position of the torque transmission member around the first axis line with respect to the shaft portion, that is, the position of the torque transmission member around the first axis line with respect to the support member can be adjusted by adjusting the position around the first axis line with respect to the shaft portion.

The timepiece movement of the present invention includes the escape speed regulator. The timepiece of the present invention includes the timepiece movement described above.

According to the present invention, a timepiece movement and a timepiece having a long duration due to the presence of an escape speed regulator having an excellent duration can be provided.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the present invention, an escape speed governor, a timepiece movement, and a timepiece having excellent duration can be provided.

Drawings

Fig. 1 is a plan view showing a timepiece according to an embodiment.

Fig. 2 is a plan view of the movement according to the embodiment as viewed from the front side.

Fig. 3 is a perspective view of the escape governor according to the embodiment as viewed from the front side.

Fig. 4 is a plan view of the governor according to the embodiment as viewed from the front side.

Fig. 5 is a cross-sectional view on line V-V of fig. 4.

Fig. 6 is a perspective view of the balance spring mechanism and the roller according to the embodiment as viewed from the front side.

Fig. 7 is a perspective view of the escape governor according to the embodiment as viewed from the back side.

Fig. 8 is a plan view of the actuator and the rocker according to the embodiment as viewed from the front side.

Fig. 9 is a plan view illustrating the operation of the escape speed governor according to the embodiment.

Fig. 10 is a plan view illustrating the operation of the escape speed governor according to the embodiment.

Fig. 11 is a plan view illustrating the operation of the escape speed governor according to the embodiment.

Fig. 12 is a plan view illustrating the operation of the escape speed governor according to the embodiment.

Fig. 13 is a plan view illustrating the operation of the escape speed governor according to the embodiment.

Fig. 14 is a plan view illustrating the operation of the escape speed governor according to the embodiment.

Fig. 15 is a plan view illustrating the operation of the escape speed governor according to the embodiment.

Fig. 16 is a plan view illustrating the operation of the escape speed governor according to the embodiment.

Fig. 17 is a plan view illustrating the operation of the escape speed governor according to the embodiment.

Fig. 18 is a plan view illustrating the operation of the escape speed governor according to the embodiment.

Fig. 19 is a plan view illustrating the operation of the escape speed governor according to the embodiment.

Fig. 20 is a plan view illustrating the operation of the escape speed governor according to the embodiment.

Fig. 21 is a graph showing the balance spring torque balance at the end of the impulse of each impulse of the escapement.

Fig. 22 is a graph showing the torque acting on the balance spring mechanism at the time of direct impact in the escape speed regulator according to the embodiment.

Fig. 23 is a graph showing the torque acting on the balance spring mechanism at the time of the indirect impact in the escape speed regulator according to the embodiment.

Fig. 24 is a graph showing the torque acting on the balance spring mechanism at the time of direct impact in the escape governor according to the comparative method.

Fig. 25 is a graph showing the torque acting on the balance spring mechanism at the time of the indirect impact in the escape governor according to the comparative method.

Fig. 26 is a graph showing the torque acting on the balance spring mechanism at the time of direct impact in the escape speed regulator according to the modification of the embodiment.

Fig. 27 is a graph showing the torque acting on the balance spring mechanism at the time of the indirect impact in the escape speed governor according to the modification of the embodiment.

Detailed Description

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

In general, a mechanical body including a driving portion of a timepiece is referred to as a "movement". The state in which the dial, the hand, and the case are mounted on the movement and the movement is completed is referred to as a "completed product" of the timepiece. Of the two sides of the main plate constituting the base plate of the timepiece, the side on which the glass of the timepiece case is present (i.e., the side on which the dial is present) is referred to as the "back side" of the movement. In addition, one of the two sides of the main plate on which the case back of the watch case is present (i.e., the side opposite to the dial) is referred to as the "watch side" of the movement. In the present embodiment, the direction from the dial toward the case back is defined as the upper side, and the opposite side is defined as the lower side.

Fig. 1 is a plan view showing a timepiece according to an embodiment. As shown in fig. 1, the finished timepiece 1 of the present embodiment includes, in a timepiece case including a glass 2 and a case back cover not shown: a movement (movement for a timepiece) 10; a dial 3 having scales representing at least information related to a timepiece; and hands including an hour hand 5, a minute hand 6, and a second hand 7.

Fig. 2 is a plan view of the movement according to the embodiment as viewed from the front side. In fig. 2, a part of the components constituting the movement 10 is omitted for easy viewing of the drawing. As shown in fig. 2, the movement 10 has a main plate 11 constituting a base plate. The movement 10 includes a front wheel train 12 and an escape governor 13 on the front side of a main plate 11.

The front wheel train 12 mainly includes a barrel wheel 20, an idler gear 21, a second wheel 22, a third wheel 23, a fourth wheel 24, and an escape intermediate wheel 25. The barrel wheel 20 is pivotally supported between the main plate 11 and a barrel plate (not shown), and houses a spring (power source) therein. The spring is wound up by rotation of stem 27 coupled to stem 26 shown in fig. 1.

Idler gear 21, second wheel 22, third wheel 23, fourth wheel 24, and escape intermediate wheel 25 are pivotally supported between main plate 11 and a train wheel bridge not shown. If the barrel wheel 20 rotates due to the elastic restoring force of the wound power spring, these idler gears 21, second wheel 22, third wheel 23, fourth wheel 24, and escape intermediate wheel 25 rotate based on the rotation.

That is, the idler gear 21 meshes with the barrel wheel 20 and rotates based on the rotation of the barrel wheel 20. The second wheel 22 meshes with the idler gear 21 and rotates based on the rotation of the idler gear 21. Third wheel 23 meshes with second wheel 22 and rotates based on the rotation of second wheel 22. The fourth wheel 24 is engaged with the third wheel 23 and rotates based on the rotation of the third wheel 23. The second hand 7 shown in fig. 1 is attached to the fourth wheel 24, and the second hand 7 displays "second" based on the rotation of the fourth wheel 24. The second hand 7 rotates one revolution in one minute at a rotational speed regulated by the escape governor 13.

If the fourth wheel 24 rotates, a minute wheel not shown rotates based on the rotation. In the minute wheel, the minute hand 6 shown in fig. 1 is attached, and the minute hand 6 displays "minute" by the rotation of the minute wheel. The minute hand 6 rotates one revolution for one hour at a rotational speed regulated by the escape governor 13.

If the minute wheel rotates, the not-shown straddle wheel rotates based on the rotation, and further, the not-shown hour wheel rotates based on the rotation of the straddle wheel. An hour hand 5 shown in fig. 1 is attached to the hour wheel, and the hour hand 5 displays "hour" by rotation of the hour wheel. The hour hand 5 rotates one revolution for twelve hours at a rotational speed regulated by an escape governor 13.

The escape intermediate wheel 25 meshes with the fourth wheel 24 and rotates based on the rotation of the fourth wheel 24. The escape intermediate wheel 25 meshes with an escape pinion 61 (see fig. 3) of an escape wheel 60 described later.

