CH713531A2 - Exhaust, timepiece movement and timepiece. - Google Patents

Abstract

The present invention aims to provide an exhaust which is excellent in terms of energy transmission. It provides an exhaust (13) having an exhaust movable (40) which rotates with energy transmitted thereto, an impact anchor unit (53) and a stop anchor unit (56) coupled to each other so as to be movable relative to each other and rotated on the basis of the rotation of a balance spring (30). Each of the units of the impact anchor unit (53) and the stop anchor unit (56) is formed by at least one or more anchors (51, 52, 55). The impact anchor unit (53) has stall vanes (60, 61) engageable with an escape wheel (42) of the escape wheel (40), and stopping anchor unit (56) has stall vanes (62, 63) engageable with and disengaged from the escape wheel (42) in the absence of mutual engagement between the escape wheel (42) and the impact vanes (60, 61).

Description

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to an escapement, a timepiece movement, and a timepiece. 2. DESCRIPTION OF THE PRIOR ART [0002] In general, a mechanical timepiece includes an escapement which transmits energy for rotating a balance-spring wheel in a reciprocating motion, and controls a Gear train with constant oscillation using the regular alternating rotation of the sprung balance. Escapes of this type have been developed conventionally, for example, while being improved several times. Currently, various types of exhausts are proposed.

For example, as an exhaust with high efficiency and high durability, the exhaust is known from a natural escapement invented by Breguet. The escapements of this type have the characteristic that the escapement includes two escapement wheels formed respectively by a wheel and a pinion, and alternately performs a direct impact and an indirect impact via an anchor on a balance-spring from the two. movable (ie the wheel & pinion) exhaust to transmit energy to the sprung balance.

In particular, unlike a crab anchor escapement which is most often used in the usual mechanical timepieces, this exhaust is designed to reduce the sliding of the ends of the mobile escapement during the impact. This eliminates wear on the ends of the mobile exhaust and improves durability. When the direct impact is made on the sprung balance, it is possible to transmit the impact from the mobile escapement sprung balance without passing through other components of the timepiece. Therefore, an improvement in efficiency is realized.

Furthermore, when the exhausts are classified roughly by focusing on the power transmission systems of the mobile exhaust (that is to say, the wheel and the exhaust pinion) to the sprung-balance, the exhausts are roughly classified roughly as a direct impact type for the direct transmission of energy from the escapement mobile to the balance spring, and a type of indirect impact for the transmission of energy indirectly from the escapement mobile to the balance-spring via other components of the timepiece such as an anchor. Exhaustions are also known that use both direct and indirect impact.

The sprung balance is a component of a timepiece constituting a speed controller and it is required to perform an alternating movement (oscillation) according to a predetermined oscillation cycle. Therefore, in general, a pivot of the sprung balance is formed extremely thinly in order to eliminate any deterioration of amplitude of the sprung balance due to friction etc. Therefore, when the sprung balance pivot is impacted from the outside, it is likely to be deformed or broken. It is conceivable that the accuracy is deteriorated accordingly, and that the sprung balance stops working.

Therefore, in order to prevent any deformation, breakage, or the like of the pivot of the sprung balance due to an impact from the outside, it adopts a bearing resistant to vibrations and shocks as bearing balance-spiral . When the sprung balance is impacted, the vibration and shock resistant bearing axially maintains the sprung balance while allowing it to move both in the axial direction and in the radial direction. As a result, the vibration and impact resistant bearing absorbs or reduces the impact applied to the pivot of the balance spring and ensures its impact resistance.

When the sprung balance is carried axially by the vibration-resistant bearing as described above, when energy is transmitted from the escapement to the sprung balance, the sprung-balance moves more or less according to the axial direction and in the radial direction. At that time, in the case of the direct impact type exhaust, because of the operation of the exhaust, the level of engagement between the end of the escapement and an impact pallet on the Spiral balance is often set at approximately several tens of micrometers. Therefore, at the moment of the beginning of the impact and at the end of the impact, the level of commitment decreases further.

Therefore, when energy is transmitted directly from the mobile escapement sprung-balance, if the sprung-balance moves, for example, in the radial direction under the action of the oscillation-resistant bearing, it is likely that the distance between the centers of the escapement mobile and the balance-spring changes, and the engagement of the end of the mobile escapement with the balance pallet of the balance spring becomes unstable or, in the worst of In this case, the end of the mobile escapement disengages from the impact pallet of the balance-spring. As a result, inconvenience can easily occur in the sense that it is difficult to ensure stable operation of the exhaust; moreover, the escape wheel rotates before the balance spring and it is difficult to transmit energy to the sprung balance.

In particular, when the escape wheel rotates before the sprung balance, the rotation of the escape wheel can not be stopped by an anchor stop pallet depending on a mutual phase relationship between the escape mobile and the anchor. It is also likely that a sudden change of frequency is caused, for example, and that the timepiece suddenly starts to advance.

On the other hand, in the case of an indirect-impact type escapement which indirectly transmits the energy of the escapement mobile to the balance-spring, even when the balance-spiral moves, for example, in the radial direction under the action of the oscillation-resistant bearing, inconvenience occurs less easily because, as in the crab anchor escapement, a safety measure is sometimes provided to allow the anchor and balance-spring return to the same relative position as that in which these elements were before they moved.

For example, patent document 1 (JP-A-2008-268209) discloses an indirect impact type escapement comprising a first anchor and a second anchor arranged so that they can engage with a mobile. exhaust and disengage. The inconvenience explained above appear less easily in this exhaust either. In such an escapement, the first anchor is able to rotate depending on the rotation of a sprung balance. The first anchor includes a first stopping pallet and a second stopping pallet capable of engaging with and disengaging from one end of the escape wheel, and comprising a first impact pallet capable of coming into play. contact with the end of the mobile escape. The second anchor makes it possible to turn on the base of the pivoting of the first anchor. The second anchor comprises a second impact pallet capable of coming into contact with the end of the escape wheel.

In an escapement whose configuration corresponds to that of the patent document 1 described above, for example, in the state where the first stopping pallet is engaged with the end of the mobile escapement (which corresponds to to a state in which the rotation of the escape wheel is stopped), when the first anchor is pushed by a sprung balance plate pin - acting as a pin pulse - and rotates on the basis of the rotation of the balance- spiral, the first stop pallet emerges from the end of the mobile escape. Consequently, since the first stopping pallet and the end of the escape wheel are no longer in mutual engagement, the escape wheel starts to rotate using the energy supplied by a train of gear.

Immediately after, the second anchor pivots according to the rotation of the first anchor. The second impact pad encroaches on the path traveled by the end of the escape wheel during its rotation. Therefore, the end of the exhaust movable, which begins its rotation, comes into contact (in collision) with the second impact pallet. Thus, it is possible to indirectly transmit the energy, which is transmitted to the escape wheel, to the sprung balance via the second anchor and the first anchor, and it is possible to provide rotational energy to the sprung balance.

Then, when the first anchor and the second anchor rotate further, the second stop pallet encroaches on the rotation path taken by the end of the mobile escapement while the second impact pallet emerges from the end of the mobile escape. As a result, the end of the mobile escapement engages with the second stop pallet, and the rotation of the escapement mobile stops.

Then, the sprung balance continues to rotate inertia and the plateau pin separates from the first anchor. When the rotational energy of the sprung balance is fully stored in a hairspring, the hairspring instantly stops, and then begins to turn in the opposite direction using the rotational energy stored in the hairspring.

Then, the first anchor is pushed again by the sprung balance plate pin and thus brought to rotate in the opposite direction on the basis of the rotation of the sprung balance. The second stopping pallet emerges from the end of the mobile escapement. Consequently, since the second stopping pallet and the end of the escape wheel are no longer in mutual engagement, the escape wheel restarts its rotation using the energy of the gear train.

Immediately after, the second anchor rotates in the opposite direction according to the pivoting of the first anchor, and the first impact pad impinges on the rotation path taken by the end of the mobile escapement. Therefore, the end of the escapement mobile, which begins its rotational movement, comes into contact (in collision) with the first impact pallet. Thus, as explained above, it is possible to indirectly transmit the energy, which is transmitted to the escape wheel, to the balance spring via the first anchor. It is possible to provide rotational energy to the sprung balance.

Subsequently, when the first anchor and the second anchor rotate further, the first stop pallet encroaches on the rotation path taken by the end of the mobile exhaust, while the first impact pallet emerges from the end of the mobile escape. Therefore, the end of the escapement mobile engages with the first stopping pallet, and the rotation of the escapement mobile stops. Then, the series of cycles explained above is repeated.

However, in a conventional escapement, the first anchor comprises the first stop pallet, the second stop pallet, and the first impact pallet. Therefore, these pallets move integrally with the first anchor, according to the pivoting of the latter. Thus, it is difficult to arrange the stop pallets (the first stop pallet and the second stop pallet) individually to stop the escape wheel and the stop pallet (the first stop pallet), with which the mobile escapement collides, according to optimal arrangements according to the design of the stopping and impact pallets.

The exhaust is explained in detail below.

When the exhaust is designed, the stopping action exerted on the mobile escapement and the impact action on the mobile exhaust are different. Therefore, it is required to individually arrange the stop pallets and the stop pallet in states close to optimal configurations that effectively achieve stop action and impact action.

The optimum design for the stopping pallets is considered to be a design in which the pivoting center of the anchor is disposed as close as possible to the outer diameter of the mobile exhaust, ie, the tip of the teeth of the mobile exhaust.

Usually, when the stopping pallets engage with the end of the mobile escapement, the stopping pallets engage with the toothing of the mobile escapement in a state in which the stopping pallets are inclined at a predetermined angle of approach relative to the contact surface of one of the teeth. This ensures a constant frictional force between the stopping vanes and the contact surface of the tooth to achieve a stable mutual engagement without slipping on the contact surface.

Since the angle of inclination is arranged on the anchor, when the stopping vanes are released from the end of the movable exhaust depending on the pivoting of the anchor, it is possible that the mobile of exhaust retracts instantly, and turns in the opposite direction. The retraction of the escape wheel is considered a movement necessary to ensure better gearing of the gear train including the escapement and to obtain a safe braking force of the anchor.

It will be noted that the pivoting angle of the anchor required to pass from the state in which the stopping pallets are engaged with the toothing of the mobile escapement to the state in which the pallets of stopping are released from the end of the movable exhaust is commonly called "working angle" (or release angle). The retraction angle is commonly referred to as the angle by which the end of the escapement retracts according to the clearance of the stopping vanes.

As explained above, the retraction of the mobile escapement as a result of the action of the engagement movement of the stopping pallets is considered to be a necessary and important movement in mechanical timepieces. On the other hand, as the retraction angle increases, the energy required to release the stopping state of the mover also increases (ie, the energy required to return the escape wheel in its original direction of rotation from its retracted state).

When the energy required for the release of the stopping state of the mobile escapement increases, a deterioration of the efficiency and an aggravation of the errors are more and more likely to be noted for the exhaust . That is why when the stopping pallets are engaged with the mating surface of the end of the muffler at a predetermined inclination angle, it is required to make the muffler retract by setting the retraction angle as the smallest possible. It is known that, for a given predetermined tilt angle, the retracting angle increases all the more as the center of pivoting of the anchor is remote from the end of the escape wheel.

Thus, as explained above, the optimal design for the stop pallets is considered to be a configuration in which the pivot center of the anchor is disposed at a position as close as possible to the end of the pallet. mobile exhaust.

