JP6901877B2 - Escapement, watch movements and watches - Google Patents

Description

The present invention relates to escapements, watch movements and watches.

In general, a mechanical timepiece is equipped with an escapement that transmits power for reciprocating rotation to the balance with hairspring and controls the train wheel with constant vibration by utilizing the regular reciprocating rotation of the balance with hairspring. This type of escapement has evolved through repeated improvements and the like, and various types of escapements have now been proposed.

For example, as one of the highly efficient and highly durable escapements, the one that originated from the natural escapement (natural escapement) devised by Breguet is known. The escapement of this system has two escapement wheels, and the direct impact on the balance with these two escape wheels and the indirect impact through the ankle alternate. By doing so, it has the characteristic of transmitting power to the balance.
In particular, this escapement is different from the club tooth lever escapement, which occupies the mainstream of mechanical watches, and is designed to reduce the slippage of the tooth tip of the escape wheel in the event of an impact. As a result, it is possible to suppress the wear of the tooth tips of the escape wheel, and the durability is improved. Further, when a direct impact is applied to the balance sheet, the impact can be transmitted from the escape wheel to the balance sheet without interposing other watch parts. This is aimed at improving efficiency.

By the way, if we focus on the method of transmitting power from the escape wheel to the balance with hairspring, the escapement can be roughly divided into the direct impact type that transmits power directly from the escape wheel to the balance with hairspring and the ankle. It is mainly divided into the indirect impact type that indirectly transmits power from the escape wheel to the balance sheet through the clock parts of the escapement, but in addition to this, the escapement that uses both direct impact and indirect impact together. Is also known.

As an escapement that uses both direct impact and indirect impact, the Coaxis escapement (coaxial escapement), which has a two-layer structure escapement in which two escape gears are coaxially overlapped, has been widely used. Are known. For example, as described in Patent Document 1 below or Non-Patent Document 1 below, escapements represented by George Daniels are known.

The Coaxial escapement is a two-layer escapement wheel in which a first escape gear and a second escape gear formed having a diameter larger than that of the first escape gear are coaxially overlapped. , A first impact claw stone, a first stop claw stone and a second stop claw stone are provided, and an ankle that is rotatable based on the rotation of the balance wheel and a second impact claw stone fixed to the balance sheet. I have.
The first impact claw stone is made come into contact with the tooth tip of the first escape gear as the ankle rotates. The second impact claw stone is made come into contact with the tooth tip of the second escape gear as the balance with hair rotation. The first stop claw stone and the second stop claw stone can be engaged with and detached from the tooth tips of the second escape gear as the ankle rotates.

According to the Coaxial escapement configured in this way, the first stop claw stone and the second stop claw stone alternately engage and disengage with respect to the second escape gear as the ankle rotates. The rotation of the gear wheel can be controlled. In addition, since the first impact claw stone comes into contact (collision) with the tooth tip of the first escape gear as the ankle rotates, the power transmitted to the escape wheel is indirectly transmitted to the balance with hair through the ankle. Can be transmitted to, and the balance can be replenished with rotational energy. Furthermore, as the balance wheel rotates, the second impact claw stone comes into contact (collision) with the tip of the second escape gear, so the power transmitted to the escape wheel can be directly transmitted to the balance wheel. , The balance can be replenished with rotational energy.
Therefore, it is possible to transmit the power transmitted to the escape wheel to the balance wheel while alternately performing indirect power transmission and direct power transmission.

Further, in Patent Document 1 and Non-Patent Document 1, there is also an escapement that uses both a direct impact and an indirect impact by using a single-layer structure escape wheel instead of a two-layer structure escape wheel. It is disclosed.
In this escape machine, the first stop claw stone and the second stop claw stone can be engaged and disengaged with respect to the escape gear, and the first impact claw stone and the second impact claw stone are further applied to the same escape gear. It is said that the claw stones can be touched.

European Patent Application Publication No. 00187796

George Daniels, "WATCHMAKING (Updated 2011 Edition)", Philip Wilson Publicers Ltd. , June 15, 2011, p238-p252

However, in the above-mentioned conventional Coaxial escapement, since the escape wheel has a two-layer structure, the inertia of the entire escape wheel becomes large, and the dynamic efficiency tends to decrease. Further, it is necessary to assemble the escape wheel while aligning the first escape gear and the second escape gear in phase, which causes an assembly tolerance. As an escapement, even if it is affected by this assembly tolerance, it is necessary to ensure stable operability. Therefore, in consideration of the assembly tolerance, the first escape gear and the second escape gear There is no choice but to secure a wide gap between the gears and each claw stone. Therefore, as a result, the power transmission efficiency tends to decrease.

Further, when a single-layer structure escape wheel is used, the first stop claw stone and the second stop claw stone are engaged with the common escape gear, and the first impact claw stone is attached. Need to contact. However, since the first stop claw stone, the second stop claw stone, and the first impact claw stone are incorporated in the same ankle, in order to properly engage or disengage or contact each claw stone with the escape gear, It was necessary to separate the center of rotation of the pallet fork from the tip of the escape gear in the radial direction of the escape wheel by a certain distance.
However, for example, when focusing on the action of stopping, the farther the center of rotation of the ankle is from the tip of the escape gear, the more the tip of the escape gear separates from the stopping claw stone. The sliding distance to slide is increased. As a result, the energy required to release the stop of the escape wheel increases, leading to a decrease in power transmission efficiency.

Furthermore, since the first stop claw stone, the second stop claw stone, and the first impact claw stone are incorporated in one common pallet fork, the pallet fork can be operated at the optimum operating angles for impact and stop, respectively. However, it caused a decrease in power transmission efficiency.

The present invention has been made in view of such circumstances, and an object of the present invention is to provide an escapement, a timepiece movement, and a timepiece having excellent power transmission efficiency.

(1) The escape machine according to the present invention includes an escape wheel that rotates by the transmitted power, and an impact ankle unit and a stop ankle unit that are connected to each other so as to be relatively displaceable and rotate based on the rotation of the balance with each other. The stop ankle unit is composed of at least one ankle and has a stop claw stone that can be engaged with and disengaged from the escape gear of the escape wheel, and has the impact. The ankle unit is composed of at least one ankle and includes a first impact claw stone that can be contacted with the escape gear when the stop claw stone is not engaged. When the first impact claw stone is not in contact with the first impact claw stone, a second impact claw stone that can be contacted with the escape gear is attached, and the impact ankle unit is an impact ankle having the first impact claw stone. The stop pallet fork has two stop pallets and has a stop pallet for which the stop pallet fork is movably connected to the impact pallet for relative displacement. The two stop pallets are the rotation of the stop pallet fork. As a result, the escape gears are alternately engaged and disengaged .

According to the present invention, the impact ankle unit and the stop ankle unit, which are connected to each other so as to be relatively displaceable, can be rotated based on the rotation (reciprocating rotation) of the balance with each other. By rotating the impact ankle unit, the first impact claw stone can be brought into contact (collision) with the escape gear. As a result, the power transmitted to the escape wheel can be indirectly transmitted to the balance wheel through the impact ankle unit, and the rotational energy can be replenished to the balance wheel. Further, since the second impact claw stone is attached to the balance with hair, the second impact claw stone can be brought into contact (collision) with the escape gear by rotating the balance with hairspring. As a result, the power transmitted to the escape wheel can be directly transmitted to the balance wheel through the second impact claw stone, and the rotational energy can be replenished to the balance wheel. Further, when the stop ankle unit rotates, the stop claw stone is engaged with the escape gear to stop the rotation of the escape wheel, or the stop claw engaged with the escape gear. The stone can be disengaged from the escape gear to release the escape of the escape wheel.
In this way, while alternating (switching) direct power transmission and indirect power transmission, the power transmitted to the escape wheel can be transmitted to the balance wheel, and constant vibration corresponding to the balance wheel can be transmitted. You can control the rotation of the escape wheel.

In particular, unlike the conventional escape machine in which the impact claw stone and the stop claw stone are incorporated in one common ankle, the impact ankle unit has only the impact claw stone (first impact claw stone), and the stop ankle. The unit has only a stop claw stone. Therefore, the relative positions of the impact ankle unit and the stop ankle unit with respect to the escape wheel can be freely designed and arranged with less restrictions, and the impact ankle unit and the stop ankle unit are arranged in the optimum layout for impact and stop, respectively. It is possible.

Therefore, for example, the operating angle of the ankle constituting the impact ankle unit and the operating angle of the ankle constituting the stop ankle unit can be set to the optimum angles in consideration of the impact action and the stop action. .. As a result, the power transmission efficiency can be improved, and the escapement with less operating error can be obtained.
Furthermore, the distance between the center of rotation of the escape wheel and the center of rotation of the ankle that constitutes the impact ankle unit, and the center of rotation of the escape wheel and the center of rotation of the ankle that constitutes the stop ankle unit. The distance between the centers can be set to the optimum distance in consideration of the action of impact and the action of stopping. Therefore, unlike the conventional escapement in which the impact claw stone and the stop claw stone are incorporated in one common ankle, it is possible to suppress an increase in the energy required to release the stop of the escape wheel, and the power can be reduced. It can lead to improvement of transmission efficiency.