Fig. 3 is a perspective view of the escape governor according to the embodiment as viewed from the front side. In fig. 3, a balance 42 to be described later is shown in phantom lines for easy viewing of the drawing, and a part of the balance 42 is not shown. As shown in fig. 2 and 3, the escape governor 13 includes: an escapement 14 that controls rotation of the wheel train 12 on the meter side; a speed regulator 15 that regulates the speed of the actuator 14; and a rocker 45 (torque transmission member) that transmits torque from the escapement 14 to the balance spring mechanism 40 of the speed regulator 15.

Fig. 4 is a plan view of the governor according to the embodiment as viewed from the front side. Fig. 5 is a cross-sectional view on line V-V of fig. 4. As shown in fig. 4 and 5, the governor 15 includes: a balance spring 30; an outer pile clamp unit 33 which holds the outer end portion of balance spring 30; a balance-spring mechanism 40 that reciprocates about a first axis O1 in accordance with the expansion and contraction of the balance spring 30; and a balance spring bridge 16 (support member) fixed to the main plate 11 (see fig. 2) and rotatably supporting the balance spring mechanism 40. The balance spring 30 is wound in a spiral shape, and a collet 31 is fixed to an inner end portion and an outer collet 34 is fixed to an outer end portion 30 a. The outer pile 34 may be fixed to the outer periphery of the balance spring 30.

The outer pile clamp unit 33 includes an outer pile 34 and an outer pile clamp plate 35 that supports the outer pile 34. The outer pile clamp plate 35 is fixedly arranged with respect to the main plate 11. Specifically, the collet plate 35 is supported by the balance spring mechanism plate 16. The collet 35 is fitted to an outer peripheral surface 16a of a shaft portion extending around the first axis O1 in the balance spring bridge 16 via an annular collet seat 36. Further, the outer pile clamp 35 may be fitted to the outer peripheral surface or the inner peripheral surface of the balance spring bridge 16 extending around the first axis O1 without passing through the outer pile clamp seat 36. The outer pile clamping plate 35 has an outer pile arm 37 holding the outer pile 34. The outer leg 37 has a slit 37a formed therethrough. A cylindrical outer pile pusher 38 is fitted into the slit 37 a.

The outer pile 34 is inserted into the inner side of the outer pile pusher 38, and is stably held by the outer pile pusher 38 in a state where it is prevented from falling off by the outer pile screw 39. Stud 34 holds the outer end of balance spring 30 by, for example, gluing or riveting. Thereby, the outer end of the balance spring 30 is fixedly disposed with respect to the balance spring bridge 16 and the main plate 11.

The balance spring mechanism 40 includes a balance shaft 41 (shaft portion) and a balance 42. The balance spring mechanism 40 is pivotally supported between the main plate 11 and the balance spring bridge 16. The balance-spring mechanism 40 reciprocates (rotates forward and backward) around the first axis O1 at a constant amplitude (swing angle) according to the output torque of the barrel wheel 20, using the balance spring 30 as a power source.

Specifically, as shown in fig. 4, the balance spring mechanism 40 reciprocally rotates in the first rotation direction M1 and the second rotation direction M2 which are opposite to each other about the first axis O1. In the present embodiment, a direction in which balance spring mechanism 40 rotates clockwise is referred to as a first rotation direction M1 and a direction in which the balance spring mechanism rotates counterclockwise is referred to as a second rotation direction M2 with respect to first axis O1 as a center in a plan view seen from the front side of movement 10.

As shown in fig. 5, the balance staff 41 is pivotally supported by the main plate 11 and the balance spring bridge 16 at both ends in the axial direction. At the pendulum shaft 41, the collet 31 is fitted. Thereby, the inner end of balance spring 30 is fixedly disposed with respect to balance spring mechanism 40. The collet 31 is fitted to an outer peripheral surface 41a of the swing shaft 41 extending about the first axis O1. A balance 42 is fixed to the balance shaft 41. The balance 42 is fitted around the balance shaft 41 below the collet 31. The shape of the balance 42 is not limited to the illustrated example, and may be freely changed.

As shown in fig. 3, a small flange 43 is formed below the outer fitting portion of the balance 42 in the balance shaft 41. The small flange 43 is formed in a cylindrical shape so that the rotation locus thereof is smaller in diameter than the wobble seat 45. A crescent portion (ツキガタ)43a (see also fig. 6) recessed in a curved shape inward in the radial direction is formed in a portion of the small flange 43 corresponding to the below-described pendulum drill 50 in the radial direction. The crescent 43a functions as a relief portion that prevents a prong pin 82, which will be described later, from coming into contact with the small flange 43 when a pallet box (アンクルハコ)81 (see fig. 8), which will be described later, engages with the pendulum stone 50. In addition, the portion other than the crescent portion 43a in the outer peripheral surface of the small flange 43 can be brought into sliding contact with the clevis nail 82.

Fig. 6 is a perspective view of the balance spring mechanism and the roller according to the embodiment as viewed from the front side. In fig. 6, the balance 42 is shown in phantom lines for ease of viewing the drawing. As shown in fig. 6, the rocker 45 is provided coaxially and integrally rotatably with the balance spring mechanism 40. The pendulum base 45 includes a pendulum base body 46 (mounting portion) fixed to the pendulum shaft 41, and a pendulum drill 50 and a contact pallet 55 fixed to the pendulum base body 46.

The pendulum base 46 is assembled to the pendulum shaft 41. The pendulum seat body 46 abuts below the small flange 43 of the pendulum shaft 41. The pendulum body 46 is disposed at a height corresponding to the escape wheel 60. The pendulum base 46 is formed of a material having a crystal orientation, such as a metal material or single crystal silicon. Examples of the method of manufacturing the pendulum base 46 include electroforming, LIGA process using optical techniques such as photolithography, DRIE, and metal powder injection molding (MIM). However, the present invention is not limited to this, and the pendulum base 46 may be formed by another method.

The swing seat body 46 is formed with a through hole 47 and a slit 48 that penetrate vertically, and the slit 48 is formed in a U shape so as to extend in the radial direction and open outward in the radial direction. The through hole 47 is formed in a semicircular shape having a flat surface on the outer side in the radial direction and bulging in an arc on the inner side in the radial direction, as viewed from the axial direction of the first axis O1.

The pendulum drill 50 is press-fitted into the through hole 47. The pendulum drill 50 is formed in a semicircular shape in plan view having a flat surface 51 on the outer side in the radial direction and an arcuate surface 52 on the inner side in the radial direction, corresponding to the shape of the through hole 47. The pendulum drill 50 is formed of an artificial gem such as ruby. The pendulum drill 50 is formed to extend more upward than the pendulum seat body 46. Thereby, the pendulum 50 can be in contact with a pallet fork 70 (see fig. 3) disposed above the escape wheel 60. The balance stone 50 reciprocates about the first axis O1 in synchronization with the balance spring mechanism 40, and is detachably engaged with a pallet fork 81 (see fig. 8) described later on the way.