The optimal design for the impact pallets is considered to be a configuration according to which the ratio between, on the one hand, the distance between the center of rotation of the mobile escapement and a high gear point between the end of the tailstock and the stop pallet, and, secondly, the distance between the center of pivoting of the anchor and the high point of gearing between the end of the mobile escapement and the stopping pallet is substantially a reverse relationship to that between the working angle of the mobile escapement and the working angle of the stopping pallet.

It may be noted that the working angle of the escapement mobile actually corresponds to the rotation angle of the escapement mobile required between the moment when the end of the mobile escapement is brought to come into contact with the stop pallet until the end of the escape wheel is clear of the stop pallet. The working angle of the anchor corresponds to a pivoting angle of the anchor between the moment when the end of the escapement has come into contact with the stop pallet until the end the escape wheel is released from the stop pallet.

For example, as a gearing point between toothed sections, the high point of the end of the mobile escapement and that of the stop pallet is equivalent to the intersection of a line of work connecting an initial point of contact at the moment the end of the escapement engages the stop pallet, and a final point of contact at the time of its release, and a center line connecting the center of rotation the escape mobile with the pivot center of the anchor.

In a conventional exhaust, the first stop pallet, the second stop pallet, and the first stop pallet are fully incorporated into the first anchor, as explained above. Thus, it is difficult to focus respectively only on the stopping pallets or on the impact pallet, and to be able to individually arrange the stopping pallets and the impact pallet in optimal configurations as described above. .

[0034] Please note that, in order to be able to arrange the stopping pallets and the impact pallet respectively in optimal configurations, for example, as for a conventional coaxial escapement, it is also conceivable to form the escape mobile according to a so-called double-layer structure in which the first escapement mobile for the stop and the second escape mobile for the impact are superposed one above the other around the same axis, with a different diameter for the first mobile exhaust and the second mobile exhaust.

However, in this case, since the mobile exhaust has a double layer structure, another problem occurs with the increase in the inertia of the entire mobile exhaust, which deteriorates its dynamic efficiency. .

SUMMARY OF THE INVENTION

The present invention has been conceived in view of such circumstances, and an object of the present invention is to provide an escapement, a timepiece movement, and a timepiece that are excellent in terms of quality. energy transmission efficiency.

(1) The exhaust according to the present invention comprises an escapement mobile which rotates thanks to the energy transmitted to it; an impact anchor unit and a stop anchor unit coupled to each other while remaining movable relative to each other to pivot on the basis of the rotation of a sprung balance. The impact anchor unit and the stop anchor unit each consist of one or more anchors. The impact anchor unit includes an impact pallet that can be brought into contact with the escape mobile, and the stop anchor unit includes a stopping pallet engageable with and escape from the escape wheel in the absence of contact of the latter with the impact pallet.

According to the present invention, it is possible to rotate respectively, on the basis of pivoting (in a reciprocating movement in alternating rotation) of the balance spring, the impact anchor unit and the stop anchor unit, which are coupled to each other so as to be movable relative to each other. By rotating the impact anchor, it is possible to bring the stopping pallet into contact (colliding) with the escape wheel and it is possible to indirectly transmit energy, which had been previously transmitted to the escapement mobile, to the balance spring via the impact anchor unit. As a result, it is possible to provide rotational energy to the balance spring. By rotating the stop anchor unit, in the absence of contact of the escape wheel with the stop pallet, it is possible to engage the stop pallet with the escape wheel. to stop the rotation of the mobile escape or release the stop pallet in engagement with the escape wheel of the latter to release the escape mobile from its shutdown state.

Thus, it is possible to indirectly transmit energy, which is transmitted to the mobile escape, the balance spring. It is possible to control the rotation of the mobile escapement so that it has a constant oscillation corresponding to that of the balance spring.

In particular, unlike conventional exhausts in which the impact pallet and the stopping pallet are incorporated in a common anchor, the impact anchor unit comprises only the impact pallet and the unit. Anchor stop only includes the stop pallet. Thus, it is possible to respectively configure and dispose freely, with fewer restrictions, the relative positions of the impact anchor unit and the stop anchor unit relative to the mobile escape. It is possible to arrange the impact anchor unit and the stop anchor unit in configurations respectively optimal for impact and for stopping.

Thus, for example, it is possible to arrange the anchors configuring the stop anchor unit as close as possible to the escape wheel and to reduce the angle of the escape wheel. Therefore, it is possible to reduce the amount of energy required to release the mover from its shutdown state, improve efficiency in terms of power transmission, and reduce operating errors. For example, it is also possible to set respectively the working angles of the anchors forming the impact anchor unit and the anchors forming the stop anchor unit to optimal values for both impact and for the stop. It is possible to improve the transmission efficiency even more.

In addition, it is possible to ensure that both the stop pallet and the stop pallet act on the escape wheel. Therefore, it is not necessary that the escape wheel is formed in a double layer structure. It is possible to form the escape mobile in a single layer structure. Therefore, it is possible to prevent any increase in the inertia of the mobile escape. Thus, it is also possible to improve the efficiency of energy transmission accordingly.

[0043] (2) The impact anchor unit may comprise a first impact anchor and a second impact anchor coupled to each other so as to be movable relative to one another. the other. Both the first impact anchor and the second impact anchor may include a stopping pallet.

[0044] (3) The first impact anchor and the second impact anchor may be coupled so that when an impact anchor of the first impact anchor and the second impact anchor rotate in the same direction as that of rotation of the escape wheel, the other impact anchor rotates in the opposite direction to that of rotation of the escape wheel.

In this case, it is possible to ensure that, on the basis of the rotation of the balance spring, the stop pallet of the first impact anchor and the stop pallet of the second anchor. impact are brought alternately into contact (in collision) with the escape wheel. It is possible to indirectly efficiently transmit the energy, which is supplied to the entrance of the escape wheel, to the balance spring. It is possible to configure the impact anchor unit as a unit with two anchors, ie the first impact anchor and the second impact anchor. It is possible to have the first impact anchor and the second impact anchor respectively in optimal configurations for the impact. Therefore, independently of the colliding impact anchor, it is possible to efficiently transmit the power to the balance spring.

(4) The stop anchor unit may comprise a first stop anchor and a second stop anchor respectively coupled to the impact anchor unit so as to be able to move relative to each other. to the latter; each of the first stop anchor and second stop anchor comprises a stop pallet.

(5) The first stop anchor and the second stop anchor may be coupled so that when one anchor among the first stop anchor and the second stop anchor rotate in the same direction than that of rotation of the mobile escapement, the other anchor rotates in the opposite direction to that of rotation of the mobile escape.

In this case, it is possible to alternately engage the stop pallet of the first stop anchor and the stop pallet of the second stop anchor with the escape wheel on the basis of the rotation of the spiral balance. It is possible to control the rotation of the escape wheel. It is possible to form a stop anchor unit so that it has two anchors, i.e., the first stop anchor and the second stop anchor. It is possible to have the first stop anchor and the second stop anchor respectively in optimal configurations for stopping. Thus, independently of the anchor that stops the rotation of the mobile escape, it is possible to reduce the amount of energy required to release the mobile escape from its shutdown state. It is possible to improve the quality of energy transmission.

(6) A movement for a timepiece according to the present invention comprises: an escapement; a speed controller including the balance spring; and a gear train that transmits energy to the escape wheel.

[0050] (7) A timepiece according to the present invention comprises: the movement for a timepiece; and a needle that rotates at the speed of rotation regulated by the exhaust and the speed regulator.

In this case, since the timepiece and the movement for a timepiece include an exhaust which is excellent in terms of energy transmission efficiency and has fewer operating errors, it is possible to producing a movement for a timepiece and a corresponding timepiece that have less gaps and have a high performance.

Thus, according to the present invention it is possible to provide an escapement, a timepiece movement, and a timepiece that are excellent in terms of efficiency in the transmission of energy.

BRIEF DESCRIPTION OF THE DRAWINGS

[0053]

Fig. 1 is a view from outside of a timepiece representing a first embodiment according to the present invention.

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

Fig. 3 is a perspective view of a double plate of a sprung balance shown in FIG. 2.

Fig. 4 is a plan view of an exhaust shown in FIG. 2.

Fig. 5 is a sectional view of the exhaust taken along a line A-B shown in FIG. 4.

Fig. 6 is a sectional view of the exhaust taken along a line A-C shown in FIG. 4.

Fig. 7 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which a first stopping pallet begins to disengage from an escape gear from the state illustrated in FIG. 4.

Fig. 8 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which the first stopping pallet has disengaged from the escape gear from the state illustrated in FIG. 7.

Fig. 9 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which the exhaust gear is in contact with a first impact pad from the state illustrated in FIG. 8.

Fig. 10 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which the first impact pallet has disengaged from the exhaust gear from the state illustrated in FIG. 9.

Fig. 11 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which the exhaust gear begins to come into contact with a second stop pallet from the state illustrated in FIG. 10.

Fig. 12 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which a restriction lever comes into contact with a limiting pin from the state illustrated in FIG. 11, and wherein the escape gear and the second stop pallet engage with each other.

Fig. 13 is an explanatory diagram of the operation of the escapement and is a diagram showing a state in which a plateau pin moves to a first impact anchor from the state illustrated in FIG. 12.

Fig. 14 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which the second stopping pallet begins to disengage from the escape gear from the state illustrated in FIG. 13.

Fig. 15 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which the second stopping pallet has disengaged from the escape gear from the state illustrated in FIG. 14.

Fig. 16 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which the exhaust gear is in contact with the second impact pad from the state illustrated in FIG. 15.

Fig. 17 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which the second impact pad has disengaged from the escape gear from the state illustrated in FIG. 16.

Fig. 18 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which the exhaust gear begins to come into contact with the first stop exhaust stone from the state shown in FIG. 17.

Fig. 19 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which the restriction lever comes into contact with the limiting pin from the state illustrated in FIG. 18 and the exhaust gear and the first stop pallet are in mutual engagement.

Fig. 20 is a diagram for explaining an optimal configuration for stopping and is a diagram showing a relation among a center of rotation of an escape wheel, a center of pivoting of a stopping anchor, and a retracting angle of the mobile escape.

Fig. 21 is a diagram for explaining an optimal configuration for the impact and is a diagram showing a relationship between the escapement gear of the escapement car and the first impact pallet which are in contact with each other.

Fig. 22 is a plan view of an escapement showing a second embodiment according to the present invention.

Fig. 23 is a plan view of an exhaust showing a third embodiment according to the present invention.

Fig. 24 is a plan view of the exhaust passing from a state shown in FIG. 23 to a state in which the escape gear and the second stop pallet are in mutual engagement.

Fig. 25 is a plan view of an exhaust showing a fourth embodiment according to the present invention.

Fig. 26 is a plan view of the exhaust passing from a state shown in FIG. 25 to a state in which the escape gear and the second stop pallet are in mutual engagement.

Fig. 27 is a plan view of an escapement showing a fifth embodiment according to the present invention.

Fig. 28 is a plan view of the exhaust passing from a state shown in FIG. 27 to a state in which the escape gear and the second stop pallet are in mutual engagement.

DESCRIPTION OF THE EMBODIMENTS

[First Embodiment] [0054] A first embodiment according to the present invention is detailed below with reference to the drawings. It may be noted that, in this embodiment, the mechanical timepiece is given as an example for a timepiece. In the drawings, the component scales are adjusted as needed to meet the need to display the components in visually recognizable sizes.

[0056] (Basic configuration of the timepiece) Generally, reference is made to a part body including a control part of a timepiece as being a "movement". One refers to the state of a completed product obtained by attaching a dial and a needle to motion and housing the movement in a timepiece case as being "the whole" of the timepiece.