Further , since the impact ankle unit can be composed of one ankle, that is, the impact ankle, and the stop ankle unit can be composed of one ankle, that is, the stop ankle, the escapement can be easily configured. In addition, even with one stop ankle, the rotation of the stop ankle allows the two stop claw stones to be alternately engaged and disengaged from the escape gear, and the cancer is generated by a constant vibration corresponding to the balance with hairspring. It is possible to appropriately control the rotation of the gear wheel.

( 2 ) The watch movement according to the present invention includes the escapement, a speed governor having the balance with hairspring, and a train wheel for transmitting power to the escape wheel.
( 3 ) The timepiece according to the present invention includes the timepiece movement and a pointer that rotates at a rotation speed adjusted by the escapement and the speed governor.

In this case, since the escapement is provided with excellent power transmission efficiency and little operating error, it is possible to obtain a high-performance watch movement and watch with little time error.

According to the present invention, an escapement, a timepiece movement, and a timepiece having excellent power transmission efficiency can be obtained.

It is an external view of the timepiece which shows the 1st Embodiment which concerns on this invention. It is a top view of the movement shown in FIG. It is a perspective view of the swing seat of the balance with reference to FIG. It is a top view of the escapement shown in FIG. It is sectional drawing of the escapement along the line AB shown in FIG. It is sectional drawing of the escapement along the line AC shown in FIG. It is an operation explanatory view of the escapement, and is the figure which shows the state which the 1st stop claw stone has begun to separate from a stubborn tooth from the state shown in FIG. It is an operation explanatory view of the escapement, and is the figure which shows the state which the 1st stop claw stone is separated from the escapement tooth from the state shown in FIG. 7, and then the escapement tooth comes into contact with a 1st impact claw stone. Is. It is an operation explanatory view of the escapement, and is the figure which shows the state which the 1st impact claw stone is separated from the escapement tooth from the state shown in FIG. 8, and then the escapement tooth comes into contact with a 2nd stop nail stone. Is. It is an operation explanatory view of the escapement, and is the figure which shows the state which the striking tooth and the 2nd stop claw stone are engaged with each other by the impact ankle coming into contact with a dote pin from the state shown in FIG. It is an operation explanatory view of the escapement, and is the figure which shows the state which the swing stone is moving toward an impact pallet from the state shown in FIG. It is an operation explanatory view of the escapement, and is the figure which shows the state which the 2nd stop claw stone is separated from the escape tooth from the state shown in FIG. It is an operation explanatory view of the escapement, and is the figure which shows the state which the escape tooth came into contact with the 2nd impact claw stone from the state shown in FIG. It is an operation explanatory view of the escapement, and is the figure which shows the state which the 2nd impact claw stone is separated from the escape tooth from the state shown in FIG. It is an operation explanatory view of the escapement, and from the state shown in FIG. 14, the escape tooth comes into contact with the first stop claw stone, and the impact ankle comes into contact with the dotepin, so that the escape tooth and the first stop claw stone come into contact with each other. It is a figure which shows the state which is engaged with. It is a figure for demonstrating the optimum layout for stopping, and is the figure which shows the relationship between the rotation center of the escape wheel, the rotation center of the stop ankle, and the retreat angle of the escape wheel. It is a figure for demonstrating the optimum layout for impact, and is the figure which shows the relationship in the case where the escape tooth of the escape wheel and the first impact claw stone are in contact with each other. It is a top view of the escapement which shows the 2nd Embodiment which concerns on this invention. It is a top view of the escapement which has shifted from the state shown in FIG. 18 to the state in which the escape tooth and the second stop claw stone are engaged. It is a top view of the escapement which shows the modification of the 2nd Embodiment which concerns on this invention.

(First Embodiment)
Hereinafter, the first embodiment according to the present invention will be described with reference to the drawings. In this embodiment, a mechanical timepiece will be described as an example of the timepiece. Further, in each drawing, the scale of each part is appropriately changed as necessary in order to make each part visible.

(Basic configuration of the clock)
Generally, a mechanical body including a driving part of a watch is referred to as a "movement". The state in which the dial and hands are attached to this movement and placed in the watch case to make a finished product is called "complete" of the watch.
Of both sides of the main plate constituting the watch substrate, the side with the glass of the watch case (that is, the side with the dial) is referred to as the "back side" of the movement. Further, of both sides of the main plate, the side of the watch case with the case back cover (that is, the side opposite to the dial) is referred to as the "front side" of the movement.
In the present embodiment, the direction from the dial toward the case back cover is defined as upward, and the opposite side is defined as downward.

As shown in FIG. 1, the complete watch 1 of the present embodiment contains a movement (a watch movement according to the present invention) 10 and at least information on time in a watch case composed of a case back cover and a glass 2 (not shown). It includes a dial 3 having a scale to show, and a pointer 4 including an hour hand 5, a minute hand 6, and a second hand 7.

As shown in FIG. 2, the movement 10 has a main plate 11 that constitutes a substrate. Note that in FIG. 2, some parts constituting the movement 10 are not shown in order to make the drawings easier to see.
On the front side of the main plate 11, there are a front train wheel (wheel train according to the present invention) 12, an escapement 13 that controls the rotation of the front wheel train 12, and a speed governor 14 that controls the escapement 13. It has.

The front wheel train 12 mainly includes a barrel wheel 20, a second wheel 21, a third wheel 22, and a fourth wheel 23. The barrel wheel 20 is pivotally supported between the main plate 11 and the barrel receiver (not shown), and a royal fern (power source) (not shown) is housed inside. The royal fern is wound up by the rotation of the square hole wheel 24. The square hole wheel 24 is rotated by the rotation of a winding stem (not shown) connected to the crown 25 shown in FIG.

The second wheel 21, the third wheel 22, and the fourth wheel 23 are pivotally supported between the main plate 11 and the train wheel receiver (not shown). When the barrel wheel 20 rotates due to the elastic restoring force of the wound zenmai, the second wheel 21, the third wheel 22, and the fourth wheel 23 rotate in order based on this rotation.

That is, the second wheel 21 meshes with the barrel wheel 20 and rotates based on the rotation of the barrel wheel 20. When the second wheel 21 rotates, a cylinder (not shown) rotates based on this rotation. The minute hand 6 shown in FIG. 1 is attached to the cylinder kana, and the minute hand 6 displays "minute" by the rotation of the cylinder kana. The minute hand 6 makes one rotation in one hour, that is, the rotation speed adjusted by the escapement 13 and the governor 14.

Further, when the second wheel 21 rotates, the back wheel of the day (not shown) rotates based on this rotation, and further, the cylinder wheel (not shown) rotates based on the rotation of the back wheel of the day. The back wheel and the cylinder wheel of the sun are clock parts constituting the front wheel train 12. The hour hand 5 shown in FIG. 1 is attached to the cylinder wheel, and the hour hand 5 displays "hour" by the rotation of the cylinder wheel. The hour hand 5 makes one rotation at a rotation speed adjusted by the escapement 13 and the governor 14, for example, in 12 hours.

The third wheel 22 meshes with the second wheel 21 and rotates based on the rotation of the second wheel 21. The fourth wheel 23 meshes with the third wheel 22, and rotates based on the rotation of the third wheel 22. The second hand 7 shown in FIG. 1 is attached to the fourth wheel 23, and the second hand 7 displays "seconds" based on the rotation of the fourth wheel 23. The second hand 7 rotates at a rotation speed adjusted by the escapement 13 and the governor 14, for example, one rotation in one minute.

The escape wheel 40, which will be described later, is engaged with the fourth wheel 23 via the escape wheel 41. As a result, the power from the royal fern housed in the barrel car 20 is transmitted to the escape wheel 40 mainly via the second wheel 21, the third wheel 22, and the fourth wheel 23. As a result, the escape wheel 40 rotates around the rotation axis O2.

The speed governor 14 mainly includes a lamp 30.
The balance sheet 30 includes a balance sheet 31, a balance wheel 32, and a hairspring (not shown), and is pivotally supported between the main plate 11 and the balance spring receiver (not shown). The balance spring 30 reciprocates (forward and reverse rotation) around the rotation axis O1 with a steady amplitude (swing angle) corresponding to the output torque of the barrel wheel 20 using the hairspring as a power source.

Tapered tenons are formed at both ends of the balance sheet 31 in the axial direction. The balance sheet 31 is pivotally supported between the main plate 11 and the balance sheet through these tenons. The balance wheel 32 is integrally fixed to the balance spring 31, and the inner end of the balance spring is fixed to the balance spring 31 via a whiskers (not shown).
In the illustrated example, the balance wheel 32 has four arm portions 33 arranged at a right angle of 90 degrees about the rotation axis O1, but the number, arrangement, and shape of the arm portions 33 are limited to this case. It is not something that is done, and you can change it freely.