The contact pallet 55 is inserted into the slit 48 of the pendulum base 46 and fixed thereto by, for example, an adhesive or the like. The contact pallet 55 is formed of an artificial gem such as ruby, like the pendulum diamond 50. The contact pallet 55 is formed in a rectangular plate shape extending in a radial direction with the first axis O1 as a center. The tip end portion of the contact yoke bush 55 projects radially outward beyond the outer peripheral edge of the rocker seat 46. The contact pallet stone 55 can contact an escapement tooth 63 (see fig. 3) of the escape wheel 60, which will be described later, and serves as a pallet stone for transmitting the torque transmitted to the escape wheel 60 to the balance spring mechanism 40.

As shown in fig. 3 and 6, the side surface of the tip end portion of contact pallet 55 facing the second rotation direction M2 is formed flat in the radial direction, and serves as a contact surface 56 with which the operation surface 63a of the escapement tooth 63 can contact (collide). Further, an inclined surface 57 is formed at the tip end portion of the contact yoke bush 55 so as to face the first rotation direction M1 side. The contact shoe 55 is fixed in the slit 48 so as not to protrude upward from the pendulum base 46. This prevents the contact pallet stone 55 and a pallet fork 70, which will be described later, from contacting each other.

The contact pallet 55 repeatedly enters and retreats from a rotational locus R (see fig. 8) of a detent gear 64 described later by the rotation of the balance spring mechanism 40. Thereby, the operation surface 63a of the escapement tooth 63 in the escapement gear 64 can be brought into contact (collision) with the contact surface 56 of the contact pallet 55. The active face 63a of the escapement tooth 63 is in contact with the contact face 56 of the contact pallet 55, so that torque is transmitted from the escape wheel 60 to the contact pallet 55.

Fig. 7 is a perspective view of the escape governor according to the embodiment as viewed from the back side. As shown in fig. 3 and 7, the escapement 14 includes: an escape wheel 60 rotated by torque transmitted from the spring of the barrel wheel 20 via the meter-side gear train 12; and a pallet fork 70 that rotates and stops the escape wheel 60 based on the rotation of the balance spring mechanism 40. Hereinafter, the rotation axis of the pallet fork 70 is referred to as a second axis O2, and the rotation axis of the escape wheel 60 is referred to as a third axis O3.

The escape wheel 60 includes: an escape shaft portion 62 formed with an escape pinion 61 that meshes with the escape intermediate wheel 25 (see fig. 2); and an escape pinion 64 integrally fixed to the escape shaft portion 62 by, for example, press fitting or the like, and having a plurality of escape teeth 63. In the present embodiment, the case where the number of escapement teeth 63 is eight teeth and the number of escapement pinion 61 is ten teeth will be described as an example. However, the number of teeth of the escape tooth 63 and the escape pinion 61 is not limited to this case, and may be appropriately changed.

In the present embodiment, a case will be described in which the escape wheel 60 rotates counterclockwise as viewed from the front side about the third axis O3 by the torque transmitted from the escape intermediate wheel 25 side via the escape pinion 61. The direction of rotation about the third axis O3 in the counterclockwise direction is referred to as the counterclockwise direction M3, and the opposite direction is referred to as the clockwise direction M4. The rotation locus R described by the tooth tip of the escape tooth 63 with the rotation of the escape wheel 60 is simply referred to as the rotation locus R of the escape gear 64 (see fig. 8).

The escape wheel 60 is pivotally supported by the main plate 11 (see fig. 2) and a train wheel bridge (not shown) at both ends in the axial direction of the escape shaft portion 62.

The escape pinion 64 is made of a metal material, a material having a crystal orientation such as single crystal silicon, or the like, for example, as in the pendulum base 46. Examples of the method for manufacturing the escape gear 64 include electroforming, LIGA process using optical techniques such as photolithography, DRIE, and metal powder injection molding (MIM). However, the present invention is not limited to this, and the escape gear 64 may be formed by another manufacturing method.

The escape pinion 64 includes: an annular hub portion 65 having an insertion through hole 65a formed in a central portion thereof, and the escape shaft portion 62 being assembled by press-fitting or the like through the insertion through hole 65 a; and eight spoke portions 66 extending radially outward from the boss portion 65 and arranged at equal intervals in the circumferential direction, and the boss portion 65 and the spoke portions 66 are integrally formed to constitute the escape gear 64.

The spoke portion 66 is formed to taper toward the radially outward side, and is formed such that the tip end portion thereof is slightly curved toward the counterclockwise direction M3. The tip portion of spoke portion 66 functions as escape tooth 63. Thus, the escape wheel 60 of the present embodiment has an escape tooth 63 of eight teeth. The side surface of escapement tooth 63 facing counterclockwise direction M3 is an operating surface 63a which comes into contact with contact pallet 55 and engages with entry pallet 72 and exit pallet 73, which will be described later.

The escape wheel 60 configured as described above is responsible for the following tasks: when the balance spring 40 rotates in the first rotation direction M1, the torque transmitted from the escape intermediate wheel 25 side is directly transmitted to the balance spring 40, and when the balance spring 40 rotates in the second rotation direction M2, the torque transmitted from the quarter wheel 24 side is indirectly transmitted to the balance spring 40 via the pallet fork 70.

The pallet fork 70 controls the rotation of the escape wheel 60, i.e., the start of rotation and the stop of rotation of the escape wheel 60. Pallet 70 has an entry pallet stone 72 and an exit pallet stone 73 which can be engaged with and disengaged from pallet tooth 63. The pallet 70 includes a pallet shaft 75 as a rotation shaft, and a pallet body 78 having two pallet beams 76A and 76B and a detent arm 77.

The escape fork 75 is disposed coaxially with the second axis O2. The pallet shaft 75 is pivotally supported at both ends in the axial direction by the main plate 11 and a pallet bridge not shown.

The escape fork 78 is fixed to the escape fork shaft 75 by press-fitting or the like, for example. The escape fork 78 is formed in a plate shape by, for example, electroforming or MEMS technology, and is arranged above the escape wheel 60 and the rocker 46. An insertion through hole for fixing the pallet shaft 75 is formed in the connecting portion 79 of the two pallet beams 76A and 76B in the pallet body 78. The pallet shaft 75 is fitted into the insertion through hole by press-fitting or the like, and the pallet body 78 and the pallet shaft 75 are integrally fixed.

Fig. 8 is a plan view of the actuator and the rocker according to the embodiment as viewed from the front side. Further, in fig. 8, the prong nails 82 are shown in phantom lines for ease of viewing the drawing. As shown in fig. 8, one pallet beam 76A is formed to extend from the connecting portion 79 to which the pallet shaft 75 is fixed toward the side of the clockwise direction M4 (i.e., toward the side of the rocker 45) opposite to the rotation direction of the escape wheel and pinion 60. The other pallet beam 76B is formed to extend from the connecting portion 79 to which the pallet shaft 75 is fixed toward the counterclockwise direction M3 side as the rotation direction of the escape wheel 60. The arm 77 is formed to extend from a connecting portion 79 to which the escape pinion 75 is fixed toward a direction away from the escape wheel 60.

A pair of dovetails (クワガタ)80 arranged side by side in the circumferential direction of the second axis O2 are provided at the tip end of one pallet fork 76A. The inner side of the dovetail 80 is a pallet fork case 81 which is open toward the small flange 43 side of the balance shaft 41 and which accommodates the balance stone 50 which moves in accordance with the reciprocating rotation of the balance spring mechanism 40 so as to be able to engage and disengage.