Among the two sides of the platen forming a substrate of the timepiece, reference is made to the side on which the glass of the timepiece case is present (that is to say, the side on which the dial is present) as the "back side" of the movement. On both sides of the platen, reference is made to the side on which a caseback of the timepiece case is present (i.e., the opposite side of the dial) as the "front side" some movement.

Please note that in the following explanation of this embodiment, the direction from the dial towards the bottom of the case is defined as upward (upward) and the opposite direction is defined as descending (to the bottom).

As illustrated in FIG. 1, the entire timepiece 1 according to this embodiment includes, in a timepiece case comprising a bottom not shown and a mirror 2, a movement (the timepiece movement according to the present invention). invention) 10, a dial 3 having a scale indicating information concerning at least the hour, and needles 4 including an hour hand 5, a minute hand 6, and a second hand 7.

As illustrated in FIG. 2, the movement 10 comprises a plate 11 forming a substrate. Please note that in fig. 2, part of the motion-configuring components 10 is not shown for the sake of clarity for the parts shown.

The movement 10 comprises, on the front side of the plate 11, a front gear train (the gear train according to the present invention) 12, an exhaust 13 which controls the rotation of the gear train before 12, and a speed controller 14 which regulates the speed of the exhaust 13.

The front gear train 12 comprises mainly a movement cylinder 20, a center mobile 21 (that is to say a wheel and a center gear), a third mobile 22 (that is to say say a third wheel and a third pinion integral with each other), and a seconds mobile 23 (that is to say a second wheel and a second pinion integral with each other). The movement barrel 20 is supported axially between the plate 11 and a not shown barrel bridge. A barrel spring (not shown) (constituting a source of energy) is housed inside the movement barrel 20. A ratchet wheel 24, through which the spring can be raised, can be rotated. Note that the ratchet wheel 24 rotates following the rotation of a not shown winding stem, coupled to a ring 25 shown in FIG. 1.

The center mobile 21, the third mobile 22, and the mobile seconds 23 are held axially between the plate 11 and a not shown gear train bridge. When the movement cylinder 20 rotates under the impulse of the elastic return force of the spring which has been raised, the center mobile 21, the third mobile 22, and the seconds mobile 23 are rotated in this order on the base of the rotation of the barrel.

In other words, the center mobile 21 meshes with the movement barrel 20 and rotates on the basis of the rotation of the movement barrel 20. Please note that, when the center mobile 21 rotates, a not shown barrel pinion also rotates on the basis of this rotation. The minute hand 6 shown in FIG. 1 is fixed to the cannon pinion. The minute hand 6 displays the current minute ("minute") according to the rotation of the cannon pinion. The minute hand 6 performs a complete revolution at a rotational speed regulated by the exhaust 13 and the speed regulator 14, i.e., in one hour.

When the center mobile 21 rotates, a not shown minute wheel rotates on the basis of this rotation. In addition, a not shown hour wheel rotates on the basis of the rotation of the minute wheel. Note that the minute wheel and the hour wheel are timepiece components forming the front gear train 12. The hour hand 5 shown in FIG. 1 is attached to the hour wheel. The hour hand 5 displays the current time ("hour") according to the rotation of the hour wheel. The hour hand 5 performs a complete revolution at a rotational speed regulated by the exhaust 13 and the speed controller 14, for example, in twelve hours.

The third mobile 22 meshes with the center mobile 21 and rotates on the basis of the rotation of the center mobile 21. The second mobile 23 meshes with the third mobile 22 and rotates on the basis of the rotation of the third mobile 22. The second hand 7 shown in FIG. 1 is attached to the seconds mobile 23. The seconds hand 7 displays the current second ("second") as a function of the rotation of the second mobile 23. The seconds hand 7 performs a complete revolution at a rotational speed regulated by the exhaust 13 and the speed regulator 14, for example, in one minute.

An escape wheel 40 as explained below meshes with the seconds mobile 23 via an exhaust pinion 41. Therefore, the energy of the spring housed in the movement barrel 20 is transmitted to the mobile exhaust system 40 essentially via the center mobile 21, the third mobile 22, and the seconds mobile 23. Therefore, the escapement mobile 40 rotates about an axis of rotation 02.

The speed regulator 14 mainly comprises a balance spring 30.

The spring balance 30 comprises a balance shaft 31, a balance wheel 32, and a spiral spring not shown. The spring balance 30 is held axially between the plate 11 and a not shown pendulum bridge. The sprung balance 30 rotates in reciprocating back and forth movements (i.e. rotates in the normal direction and in the opposite direction) around the axis of rotation 01 with an amplitude (that is ie a constant oscillation angle), corresponding to the output torque of the movement barrel 20 using the hairspring as energy source.

Conical posts are formed at both ends of the balance shaft 31 in the axial direction. The balance shaft 31 is held axially between the plate 11 and the balance bridge via the tenons. The rocker wheel 32 is formed in one piece mounted on the outside and fixed to the rocker shaft 31. An inner end of the hairspring is fixed to the rocker shaft 31 via a ferrule not shown.

Note that, in the example shown in this figure, in the balance wheel 32, four arms 33 are arranged at a 90-degree interval centered on the axis of rotation 01. However, the number, the layout, and the shape of the arms 33 are not limited to those of this example and can be changed freely.

A double annular plate 35 is mounted outside the balance shaft 31, and fixed thereto as shown in FIG. 3.

The double plate 35 includes a large collar 36 and a small collar 37 located below (on the side of the plate 11) of the large collar 36. A plateau pin 38 formed of an artificial gem such as a ruby is, for example, hunted in a large collar 36 and fixed in the latter.

The plate pin 38 has a semicircular shape in a plan view and is formed such that it extends downwardly from the large collar 36. The plate pin 38 makes movements of rotary reciprocating around the axis of rotation 01 following those of the spring balance 30, and engages with and reciprocally emerges from a fork 74, as explained below, halfway in the movement of rotation.

The small collar 37 has a smaller diameter than the diameter of the large collar 36. In the small collar 37, a lunar recess 39 in the form of a crescent-shaped notch facing inwards in the radial direction is arranged in a position corresponding to that of the plate pin 38. The lunar recesses 39 function as an exhaust section which prevents a stinger 75 - as explained below - to come into contact with the small collar 37 when the fork 74 and the plateau pin 38 are in mutual engagement.

[0077] Please note that in the drawings other than fig. 3, the small collar 37 and the plateau pin 38 of the double plate 35 are essentially shown for the sake of clarity for the drawings.

(Configuration of the exhaust) As shown in Figure 4, the exhaust 13 comprises the double plate 35 as explained above, the exhaust mobile 40 (that is, say the wheel & the exhaust pinion) which is rotated by the energy transmitted from the mainspring of the barrel, a chain of anchors 50, a first impact pallet (the impact pallet according to the present invention) 60 and a second impact pallet (the impact pallet according to the present invention) 61, and a first stop pallet (the stop pallet according to the present invention) 62 and a second stop pallet (the stop pallet according to the present invention) 63.

[0080] Please note that the double plate 35 is a component forming part of both the sprung balance 30 and the speed regulator 14 as explained above, and is also a component forming part of the exhaust 13.

The escape wheel 40 (that is to say the wheel and the exhaust pinion) is formed according to a single layer structure including the exhaust pinion 41 which meshes with the mobile seconds 23 and the escape wheel 42 having a plurality of exhaust gear teeth 43. The escapement wheel 40 is held axially between the plate 11 and the gear train deck (not shown). Please note that in drawings other than fig. 2, the exhaust pinion 41 is not illustrated.

In the example shown in this figure, the number of exhaust gear teeth 43 is eight. However, the number of exhaust gear teeth 43 is not limited to such a configuration and can be changed as needed. The escape wheel 42 may comprise an escape gear toothing 43 of, for example, six teeth, ten teeth, or twelve teeth.

According to this embodiment, an example is explained in which the escapement wheel 40, seen according to a plan view of the movement 10 from the front side, as illustrated in FIG. 4, rotates clockwise about the axis of rotation 02 thanks to the energy transmitted from the mobile seconds 23 via the exhaust pinion 41.

Please note that in fig. 4, reference is made to the direction of rotation in the clockwise direction about the axis of rotation O2 as constituting the first direction of rotation M1, and the opposite direction is referred to as constituting the second direction of rotation. direction of rotation M2. In addition, reference is made to the rotation path R drawn by the tip of the escape gear toothing 43 during rotation of the escapement wheel 40 as being merely the rotation path R followed by the escape wheel 40.

In the escape gear teeth 43, the lateral surface facing the first direction of rotation M1 is shaped as a working surface 43a which comes into contact with the first impact pad 60 and the second paddle. 61, and with which the first stop pallet 62 and the second stop pallet 63 engage.

Note that the escape wheel 40 is formed by, for example, a metal material or a material having a crystalline orientation such as monocrystalline silicon. Examples of a manufacturing method for the escapement mobile 40 include electrofusion, 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 for the mobile 40 exhaust are not limited to the case explained below and can be modified as needed. A reduction in the weight of the escapement 40 can be achieved by performing a lightening hole or by providing a refined portion in the exhaust mobile 40 as required, in proportions that do not affect the performance, stiffness, etc. of the escape wheel 40. In the example shown in the figure, a plurality of lightening holes is made in the escape wheel 40.

The chain of anchors 50 is configured so that it couples a plurality of anchors to each other, while they can move relative to each other, and which are connected in series one after the other. The chain of anchors 50 moves in such a manner that it individually pivots (oscillates) the plurality of anchors on the basis of the alternating rotation of the balance-spring 30 in a back and forth motion.

Specifically, the anchor chain 50 includes an impact anchor unit 53 including a first impact anchor 51 and a second impact anchor 52, as well as a stop anchor unit 56. comprising a stop anchor 55. The impact anchor unit 53 and the stop anchor unit 56 are coupled to each other while being movable relative to each other. 'other.

In other words, the first impact anchor 51 and the second impact anchor 52 are coupled to each other, but can move relative to each other. The first impact anchor 51 and the stop anchor 55 are coupled to each other while being movable relative to each other. Therefore, the stop anchor 55, the first impact anchor 51, and the second impact anchor are coupled to each other by being connected in series.

[0091] Please note that the impact anchor unit 53 and the stop anchor unit 56 must only be formed by at least one or more anchors. According to this embodiment, as explained above, the impact anchor unit 53 is formed by two anchors, and the stop anchor unit 54 is formed by a single anchor.

The first impact pallet 60 and the second impact pallet 61 may be brought into contact with the working surface 43a of the escape gear teeth 43 of the escape wheel 42, and are configured as energy transmission pallets, passing the one that has been transmitted to the escapement wheel 40 to the balance spring 30. Among the first impact pallet 60 and the second impact pallet 61, it is the first impact pallet 60 which is attached to the impact anchor 51; the second impact pallet 61 is attached to the second impact pallet 52.

The first stop pallet 62 and the second stop pallet 63 may engage with and disengage from the working surface 43a of the escape gear teeth 43 of the escape wheel 42, and are arranged as pallets to both stop the escape wheel 40 and release it from its shutdown state. Each of the first stop pallet 62 and the second stop pallet 63 are attached to the stop anchor 55.

[0094] Please note that the first impact pad 60 and the second impact pad 61 come into contact with the escape wheel 42 in the absence of engagement of the first stop pallet 62 and the second paddle 63. The first stop pallet 62 and the second stop pallet 63 engage, that is, engage, with the escape wheel 42, in the absence of contact with the first impact pallet 60 with the second impact pallet 61. The pallets are formed of an artificial gem such as a ruby, such as the plateau pin 38.

In what follows, the impact anchor 51 is explained in detail.