As shown in FIG. 3, an annular swing seat 35 is externally fitted and fixed to the balance sheet 31.
The swing seat 35 has a large brim 36 and a small brim 37 located below the large brim 36 (on the side of the main plate 11). A flutter stone 38 formed from an artificial jewel such as a ruby is press-fitted and fixed to the large brim 36, for example.
The flutter stone 38 is formed in a semicircular shape in a plan view, and is formed so as to extend downward from the large brim 36. The flutter stone 38 reciprocates around the rotation axis O1 along with the balance with hairspring 30, and engages with the pallet fork 74, which will be described later, in a detachable manner on the way.

The small brim 37 is formed to have a smaller diameter than the large brim 36. The small brim 37 is formed with a knuckle 39 that is recessed in a curved shape toward the inside in the radial direction at a position corresponding to the swing stone 38. The Tsukigata 39 functions as an escape portion for preventing the sword tip 75, which will be described later, from coming into contact with the small brim 37 when the ankle haco 74 and the swing stone 38 are engaged.
In each drawing other than FIG. 3, the small brim 37 and the swing stone 38 of the swing seat 35 are mainly shown in order to make the drawings easier to see.

(Escapement configuration)
As shown in FIG. 4, the escape machine 13 includes the above-mentioned swing seat 35, an escape wheel 40 that is rotated by power transmitted from the zenmai, an ankle chain 50, and a first impact claw stone (to the present invention). Impact claw stone) 60 and second impact claw stone (impact claw stone according to the present invention) 61, first stop claw stone (stop claw stone according to the present invention) 62 and second stop claw stone (related to the present invention). It is equipped with a stop claw stone) 63.
The swing seat 35 is a component that constitutes the balance 30 and the speed governor 14 as described above, and is also a component that constitutes the escapement 13.

The escape wheel 40 has a single-layer structure including an escape wheel 41 that meshes with the fourth wheel 23 and an escape gear 42 having a plurality of escape teeth 43, and is shown as a main plate 11. It is not supported by the train wheel. In each drawing other than FIG. 2, the illustration of the stubborn 41 is simplified.
In the illustrated example, the number of escape teeth 43 is eight. However, the present invention is not limited to this case, and the number of escape teeth 43 may be appropriately changed. For example, an escape gear 42 having 6-tooth, 10-tooth, and 12-tooth escape teeth 43 may be used.

In the present embodiment, as shown in FIG. 4, in a plan view of the movement 10 viewed from the front side, the escape wheel 40 is rotated by the power transmitted from the fourth wheel 23 side via the escape wheel 41. A case of rotating clockwise around O2 will be described as an example.
In FIG. 4, the direction of clockwise rotation about the rotation axis O2 is referred to as the first rotation direction M1, and the opposite direction is referred to as the second rotation direction M2. Further, the rotation locus R drawn by the tip of the escape wheel 43 as the escape wheel 40 rotates is simply referred to as the rotation trajectory R of the escape gear 42.

Of the escape teeth 43, the side surface facing the first rotation direction M1 contacts the first impact claw stone 60 and the second impact claw stone 61, and the first stop claw stone 62 and the second stop claw It is said that the working surface 43a with which the stone 63 is engaged.

The escape wheel 40 is formed of, for example, a metal material, a material having a crystal orientation such as single crystal silicon, or the like. Examples of the method for manufacturing the escape wheel 40 include electroforming, a LIGA process incorporating an optical method such as a photolithography technique, DRIE, and metal powder injection molding (MIM).
However, the material and manufacturing method of the escape wheel 40 are not limited to the above cases, and may be changed as appropriate. Further, the escape wheel 40 may be appropriately provided with a lightening hole or a thin wall portion to reduce the weight as long as the performance and rigidity of the escape wheel 40 are not affected. In the illustrated example, a plurality of lightening holes are formed in the escape wheel 40.

The ankle chain 50 is configured to be connected to each other so as to be relatively displaceable so that a plurality of ankles are connected in a row, and the plurality of ankles are rotated (swinged) separately based on the reciprocating rotation of the balance with hairspring 30. Displace like.
Specifically, the ankle chain 50 includes an impact ankle unit 52 having an impact ankle 51 and a stop ankle unit 54 having a stop ankle 53. The impact ankle unit 52 and the stop ankle unit 54 are connected to each other so as to be relatively displaceable. That is, the impact ankle 51 and the stop ankle 53 are connected to each other so as to be relatively displaceable, whereby the impact ankle 51 and the stop ankle 53 are connected so as to be connected in a row.

The impact ankle unit 52 and the stop ankle unit 54 may be composed of at least one or more ankles. In the present embodiment, as described above, the impact ankle unit 52 and the stop ankle unit 54 are each composed of one ankle.

The first impact claw stone 60 and the second impact claw stone 61 are made in contact with the working surface 43a of the escape tooth 43 in the escape gear 42, and the power transmitted to the escape wheel 40 is transmitted to the balance with hairspring 30. It is said to be a nail stone to convey to.
Of the first impact claw stone 60 and the second impact claw stone 61, the first impact claw stone 60 is attached to the impact ankle 51, and the second impact claw stone 61 is attached to the swing seat 35 fixed to the balance with hairspring 30. There is.

The first stop claw stone 62 and the second stop claw stone 63 can be engaged with and detached from the working surface 43a of the escape tooth 43 in the escape gear 42, and the escape wheel 40 can be stopped and released. It is said to be a nail stone to do. Both the first stop claw stone 62 and the second stop claw stone 63 are attached to the stop ankle 53.

The first impact claw stone 60 and the second impact claw stone 61 come into contact with the escape gear 42 when the first stop claw stone 62 and the second stop claw stone 63 are not engaged, and the first stop claw stone 62 And the second stop claw stone 63 engages with the escape gear 42 when the first impact claw stone 60 and the second impact claw stone 61 are not in contact with each other. Each of these claw stones is formed from an artificial gemstone such as a ruby, like the swing stone 38.

The impact ankle 51 will be described in detail.
As shown in FIGS. 4 to 6, the impact ankle 51 includes an ankle true 70, an ankle body 71, and an ankle arm 72, which are rotation shafts. Then, the impact ankle 51 rotates around the rotation axis O3 based on the reciprocating rotation of the balance with hairspring 30.

The pallet fork 70 is arranged coaxially with the rotation axis O3, and is pivotally supported between the main plate 11 and the train wheel receiver (not shown). The pallet fork 70 is press-fitted into the base of the pallet fork 71 from below (on the side of the main plate 11) and is integrally fixed.

The ankle body 71 and the ankle arm 72 are integrally formed in a plate shape by, for example, electroplating or MEMS technology. The ankle body 71 and the ankle arm 72 are arranged above the escape wheel 40.
As with the escape wheel 40, the ankle body 71 and the ankle arm 72 may be appropriately provided with lightening holes and thin-walled portions to reduce the weight. In the illustrated example, a plurality of lightening holes are formed in the ankle body 71.

The pallet fork 71 is formed so as to extend from the base to which the pallet fork 70 is fixed toward the second rotation direction M2 side, that is, toward the balance with hairspring 30 side. A pair of stag beetles 73 arranged side by side in the circumferential direction of the rotation axis O3 are provided at the tip of the ankle body 71. The inside of the stag beetle 73 is an ankle haco 74 that opens toward the balance sheet 31 side and accommodates a flutter stone 38 that moves with the reciprocating rotation of the balance sheet 30 so that it can be disengaged.

A sword tip 75 is attached to the tip of the ankle body 71.
The sword tip 75 is fixed to the tip of the ankle body 71 from below by, for example, press fitting. The sword tip 75 is located between the pair of stag beetles 73 in a plan view (that is, is located inside the stag beetle 74), and extends so as to project toward the stag beetle 31 from the stag beetle 73. The sword tip 75 is fixed so as to be located below the swing stone 38 and above the escape wheel 40.
The tip of the sword tip 75 faces the outer peripheral surface of the small brim 37 in the radial direction with a slight gap with respect to the portion of the outer peripheral surface of the small brim 37 excluding the tsukigata 39, in a state where the swing stone 38 is separated from the pallet fork 74. In addition, the swing stone 38 is housed in the Tsukigata 39 in a state of being engaged with the ankle haco 74.

When the swing stone 38 is separated from the ankle hook 74, the tip of the sword tip 75 faces the outer peripheral surface of the small brim 37 in the radial direction with a slight gap. Therefore, for example, the balance with hairspring 30 Even if a disturbance is input during the free vibration and the stop of the entire ankle chain 50 is released due to the influence of the disturbance, the tip of the sword tip 75 can be brought into contact with the outer peripheral surface of the small brim 37 first. As a result, the displacement of the impact pallet fork 51 due to disturbance can be suppressed, and the stop of the entire pallet fork chain 50 can be prevented from being released. The stopping of the ankle chain 50 will be described in detail later.