A fork pin 82 is attached to the tip end of one pallet fork 76A. The fork pin 82 is fitted into the tip of one pallet beam 76A from above by, for example, press-fitting, and is fixed to the pallet beam 76A. However, the present invention is not limited to this, and the fork pin 82 may be fixed to the distal end portion of the one pallet fork 76A by, for example, an adhesive, caulking, or the like.

The clevis pin 82 is located between the pair of dovetails 80 in a plan view (i.e., located inside the pallet fork 81), and extends so as to slightly protrude toward the small flange 43 side of the balance staff 41 than the dovetails 80. The clevis pin 82 is fixed to be located above the pendulum drill 50 and at the same height as the small flange 43 of the pendulum shaft 41. Further, in a state where the pendulum stone 50 is detached from the pallet fork 81, the tip end portion of the prong nail 82 is opposed to the portion of the outer peripheral surface of the small flange 43 other than the crescent portion 43a in the radial direction with a slight gap therebetween, and is accommodated in the crescent portion 43a in a state where the pendulum stone 50 is engaged with the pallet fork 81.

Further, since the tip of the prong pin 82 faces the outer peripheral surface of the small flange 43 in the radial direction with a slight gap therebetween when the balance stone 50 is detached from the pallet box 81, even if the stoppage of the pallet 70 is released due to the influence of the disturbance, for example, in the free oscillation in which the balance spring mechanism 40 is input, the tip of the prong pin 82 can be brought into contact with the outer peripheral surface of the small flange 43 first. This can suppress displacement of the pallet 70 due to disturbance, and can prevent the pallet 70 from being stopped.

Further, a drill attachment hole 83 for fixing the pallet stone 72 is formed in a portion of one pallet beam 76A on the side of the pallet shaft 75 with respect to the fork pin 82. The drill attachment hole 83 is formed to penetrate the pallet fork 76A vertically. The entry pallet 72 can engage with and disengage from the action surface 63a of the escapement tooth 63 in the escapement gear 64, and serves as a pallet for stopping and releasing the escape wheel 60.

The entry shoe 72 is formed of an artificial gem such as ruby, as in the pendulum drill 50, and is adhesively fixed in the drill attachment hole 83 by, for example, press-fitting or adhesive. The entry pallet stone 72 is formed in a quadrangular prism shape extending downward from the pallet beam 76A, and is fixed so as to have a height equivalent to that of the escape wheel 60. The side surface of the pallet stone 72 facing the clockwise direction M4 opposite to the rotation direction of the escape wheel 60 serves as an engagement surface 72a with which the operation surface 63a of the escape tooth 63 in the escape gear 64 engages.

At the tip end portion of the other pallet fork 76B, a slit 85 for fixing the escape pallet stone 73 is formed. The slit 85 is formed to penetrate the pallet 76B vertically and open toward the escape wheel 60 side. The escape pallet 73 is a pallet for stopping and releasing the escape wheel 60, which can be engaged with and disengaged from the action surface 63a of the escape tooth 63 in the escape gear 64, and serves as a pallet for transmitting the torque transmitted to the escape wheel 60 to the balance spring mechanism 40 via the escape pallet 70.

The ejector pallet 73 is formed of an artificial stone such as ruby, and is fixed by, for example, press-fitting or adhesive bonding in the slit 85, as in the pendulum drill 50. The ejection pallet stone 73 is formed in a rectangular plate shape extending along the slit 85, and is fixed so as to protrude further toward the escape wheel 60 than the escape pallet beam 76B. The escape pallet 73 is formed to extend downward from the pallet beam 76B, and is fixed to have the same height as the escape wheel 60.

An engagement surface 73a and a sliding surface 73b are formed at the tip end of the escape pallet 73 so as to face a clockwise direction M4 opposite to the rotation direction of the escape wheel 60. The engagement surface 73a is formed flat along the slit 85 and can engage with the operation surface 63a of the escapement tooth 63 in the escapement gear 64. The sliding surface 73b is an inclined surface which is located on the escape wheel 60 side with respect to the engaging surface 73a, extends from the slit 85 side toward the escape wheel 60 side in the counterclockwise direction M3 which is the rotation direction of the escape wheel 60, and is formed so that the escape tooth 63 can slide.

Specifically, the escape tooth 63 of the escape wheel 60 slides on the sliding surface 73b after the engagement with the engagement surface 73a is released. The active face 63a of the escapement tooth 63 slides on the sliding face 73b, so that the torque is transmitted from the escape wheel 60 to the exit pallet 73 side.

The pallet fork 70 configured as described above rotates around the second axis O2 based on the rotation of the balance spring mechanism 40 as described above. Specifically, the pallet fork 70 is rotated around the second axis O2 in the direction opposite to the rotation direction of the balance spring mechanism 40 by the balance stone 50 moving with the reciprocating rotation of the balance spring mechanism 40. At this time, the entry pallet stone 72 and the exit pallet stone 73 alternately repeat entry and retreat with respect to the rotation locus R of the escape pinion 64 by the rotation of the pallet 70. Thereby, the operation surface 63a of the escapement tooth 63 in the escapement gear 64 can be engaged with the engaging surface 72a of the entering pallet 72 or the engaging surface 73a of the exiting pallet 73. In particular, since entry pallet-stone 72 and exit pallet-stone 73 are arranged so as to sandwich second axis O2, exit pallet-stone 73 is disengaged from entry pallet-stone 63 when pallet-stone 63 engages with entry pallet-stone 72, and entry pallet-stone 72 is disengaged from pallet-stone 63 when pallet-stone 63 engages with exit pallet-stone 73.

More specifically, when balance spring mechanism 40 rotates in first rotation direction M1, engagement of escapement tooth 63 with entry pallet 72 is released, and after escapement tooth 63 comes into contact with contact pallet 55, escapement tooth 63 engages with exit pallet 73. When balance spring mechanism 40 rotates in second rotation direction M2, engagement between escapement tooth 63 and escape pallet 73 is released, and after escapement tooth 63 slides on sliding surface 73b of escape pallet 73 and relatively moves, escapement tooth 63 engages with entry pallet 72. This point will be described in detail later.

The escapement 14 further includes a stopper pin (ドテピン)90, and the stopper pin 90 positions the escapement pallet 70 when the entry pallet stone 72 and the exit pallet stone 73 engage with the escape wheel 64 of the escape wheel 60. The stopper pin 90 is disposed on the opposite side of the escape wheel 60 across one pallet fork 76A. The stopper pin 90 is disposed between the one pallet beam 76A and the arm 77 at a distance from the one pallet beam 76A and the arm 77 in a plan view. The stopper pin 90 is fixed to protrude upward from the main plate 11, for example, and is located at the same height as the escape fork 78.

Since the stopper pin 90 is configured as such, one pallet fork 76A and the arm 77 can be in contact with respect to the stopper pin 90. This can restrict the rotation of the pallet fork 70 and position the pallet fork.