As shown in FIGS. 4 to 6, the first impact anchor 51 is disposed between the escape wheel 40 and the rocker shaft 31 in a plan view, and includes an anchor shaft 70, which is a rotating shaft, a body an anchor arm 72. The first impact anchor 51 rotates about a pivot axis 03 on the basis of the alternating rotation of the balance spring 30.

The anchor axis 70 is disposed coaxially with respect to the pivot axis 03, and is held axially between the plate 11 and the gear train bridge (not shown). In the example illustrated in the figure, the anchor axis 70 is arranged such that it is located on a center line connecting the axis of rotation 02 of the escapement wheel 40 and the axis of rotation 01 spiral balance according to a plan view. The anchor pin 70 is driven away and fixed in a base of the anchor body 71, for example, from top to bottom (platinum side 11) and integrally fixed to a base of the anchor body 71.

The anchor body 71 and the anchor arm 72 are formed integrally in a tabular form, for example, by electrofusion or via the MEMS technique. The anchor body 71 and the anchor arm 72 are arranged above the escape wheel 40.

[0099] Please note that, as for the escapement mobile 40, a reduction of the weight of the anchor body 71 and the anchor arm 72 can be achieved by making lightening holes or portions refined in the body anchor 71 and the anchor arm 72 as required. In the example shown in the figure, pluralities of lightening holes are formed in the anchor body 71.

The anchor body 71 is designed so that it extends from the base, to which the anchor axis 70 is fixed, in the direction of the balance spring 30 in the radial direction of the An anchor pin 70. A pair of horns 73 disposed side by side in the circumferential direction of the pivot axis 03 is provided at the distal end of the anchor body 71. The interior of the horns 73 opens towards the balance shaft 31, and is designed to form the fork 74 in which the plate pin 38, moving in the alternating rotation of the balance-spring 30, is housed so as to engage with these last and clear them.

The stinger 75 is attached to the distal end of the anchor body 71.

The stinger 75 is attached to the distal end of the anchor body 71 from the top by, for example, driving or the like. The stinger 75 is located between the pair of horns 73 (i.e., within the fork 74) in a plan view and extends so as to project beyond the horns 73. to the balance shaft 31. In the state where the plateau pin 38 is disengaged from the fork 74, the distal end of the stinger 75 faces a portion excluding the lunar recess 39 of the outer circumferential surface of the small flange 37 with a slight clearance in the radial direction. In the state where the plateau pin 38 is engaged in the fork 74, the distal end of the stinger 75 is housed in the lunar recess 39.

[0103] Please note that when the plateau pin 38 is disengaged from the fork 74, the distal end of the stinger 75 faces the outer circumferential surface of the small collar 37 with a small spacing in the radial direction. Therefore, for example, even if a disturbance occurs during the free oscillation of the sprung balance 30, and the stopping of the entire chain of anchors 50 is released under the influence of such disturbance, it is possible to first put the distal end of the stinger 75 in contact with the outer circumferential surface of the small flange 37. Therefore, it is possible to eliminate the displacement of the impact anchor 51 due to the perturbation. It is thus possible to prevent the entire anchor chain 50 from being released from its stopped state. Please note that the anchor chain stop 50 is explained in detail below.

A first pallet holding portion 76 is arranged in the base of the anchor body 71 so as to protrude from the opposite side with respect to the axis of rotation 03 in the radial direction of the anchor body 71. The first pallet holding portion 76 is open towards the escape wheel 40 and holds the first impact pallet 60 using this opening.

The first impact pallet 60 is maintained in a state in which it projects further towards the escapement wheel 40 than the first holding part of the pallet 76. A lateral surface facing the second direction of rotation M2 in a projection portion of the first impact pallet 60 is designed to form a first impact surface 60a with which the working surface 43a of the toothing of the escape gear 43 of the escape wheel 42 comes in contact.

Furthermore, an engagement pin 77 is arranged prominently at the base of the anchor body 71, and is directed in the first direction of rotation M1. In the example shown in the figure, the engagement pin 77 is of a thickness equal to that of the anchor body 71 and has a circular shape in a plan view.

The anchor arm 72 is designed such that it extends from the base of the anchor body 71 towards the second direction of rotation M2. An engagement fork 78 having a fork shape whose branches extend in the circumferential direction of the axis of rotation 03 is formed at the distal end of the anchor arm 72.

The impact anchor 51 configured in this manner pivots on the basis of the rotation of the balance spring 30 as explained above.

Specifically, the first impact anchor 51 is rotated about the pivot axis 03 in the opposite direction to that of the rotation of the balance spring 30 by the plate pin 38, which moves together with the alternating rotation of the sprung balance 30. At this moment, the first impact pallet 60 repeats forward and retracting movements with respect to the rotation path R of the escape wheel 42 according to the direction of rotation. pivoting of the first impact anchor 51. Therefore, it is possible to cause the working surface 43a of the escape gear teeth 43 of the escape wheel 42 to come into contact (in collision) with the first impact surface 60a of the first impact pallet 60.

The second impact anchor 52 is explained in detail hereinafter.

The second impact anchor 52 is further disposed in the second direction of rotation M2 relative to the first impact anchor 51 in a plan view, and includes an anchor axis 80, which is a rotary shaft. , and an anchor body 81. The second impact anchor 52 rotates about an axis of rotation 04 in a direction opposite to that of the first impact anchor 51 based on the rotation of the first anchor. impact 51.

The anchor shaft 80 is coaxially disposed with the axis of rotation 04 and is supported axially between the plate 11 and the not shown gear train bridge. The anchor axis 80 is driven, for example, from the bottom, and is integrally fixed to the anchor body 81.

The anchor body 81 is formed to take a tabular form, for example, by electrofusion or via the MEMS technique. In the example shown in the figure, the anchor body 81 is formed to extend along the circumferential direction of the escapement wheel 40. It should be noted that a weight reduction of the body of anchor 81 may be made by arranging a lightening hole or a thin portion in the anchor body 81 as appropriate.

The anchor pin 80 is attached to a circumferential end 81b of the anchor body 81 located in the second direction of rotation M2. It should be noted that the anchor body 81 is disposed above the anchor body 71 of the first impact anchor 51. In other words, the anchor body 81 of the second impact anchor 52 is disposed above the exhaust mobile 40.

A downwardly extending engagement pin 82 is attached by driving or the like to a circumferential end portion 81a of the anchor body 81 located in the first direction of rotation M1. The engagement pin 82 takes the form, for example, of a massive column. The lower end of the engagement pin 82 penetrates inside the engagement fork 78 of the first impact anchor 51. The outer circumferential surface of the engagement pin 82 and the inner surface of the fork engagement members 78 are slidably engaged with each other.

Therefore, the first impact anchor 51 and the second impact anchor 52 are coupled to each other so as to be movable relative to each other, and they rotate in opposite directions with respect to each other.

At the circumferential end 81b of the anchor body 81, a second pallet holding section 83 is provided; it projects in the direction of the escape wheel 40. The second pallet holding section 83 is open towards the escape wheel 40 and holds the second impact pallet 61 using this opening.

The second impact pallet 61 is maintained in a state in which the second impact pallet 61 projects more towards the escapement wheel 40 with respect to the second pallet holding section 83. A lateral surface facing the second direction of rotation M2 at a projecting portion of the second impact pallet 61 is formed as a second impact surface 61a, with which the working surface 43a of the escape gear 43 in the escape wheel 42 comes into contact.

As explained above, the second impact anchor 52 configured in this way pivots about the axis of rotation 04 on the basis of the pivoting of the first impact anchor 51, which rotates it according to the alternating rotation of the spring balance 30. At this moment, the second impact pallet 61 repeats a movement of encroachment on the rotation path R of the escapement wheel 40, and of retraction with respect thereto following the pivoting of the second impact anchor 52. Therefore, it is possible to cause the working surface 43a of the escape gear 43 of the escape wheel 42 to come into contact (collide) with the second surface. impact 61a of the second impact pallet 61.

In particular, the first impact anchor 51 and the second impact anchor 52 are coupled so that they rotate in opposite directions. Consequently, when an impact anchor of the first impact anchor 51 and the second impact anchor 52 rotate in the same direction as that of the rotation of the escape wheel 40, the other impact anchor rotates. in the opposite direction to that of rotation of the escapement wheel 40. Consequently, the second impact pallet 61 disengages from the escape wheel 40 when the first impact pallet 60 comes into contact with the escape wheel 42. The second impact pallet 61 comes into contact with the escape wheel 40 when the first impact pallet 60 emerges from the escape wheel 42.

[0121] It should be noted that, according to this embodiment, the first impact anchor 51 and the second impact anchor 52 are coupled to rotate in opposite pivoting directions. However, the first impact anchor 51 and the second impact anchor 52 are not limited to such a configuration and could be coupled to rotate in the same direction.

In what follows, the stop anchor 55 is described in detail.

The stop anchor 55 is arranged more in the first direction of rotation M1 than the first impact anchor 51 in a plan view, and it comprises an anchor axis 90, which is a rotary shaft, and an anchor body 91. The stop anchor 55 rotates about an axis of rotation 05 in the opposite direction to that of pivoting the first impact anchor 51 based on the rotation of the first anchor impact 51.

The anchor axis 90 is disposed coaxially with respect to the axis of rotation 05 and held axially between the plate 11 and the gear train bridge (not shown). The anchor pin 90 is driven, for example, from the bottom, and integrally fixed to the anchor body 91.

The anchor body 91 is formed in a tabular form, for example by electrofusion or thanks to the MEMS technique. In the example shown in the figure, the anchor body 91 has an arcuate shape which extends along the circumferential direction of the escapement wheel 40. It should be noted that the weight of the body anchor 91 by arranging a lightening hole or a thin portion in the anchor body 91 where appropriate.

The anchor pin 90 is fixed to the central part of the anchor body 91. It should be noted that the anchor body 91 is disposed in a position equivalent to the anchor body 71 of the first anchor In other words, the anchor body 91 of the stop anchor 55 is disposed above the escape wheel 40.

Therefore, the relative positioning in height between the first impact anchor 51, the second impact anchor 52, the stop anchor 55, and the escape wheel 40 is as follows: 40 is located in the bottom layer closest to the plate 11, the anchor body 71 of the first impact anchor 51 and the anchor body 91 of the stop anchor 55 are located at above the escape wheel 40, and the anchor body 81 of the second impact anchor 52 is located above the anchor body 71 and the anchor body 91.

An engagement fork 92 having a forked shape projecting towards the second direction of rotation M2 and bifurcating in the circumferential direction of the pivot axis 05 is formed at a circumferential end 91a located in the anchor body 91 in the second direction of rotation M2. The engagement plate 77 of the first impact anchor 51 is engaged within the engagement fork 92. The outer circumferential surface of the engagement plate 77 and the inner surface of the engagement fork 92 are slidably engaged with each other. Therefore, the first impact anchor 51 and the stop anchor 55 are coupled to each other so that they can move relative to each other, and they pivot in directions opposed to each other.

In a part located between the anchor axis 90 and the engagement fork 92 in the anchor body 91, a third pallet holding portion 93 is provided, which is open towards the moving part. Exhaust 40. The third pallet holding portion 93 holds the first stop pallet 62 using this opening.

The first stop pallet 62 is maintained in a state in which it projects further towards the escapement wheel 40 than the third pallet holding portion 93. A side surface facing the second direction of rotation M2 in a projection portion of the first stop pallet 62 constitutes a first engagement surface 62a, with which the working surface 43a of the escape gear toothing 43 of the escape wheel 42 engages that is to say, comes into mutual engagement. Note that the first stop pad 62 functions as a palette commonly referred to as an input paddle.