At the base of the ankle body 71, a first claw stone holding portion 76 is provided so as to project toward the escape wheel 40 side. The first claw stone holding portion 76 is opened toward the escape wheel 40 side, and the first impact claw stone 60 is held by using this opening.
The first impact claw stone 60 is held in a state of extending downward from the ankle body 71 to the extent that it reaches a height position equivalent to that of the escape gear 42. Therefore, the first impact claw stone 60 can come into contact (collision) with the escape tooth 43. Further, the first impact claw stone 60 is held in a state of protruding toward the escape wheel 40 side from the first claw stone holding portion 76. The side surface of the protruding portion of the first impact claw stone 60 facing the M2 side in the second rotation direction is the first impact surface 60a with which the working surface 43a of the escape tooth 43 of the escape gear 42 comes into contact. Has been done.

The pallet fork 72 is formed so as to extend from the base of the pallet fork 71 toward the M1 side in the first rotation direction. An engaging pin 77 extending downward is fixed to the tip of the ankle arm 72 by press fitting or the like. The engaging pin 77 is formed, for example, in a solid columnar shape, and its lower end portion is inserted inside the engaging fork 92 of the stop ankle 53, which will be described later.

The impact ankle 51 configured in this way rotates based on the rotation of the balance with hairspring 30 as described above.
Specifically, the impact pallet fork 51 is rotated around the rotation axis O3 in a direction opposite to the rotation direction of the balance with hairspring 30 by the swing stone 38 that moves with the reciprocating rotation of the balance with hairspring 30. At this time, the first impact claw stone 60 repeatedly enters and retracts from the rotation locus R of the escape gear 42 by rotating the impact ankle 51. As a result, the working surface 43a of the escape tooth 43 of the escape gear 42 can be brought into contact (collision) with the first impact surface 60a of the first impact claw stone 60.

The second impact claw stone 61 will be described.
As shown in FIGS. 3 and 4, the second impact claw stone 61 is attached to the small brim 37 of the swing seat 35. Specifically, the second impact claw stone 61 is held by the second claw stone holding portion 80 formed on the small brim 37. The second claw stone holding portion 80 is formed at a position shifted by a predetermined phase in the clockwise direction of the rotation axis O1 from the Tsukigata 39 in FIG. 4, and is opened toward the escape wheel 40 side. The second impact claw stone 61 is held by the second claw stone holding portion 80 by utilizing this opening.

The second impact claw stone 61 is held in a state of protruding toward the escape wheel 40 from the outer peripheral surface of the small brim 37. Of the protruding portion of the second impact claw stone 61, the side surface of the rotation axis O1 facing the clockwise side is defined as the second impact surface 61a with which the working surface of the escape tooth 43 of the escape gear 42 comes into contact. ing.
A predetermined gap is secured between the second impact claw stone 61 and the swing stone 38 in the direction of the rotation axis O1, and the sword tip 75 approaches the tsukigata 39 through this gap.

The second impact claw stone 61 is not limited to the case where it is attached to the small brim 37, and if it is the swing seat 35, it may be attached to, for example, the large brim 36 or the balance wheel 32. The mounting position of the second impact claw stone 61 may be changed according to, for example, the relative positional relationship with the escape gear 42. In any case, the second impact claw stone 61 may be attached to the balance with hairspring 30.

The second impact claw stone 61 attached to the balance with hairspring 30 as described above repeats entering and retreating from the rotation locus R of the escape gear 42 by the rotation of the balance with hairspring 30. As a result, the working surface 43a of the escape tooth 43 of the escape gear 42 can be brought into contact (collision) with the second impact surface 61a of the second impact claw stone 61.

As described above, since the rotation direction of the balance with hairspring 30 and the rotation direction of the impact ankle 51 are opposite to each other, the second impact when the first impact claw stone 60 comes into contact with the escape gear 42. When the claw stone 61 is separated from the escape gear 42 and the first impact claw stone 60 is separated from the escape gear 42, the second impact claw stone 61 comes into contact with the escape gear 42.

The stop ankle 53 will be described in detail.
As shown in FIGS. 4 to 6, the stop ankle 53 is arranged on the first rotation direction M1 side of the impact ankle 51 in a plan view, and includes an ankle true 90 and an ankle body 91 as rotation axes. Then, the stop ankle 53 rotates around the rotation axis O4 in a direction opposite to the rotation direction of the impact ankle 51 based on the rotation of the impact ankle 51.

The pallet fork 90 is arranged coaxially with the rotation axis O4, and is pivotally supported between the main plate 11 and the train wheel receiver (not shown). The pallet fork 90 is press-fitted into the pallet fork 91 from below, for example, and is integrally fixed to the pallet fork 91.

The ankle body 91 is formed in a plate shape by, for example, electroplating or MEMS technology. In the illustrated example, the ankle body 91 is formed in an arc shape so as to extend along the circumferential direction of the escape wheel 40. In the illustrated example, a plurality of lightening holes are formed in the ankle body 91.

The pallet fork 90 is fixed to the central portion of the pallet fork 91. The ankle body 91 is arranged below the ankle body 71 of the impact ankle 51 and is arranged on the same plane as the escape wheel 40.
Therefore, regarding the height relationship between the impact pallet fork 51, the stop pallet fork 53, and the escape wheel 40, the pallet fork body 91 for the escape wheel 40 and the stop pallet fork 53 is located at the lowest layer closest to the main plate 11 and above it. The pallet fork 71 of the impact pallet fork 51 is located.

However, the ankle body 91 of the stop ankle 53 may be arranged below the ankle body 71 of the impact ankle 51 and above the escape wheel 40. In this case, the first stop claw stone 62 and the second stop claw stone 63 are higher than the ankle body 91 to the extent that they reach the same height position as the escape gear 42, similarly to the first impact claw stone 60. You can extend it downward.

Of the ankle body 91, the peripheral end portion 91a located on the second rotation direction M2 side protrudes toward the second rotation direction M2 side and has a bifurcated engaging fork 92 branched in the circumferential direction of the rotation axis O4. Is formed. The engaging pin 77 of the impact ankle 51 is inserted inside the engaging fork 92. The outer peripheral surface of the engaging pin 77 and the inner surface of the engaging fork 92 are slidably engaged with each other. As a result, the impact pallet fork 51 and the stop pallet fork 53 are connected to each other so as to be relatively displaceable, and rotate in opposite directions.

A third claw stone holding portion 93 opened toward the escape wheel 40 side is provided in a portion of the pallet fork 91 located between the pallet fork 90 and the engaging fork 92. The third claw stone holding portion 93 holds the first stop claw stone 62 by utilizing this opening.
The first stop claw stone 62 is held in a state of protruding toward the escape wheel 40 side from the third claw stone holding portion 93. Of the protruding portion of the first stop claw stone 62, the side surface facing the M2 side in the second rotation direction is the first engaging surface 62a to which the working surface 43a of the escape tooth 43 of the escape gear 42 engages. It is said that. The first stop claw stone 62 functions as a so-called claw stone.

The first stop claw stone 62 is attached so that the first engaging surface 62a engages with the working surface 43a of the escape tooth 43 while having a predetermined pulling angle.

Of the ankle body 91, the peripheral end portion 91b located on the M1 side in the first rotation direction is provided with a fourth claw stone holding portion 94 opened toward the escape wheel 40 side. The fourth claw stone holding portion 94 uses this opening to hold the second stop claw stone 63.
The second stop claw stone 63 is held in a state of protruding toward the escape wheel 40 side from the fourth claw stone holding portion 94. Of the protruding portion of the second stop claw stone 63, the side surface facing the M2 side in the second rotation direction is the second engaging surface 63a to which the working surface 43a of the escape tooth 43 of the escape gear 42 engages. It is said that. The second stop claw stone 63 functions as a so-called claw stone.

In the second stop claw stone 63, similarly to the first stop claw stone 62, the second engaging surface 63a engages with the working surface 43a of the escape tooth 43 while having a predetermined pulling angle. It is attached to.

As described above, the stop ankle 53 configured in this way rotates around the rotation axis O4 based on the rotation of the impact ankle 51 that rotates based on the reciprocating rotation of the balance with hairspring 30. At this time, the first stop claw stone 62 and the second stop claw stone 63 alternately repeat entering and retreating with respect to the rotation locus R of the escape gear 42 by the rotation of the stop ankle 53.
As a result, the working surface 43a of the escape tooth 43 on the escape gear 42 is attached to the first engaging surface 62a of the first stop claw stone 62 or the second engaging surface 63a of the second stop claw stone 63. It becomes possible to engage with each other.

In particular, since the first stop claw stone 62 and the second stop claw stone 63 are arranged with the rotation axis O4 interposed therebetween, when the first stop claw stone 62 engages with the escape gear 42, When the second stop claw stone 63 disengages from the escape gear 42 and the first stop claw stone 62 disengages from the escape gear 42, the second stop claw stone 63 engages with the escape gear 42.