In the escape governor 13 configured as described above, the center C of the balance stone 50 is disposed at a position deviated by a predetermined angle θ around the first axis O1 with respect to the virtual straight line L passing through the first axis O1 and the second axis O2 in a stationary state in which the torque of the balance spring 30 does not act on the balance spring mechanism 40 when viewed from the axial direction of the first axis O1. Specifically, the center C of the pendulum drill 50 is disposed at a position shifted by a predetermined angle θ from the virtual straight line L in the second rotational direction M2 when viewed from the axial direction of the first axis O1. The predetermined angle θ is greater than 0 ° and 15 ° or less. Thus, the balance 45 is formed so that the balance spring torque balance at the end of each impact of the escapement 14 becomes uniform. This is explained in detail later. Further, the center C of the pendulum drill 50 in the case of being viewed from the axial direction of the first axis O1 is the center between both end portions of the pendulum drill 50 in the circumferential direction around the first axis O1.

Returning to fig. 5, the escape governor 13 includes a plurality of adjusting devices 101, 102, 103 that adjust the position of the pendulum base 45 about the first axis O1. The first adjusting device 101 includes a balance spring mechanism bridge 16, an outer pile 34, and an outer pile bridge 35. The first adjusting device 101 is configured to adjust the position of the balance spring 30, the balance spring mechanism 40, and the balance staff 45 with respect to the balance spring bridge 16 by adjusting the position around the first axis O1 with respect to the balance spring bridge 16 when the collet 35 is assembled to the balance spring bridge 16. The second adjusting device 102 includes the swing shaft 41 and the inner pile 31. When the collet 31 is assembled to the balance staff 41, the second adjusting device 102 adjusts the position of the balance spring 40 and the roller 45 with respect to the balance spring bridge 16 by adjusting the position of the balance staff 41 around the first axis O1. The third adjusting device 103 includes the swing shaft 41 and the swing seat 46. The third adjustment device adjusts the position of the rocker base 45 with respect to the balance spring mechanism 40 by adjusting the position around the first axis O1 with respect to the balance shaft 41 when the rocker body 46 is assembled to the balance shaft 41. The position of the center C of the pendulum drill 50 when viewed from the axial direction of the first axis O1 is adjusted by at least one of the plurality of adjusting devices 101, 102, 103.

Next, the operation of escapement governor 13 configured as described above will be described with reference to fig. 9 to 20. Fig. 9 to 20 are plan views illustrating the operation of the escape speed governor according to the embodiment. In the operation starting state in the following description, as shown in fig. 9, the operation surface 63a of the escapement tooth 63 is engaged with the engagement surface 72a of the pallet stone 72, and the arm 77 of the pallet 70 is brought into contact with the stopper pin 90, whereby the pallet 70 is positioned. Thereby, the rotation of the escape wheel 60 is stopped. Then, the balance stone 50 moves in the first rotational direction M1 by the free oscillation of the balance spring mechanism 40, and enters the inside of the pallet fork case 81. Further, contact pallet 55 is retreated from rotation locus R of escape pinion 64.

From such an operation start state, the operation of escape governor 13 accompanying the reciprocating rotation of balance spring mechanism 40 will be described in order.

From the state shown in fig. 9, if the balance spring mechanism 40 further rotates in the first rotation direction M1 by the elastic energy accumulated in the balance spring 30, the balance stone 50 comes into contact with and engages with the inner surface of the pallet fork box 81 on the dovetail 80 side positioned in the traveling direction of the balance stone 50 than the balance stone 50, and presses the pallet fork box 81 in the first rotation direction M1. Thereby, the torque of balance spring 30 is transmitted to pallet fork 70 via balance stone 50. Further, when the pallet fork 81 is engaged with the pendulum stone 50, the small flange 43 and the prong pin 82 do not contact each other because the crescent 43a is formed. Therefore, the torque of the balance spring 30 can be efficiently transmitted to the pallet fork 70.

As a result, as shown in fig. 10, the pallet fork 70 rotates counterclockwise as viewed from the front about the second axis O2, and the arm 77 of the pallet fork 70 is separated from the stopper pin 90. Further, the pallet 70 rotates, so that the entry pallet stone 72 moves in a direction of escaping from the escape pinion 64 (a direction of retreating from the rotation locus R of the escape pinion 64). Then, entry pallet 72 moves to a position slightly shifted from rotation locus R of escape pinion 64, and entry pallet 72 can be disengaged from escape tooth 63, and engagement with escape tooth 63 can be released. This enables the escape wheel 60 to be released from the stop.

When the engagement between the escapement tooth 63 and the entry pallet 72 is released, the entry pallet 72 is retreated, and thus the escape wheel 60 is instantaneously retreated in the clockwise direction M4 opposite to the counterclockwise direction M3, which is the original rotation direction. After the instant backward movement, the escape wheel 60 starts to rotate again in the counterclockwise direction M3 by the torque transmitted through the wheel train 12. Thus, the escape wheel 60 is instantaneously retracted, so that the engagement of the front wheel train 12 is more reliable, and the front wheel train 12 can be operated stably and with high reliability.

Then, as shown in fig. 11, if the escape wheel 60 starts rotating again in the counterclockwise direction M3, the action surface 63a of the escapement tooth 63 comes into contact (collides) with the contact surface 56 of the contact pallet stone 55 entering into the rotation locus R of the escape wheel 64 as the balance spring 40 rotates in the first rotation direction M1. By the impact when the contact pallet 55 comes into contact with the escapement tooth 63, the torque transmitted to the escape wheel 60 can be directly transmitted to the balance hairspring mechanism 40 via the balance 45, and the pallet 70 can be made to continue to rotate in a manner to track the balance stone 50. In this way, the torque transmitted to escape wheel and pinion 60 can be directly transmitted to balance spring mechanism 40, and the torque can be supplemented to balance spring mechanism 40. When active surface 63a of escapement tooth 63 contacts contact surface 56 of contact pallet 55, rocker 45 is positioned in second rotational direction M2 further than the rest position (see fig. 8) in the case where balance spring mechanism 40 is in the rest state.

As described above, if escapement tooth 63 comes into contact with contact pallet 55, escapement tooth 63 slips on contact surface 56 while rotating in counterclockwise direction M3, and contact pallet 55 moves gently in a direction of disengaging from escapement gear 64 (a direction of retreating from rotational trajectory R of escapement gear 64) with the rotation of balance spring 40. As shown in fig. 12, when contact pallet 55 moves in the direction of disengaging from escape pinion 64 by the rotation of balance spring 40, escape pallet stone 73 starts entering rotation locus R of escape pinion 64 by the rotation of pallet 70 in the counterclockwise direction.

Then, if contact pallet 55 moves to a position shifted from rotation locus R of escape pinion 64, as shown in fig. 13, contact pallet 55 is disengaged from escape tooth 63, and engaging surface 63a of escape tooth 63 comes into contact with engaging surface 73a of escape pallet 73 entering rotation locus R of escape pinion 64. Thereby, the escape gear 64 is in a state where the rotation is stopped (first stop). Moreover, in the disengagement of contact pallet 55 from escapement tooth 63, pendulum 45 is positioned more in first direction of rotation M1 than in the rest position.