Note that the first stop pallet 62 is fixed such that the first engagement surface 62a engages with the working surface 43a of the escape gear teeth 43 in a state where the first stop pallet 62 forms a predetermined angle of incidence therewith.

At a circumferential end 91b located in the first direction of rotation M1 in the anchor body 91, a fourth pallet holding portion 94 open to the escapement wheel 40 is provided. The fourth pallet holding portion 94 holds the second stopping pallet 63 using this aperture.

The second stopping pallet 63 is maintained in a state in which it projects further towards the escapement wheel 40 than the fourth pallet holding portion 94. A lateral surface facing the second direction of rotation M2 in a projection part of the second stop pallet 63 constitutes a second engagement surface 63a with which the working surface 43a of the toothing of the escape gear 43 in the escape wheel 42 engages. Note that the second stopping pallet 63 functions as a pallet commonly referred to as an output pallet.

Note that, like the first stop pallet 62, the second stop pallet 63 is fixed so that the second engagement surface 63a engages with the working surface 43a of the toothing. escape gear 43 in a state where the second stopping pallet 63 forms a predetermined angle of incidence therewith.

As explained above, the stop anchor 55 configured in this manner rotates about the pivot axis 05 on the basis of the pivoting of the first impact anchor 51, which turns it on the basis of the alternating rotation of the sprung balance 30. At this moment, the first stopping pallet 62 and the second stopping pallet 63 advance beyond the rotation path R of the escapement wheel 40 and retract below the latter in the direction of pivoting of the stop anchor 55.

Therefore, it is possible to engage the work surface 43a of the escape gear teeth 43 of the escape wheel 42 with the first engagement surface 62a of the first pallet stop 62 or the second engagement surface 63a of the second stopping pallet 63.

In particular, the first stop pallet 62 and the second stop pallet 63 are disposed on either side of the pivot axis 05. Therefore, the second stop pallet 63 is disengaged from the mobile exhaust 40 when the first stop pallet 62 engages with the mobile escape 40. The second stop pallet 63 engages with the escape wheel 42 when the first stop pallet 62 is released from the escape wheel 42.

As explained above, the anchor chain 50 is formed by coupling the first impact anchor 51,1a second impact anchor 52, and the stop anchor 55 so that they are connected to one another in series. The anchors 51, 52 and 55 are moved in such a way that they pivot individually on the basis of the alternating rotation of the balance spring 30. In other words, the first impact anchor 51 rotates in the opposite direction to that of rotation of the 30. The second impact anchor 52 and the stop anchor 55 respectively rotate in the opposite direction to that of the first impact anchor 51.

Please note that the second impact anchor 52 and the stop anchor 55 are equivalent to an anchor located at the coupling end of the anchor chain 50. In the second impact anchor 52 is A restriction lever 85 positions the second impact anchor 52 and limits the movement of the entire anchor chain 50 when the first stop pallet 62 and the second stop pallet 63 are engaged with the escape wheel 42 of the escape wheel 40.

The restriction lever 85 is formed so as to project from the circumferential end 81b of the anchor body 81 towards a direction away from the escapement wheel 40. The restriction lever 85 is able to restrict the pivoting the second impact anchor 52 and positioning the second impact anchor 52 by contacting limiting pins 86 and 87 disposed on both sides on either side of the restriction lever 85.

A pair of limiting pins 86 and 87 is fixed so as to project, for example, from the plate 11 upwards. A limiting pin 86 is arranged such that it is located more in the second direction of rotation M2 with respect to the restriction lever 85. The other limiting pin 87 is arranged so that it is located more in the first direction of rotation M1 with respect to the restriction lever 85.

When the first stop pallet 62 comes into engagement with the escape wheel 42 of the escape wheel 40, the restriction lever 85 is brought into contact with the limiting pin 86 situated in the second direction of rotation. M2 and positions the second impact anchor 52. When the second stop pallet 63 engages with the escape wheel 42 of the escape wheel 40, the restriction lever 85 is brought into contact with the locking pin 87 located in the first direction of rotation M1 and positions the second impact anchor 52.

[0143] (Operation of the exhaust) [0144] In what follows, it explains the operation of an exhaust 13 configured as explained above.

Please note that, in the following explanations, at the beginning of operation as shown in FIG. 4, the working surface 43a of the escape gear teeth 43 is engaged with the first engagement surface 62a of the first stop pallet 62 and the restriction lever 85 is in contact with the limiting pin 86, defining the positioning of the second impact pallet 52. Therefore, the rotation of the escape wheel 40 is stopped. In addition, the plate pin 38 moves in a clockwise direction according to the free oscillation of the balance-spring 30 and advances towards the inside of the fork 74.

The operation of the exhaust 13 according to the alternating rotation of the sprung balance 30 is explained sequentially from such an operating state.

When the spring balance 30 continues to rotate in the direction of clockwise thanks to the rotational energy (power) stored in the spring from the state shown in FIG. 4, the plate pin 38 comes into contact and engages with the inner surface of the horns 73 located in the direction of its progression at the inner surface of the fork 74, and abuts against the fork 74 in the direction clockwise. Therefore, the spiral energy is transmitted to the first impact anchor 51 via the plateau pin 38.

[0148] Please note that the small flange 37 and the stinger 75 are not brought into mutual contact during the engagement of the fork 74 with the plate pin 38. Therefore, it is possible to transmit the energy efficiently. from the balance-spring 30 to the first impact anchor 51.

Therefore, as shown in FIG. 7, the entire complete anchor chain 50 moves in such a way that the first impact anchor 51, the second impact anchor 52 and the stop anchor 55 respectively pivot.

In other words, the first impact anchor 51 rotates in the counterclockwise direction about the pivot axis 03, the second impact anchor 52 rotates in the direction of clockwise around the pivot axis 04, and the stop anchor 55 rotates clockwise about the pivot axis 05.

When the second impact anchor 52 pivots, the restriction lever 85 separates from the limiting pin 86. When the stop anchor 55 pivots, the first stop pallet 62 moves in a direction allowing the release of the escapement wheel 40 (a direction of retraction relative to an incursion inside the rotation path R of the escapement wheel 40) by sliding on the working surface 43a of the escape gear 43 .

As illustrated in FIG. 8, the first stopping pallet 62 moves to a position slightly diverging from the rotation path R of the escapement wheel 40. It is then possible to separate the first stopping pallet 62 from the tooth gear of FIG. 43 and escape the first pallet stop 62 of the exhaust gear 43. Therefore, it is possible to release the escapement 40 from its shutdown state.

Moreover, when the escape gear teeth 43 and the first stop pallet 62 are no longer in mutual engagement, because of the angle of incidence of the first stop pallet 62, as represented in FIG. 7, the escapement wheel 40 retracts instantaneously in the second direction of rotation M2 (in a counter-clockwise direction) rather than the first direction of rotation M1 (in the direction of clockwise), which is the original direction of rotation. After the instantaneous retraction, the escape wheel 40 resumes its rotation in the first direction of rotation M1, as illustrated in FIG. 8, thanks to the energy transmitted via the front gear train 12.

With the instant retraction of the escapement wheel 40 in this way, it is possible to ensure a safer gear with the front gear train 12. It is thus possible to operate the front gear train. 12 stably and with high reliability.

When the first stopping pallet 62 moves in the direction of disengagement with respect to the escapement wheel 40 in the pivoting direction of the stopping anchor 55, as illustrated in FIGS. 7 and 8, the first impact pallet 60 encroaches on the rotation path R of the escapement wheel 40 as a function of the pivoting of the first impact anchor 51.

However, since, as explained above, the mobile escapement instantly retracts through the first impact paddle 62, and rotates in the second direction of rotation M2, at that time, the toothing exhaust gear 43 and the first stop pallet 62 are brought into contact.

As shown in FIG. 8, when the retracted exhaust wheel 40 resumes its rotation in the first direction of rotation M1, just after, as illustrated in FIG. 9, the working surface 43a of the escape gear teeth 43 is brought into contact (in collision) with the first impact surface 60a of the first impact pad 60 which encroaches on the rotation path R of the exhaust mobile 40.

Therefore, it is possible to transmit the rotational force of the escapement wheel 40 to the first impact anchor 51. The inner surface of the horns 73 on the inner surface of the fork 74 located upstream of the direction of progress of the plate pin 38 comes into contact with the plate pin 38 and engages with the latter. Consequently, it is possible to indirectly transmit the energy, which is transmitted to the escapement wheel 40, to the balance-spring 30 via the first impact anchor 51.11. It is possible to continue to rotate the first impact anchor 51 so that it follows the plateau pin 38.

By indirectly transmitting the energy, which is transmitted to the escapement wheel 40, to the sprung balance 30 via the first impact anchor 51 in this manner, it is possible to provide a rotational energy to the sprung balance. 30.

When the escape gear teeth 43 are brought into contact with the first impact pallet 60 as explained above, the escape gear teeth 43 rotate in the first direction of rotation M1 and slide on the first impact surface 60a. The first impact pallet 60 moves gradually in the direction of clearance of the escapement wheel 40 (the direction retracting from an encroachment inside the rotation path R of the escapement wheel 40) according to the direction pivoting the first impact anchor 51.

As illustrated in FIG. 10, when the first impact pallet 60 moves to reach a position slightly deviating from the rotation path R of the escapement wheel 40, the indirect impact on the balance spring 30 explained above ends.

When the first impact pallet 60 moves in the direction of disengagement with respect to the escapement wheel 40 as a function of the pivoting direction of the first impact anchor 51, as illustrated in FIG. 10, the second stopping pallet 63 advances to encroach on the rotation path R of the escapement wheel 40 following the pivoting of the stopping anchor 55 in the direction of clockwise.

Immediately after the first impact pallet 60 has moved to a position remote from the rotation path R of the escapement wheel 40, as shown in FIG. 11, the working surface 43a of the toothing of the escape gear 43 is brought into contact with the second engagement surface 63a of the second stop pallet 63 which encroaches on the rotation path R of the moving wheel. exhaust 40.

At this moment, the restriction lever 85 moves towards the other limiting pin 87 in accordance with the pivoting of the second impact anchor 52 in the direction of clockwise. However, at this point, the restriction lever 85 is configured not to be in contact with the other limiting pin 87. Therefore, the stop anchor 55, the second impact anchor 52 and the first anchor impact 51 respectively turn slightly while the escape gear teeth 43, and the second stop pallet 63 remain in contact.

As shown in FIG. 12, when the restriction lever 85 comes into contact with the other limiting pin 87, the second impact anchor 52 can not perform additional rotational movement and is thus positioned. As a result, the movement of the entire anchor chain 50 is restricted and the escape gear teeth 43 and the second stopping pallet 63 are caused to be in a state of engagement. that is, mutual control. Therefore, the rotation of the escape wheel 40 stops.

Then, the plate pin 38 is disengaged from the inside of the fork 74 and separates from the first impact anchor 51 following the rotation of the balance spring 30 in the direction of clockwise. Then, the sprung balance 30 continues to rotate clockwise by inertia. Rotational energy of the sprung balance 30 is stored in the hairspring. When all the rotational energy is stored in the hairspring, the hairspring 30 stops its rotation in a clockwise direction, goes into neutral for a moment, and a rotation in the opposite direction of the needles. a watch then starts under the impulse of the rotational energy stored in the spiral.

[0167] Thus, as shown in FIG. 13, the plateau pin 38 begins a movement to approach the first impact anchor 51 following the rotation of the balance spring 30 in the direction of clockwise.

As shown in FIG. 14, when the plate pin 38 advances inwardly of the fork 74 of the first impact anchor 51, the plate pin 38 comes into contact and engages with the inner surface of the horns 73 further downstream in the direction of progression of the plateau pin at the inner surface of the fork 74, and exerts a pressure against the fork 74 in the counterclockwise direction. Therefore, the spiral energy is transmitted to the impact anchor 51 via the plate pin 38.