As described above, the pallet fork 50 is configured by connecting the impact pallet fork 51 and the stop pallet fork 53 so as to be connected to each other in a row, and the pallet fork 51 and 53 rotate separately based on the reciprocating rotation of the balance with hairspring 30. Displace to do. That is, the impact ankle 51 rotates in the direction opposite to the rotation direction of the balance with hairspring 30, and the stop ankle 53 rotates in the direction opposite to the rotation direction of the impact ankle 51.

In the case of the present embodiment, the impact pallet fork 51 and the stop pallet fork 53 both correspond to pallets located at the connecting ends of the pallet fork chain 50. Of these, the impact pallet fork 51 positions the impact pallet fork 51 and ankle chain when the first stop claw stone 62 and the second stop claw stone 63 engage with the escape gear 42 of the escape wheel 40. A regulatory section is formed to regulate the displacement of the entire 50.

That is, of the pallet fork 71 in the impact pallet fork 51, the outer surface 100 located on the side opposite to the outer surface facing the escape wheel 40 is arranged on the second rotation direction M2 side with respect to the pallet fork 70. By contacting the dote pin 102 of the above, the impact ankle 51 functions as the above-mentioned regulating portion for regulating and positioning the rotation of the impact ankle 51.
Similarly, of the pallet fork 72 in the impact pallet fork 51, the outer surface 101 located on the side opposite to the outer surface facing the escape wheel 40 is arranged on the first rotation direction M1 side with respect to the pallet fork 70. By coming into contact with the other dote pin 103, it functions as the above-mentioned regulating unit that regulates and positions the rotation of the impact ankle 51.
The pair of dotepins 102 and 103 are fixed so as to project upward from, for example, the main plate 11.

When the first stop claw stone 62 engages with the escape tooth 43 of the escape gear 42, the outer surface 100 of the pallet fork 71 contacts one of the dote pins 102 to position the impact pallet 51. Further, when the second stop claw stone 63 engages with the escape tooth 43 of the escape gear 42, the outer surface 101 of the ankle arm 72 contacts the other dote pin 103 to position the impact ankle 51. ..

(Operation of escapement)
Next, the operation of the escapement 13 configured as described above will be described.
In the operation start state in the following description, as shown in FIG. 4, the working surface 43a of the escape tooth 43 is engaged with the first engaging surface 62a of the first stop claw stone 62, and the impact is applied. The outer surface 100 of the pallet fork 51 is in contact with one of the dote pins 102, and the impact pallet fork 51 is positioned. As a result, the escape wheel 40 has stopped rotating. Further, the free vibration of the balance with hairspring 30 causes the flutter stone 38 to move clockwise and enter the inside of the ankle haco 74.

Further, the first impact claw stone 60 has already entered the rotation locus R of the escape gear 42. However, a gap is secured between the first impact surface 60a of the first impact claw stone 60 and the working surface 43a of the escape tooth 43, and the escape tooth 43 has a gap with respect to the first impact claw stone 60. It is said to be non-contact.

From such an operation start state, the operation of the escapement 13 accompanying the reciprocating rotation of the balance with hairspring 30 will be described step by step.

From the state shown in FIG. 4, when the balance with hairspring 30 is further rotated clockwise by the rotational energy (power) stored in the whiskers, the flutter stone 38 is placed on the inner surface of the pallet fork 74 rather than the flutter stone 38. It contacts and engages with the inner surface of the quail 73 side located on the traveling direction side, and presses the pallet fork 74 clockwise. As a result, the power from the hairspring is transmitted to the impact ankle 51 via the swing stone 38.
Since the small brim 37 and the sword tip 75 do not come into contact with each other when the pallet fork 74 and the swing stone 38 are engaged with each other, the power from the balance with hairspring 30 can be efficiently transmitted to the impact pallet fork 51.

As a result, as shown in FIG. 7, the entire pallet fork 50 is displaced so that the impact pallet fork 51 and the stop pallet fork 53 rotate respectively. That is, the impact ankle 51 rotates counterclockwise around the rotation axis O3, and the stop ankle 53 rotates clockwise around the rotation axis O4.

As the impact ankle 51 rotates, the outer surface 100 of the impact ankle 51 is separated from one of the dote pins 102. Further, when the stop ankle 53 rotates, the first stop claw stone 62 slides on the working surface 43a of the escape gear 43 and is separated from the escape gear 42 (the escape gear 42). It moves in the direction of retracting from the rotation locus R).
Then, the first stop claw stone 62 moves to a position slightly deviated from the rotation locus R of the escape gear 42, so that the first stop claw stone 62 is separated from the escape tooth 43 to perform escape. The engagement with the tooth 43 can be released. As a result, the stop of the escape wheel 40 can be released.

By the way, when the engagement between the escape tooth 43 and the first stop claw stone 62 is released, the first stop claw stone 62 has a pulling angle. Therefore, as shown in FIG. 7, the escape wheel 40 Momentarily retreats in the second rotation direction M2 (counterclockwise) instead of the first rotation direction M1 (clockwise) which is the original rotation direction. After undergoing this momentary retreat, the escape wheel 40 resumes rotation in the first rotation direction M1 by the power transmitted via the front wheel train 12.
In this way, by momentarily retracting the escape wheel 40, the engagement of the front train wheel 12 can be made more reliable, and the front wheel train 12 can be operated with stability and high reliability.

Then, as shown in FIG. 8, when the retracted escape wheel 40 resumes rotation in the first rotation direction M1, the first impact claw stone that has already entered the rotation locus R of the escape gear 42. The working surface 43a of the escape tooth 43 comes into contact (collision) with the first impact surface 60a of the 60.

As a result, the rotational force of the escape wheel 40 can be transmitted to the impact pallet fork 51, and the stag beetle 73 side of the inner surface of the pallet fork 74, which is located on the side opposite to the traveling direction of the stag beetle 38. The inner surface of the stag beetle 38 contacts and engages with the stag beetle 38. Therefore, the power transmitted to the escape wheel 40 can be indirectly transmitted to the balance sheet 30 via the impact ankle 51, and the impact ankle 51 can be continuously rotated so as to follow the swing stone 38. it can.
In this way, the power transmitted to the escape wheel 40 is indirectly transmitted to the balance wheel 30 via the impact ankle 51, so that the balance wheel 30 can be replenished with rotational energy.

When the escape wheel 43 comes into contact with the first impact claw stone 60 as described above, the escape tooth 43 rotates in the first rotation direction M1 so as to slide on the first impact surface 60a, and the first impact claw The stone 60 gradually moves away from the escape gear 42 (direction of retracting from the rotation locus R of the escape gear 42) as the impact ankle 51 rotates.
Then, when the first impact claw stone 60 moves to a position slightly deviated from the rotation locus R of the escape gear 42, the indirect impact on the balance with hairspring 30 described above is completed.
Further, when the first impact claw stone 60 is moving in the direction of detaching from the escape gear 42 due to the rotation of the impact pallet fork 51, the second stop claw stone 63 is moved by the clockwise rotation of the stop pallet fork 53. Enter the rotation locus R of the gear 42.

Immediately after the first impact claw stone 60 moves to a position deviated from the rotation locus R of the escape gear 42, as shown in FIG. 9, the first impact claw stone 60 has entered the rotation locus R of the escape gear 42. 2 The working surface 43a of the escape tooth 43 comes into contact with the second engaging surface 63a of the stop claw stone 63.
At this time, the impact pallet fork 51 moves toward the other dotepin 103 as it rotates counterclockwise, but at this stage, it is not in contact with the other dotepin 103. Therefore, the impact ankle 51 and the stop ankle 53 rotate slightly while the escape tooth 43 and the second stop claw stone 63 are in contact with each other.

Then, as shown in FIG. 10, when the outer surface 101 of the impact pallet fork 51 comes into contact with the other dote pin 103, the impact pallet fork 51 is positioned with its further rotation restricted. Therefore, the displacement of the entire ankle chain 50 is restricted, and the escape tooth 43 and the second stop claw stone 63 are engaged with each other. As a result, the escape wheel 40 stops rotating, and the ankle chain 50 stops.

After that, the swing stone 38 separates from the inside of the pallet fork 74 and separates from the impact pallet fork 51 as the balance with hairspring 30 rotates clockwise. After that, the balance with hairspring 30 continues to rotate clockwise due to inertia, and the rotational energy is stored in the hairspring. Then, when all the rotational energy is stored in the whiskers, the balance with hairspring 30 stops clockwise rotation, stands still for a moment, and then starts rotating counterclockwise by the rotational energy stored in the whiskers.
As a result, as shown in FIG. 11, the flutter stone 38 starts moving toward the impact pallet fork 51 as the balance with hairspring 30 rotates counterclockwise.