Further, at the stage of initial contact, one pallet beam 76A of the pallet 70 moves toward the stopper pin 90 with the counterclockwise rotation of the pallet 70, but does not contact with respect to the stopper pin 90. Thus, the escape tooth 63 remains in contact with the exit pallet stone 73, and the pallet 70 rotates slightly. Then, if one of the pallet beams 76A comes into contact with the stopper pin 90, further rotation of the pallet 70 is restricted to be positioned. Therefore, the escapement tooth 63 is engaged with the escape pallet 73. Thereby, the pallet 70 is stopped, and the escape wheel 60 is in a state where the rotation is stopped (second stop). At this stage, the operation of directly transmitting the torque to the pendulum drill 50 is completed.

Subsequently, as shown in fig. 14, the balance stone 50 is disengaged from the pallet fork case 81, and is separated from the pallet fork 70 with the rotation of the balance spring mechanism 40 in the first rotational direction M1. Thereafter, the balance-spring mechanism 40 continues to rotate in the first rotation direction M1 due to inertia, and the rotational energy thereof is accumulated as elastic energy in the balance spring 30. Then, if all the rotational energy is accumulated in the balance spring 30, the balance-spring mechanism 40 stops rotating in the first rotational direction M1, and after the instantaneous standstill, starts rotating in the opposite second rotational direction M2 due to the elastic energy accumulated in the balance spring 30.

Thereby, the balance stone 50 starts moving so as to approach the pallet fork 70 again with the rotation of the balance spring mechanism 40 in the second rotation direction M2. Then, as shown in fig. 15, if the pendulum stone 50 enters the pallet box 81 of the pallet 70, the pendulum stone 50 comes into contact with and engages with the inner surface of the pallet box 81 on the dovetail 80 side located on the traveling direction side of the pendulum stone 50 with respect to the pendulum stone 50, and pushes the pallet box 81 in the second rotation direction M2. Thereby, the torque of balance spring 30 is transmitted to pallet fork 70 via balance stone 50.

As a result, as shown in fig. 16, the pallet fork 70 rotates clockwise about the second axis O2 as viewed from the front, and one pallet fork beam 76A is separated from the stopper pin 90. Further, the pallet 70 rotates, and the escape pallet 73 moves in a direction of escaping from the escape pinion 64 (a direction of retreating from the rotation locus R of the escape pinion 64). Then, as shown in fig. 17, the engagement surface 73a of the escape pallet 73 moves to a position slightly shifted from the rotation locus R of the escape pinion 64, and the engagement between the engagement surface 73a and the escape tooth 63 can be released. This enables the escape wheel 60 to be released from the stop.

Further, since the escape pallet 73 is retracted similarly to the entry pallet 72, after the escape wheel 60 is momentarily retracted in the counterclockwise direction M4, the rotation is started again in the counterclockwise direction M3 by the torque transmitted through the case side gear train 12. Then, if the escape wheel 60 starts rotating again in the counterclockwise direction M3, as shown in fig. 18, the escape tooth 63 slides on the sliding surface 73b of the escape pallet 73 while relatively moving, and the escape wheel 60 rotates in the counterclockwise direction M3. The torque transmitted to the escape wheel 60 can be transmitted to the pallet 70 via the escape pallet stone 73 by the impact when the escape pallet stone 73 and the pallet tooth 63 slide, and the pendulum stone 50 comes into contact with and engages with the inner surface of the pallet box 81 on the dovetail 80 side on the opposite side of the direction of travel of the pendulum stone 50 from the pendulum stone 50. When the escapement tooth 63 contacts the engagement surface 73a of the escape pallet 73, the saddle 45 is positioned in the first rotational direction M1 from the rest position. In addition, in the disengagement of escape pallet 73 from escapement tooth 63, pendulum 45 is positioned in second direction of rotation M2 further than the rest position.

Therefore, the torque transmitted to the escape wheel and pinion 60 can be indirectly transmitted to the balance spring mechanism 40 via the pallet fork 70, and the pallet fork 70 can be caused to continue to rotate in a manner of tracking the balance stone 50. In this way, the torque transmitted to escape wheel and pinion 60 can be indirectly transmitted to balance spring mechanism 40, and the torque can be supplemented to balance spring mechanism 40.

Subsequently, if escape pallet 73 is moved to a position shifted from rotation locus R of escape pinion 64 by the rotation of pallet 70, as shown in fig. 19, action face 63a of escape tooth 63 comes into contact with engagement face 72a of entry pallet 72 of rotation locus R of entry pallet 64. Thereby, the escape gear 64 is in a state where the rotation is stopped (first stop).

Further, at the stage of initial contact, the arm 77 of the pallet 70 moves toward the stopper pin 90 with the clockwise rotation of the pallet 70, but does not contact with respect to the stopper pin 90. Thus, the escape tooth 63 remains in contact with the entry pallet stone 72, and the pallet 70 rotates slightly. Then, as shown in fig. 20, if the arm 77 of the pallet fork 70 comes into contact with the stopper pin 90, further rotation of the pallet fork 70 is restricted to be positioned. Therefore, the escape tooth 63 is engaged with the entry pallet 72. Thereby, the pallet 70 is stopped, and the escape wheel 60 is in a state where the rotation is stopped (second stop). At this stage, the operation of indirectly transmitting the torque to the pendulum drill 50 is ended.

Subsequently, the balance stone 50 is disengaged from the pallet fork case 81, and is separated from the pallet fork 70 with the rotation of the balance spring mechanism 40 in the second rotation direction M2. Thereafter, the balance-spring mechanism 40 continues to rotate in the second rotation direction M2 due to inertia, and the rotational energy thereof is accumulated as elastic energy in the balance spring 30. Then, if all the rotational energy is accumulated in the balance spring 30, the balance-spring mechanism 40 stops rotating in the second rotational direction M2, and after the instantaneous standstill, starts rotating in the opposite first rotational direction M1 due to the elastic energy accumulated in the balance spring 30.

Thereafter, the escapement governor 13 repeats the above-described operation as the balance spring mechanism 40 reciprocates. Therefore, in one cycle of balance spring 40, escapement 14 gives torque to balance spring 40 by two impacts, a direct impact when escape wheel 64 comes into contact with contact pallet stone 55 of balance 45 and an indirect impact when escape wheel 64 comes into contact with exit pallet stone 73 of pallet 70. That is, while the balance spring mechanism 40 makes one round trip, the escape speed regulator 13 can alternately perform (switch) direct torque transmission via the rocker 45 that rotates coaxially with the balance spring mechanism 40 and indirect torque transmission via the pallet fork 70 that rotates around an axis different from the balance spring mechanism 40, supplement power to the balance spring mechanism 40, and control the rotation of the escape wheel 60 with a constant vibration in correspondence with the balance spring mechanism 40. That is, the detent escapement can operate as a semi-indirect-semi-direct impact type escapement 14 using both direct impact and indirect impact, and can improve torque transmission efficiency as compared with a conventional crab claw/lever escapement of an indirect impact type.