The entire anchor chain 50 is then moved again so that the first impact anchor 51, the second impact anchor 52, and respectively the stop anchor 55 are pivoted. In other words, the first impact anchor 51 rotates clockwise around the pivot axis 03, the second impact anchor 52 rotates counterclockwise around the pivot axis 04, and the stop anchor 55 rotates counterclockwise about the pivot axis 05.

When the second impact anchor 52 rotates, the restriction lever 85 separates from the other locking pin 87. When the stop anchor 55 rotates, the second stop pallet 63 moves into the direction of clearance of the escapement wheel 40 (the direction of retraction relative to the rotation path R of the escapement wheel 40) to slide on the working surface 43a of the escape gear 43. As shown in FIG. . 15, the second stopping pallet 63 moves to a position slightly diverging from the rotation path R of the escapement wheel 40. Then, it is possible to separate the second stopping pallet 63 from the gear wheel. exhaust 43 and escape from the second pallet stop 63 of the exhaust gear 43. Therefore, it is possible to release the escapement 40 from its shutdown state.

Like the first stopping pallet 62, the second stopping pallet 63 has an angle of incidence. Therefore, as shown in FIG. 14, after an instantaneous retraction in the second direction of rotation M2, the escapement wheel 40 continues its rotation in the first direction of rotation M1, as illustrated in FIG. 15, thanks to the energy transmitted by the gear train 12 before.

When the second stopping pallet 63 moves in the direction of clearance of the escapement 40 following the pivoting of the stop anchor 55, as shown in FIG. 14 and FIG. 15, the second impact pallet 61 encroaches on the rotational path R of the escapement wheel 40 following the anti-clockwise pivoting of the second impact anchor 52.

However, the escapement mobile 40 retracts instantly, as explained above, under the action of the second stopping pallet 63, and rotates in the second direction of rotation M2. Therefore, at this point, the escape gear 43 and the second stop pallet 63 are not brought into contact.

As shown in FIG. 16, when the retracted movable wheel 40 begins to rotate in the first direction of rotation M1, the working surface 43a of the escape gear 43 comes into contact (in collision) with the second impact surface 61a of the second impact pad 61 which encroaches on the rotation path R of the escapement wheel 40.

Therefore, it is possible to transmit the rotational force of the escape wheel 40 to the first impact anchor 51 via the second impact anchor 52. The inner surface of the horns 73 located further downstream than the Anchor plate 38 with respect to the direction of advancement of the latter within the fork 74 comes into contact with the plate pin 38 and engages with the latter. Consequently, it is possible to indirectly transmit the energy, which is transmitted to the escapement wheel 40, to the balance-spring 30 via the second impact anchor 52 and the first impact anchor 51. It is possible to make continuously rotating the first impact anchor 51 so that it follows the plateau pin 38.

By indirectly transmitting the energy, which is transmitted to the escapement wheel 40, to the sprung balance 30 via the second impact anchor 52 and the first impact anchor 51 in this way, it is possible to provide a rotation energy to the balance-spring 30.

When the escape gear 43 comes into contact with the second impact pallet 61 as explained above, the escape gear 43 rotates in the first direction of rotation M1 and slides on the second surface of the engine. 61a impact. The second impact pallet 61 moves gradually in the direction of clearance of the escapement wheel 40 (the direction of retraction of the rotation path R of the escapement wheel 40) following the pivoting of the second impact anchor 52.

[0178] As illustrated in FIG. 17, when the second impact pallet 61 moves to reach a position slightly deviating from the rotation path R of the escape wheel 40, the indirect impact on the balance spring 30 explained above ends.

When the second impact pallet 61 moves in the release direction of the escapement wheel 40 following the pivoting of the second impact anchor 52, as shown in FIG. 17, the first stop pallet 62 encroaches on the rotational path R of the escapement wheel 40 following the anti-clockwise pivoting of the stop anchor 55.

Immediately after, the second impact pallet 61 moves in a position deviating from the rotation path R of the escapement wheel 40, as shown in FIG. 18, and the working surface 43a of the escape gear 43 comes into contact with the first engagement surface 62a of the first stop pallet 62, which encroaches on the rotation path R of the escape wheel 40.

At this time, the restriction lever 85 moves towards a limiting pin 86 following the counterclockwise pivoting of the second impact anchor 52. However, at this stage, the restriction lever 85 is positioned such that it is not in contact with a limiting pin 86.

Therefore, the stop anchor 55, the first impact anchor 51, and the second impact anchor 52 respectively rotate slightly while the escape gear 43 and the first stop pallet 62 stay in touch. As shown in FIG. 19, when the restriction lever 85 comes into contact with a limiting pin 86, the second impact anchor 52 can no longer rotate further and position itself. As a result, the movement of the entire chain of anchors 50 is limited and the escape gear 43 and the first stop pallet 62 enter a state of mutual engagement. Therefore, the rotation of the escape wheel 40 stops.

Then, by repeating the operation explained above according to the alternating rotation of the balance spring 30, the exhaust 13 engages and disengages repeatedly from the escape gear 43, and the first pallet of stop 62 as well as the second stopping pallet 63 effect an indirect transmission of energy to the sprung balance 30 using the contact of the escape gear 43 with the first impact pallet 60 and the second pallet impact 61.

Therefore, it is possible to ensure that the exhaust 13 operates as an exhaust 13 of the type of those whose impact is often called indirect impact. It is possible to guarantee a stable operation and a stable energy transmission compared to the case where the energy is directly transmitted to the spring balance 30.

In particular, with an exhaust 13 according to this embodiment, unlike a conventional exhaust in which the impact pallet and the stop pallet are incorporated in a common anchor, the first impact anchor 51 and the second impact anchor 52 respectively include the first impact pallet 60 and the second impact pallet 61, and the stop anchor 55 includes the first stop pallet 62 and the second stop pallet 63.

Therefore, it is possible to freely design and respectively dispose, with fewer restrictions, a relative position of the impact anchor unit 53 (the first impact anchor 51 and the second anchor of the impact anchor 53). impact 52) relative to the escape wheel 40 and a relative position of the stop anchor unit 56 (the stop anchor 55) relative to the escape wheel 40. It is possible to arrange impact anchor unit 53 and stopping anchor unit 56 in optimal configurations respectively for impact and stopping.

The stop anchor 55 is disposed, according to this embodiment, on the basis of a design concept explained below.

[0188] FIG. 20 illustrates a relationship between the center of rotation (i.e., the axis of rotation 02) of the escapement wheel 40, the pivot center (i.e., the axis of rotation 05) of the stop anchor 55, and the retracting angle of the escape wheel 40.

[0189] It should be noted that in FIG. 20, the escape wheel 40 is not illustrated. However, the rotation path R followed by the end of the escape gear 43 is illustrated. Consequently, the rotation path R corresponds to the external diameter of the escapement wheel 40.

[0190] Moreover, FIG. 20 represents a case where the center of pivoting of the stop anchor 55 is disposed in a position spaced a distance L1 from that of the rotation path R of the escapement wheel 40 and a case where the pivot center of the stop anchor 55 is disposed in a position spaced a distance L2, longer than the distance L1, from the rotation path R of the escapement wheel 40.

In both cases, the first stop pallet 62 moves, according to the pivoting of the stop anchor 55, between an engagement position X1 where the escape gear 43 comes into contact with the first stop pallet 62, and a release position X2, where the first stop pallet 62 moves to a position deviating from the rotation path R of the escapement wheel 40, and is disengaged from the transmission gear. 43 exhaust.

The angle between a linear segment connecting the first engagement surface 62a of the first stop pallet 62 to the pivot center of the stop anchor 55 and a direction normal to the first surface of commitment 62a is the angle of incidence a1. The pivot angle of the required stop anchor 55 as the first stopping pallet 62 moves from the engagement position X1 to the stowage position X2 is considered to be a working angle (or an angle liberation) a2. Furthermore, reference is made to the retraction angle a3 as being that corresponding to the retraction angle of the escapement wheel 40 involved in the movement of the first stopping pallet 62 between the engagement position X1 and the clearance position X2.

In the foregoing conditions, it is explained how the distance between the pivot center of the stop anchor 55 and the rotation path R of the escapement wheel 40 affects the retraction angle a3 when the working angle a2 is set to a predetermined value.

As shown in FIG. 20, when the stop anchor 55 rotates at the same working angle a2 respectively in a state in which the pivot center of the stop anchor 55 is spaced a distance L2 from the rotational path R of the escape wheel 40, and in a state in which the center of pivoting of the stop anchor 55 is spaced a distance L1 from the rotational path R of the escape wheel 40, it is possible to define a retraction angle a3 smaller in the case of a distance L1 than for a distance L2. In other words, it is possible to define a smaller retraction angle a3 when the pivot center of the stop anchor 55 is closer to the rotation path R.

Therefore, it is possible to reduce the retraction angle of the escapement wheel 40 by putting the pivot center of the stop anchor 55 as close as possible to the rotation path R of the escape wheel 40. It is possible to reduce the energy required to release the escapement 40 from its shutdown state (that is, the energy required to turn the escapement wheel 40 retracted into its position). original direction of rotation).

[0196] It should be noted that in FIG. 20, the explanation is focused on the first stop pad 62. However, the same reasoning applies to the second stop pad 63. Therefore, an optimal setup for the stop is to put the pivot center the stop anchor 55 as close as possible to the rotational path R of the escape wheel 40 (that is, the outer diameter of the escape wheel 40).

According to this embodiment, it is possible to have the stop anchor 55 in an optimal configuration for a stop. Therefore, it is possible to reduce the energy required to release the escape wheel 40 from its shutdown state, improve the energy transmission efficiency, and reduce operating errors.

[0198] It is also possible, for example, to design the working angle of the stop anchor 55 as being equal to an optimum angle. It is thus easy to improve the efficiency of energy transmission.

[0199] The first impact anchor 51 and the second impact anchor 52 are, according to this embodiment, arranged on the basis of a design concept explained below.

[0200] FIG. 21 is a diagram showing a relationship between the escape gear teeth 43 of the escape wheel 42 and the first impact pallet 60 which are in contact with each other. Please note that in fig. 21, it is assumed that the tip of the escape gear teeth 43 and the first impact pad 60 are in contact in a state close to the nip.

The working angle a4, which is a pivot angle of the escapement wheel 40 required between the start of the contact of the escape gear teeth 43 and the first impact pallet 60 to the end of the contact, is determined, for example, by the number of teeth of the escape wheel 42. The working angle a5, which is a pivot angle of the impact anchor 51 required between the beginning of the contact of the exhaust gear teeth 43 and the first impact pad 60 to the end of the contact is determined on the basis of the working angle a4 of the escapement wheel 40.

When energy is effectively transmitted from the escapement wheel 40 to the first impact pallet 60 following the contact of the escape gear teeth 43 with the first impact pallet 60, for example, as at a high point in the meshing of the toothed parts, it is desirable to transmit the energy at the high point PO of the gear between the toothing of the escape gear 43 and the first impact pallet 60 .

[0203] Please note that the high point PO gear is equivalent to the intersection of a line of work connecting a contact point P1 corresponding to the moment of contact start of the gearing of the escape gear 43 with the first impact pallet 60, and a point of contact P2 corresponding to the end of the contact, and a center line connecting the center of rotation (that is to say, the axis of rotation 02) of the mobile d exhaust 40 and the pivot center (i.e., pivot axis 03) of the impact anchor 51.