Then, as shown in FIG. 12, when the stag beetle 38 enters the stag beetle 74 of the impact pallet fork 51, the stag beetle 38 is located on the inner surface of the stag beetle 74 on the traveling direction side of the stag beetle 38. It contacts and engages with the inner surface on the stag beetle 73 side, and presses the pallet fork 74 counterclockwise. As a result, the power from the hairspring is transmitted to the impact ankle 51 via the swing stone 38.

As a result, the entire pallet fork 50 is displaced again so that the impact pallet fork 51 and the stop pallet fork 53 rotate respectively. That is, the impact ankle 51 rotates clockwise around the rotation axis O3, and the stop ankle 53 rotates counterclockwise around the rotation axis O4.

The second impact claw stone 61 gradually approaches the rotation locus R of the escape gear 42 after the balance with hairspring 30 starts to rotate counterclockwise, and the swing stone 38 turns counterclockwise with the pallet fork 74. When pressed against, as shown in FIG. 12, the escape gear 42 enters the rotation locus R of the escape gear 42.
However, at the stage where the second stop claw stone 63 and the escape tooth 43 are engaged and the outer surface 101 of the impact ankle 51 is in contact with the other dotepin 103, the second impact claw stone 61 is the second. A gap is secured between the impact surface 61a and the working surface 43a of the escape tooth 43. As a result, the escape tooth 43 is not in contact with the second impact claw stone 61.

The rotation of the impact ankle 51 separates the outer surface 101 of the impact ankle 51 from the other dotepin 103. Further, when the stop ankle 53 rotates, the second stop claw stone 63 slides on the working surface 43a of the escape gear 43 and is separated from the escape gear 42 (the escape gear 42). It moves in the direction of retracting from the rotation locus R). Then, the second stop claw stone 63 moves to a position slightly deviated from the rotation locus R of the escape gear 42, so that the second stop claw stone 63 is separated from the escape gear 42 and escapes. The engagement with the tooth 43 can be released. As a result, the stop of the escape wheel 40 can be released.

Further, similarly to the first stop claw stone 62, the second stop claw stone 63 has a pulling angle, so that the escape wheel 40 momentarily retreats in the second rotation direction M2 as shown in FIG. After that, the rotation is restarted in the first rotation direction M1 by the power transmitted through the front wheel train 12.

Then, as shown in FIG. 13, when the retracted escape wheel 40 resumes rotation in the first rotation direction M1, the second impact claw stone 61 that has entered the rotation locus R of the escape gear 42 The working surface 43a of the escape tooth 43 comes into contact (collision) with the second impact surface 61a.

As a result, the rotational force of the escape wheel 40 can be directly transmitted to the balance with hairspring 30 via the second impact claw stone 61, and the rotational energy can be replenished to the balance with hairspring 30. Further, the impact pallet fork 51 can be continuously rotated so as to follow the swing stone 38.

When the escape wheel 43 comes into contact with the second impact claw stone 61 as described above, the escape tooth 43 rotates in the first rotation direction M1 so as to slide on the second impact surface 61a, and the second impact claw The stone 61 gradually moves away from the escape gear 42 (direction of retracting from the rotation locus R of the escape gear 42) with the rotation of the balance with hairspring 30.
Then, as shown in FIG. 14, when the second impact claw stone 61 moves to a position slightly deviated from the rotation locus R of the escape gear 42, the direct impact on the balance with hairspring 30 described above is completed. ..

Further, when the second impact claw stone 61 is moving in the direction of being separated from the escape gear 42 by the rotation of the balance with hair wheel 30, the first stop claw stone 62 is rotated counterclockwise by the stop ankle 53 to cause cancer. Enter the rotation locus R of the gear 42.
Then, immediately after the second impact claw stone 61 moves to a position deviated from the rotation locus R of the escape gear 42, the first stop claw stone 62 that has entered the rotation locus R of the escape gear 42 is the first. 1 The working surface 43a of the escape tooth 43 comes into contact with the engaging surface 62a. At this time, the impact pallet fork 51 moves toward one dote pin 102 as it rotates clockwise, but at this stage, it is not in contact with one dote pin 102. Therefore, the impact ankle 51 and the stop ankle 53 rotate slightly while the escape tooth 43 and the first stop claw stone 62 are in contact with each other.

Then, as shown in FIG. 15, when the outer surface 100 of the impact ankle 51 comes into contact with one of the dote pins 102, the impact ankle 51 is positioned with its further rotation restricted. Therefore, the displacement of the entire ankle chain 50 is restricted, and the escape tooth 43 and the first stop claw stone 62 are engaged with each other. As a result, the escape wheel 40 stops rotating, and the ankle chain 50 stops.

After that, by repeating the above-mentioned operation with the reciprocating rotation of the balance with hairspring 30, the escapement 13 repeatedly engages and disengages the escape tooth 43 with the first stop claw stone 62 and the second stop claw stone 63. At the same time, power is transmitted to the balance with hairspring 30 by utilizing the contact between the escapement tooth 43 and the first impact claw stone 60 and the second impact claw stone 61. In particular, while alternately performing (switching) indirect power transmission using the first impact claw stone 60 and indirect power transmission using the second impact claw stone 61, the escape wheel 40 The transmitted power can be transmitted to the balance with hairspring 30.

Therefore, it can be operated as a so-called semi-direct impact type escapement 13 in which direct impact and indirect impact are used in combination, and stable operation and power transmission can be ensured.

In particular, according to the escape machine 13 of the present embodiment, unlike the conventional one in which the impact claw stone and the stop claw stone are incorporated in one common pallet fork, the impact pallet fork 51 uses the first impact claw stone 60. The stop pallet fork 53 has a first stop claw stone 62 and a second stop claw stone 63.
Therefore, the relative positions of the impact ankle unit 52 (impact ankle 51) with respect to the escape wheel 40 and the relative positions of the stop ankle unit 54 (stop ankle 53) with respect to the escape wheel 40 can be freely designed and arranged with less restrictions. It is possible to arrange the impact ankle unit 52 and the stop ankle unit 54 in the optimum layouts for impact and stop, respectively.

Here, the operation relationship between the stop ankle 53 and the escape wheel 40 will be described.
FIG. 16 shows the relationship between the center of rotation of the escape wheel 40 (that is, the rotation axis O2), the center of rotation of the stop ankle 53 (that is, the rotation axis O4), and the retreat angle of the escape wheel 40. ..
Although the escape wheel 40 is not shown in FIG. 16, the rotation locus R drawn by the tip of the escape wheel 43 is shown. Therefore, the rotation locus R corresponds to the outer diameter of the escape gear 42.

Further, in FIG. 16, the rotation center of the stop ankle 53 is arranged at a position separated by a distance L1 from the rotation locus R of the escape gear 42, and is separated by a distance L2 farther than the distance L1. The case where it is arranged at the position is shown.
In any of these cases, the first stop claw stone 62 moves to a position deviating from the engagement position X1 with which the escape wheel 43 is engaged and the rotation locus R of the escape gear 42. , It moves with the rotation of the stop ankle 53 between the release position X2 from which the engagement with the escape tooth 43 is released.

Further, the angle between the line segment connecting the first engaging surface 62a of the first stop claw stone 62 and the rotation center of the stop ankle 53 and the normal line with respect to the first engaging surface 62a is the pulling angle α1. Become. Further, the rotation angle of the stop ankle 53 required while the first stop claw stone 62 moves from the engagement position X1 to the release position X2 is the operating angle (or release angle) α2. Further, the retreat angle of the escape wheel 40 as the first stop claw stone 62 moves from the engagement position X1 to the disengagement position X2 is called a retreat angle α3.

Under the above-mentioned conditions, when the operating angle α2 is fixed to a predetermined value, what is the distance between the rotation center of the stop ankle 53 and the rotation locus R of the escape gear 42 in the retreat angle α3? Explain whether it affects.
As shown in FIG. 16, the rotation center of the stop ankle 53 is separated from the rotation locus R of the escape gear 42 by a distance L2, and the rotation center of the stop ankle 53 is the escape gear 42. When the stop ankle 53 is rotated by the same operating angle α2 in the state where the stop ankle 53 is separated from the rotation locus R by the distance L1, the retreat angle α3 is smaller at the distance L1 than at the distance L2. can do. That is, the retreat angle α3 can be made smaller when the rotation center of the stop ankle 53 is closer to the rotation locus R.

Therefore, by making the rotation center of the stop ankle 53 as close as possible to the rotation locus R of the escape gear 42, the retreat angle of the escape wheel 40 can be reduced, and the escape angle of the escape wheel 40 can be reduced. The energy required to release the stop (that is, the energy required to return the retracted escape wheel 40 to the original rotation direction) can be reduced.

Although the description has been focused on the first stop claw stone 62 in FIG. 16, the same applies to the second stop claw stone 63. Therefore, the optimum layout for stopping is to make the rotation center of the stop ankle 53 as close as possible to the rotation locus R of the escape gear 42 (that is, the outer diameter of the escape gear 42).