Here, the balance spring torque balance is defined as a difference obtained by subtracting the torque applied to the balance spring 40 from the hairspring 30 from the torque applied to the balance spring 40 from the escapement 14. Fig. 21 is a graph showing the balance spring torque balance at the end of the impulse of each impulse of the escapement. In fig. 21, the horizontal axis represents the rest position of the swing seat 45 with reference to the predetermined position in the circumferential direction around the first axis O1, and the horizontal axis represents the positive first rotation direction M1 with respect to the predetermined position. In fig. 21, the vertical axis represents the balance spring torque balance at the end of the impact. In fig. 21, the solid line indicates the balance spring torque balance at the end of the impact of the direct impact, and the broken line indicates the balance spring torque balance at the end of the impact of the indirect impact. The balance spring torque balance shown in fig. 21 is a balance when the torque of barrel wheel 20 is constant.

As shown in fig. 21, the more the rest position of the balance drill 50 is located in the first rotation direction M1, the greater the balance spring torque balance at the end of the impact of the direct impact. That is, when the torque of barrel wheel 20 is smaller as the rest position of wobbler 50 is positioned in second rotation direction M2, the balance torque balance is likely to be 0 or less. Therefore, the operation of the escape governor 13 is easily stopped until the end of the impact. On the other hand, the more the rest position of the balance 50 is located in the first rotation direction M1, the smaller the balance spring torque balance at the end of the impact of the indirect impact. That is, when the torque of barrel wheel 20 is smaller as the rest position of wobbler 50 is positioned in first rotational direction M1, the balance torque balance is likely to be 0 or less. Therefore, the operation of the escape governor 13 is easily stopped without the indirect impact being ended. For example, in the configuration in which the center C of the pendulum drill 50 is located on the virtual straight line L in the stationary state when viewed from the axial direction of the first axis O1, the indirect impact is less than the end of the impact than the direct impact.

In the present embodiment, the rest position of the pendulum seat 45 is set such that the center C of the pendulum drill 50 of the pendulum seat 45 in the rest position is disposed at a position deviated by a predetermined angle θ about the first axis O1 with respect to the virtual straight line L, when viewed in the axial direction of the first axis O1. Thus, the balance 45 is formed (disposed) so that the balance spring torque balance at the end of the impulse of each impulse of the escapement 14 becomes uniform.

Fig. 22 is a graph showing the torque acting on the balance spring mechanism at the time of direct impact in the escape speed regulator according to the embodiment. Fig. 23 is a graph showing the torque acting on the balance spring mechanism at the time of the indirect impact in the escape speed regulator according to the embodiment. In each figure, the horizontal axis represents the rotation angle of balance spring mechanism 40 when the state in which the torque of balance spring 30 does not act on balance spring mechanism 40 is 0 and the direction of rotation of balance spring mechanism 40 is positive. In the drawings, the vertical axis represents the torque applied to the balance spring mechanism 40. In each of the drawings, a solid line indicates torque applied from the escapement 14 to the balance spring mechanism 40 in a first state where the spring accommodated in the barrel wheel 20 is sufficiently wound, a broken line indicates torque applied from the escapement 14 to the balance spring mechanism 40 in a state where the spring accommodated in the barrel wheel 20 is unwound from the first state, and a one-dot chain line indicates torque applied from the balance spring 30 to the balance spring mechanism 40.

As shown in fig. 22 and 23, in the first state where the spiral spring of barrel wheel 20 is sufficiently wound, the balance-spring torque balance at the end of the impact of each impulse of escapement 14 becomes uniform. Thus, even if the mainspring of barrel wheel 20 is unwound and the torque applied from escapement 14 to balance-spring mechanism 40 is reduced, the torque shortage at the time of the end of the impact earlier than the other of the direct impact and the indirect impact can be suppressed.

Here, as a comparative method, the following case will be explained: the rest position of the pendulum socket 45 is set such that the center C of the pendulum drill 50 of the pendulum socket 45 in the rest position is arranged on the virtual straight line L as described above, when viewed in the axial direction of the first axis O1. Fig. 24 is a graph of a comparison method corresponding to fig. 22. Fig. 25 is a graph of a comparative method corresponding to fig. 23. As shown in fig. 24 and 25, in the first state in which the spiral spring of barrel wheel 20 is sufficiently wound, the balance-spring torque balance at the end of the impulse of the indirect impulse of escapement 14 is smaller than the balance-spring torque balance at the end of the impulse of the direct impulse. Thus, when the torque applied to the balance spring 40 from the escapement 14 becomes small, the balance spring torque balance at the end of the impact becomes 0 earlier than the direct impact in the indirect impact, and the indirect impact becomes less than the end of the impact earlier than the direct impact.

Therefore, according to the present embodiment, it is possible to suppress one of the direct impact and the indirect impact from reaching a state where the impact is not completed earlier than the other. Therefore, the duration of escape governor 13 can be increased.

The rocker base 45 rotates integrally with the balance spring mechanism 40. Therefore, as compared with a configuration including meshing of gears and the like on a transmission path of the torque from the rocker to the balance spring, the torque from the escapement 14 to the balance spring 40 can be transmitted efficiently.

The escape wheel 60 contacts the rocker 45 and transmits torque to the balance spring 40 when the balance spring 40 rotates in the first rotation direction M1, and contacts the pallet 70 and transmits torque to the balance spring 40 when the balance spring 40 rotates in the second rotation direction M2. According to this configuration, since the escapement 14 can be configured as a so-called semi-indirect-semi-direct impulse type, the escapement 14 having excellent torque transmission efficiency can be obtained as compared with a case where the escapement is configured as a so-called indirect impulse type such as a crab claw/lever escapement.

Here, when viewed from the axial direction of the first axis O1, in a configuration in which the center C of the balance stone 50 of the rocker 45 is arranged on the virtual straight line L passing through the first axis O1 and the second axis O2 in a stationary state in which the torque of the balance spring 30 does not act on the balance spring mechanism 40, a difference occurs in balance torque balance at the end of the impact due to a difference in the rotational direction of the balance spring mechanism 40 (difference in the impact). In the present embodiment, the center C of the pendulum drill 50 is disposed at a position deviated from the virtual straight line L around the first axis O1 in the stationary state when viewed from the axial direction of the first axis O1. According to this configuration, the balance 45 can be arranged so that the balance spring torque balance at the end of each impulse of the escapement 14 becomes uniform. Therefore, the above-described effects can be obtained.

Further, when viewed from the axial direction of the first axis O1, the center C of the pendulum drill 50 is disposed at a position deviated by more than 0 ° and 15 ° or less around the first axis O1 on the third axis O3 side with respect to the virtual straight line L in the stationary state. According to this configuration, the escape speed regulator 13 can be formed such that the rocker 45 passes through the rest position during an impact after the stop of the escape wheel 60 is released. Thus, when the spring of barrel 20 unwinds and the torque transmitted to escape wheel 60 decreases, escape wheel 60 stops at the position of impact, and thus the restart performance at the time of winding up the spring and increasing the torque transmitted to escape wheel 60 can be ensured.