When the transmission of the energy at the high point PO of gearing is taken into account, the ratio between the distance L3 between the center of rotation of the escapement wheel 40 and the high point PO of the vehicle is determined. gear, and a distance L4 between the pivot center of the impact anchor 51 and the high point PO gear.

In this case, the ratio between the distance L3 between the center of rotation of the escapement wheel 40 and the high point PO gear, and the distance L4 between the pivot center of the anchor impact 51 and the high point PO of gearing is substantially an inverse relationship between that of the working angle a4 of the escapement wheel 40 and the working angle a5 of the impact anchor 51. In other words, the distance L3, distance L4, working angle a4 and working angle a5 substantially satisfy the mathematical relation (L3 / L4) = (α5 / α4).

[0206] Therefore, such a design constitutes an optimal configuration for the impact. It should be noted that the same applies to the second impact pallet 61 and the second impact anchor 52.

Therefore, according to this embodiment, it is possible to respectively have the first impact anchor 51 and the second impact anchor 52 in optimal configurations for the impact. Therefore, in the two impact anchors, it is possible to efficiently transmit the energy, which is transmitted to the escapement wheel 40, the spiral balance 30. It is also possible to, for example, design the angles of working the first impact anchor 51 and the second impact anchor 52 to optimal values. It is easier to improve the efficiency of energy transmission.

As explained above, with the exhaust 13 in this embodiment, it is possible to achieve an optimized design for impact and stopping. The exhaust can be configured as an exhaust that is excellent in energy transmission efficiency and has fewer operating errors.

The first impact pallet 60 and the second impact pallet 61 come into contact with the first stop pallet 62, and the second stop pallet 63 engages with the work surface 43a of the Exhaust gear 43. Therefore, it is possible to form the escape wheel 40 in a single layer structure. Therefore, it is possible to prevent any increase in the inertia of the escape wheel 40. Thus, it is also possible to improve the energy transmission efficiency.

Furthermore, when the toothing of the escapement wheel 43 is engaged with the first stop pallet 62 or the second stop pallet 63, and that the rotation of the escape wheel 40 stops, that is to say, when the plate pin 38 disengages from the fork 74, and the balance spring 30 oscillates freely, the restriction lever 85 comes into contact with one or the other of the limiting pins 86 or 87. Therefore, it is possible to position the second anchor 52 located at the coupling end of the chain of anchors 50. It is possible to restrict the displacement of the entire chain of anchors 50.

Thus, for example, if a disturbance occurs while the balance spring 30 oscillates freely, it is possible to prevent any undesirable undulation or floating of the chain of anchors 50, and thus to operate the exhaust 13 stably.

With the movement 10 and the timepiece 1 according to this embodiment, since the movement 10 and the timepiece 1 comprise the exhaust 13 explained above, which is excellent in terms of efficiency of transmission of energy, and which has fewer operating errors, the movement 10 and the timepiece 1 are a movement and a timepiece that have reduced walking distances and high performance.

[0213] (Second Embodiment) [0214] A second embodiment according to the present invention is explained with reference to the drawings. It should be noted that in this second embodiment, the same parts as the components in the first embodiment are indicated by the same reference numbers and signs and an explanation relating to these parts will not be repeated.

In the first embodiment, the stop anchor unit is formed by a single anchor. However, in the second embodiment, the stop anchor unit is formed by two anchors.

As illustrated in FIG. 22, in an escapement 100 according to this embodiment, the stop anchor unit 101 is formed by a first stop anchor 102 and a second stop anchor 103.

Therefore, the chain of anchors 105 is formed, according to this embodiment, by four anchors, that is to say, the first impact anchor 51, the second impact anchor 52, the first stop anchor 102, and the second stop anchor 103.

[0218] The first stop anchor 102 and the second stop anchor 103 are respectively coupled to the impact anchor unit 53 so as to be movable relative thereto. In the example shown in the figure, the first stop anchor 102 is coupled to the first impact anchor 51. The second stop anchor 103 is coupled to the second impact anchor 52. The first pallet stop 62 is attached to the first stop anchor 102. The second stop pallet 63 is attached to the second stop anchor 103.

The first stop anchor 102 is further disposed in the first direction of rotation M1 by inserting the first impact anchor 51 in a plan view, and includes an anchor shaft 110, which is a rotating shaft. , and an anchor body 111. The first stop anchor 102 rotates about an axis of rotation 06 in the opposite direction to that of the pivoting of the first impact anchor 51, based on the rotation of the first impact anchor 51.

The anchor pin 110 is held axially between the plate 11 and the gear train deck (not shown) and driven for example from the bottom to be integrally fixed to the anchor body 111 and form only a single piece.

The anchor body 111 is arranged to extend along the circumferential direction of the escapement wheel 40. The anchor shaft 110 is attached to a circumferential end 111a of the anchor body 111 located in the first direction of rotation M1. It should be noted that the anchor body 111 is disposed at a height equivalent to that of the anchor body 71 of the first impact anchor 51, and disposed above the escape wheel 40 located in the background.

The engagement fork 92 is formed at the circumferential end 111b of the anchor body 111 located in the second direction of rotation M2. The engagement plate 77 of the first impact anchor 51 engages inside the engagement fork 92. Therefore, the first impact anchor 51 and the first stop anchor 102 are coupled with each other. so that they can move relative to each other, and rotate in opposite directions relative to each other.

[0223] The third pallet holding section 93 opening towards the escape wheel 40 is arranged in the central part of the anchor body 111. The third pallet holding section 93 holds the first pallet stop 62 using this opening.

The second stop anchor 103 is further disposed in the second direction of rotation M2 relative to the second impact anchor 52 in a plan view, and includes an anchor axis 120, which is a rotary shaft. , and an anchor body 121. The second stop anchor 103 rotates about an axis of rotation 07 in the opposite direction to that of the pivoting of the second impact anchor 52 on the basis of the rotation of the second impact anchor 52.

The anchor pin 120 is held axially between the plate 11 and the gear train deck (not shown) and is driven into the anchor body 121 from, for example, the bottom so as to be integrally attached to the latter forming a single piece.

The anchor body 121 is formed so that it extends along the circumferential direction of the escapement wheel 40. The anchor shaft 120 is fixed to the central part of the body of the body. Anchor 121. It should be noted that the anchor body 121 is disposed in a position equivalent to that of the anchor body 81 of the second impact anchor 52, and is disposed above the escape wheel 40 .

The fourth pallet holding section 94 opening towards the escape wheel 40 is arranged in the anchor body 121 at a circumferential end 121a located in the second direction of rotation M2. The fourth pallet holding section 94 holds the second stopping pallet 63 using this opening.

The second stop anchor 103 configured in this way is coupled to the second impact anchor 52 through a gear using a toothed sector.

In other words, a plurality of teeth 125 is arranged at the circumferential end 81b to which is attached the second impact pad 61 in the second impact anchor 52. Teeth 126 meshing with the teeth 125 of the second impact anchor 52 are formed at a circumferential end 121b of the second stop anchor 103 in the first direction of rotation M1, so as to correspond to the teeth 125.

[0230] Therefore, the second impact anchor 52 and the second stop anchor 103 are coupled to each other so as to be movable relative to each other, and rotate in opposite directions with respect to each other.

[0231] It should be noted that in this embodiment, the first stop anchor 102 and the second stop anchor 103 rotate in opposite directions relative to each other. However, the first stop anchor 102 and the second stop anchor 103 are not limited to such a configuration and could be coupled to rotate in the same direction as each other.

[0232] It may also be noted that, according to this embodiment, a limiting pin 86 is arranged to be able to come into contact with an external lateral surface 121c located on the opposite side with respect to the second stopping pallet 63. at the circumferential end 121a of the second stop anchor 103. The other limiting pin 87 is arranged to be in contact with an external side surface 111c located on the opposite side from the first pallet. stop 62 in the central part of the first stop anchor 102.

When the escape gear 43 and the first stop pallet 62 are in mutual engagement, the outer lateral surface 121c of the second stop anchor 103 comes into contact with the limiting pin 86 and positions the second stop anchor On the other hand, when the escape gear 43 and the second stopping pallet 63 are in mutual engagement, the outer side surface 111c of the first stopping anchor 102 comes into contact with each other. the other limiting pin 87 and positioning the first stop anchor 102.

[0234] (Operation of the Exhaust) [0235] As in the first embodiment, the exhaust 100 according to this embodiment configured as explained above can alternatively and repeatedly perform an engagement between the exhaust gear 43 and the first stop pallet 62, and a clearance therebetween; the second stopping pallet 63 can effect an indirect transmission of energy to the sprung balance 30 using the contact of the escape gear 43 with the first impact pallet 60 and the second impact pallet 61.

The external lateral surfaces 111c and 121c respectively coming into contact with the limiting pins 86 and 87 are arranged on the first stop anchor 102 and the second stop anchor 103, equivalent to the coupling end of the chain of anchors 105. Therefore, when the escape gear 43 is engaged with the first stop pallet 62 or the second stop pallet 63, and the rotation of the escape wheel 40 is stopped, it is possible to restrict the movement of the entire chain of anchors 105.

Thus, even if a disturbance occurs while the spring balance 30 oscillates freely, it is possible to prevent the anchor chain 105 undulates by floating or vibrating. Therefore, it is possible to operate the exhaust 100 stably.

Therefore, with an exhaust 100 according to this embodiment, it is possible to perform the same actions and to obtain the same results as those and those of the first embodiment.

[0239] (Third Embodiment) [0240] A third embodiment according to the present invention is explained below with reference to the drawings. It should be noted that in this third embodiment, the same parts as the components of the first embodiment are indicated by the same signs and reference numbers, and no explanation will be provided again as to these elements.

In the first embodiment, the first impact anchor 51 rotates to follow the plate pin 38 of the balance spring 30. However, in the third embodiment, the second impact anchor 52 is configured to turn following the plate pin 38 of the sprung balance 30.

As shown in FIGS. 23 and 24, in an exhaust 130 according to this embodiment, the pairs of horns 73 defining the fork 74 is integrally formed with the second impact anchor 52 at the circumferential end 81b. It should be noted that, in this embodiment, the position of the sprung balance 30 is different from that of the first embodiment according to the position of the fork 74.

[0243] (Operation of the Exhaust) [0244] The escapement 130 thus configured according to this embodiment differs from the first embodiment only in that the second impact anchor 52 is rotated firstly by the ankle The anchors can be pivoted as in the first embodiment.

[0245] In other words, with an exhaust 130 according to this embodiment, it is also possible alternately and repeatedly to engage the exhaust gear 43 with the first stop pallet 62 and the second stopping pallet 63, and their mutual clearance, as well as effecting an indirect transmission of energy to the sprung balance 30 using the contact of the escape gear 43 with the first impact pallet 60 and the second impact pallet 61.

In particular, the second impact anchor 52 located at the coupling end of the chain of anchors 50 is configured to turn following the plate pin 38 of the balance-spring 30. Therefore, it It is possible to arrange the balance spring 30 and the escapement 40 in close positions compared to the first embodiment.

Therefore, for example, when an exhaust 130 according to this embodiment is applied to a vortex, it is possible to contribute to a size reduction of a cage on which a mechanism including the exhaust 130 would be mounted . Therefore, it is possible to make an exhaust 130 particularly suitable for a Tourbillon.

[04248] (Fourth Embodiment) A fourth embodiment according to the present invention is explained below with reference to the drawings. It should be noted that in the fourth embodiment the same parts as the components of the first embodiment are indicated by the same reference numerals and an explanation of these parts will not be repeated.

In the first embodiment, the first impact anchor 51 rotates following the plate pin 38 of the balance spring 30. However, in the fourth embodiment, the stop anchor 55 is configured to turn following the plate pin 38 of the sprung balance 30.