In particular, the operating angle of the pallet fork is a very important parameter for operating the escapement 13. In this regard, according to the present embodiment, the stop ankle 53 is not attached with the impact claw stone, but only the first stop claw stone 62 and the second stop claw stone 63, which are the stop claw stones, are attached. Therefore, the operating angle α2 of the stop pallet fork 53 can be set to the optimum angle by paying attention only to the action of the stop, and the rotation center of the stop pallet fork 53 is set to the rotation locus R side of the escape gear 42. It is possible to arrange the stop ankle 53 so that it approaches.
Therefore, according to the present embodiment, it is possible to reduce the energy required to release the stop of the escape wheel 40, improve the power transmission efficiency, and reduce the operation error.

Further, the operation relationship between the impact ankle 51 and the escape wheel 40 will be described.
FIG. 17 is a diagram showing a relationship when the escape tooth 43 of the escape gear 42 and the first impact claw stone 60 are in contact with each other. In FIG. 17, the tip of the escape tooth 43 and the first impact claw stone 60 will be described as being in contact with each other in a state close to line contact.

The operating angle α4, which is the rotation angle of the escape wheel 40 required from the start of contact between the escape tooth 43 and the first impact claw stone 60 to the end of contact, is, for example, the escape gear 42. Determined by the number of teeth. Then, based on the operating angle α4 of the escape wheel 40, the rotation angle of the impact ankle 51 required from the start of contact between the escape tooth 43 and the first impact claw stone 60 to the end of contact is obtained. A certain working angle α5 is also determined.
When power is efficiently transmitted from the escape wheel 40 to the first impact claw stone 60 by the contact between the escape tooth 43 and the first impact claw stone 60, for example, the pitch point in the meshing of the tooth portions is the same. It is preferable to transmit power at the pitch point P0 between the escape tooth 43 and the first impact claw stone 60.

The pitch point P0 is an action line connecting the contact point P1 at the start of contact between the escape tooth 43 and the first impact claw stone 60 and the contact point P2 at the end of contact, and the escape wheel. It corresponds to the intersection of the center of rotation of 40 (that is, the axis of rotation O2) and the center of rotation of the impact ankle 51 (that is, the center of rotation O3).

Then, when considering the transmission of power at the pitch point P0, the distance L3 between the center of rotation of the escape wheel 40 and the pitch point P0 and the distance L4 between the center of rotation of the impact ankle 51 and the pitch point P0 The ratio of, is determined.
In this case, the ratio of the distance L3 between the center of rotation of the escape wheel 40 and the pitch point P0 and the distance L4 between the center of rotation of the impact ankle 51 and the pitch point P0 is the escape wheel 40. It is a substantially inverse ratio with respect to the ratio of the operating angle α4 of the above and the operating angle α5 of the impact ankle 51. That is, the relationship is such that (L3 / L4) ≈ (α5 / α4) is almost satisfied.

Therefore, designing in this way provides the optimum layout for impact.
According to the present embodiment, the impact pallet fork 51 is not attached with a claw stone for stopping, and only the first impact claw stone 60, which is a claw stone for impact, is attached. Therefore, it is possible to set the operating angle of the impact ankle 51 to an optimum angle by paying attention only to the action of the impact. Therefore, the power transmitted to the escape wheel 40 can be efficiently and indirectly transmitted to the balance with hairspring 30.

As described above, according to the escapement 13 of the present embodiment, it is possible to design the escapement optimized for impact and stop, and it is possible to obtain an escapement having excellent power transmission efficiency and less operating error.
Further, the first impact claw stone 60 and the second impact claw stone 61 come into contact with the working surface 43a of the escape tooth 43, and the first stop claw stone 62 and the second stop claw stone 63 engage with each other. , The escape wheel 40 can have a single-layer structure. Therefore, it is possible to suppress an increase in the inertia of the escape wheel 40, which also improves the power transmission efficiency.

Further, when the escape wheel 43 is engaged with the first stop claw stone 62 or the second stop claw stone 63 and the rotation of the escape wheel 40 is stopped, that is, the swing stone 38 is separated from the pallet fork 74. When the balance with hairspring 30 is freely vibrating, the impact ankle 51 comes into contact with any of the pair of dote pins 102 and 103 using the outer surfaces 100 and 101. As a result, the impact ankle 51 located at the connecting end of the ankle chain 50 can be positioned, and the displacement of the entire ankle chain 50 can be regulated.

Therefore, for example, even if some disturbance is input while the balance with hairspring 30 is freely vibrating, it is possible to prevent the ankle chain 50 from rattling or vibrating. As a result, the escapement 13 can be operated stably.

In addition, since the escapement 13 of the present embodiment is a so-called semi-direct impact type escapement, the balance with hairspring 30 and the escape wheel 40 can be arranged at positions close to each other. Therefore, for example, when the escapement 13 of the present embodiment is applied to the tourbillon, it can contribute to the miniaturization of the carriage unit on which the mechanism including the escapement 13 is mounted. Therefore, the escapement 13 that is particularly suitable for the tourbillon can be used.

Further, according to the movement 10 and the timepiece 1 of the present embodiment, since the above-mentioned escapement 13 having excellent power transmission efficiency and little operation error is provided, a high-performance movement and timepiece with little time error can be obtained. ..

(Second Embodiment)
Next, the second embodiment according to the present invention will be described with reference to the drawings. In the second embodiment, the same parts as the components in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.
In the first embodiment, the impact ankle 51 is positioned by using a pair of dote pins 102 and 103, but in the second embodiment, the impact ankle 51 is positioned by using one dote pin. Further, in the first embodiment, the stop ankle 53 is arranged below the impact ankle 51, but in the second embodiment, the impact ankle 51 and the stop ankle 53 are arranged so as to be arranged on the same plane. There is.

As shown in FIGS. 18 and 19, the escapement 110 of the present embodiment is formed with a positioning hole 112 through which the dote pin 111 is inserted into the impact ankle 51.
In the impact pallet fork 51, a connecting piece 113 for connecting the pallet fork 71 and the first claw stone holding portion 76 is integrally formed between the pallet fork 71 and the first claw stone holding portion 76. The positioning hole 112 is formed in the connecting piece 113.
Specifically, the positioning hole 112 has a plan view arc shape that penetrates the connecting piece 113 in the thickness direction and extends along the rotation direction of the impact ankle 51 (that is, the direction that orbits around the rotation axis O3). Is formed in. The length (perimeter) of the positioning hole 112 along the circumferential direction of the rotation axis O3 is a state in which the first stop claw stone 62 and the escape tooth 43 of the escape gear 42 are engaged with each other, and the second It corresponds to the rotation angle (operating angle) at which the impact ankle 51 rotates between the state in which the stop claw stone 63 and the escape tooth 43 of the escape gear 42 are engaged with each other.

The dote pin 111 is arranged in the positioning hole 112 described above. The dote pin 111 is fixed to the main plate 11 and inserted into the positioning hole 112 from below. At this time, the outer peripheral surface of the dote pin 111 is in sliding contact with the inner peripheral surface of the positioning hole 112. As a result, the dote pin 111 relatively moves in the positioning hole 112 as the impact ankle 51 rotates.

At this time, since the length of the positioning hole 112 along the circumferential direction corresponds to the rotation angle of the impact ankle 51, as shown in FIG. 18, the first stop claw stone 62 and the escape tooth 43 When engaged, the first inner peripheral surface 112a located on the first impact claw stone 60 side of the inner peripheral surface of the positioning hole 112 and the dote pin 111 come into contact with each other. As a result, the impact ankle 51 is positioned by the dote pin 111.
Further, as shown in FIG. 19, when the second stop claw stone 63 and the escape tooth 43 are engaged with each other, the second inner circumference located on the ankle body 71 side of the inner peripheral surface of the positioning hole 112. The surface 112b and the dote pin 111 come into contact with each other. As a result, the impact ankle 51 is positioned by the dote pin 111.

Therefore, it is possible to position the impact ankle 51 even with one dote pin 111. The first inner peripheral surface 112a and the second inner peripheral surface 112b of the positioning hole 112 position the impact ankle 51 by contacting the dote pin 111, and function as a regulating unit that regulates the displacement of the entire ankle chain 50. To do.

In the present embodiment, since the impact pallet fork 51 and the stop pallet fork 53 are arranged on the same plane, the first stop claw stone 62 and the second stop claw stone 63 are positioned at the same height as the escape gear 42. It is held in a state of extending downward from the ankle body 91 to the extent that it reaches. Therefore, the first stop claw stone 62 and the second stop claw stone 63 can be engaged with and detached from the escape tooth 43.

Further, at the tip of the ankle arm 72 in the impact ankle 51, an engaging plate 115 formed in a circular shape in a plan view is formed instead of the engaging pin 77.
The engagement plate 115 is composed of a pair of elastic portions 116. The pair of elastic portions 116 are each formed in a semicircular shape in a plan view, and are urged so as to be separated from each other as shown by the arrows shown in FIGS. 18 and 19.