The escape governor 13 includes adjusting devices 101, 102, and 103 that adjust the position of the rocker 45 about the first axis O1. According to this configuration, the rocker 45 can be disposed so that the balance spring torque balance at the end of the impact of each impact of the escapement 14 becomes uniform, and the above-described operational effects can be obtained.

In the above embodiment, in the first state where the balance spring is sufficiently wound, the balance-spring torque balance at the end of the impact of each impact of the escapement 14 becomes uniform. However, the balance-spring torque balance at the end of the impact of each impact of the escapement 14 may be more uniform in any state where the spring is wound, than in a state where the spring becomes 0 at least in any one of the direct impact and the indirect impact (a state where the escapement 14 is stopped).

Fig. 26 is a graph of a modification of the embodiment corresponding to fig. 22. Fig. 27 is a graph of a modification of the embodiment corresponding to fig. 23. As shown in fig. 26 and 27, in the present modification, in the state of unwinding from the first state in which the power spring of barrel wheel 20 is sufficiently wound, the balance spring torque balance at the time of the end of the impact of each impact of escapement 14 becomes uniform. Thus, when the spiral spring of barrel wheel 20 is further unwound, the balance-spring torque balance becomes 0 in both the direct impact and the indirect impact. Therefore, the torque at the time of the end of the impact can be more reliably suppressed from being insufficient earlier than the other of the direct impact and the indirect impact.

The present invention is not limited to the above-described embodiments described with reference to the drawings, and various modifications are conceivable within the technical scope thereof. For example, in the above-described embodiment, the case where the escapement 14 is configured as a so-called semi-indirect-semi-direct impulse type has been described, but the configuration of the escapement governor is not limited thereto. That is, the escapement may be a so-called crab claw/lever escapement that applies torque to the balance spring mechanism by indirect impact when the escapement gear comes into contact with the pallet stone of the pallet in each of the rotation of the balance spring mechanism in the first rotation direction and the rotation of the balance spring mechanism in the second rotation direction. Even in this case, the above-described operational effects can be achieved by arranging the pendulum drill of the pendulum base in the same manner as in the above-described embodiment.

In the above embodiment, the escape wheel 60 has a single-layer structure, but the escape wheel may have a double-layer structure.

In the above embodiment, the escapement 14 includes one pallet fork 70, but the escapement may include a pallet unit including a plurality of pallet forks. The escapement may be configured to apply torque to the balance spring mechanism by three or more impacts in one cycle of the balance spring mechanism.

In the above embodiment, the escape governor 13 includes a plurality of adjusting devices for adjusting the position of the rocker 45 around the first axis O1, but at least one of the adjusting devices 101, 102, and 103 may be provided. In addition, the adjustment device for adjusting the position of the oscillating seat 45 about the first axis O1 may also have a balance spring 30 and a stud capable of adjusting the fixing position with the balance spring 30. That is, the positions of the balance spring 30, the balance spring mechanism 40, and the roller 45 with respect to the balance spring bridge 16 can be adjusted by adjusting the fixing positions of the stud fixedly disposed with respect to the balance spring bridge 16 and the main plate 11 and the outer peripheral portion of the balance spring 30.

It is to be noted that the components in the above embodiments may be replaced with well-known components without departing from the scope of the present invention.

Description of the symbols

1 … clock 10 … movement (clock movement) 13 … escape speed regulator 14 … escape 16 … balance spring mechanism splint (supporting member) 16a … peripheral surface (circumferential surface) 30 … balance spring 31 … collet 34 … collet 35 … collet splint 40 … balance spring mechanism 41 … pendulum shaft (shaft portion) 45 … pendulum seat (torque transmission member) 46 … pendulum seat body (assembling portion) 50 … pendulum drill 60 … escape wheel 70 … escape wheel 101, 102, 103 … adjusting device C … pendulum drill center L … imaginary straight line M1 … first rotation direction M2 … second rotation direction O1 … first axis O2 … second axis.

Claims (12)

1. An escape speed regulator includes:

a balance spring;

a balance spring mechanism that reciprocates in a first rotational direction and a second rotational direction opposite to each other about a first axis as a center in accordance with expansion and contraction of the balance spring;

an escapement including an escape fork that rotates about a second axis and an escape wheel that can be engaged with and disengaged from the escape fork; and

a torque transmission member that transmits torque from the escapement to the balance spring mechanism,

the escapement imparts a torque to the balance spring mechanism by at least two impacts in one cycle of the balance spring mechanism,

when a difference obtained by subtracting the torque of the balance spring from the torque applied to the balance spring by the escapement is defined as a balance spring torque balance, the torque transmission member is formed so that the balance spring torque balance at the end of the impact of each impact of the escapement becomes equal.

2. The escape speed regulator according to claim 1, wherein the torque transmission member rotates integrally with the balance spring mechanism.

3. The escape speed regulator according to claim 1 or claim 2, wherein the escape wheel contacts the torque transmission member to apply torque to the balance spring when the balance spring rotates in the first rotational direction, and contacts the pallet to apply torque to the balance spring when the balance spring rotates in the second rotational direction.

4. The escape speed regulator according to claim 1 or claim 2, wherein the escape wheel contacts the pallet to apply torque to the balance spring mechanism when the balance spring mechanism rotates in the first rotational direction and when the balance spring mechanism rotates in the second rotational direction.

5. The escape speed governor according to any one of claims 1 to 4, wherein,

the torque transmission member includes a pendulum drill capable of engaging with and disengaging from the pallet fork,

the center of the balance drill is disposed at a position offset around the first axis line with respect to an imaginary straight line passing through the first axis line and the second axis line in a stationary state in which the torque of the balance spring does not act on the balance spring mechanism when viewed from the axial direction of the first axis line.

6. The escape governor of claim 5, wherein,

the center of the pendulum drill is disposed at a position that is deviated from the imaginary straight line by more than 0 ° and 15 ° or less around the first axis in the stationary state when viewed from the axial direction.

7. The escape speed regulator according to claim 5 or claim 6, including an adjustment device that adjusts a position of the torque transmission member about the first axis.

8. The escape governor of claim 7, wherein,

the torque transmitting member is fixedly arranged with respect to the balance spring mechanism,

the adjusting device has:

a support member that rotatably supports the balance spring mechanism;

an outer pile fixed to an outer peripheral portion of the hairspring; and

and an outer pile clamping plate which is assembled on the circumferential surface of the supporting component and extends by taking the first axis as the center, and supports the outer pile.

9. The escape speed governor according to claim 7 or claim 8,

the torque transmitting member is fixedly arranged with respect to the balance spring mechanism,

the adjusting device has:

a shaft portion of the balance spring mechanism; and

and a collet fitted to the shaft portion and fixed to an inner end portion of the balance spring.

10. The escape speed governor according to any one of claims 7 to 9, wherein,

the balance spring mechanism includes a shaft portion,

the torque transmission member has a fitting portion fitted to a shaft portion of the balance spring mechanism,

the adjusting device has:

the shaft portion of the balance spring mechanism; and

the fitting portion.

11. A timepiece movement provided with the escape speed governor according to any one of claims 1 to 10.

12. A timepiece provided with the timepiece movement of claim 11.

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