The ankle body 91 of the stop ankle 53 is arranged on the same plane as the ankle body 71 and the ankle arm 72 of the impact ankle 51 in a state where the engagement plate 115 is engaged inside the engagement fork 92. The outer peripheral surface of the engaging plate 115 and the inner surface of the engaging fork 92 are slidably engaged with each other. As a result, the impact pallet fork 51 and the stop pallet fork 53 are connected to each other so as to be relatively displaceable while being arranged on the same plane, and rotate in opposite directions.
In particular, the engaging plate 115 of the impact ankle 51 and the engaging fork 92 of the stop ankle 53 are connected to each other in a state where the outer peripheral surfaces of the pair of elastic portions 116 are pressed against the inner surface of the engaging fork 92. There is.

(Operation of escapement)
Even the escapement 110 of the present embodiment configured in this way can achieve the same effects as those of the first embodiment.
That is, even in the escape machine 110 of the present embodiment, the escaper 43 can alternately and repeatedly engage and disengage the first stop claw stone 62 and the second stop claw stone 63, and the first stop claw stone 63 can be repeatedly engaged and disengaged. It is possible to transmit the power transmitted to the escape wheel 40 to the balance sheet 30 while alternately performing indirect power transmission using the impact claw stone 60 and indirect power transmission using the second impact claw stone 61. it can.

Further, as shown in FIG. 18, when the escape tooth 43 and the first stop claw stone 62 are engaged, the first inner peripheral surface 112a of the positioning hole 112 comes into contact with the dote pin 111 and impacts. The ankle 51 is positioned. Further, as shown in FIG. 19, when the escape tooth 43 and the second stop claw stone 63 are engaged, the second inner peripheral surface 112b of the positioning hole 112 comes into contact with the dote pin 111 and impacts. The ankle 51 is positioned.
In either case, since the impact ankle 51 is an ankle corresponding to the connecting end of the ankle chain 50, the escape tooth 43 engages with the first stop claw stone 62 or the second stop claw stone 63. Therefore, when the rotation of the escape wheel 40 is stopped, the displacement of the entire ankle chain 50 can be regulated.

Therefore, even in the present embodiment, it is possible to prevent the ankle chain 50 from rattling or vibrating even if some disturbance is input while the balance with hairspring 30 is freely vibrating, for example. .. As a result, the escapement 110 can be operated stably.
In particular, unlike the first embodiment, only one dote pin 111 is required, and since the dote pin 111 can be arranged in the plane space of the impact ankle 51, the pair of dote pins 102 and 103 occupy the first embodiment. Spaces can be omitted or effectively used.

Further, the engaging plate 115 of the impact ankle 51 and the engaging fork 92 of the stop ankle 53 are connected to each other in a state where the outer peripheral surfaces of the pair of elastic portions 116 are pressed against the inner surface of the engaging fork 92. Therefore, it is possible to suppress the formation of a gap between the engaging plate 115 and the engaging fork 92. As a result, the impact pallet fork 51 and the stop pallet fork 53 can be connected to each other with less rattling.
Therefore, it is possible to effectively suppress the occurrence of backlash between the impact ankle 51 and the stop ankle 53, and the impact ankle 51 and the stop ankle 53 can be rotated responsively. .. As a result, the escapement 110 can be operated more smoothly, and the operating performance can be further improved.

In the second embodiment, the impact pallet fork 51 and the stop pallet fork 53 are connected so as to be relatively displaceable by engaging the engaging plate 115 and the engaging fork 92, but the present invention is not limited to this case. Instead, for example, the teeth may be connected by meshing with each other.

For example, in the escapement 120 shown in FIG. 20, a plurality of tooth portions 121 arranged along the rotation direction of the impact pallet fork 51 are arranged on the first claw stone holding portion 76 in the impact pallet fork 51 on the first rotation direction M1 side. It is formed toward. Correspondingly, at the peripheral end portion 91b of the ankle body 91 in the stop ankle 53, a plurality of tooth portions 122 that mesh with the tooth portions 121 on the impact ankle 51 side are provided instead of the engaging fork 92 of the second embodiment. It is formed. As a result, the impact pallet fork 51 is connected to the stop pallet fork 53 by meshing the tooth portions 121 and 122 with each other.

Even with the escapement 120 configured in this way, the same effects as those of the second embodiment can be achieved.

Although the embodiments of the present invention have been described above, these embodiments are presented as examples and are not intended to limit the scope of the invention. Each embodiment can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the gist of the invention. These embodiments and variations thereof include, for example, those that can be easily assumed by those skilled in the art, those that are substantially the same, those that have an equal range, and the like.

For example, in each of the above embodiments, the configuration in which the power of the royal fern housed in the barrel car is transmitted to the escape wheel is described as an example, but the present invention is not limited to this case. It may be configured so that power is transmitted from the royal fern to the escape wheel.

Further, in each of the above embodiments, the manual winding type movement in which the royal fern is manually wound by using the crown is used, but the present invention is not limited to this case, and for example, it may be a self-winding type movement equipped with a rotary weight. I do not care.

Further, in each of the above embodiments, the case where each claw stone of the impact claw stone and the stop claw stone is formed of an artificial jewel such as ruby has been described as an example, but the present invention is not limited to this case, and for example, other It may be formed of a brittle material or a metal material such as an iron-based alloy. Further, the nail stone may be integrally formed with the ankle by using a semiconductor material such as silicon by a semiconductor processing technique such as DeepRIE. In any case, the material, shape, etc. may be appropriately changed as long as the above-mentioned function as a nail stone can be achieved.

Further, in each of the above embodiments, the impact ankle unit is composed of one ankle, but the present invention is not limited to this case. For example, the impact ankle unit is composed of two or more ankles, and the first impact claw is attached to any one of the ankles. You can attach stones.
Similarly, in each of the above embodiments, the stop pallet fork is composed of one pallet fork, but the present invention is not limited to this case. May be attached respectively.

Further, in each of the above embodiments, the case where a single-layer structure escapement wheel is used has been described as an example, but the present invention is not limited to this case, and for example, the first escape gear and the second escapement gear are used. A double-layered escape wheel in which the gears are coaxially overlapped may be adopted, and the configuration may be similar to that of a so-called Coaxial escapement.

Even in this case, according to the present embodiment, since the impact pallet fork has the first impact pallet fork and the stop pallet fork has the first stop pallet fork and the second stop pallet fork. Impact pallets and stop pallets can be placed on the double-layered escape wheel so that the action is optimal. For example, it is configured so that the first impact claw stone attached to the impact ankle and the second impact claw stone attached to the balance with each other can come into contact with the escape teeth of the first escape gear. It can be configured so that the first stop claw stone and the second stop claw stone attached to the stop ankle can be engaged and disengaged with respect to the escape teeth of the second escape gear.
Therefore, for example, the same effect as that of the first embodiment can be achieved. However, in the case of a single-layer structure escape wheel as in each of the above embodiments, it is possible to suppress the increase in inertia of the escape wheel as compared with the case of the two-layer structure. It becomes easy to improve the power transmission efficiency.

1 ... Clock (mechanical clock)
4 ... Pointer 10 ... Movement (clock movement)
12 ... Front train wheel (wheel train)
13, 110, 120 ... Escapement 14 ... Governor 40 ... Gangster 51 ... Impact ankle (Uncle)
52 ... Impact ankle unit 53 ... Stop ankle (Uncle)
54 ... Stop ankle unit 60 ... 1st impact claw stone 61 ... 2nd impact claw stone 62 ... 1st stop claw stone (stop claw stone)
63 ... 2nd stop claw stone (stop claw stone)

Claims (3)

An escape wheel that rotates by the transmitted power,
It is equipped with an impact ankle unit and a stop ankle unit that are connected to each other so as to be relatively displaceable and rotate based on the rotation of the balance.
The stop ankle unit is composed of at least one ankle and has a stop claw stone that can be engaged with and detached from the escape gear of the escape wheel.
The impact pallet fork comprises at least one pallet fork and includes a first impact pallet that is accessible to the escape gear when the stop claw is not engaged.
A second impact claw stone that can be contacted with the escape gear when the first impact claw stone is not in contact is attached to the balance wheel.
The impact pallet fork has an impact pallet fork with the first impact claw stone.
The stop pallet fork has two stop claw stones and a stop pallet for which is relatively displaceably connected to the impact pallet fork.
An escapement in which the two stop claw stones are alternately engaged and disengaged with respect to the escape gear as the stop ankle rotates. The escapement according to claim 1 and
With the governor having the balance
A watch movement equipped with a train wheel that transmits power to the escape wheel. The watch movement according to claim 2 and
A timepiece comprising the escapement and a pointer that rotates at a rotational speed regulated by the speed governor.

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