[0251] As shown in FIG. 25 and FIG. 26, in an exhaust 140 according to this embodiment, the pair of horns 73 defining the fork 74 is integrally formed at a circumferential end 91b of the stop anchor 55. It should be noted that in this embodiment embodiment, the position of the sprung balance 30 differs from that of the first embodiment according to the position of the fork 74.

The engagement plate 77 of the first impact anchor 51 is formed by a pair of elastic sections 141. Each of the elastic sections of the pair of elastic sections 141 respectively has a semicircular shape according to a plan view. . As indicated by arrows shown in FIG. 25, a force is applied on the elastic sections 141 outwardly so that they deviate from each other.

Therefore, the engagement plate 77 of the first impact anchor 51 and the engagement fork 92 of the stop anchor 55 are coupled to each other in a state in which the outer circumferential surfaces of the pair of elastic sections 141 are held in compression against the inner surface of the engagement fork 92.

Moreover, the engagement fork 78 of the first impact anchor 51 is configured so that it can hold the engagement pin 82 of the second impact anchor 52. In other words, a section curved 142 is formed in a section at the base of the engagement fork 78. As indicated by an arrow shown in FIG. 25, this has the consequence that the distal end of this branch of the fork tends to approach the other branch of the fork by pivoting at the level of the curved section 142.

Therefore, the engagement pin 82 of the second impact anchor 52 and the engagement fork 78 of the first impact anchor 51 are coupled to each other in a state in which the the inner surface of the engagement fork 78 is held in compression against the outer circumferential surface of the engagement pin 82. [0256] (Exhaust operation) [0257] In this embodiment, the exhaust 140 is configured as indicated above differs from that of the first embodiment only in that the stop anchor 55 is rotated first by the plate pin 38 of the balance spring 30. The anchors can otherwise be rotated as in FIG. first embodiment.

In other words, with the escapement 140 according to this embodiment, it is also possible to alternately engage the escape gear 43 with the first stop pallet 62 and the second stop pallet 63, and then releasing it from the latter repeatedly, and effecting an indirect transmission of energy to the sprung balance 30 using the contact of the escape gear 43 with the first impact pallet 60 and the second impact pallet 61.

In particular, with an escapement 140 according to this embodiment, as in the context of the third embodiment, it is possible to have the balance spring 30 and the escapement 40 in close positions compared to the first embodiment. Therefore, it is possible to make an exhaust 140 particularly suitable for a Tourbillon.

[0260] In addition, the engagement plate 77 of the first impact anchor 51 and the engagement fork 92 of the stop anchor 55 are coupled here to each other in a state in which the outer circumferential surfaces of the pair of elastic sections 141 are held in compression against the inner surface of the engagement fork 92. Therefore, it is possible to prevent the formation of any gap between the engagement plate 77 and the engagement fork 92. Thus, it is possible to couple the first impact anchor 51 to the stop anchor 55 with fewer jerks.

[0261] Similarly, the engagement pin 82 of the second impact anchor 52 and the engagement fork 78 of the first impact anchor 51 are coupled to each other in a state in which the surface The engagement fork 78 is held in compression against the outer circumferential surface of the engagement pin 82. Therefore, it is possible to prevent the formation of any gap between the engagement pin 82 and the fork of the engagement pin 82. As a result, it is possible to couple the second impact anchor 52 to the first impact anchor 51 with fewer jerks.

[0262] Therefore, it is possible effectively to prevent the occurrence of jolts and kickbacks between the first impact anchor 51 and the stop anchor 55, and between the first impact anchor 51 and the second impact anchor 52. It is thus possible to rotate the first impact anchor 51, the second impact anchor 52, and the stop anchor 55 with a good mutual feedback. Thus, it is possible to operate the exhaust 140 more smoothly, and further improve operational performance.

[0263] (Fifth Embodiment) [0264] In what follows, a fifth embodiment according to the present invention will be described with reference to the drawings. It will be appreciated that according to this fifth embodiment, the same components and parts as those of the first embodiment will bear the same reference numerals and no explanation will be provided again about them.

In the first embodiment, the first impact anchor 51 and the stop anchor 55 are disposed above the escape wheel 40, located in the bottom layer. The second impact anchor 52 is disposed again above the first impact anchor 51 and the stop anchor 55. However, in the fifth embodiment, the first impact anchor 51, the second impact anchor 52, the stop anchor 55, and the escape wheel 40 are configured to all be on the same plane.

[0266] As illustrated in FIGS. 27 and fig. 28, in an escapement 150 according to this embodiment, a toothed sector 151 is formed at the proximal end of the body of the anchor 71 on the first impact anchor 51.

In the second impact anchor 52, the body of the anchor 81 is designed in a circular shape according to a plan view, and is centered around the pivot axis 04. The body of the anchor 81 is disposed at the same height as the body of the anchor 71 of the first impact anchor 51. In the body of the anchor 81 is also a toothed sector 152 meshing with the other gear sector 151 of the first anchor As a result, the second impact anchor 52 is coupled to the first impact anchor 51 via the toothed sector gear.

In particular, it is possible to reduce the radius of pivoting of the second impact anchor 52 relative to the first embodiment. In addition, by coupling the first impact anchor 51 with the second impact anchor 52 via a meshing between two toothed sectors, it is possible to determine a distance between the pivot axis 03 of the first impact anchor 51 and the pivot axis 04 of the impact anchor 52 as being smaller than the distance defined in the context of the first embodiment.

Therefore, it is possible to arrange the body of the anchor 81 of the impact anchor 52 at the same height as the anchor body 71 of the first impact anchor 51, without interfering with the Mobile exhaust 40. Thus, it is possible to have the first impact anchor 51, the second impact anchor 52, and the stop anchor 55 on the same plane as that of the escape mobile 40.

In this embodiment, a limiting pin 86 is disposed further in the first direction of rotation M1 with respect to the anchor body 71 of the first impact anchor 51. The other limiting pin 87 is disposed further in the second direction of rotation M2 relative to the anchor body 71.

[0271] Therefore, as illustrated in FIG. 27, when the toothing 43 of the escape wheel and the first stop pad 62 are in mutual engagement, the first impact anchor 51 is brought into contact with a limiting pin 86, and thus positioned. As illustrated in FIG. 28, when the escape toothing 43 and the second stop pallet 63 are in mutual engagement, the first impact anchor 51 comes into contact with the other locking pin 87 and is thus positioned.

[0272] (Operation of the Exhaust) [0273] In the case of the escapement 150 configured in this manner according to this embodiment, it is possible to alternatively engage the escape toothing 43 with the first stop pallet 62 and the second stop pallet 63, then their release, and this repeatedly. It is possible to realize an indirect transmission of energy to the balance spring 30 using the contact of the escape toothing 43 with the first stop pallet 60 and the second stop pallet 61.11 is possible to perform the same actions and to obtain the same effects as those achieved and those obtained in the context of the first embodiment.

In particular, it is possible to have the first impact anchor 51, the second impact anchor 52, the stop anchor 55, and the escape wheel 40 on the same plane. Thus, it is possible to make an exhaust 150 having a thin shape. Therefore, it is possible to use the escapement 150 appropriately in a thin timepiece 1.

The embodiments of the present invention explained above are presented as examples and are not intended to limit the scope of the invention. Other embodiments could be made according to other variants. Various omissions, replacements, and changes in features could be made to an extent that does not depart from the spirit of the invention. Alternative embodiments and modifications of the proposed embodiments include, for example, alternative embodiments and modifications readily adopted by those skilled in the art, embodiments and modifications substantially identical to the proposed embodiments and their variants, as well as the embodiments and modifications falling within the framework of the doctrine of equivalents.

For example, in the embodiments described, the proposed configuration for transmitting the energy of the mainspring housed in the movement barrel to the escape mobile is given by way of example. However, the transmission of energy is not limited to such a case. For example, the energy could be transmitted to the escapement mobile from a motor spring provided in another component than the movement barrel.

In the embodiments described, the movement adopted is of the manual winding type to manually raise the spring of the barrel using the crown. However, the movement is not limited to such a case. For example, the movement could be a self-winding type movement including a rotor (i.e. oscillating mass).

In the embodiments described, an example is detailed according to which the pallets such as the impact pallet and the stopping pallet are made of artificial precious stones such as a ruby. However, pallets are not limited to such a case. For example, the pallets may be other brittle materials and metal materials such as iron-based alloys. In addition, the pallets can be formed of a semiconductor material

Claims (7)

such as silicon and formed integrally with the anchor integrally by a semiconductor fabrication technique such as DeepRIE. In any case, the material, shape, and other pallets can be modified as needed as long as the functions of the pallets can be realized. From the first embodiment to the fourth embodiment, the impact anchor unit is formed by two anchors. However, the impact anchor unit is not limited to such a configuration. For example, the impact anchor unit could be configured by, for example, an anchor or three or more anchors. Impact pallets can be attached to two anchors of three or more anchors. [0280] It should be noted that when the impact anchor unit is formed by a single anchor, for example, the anchor only needs to be configured to take an arcuate shape extending along the circumferential direction. of the escape wheel and have a shape such that the two ends in the circumferential direction are located opposite sides in the radial direction on either side of the mobile escape. The impact pallets only have to be attached respectively to both ends of the anchor. [0281] By configuring the impact anchor unit in this way, even with the pivoting of a single anchor, it is possible to make the impact pallets attached to both ends of the anchor alternately in contact (in collision) with the escape wheel. Therefore, it is possible to perform the same actions and obtain the same effects as those of the first embodiment. In the foregoing embodiments, the stop anchor unit is formed by a single anchor or two anchors. However, the stop anchor unit is not limited to such a configuration. The stop anchor unit could be formed, for example, of three or more anchors. Stop pallets can be attached to two anchors of three or more anchors. claims An exhaust (13, 100, 130, 140, 150) comprising: an escapement wheel (40) which rotates due to energy transmitted thereto; and an impact anchor unit (53) and a stop anchor unit (56, 101) coupled to each other while remaining movable relative to each other to pivot on the basis of the rotation of a sprung balance (30), wherein the impact anchor unit (53) and the stop anchor unit (56, 101) each consist of one or more anchors, the impact anchor unit (53) comprises an impact pallet (60, 61) engageable with the escape wheel (40), and the stop anchor (56,101) includes a stop pallet (62,63) engageable with and disengaged from the escape wheel (42) in the absence of contact thereof with the pallet impact (60, 61). An exhaust (13, 100, 130, 140, 150) according to claim 1, wherein the impact anchor unit (53) comprises a first impact anchor (51) and a second impact anchor (52) coupled to each other so as to be movable relative to each other, and each of the first impact anchor (51) and the second impact anchor (52) comprises a pallet impact. An exhaust (13, 100, 130, 140, 150) according to claim 2, wherein the first impact anchor (51) and a second impact anchor (52) are coupled to each other in a manner when one of the two impact anchors among the first impact anchor (51) and the second impact anchor (52) rotates in the same direction of rotation as that of the escape wheel (40). ), the other impact anchor rotates in the opposite direction to that of the rotation of the escapement wheel (40). An exhaust (100) according to claim 3, wherein the stop anchor unit (101) comprises a first stop anchor (102) and a second stop anchor (103) coupled respectively to the an impact anchor unit (53) so as to be movable relative thereto, and wherein each of the first stop anchor (102) and second stop anchor (103) comprises a stop pallet (62, 63). An exhaust (100) according to claim 4, wherein the first stop anchor (102) and the second stop anchor (103) are coupled so that when one of the two stop anchors among the first stop anchor (101) and the second stop anchor (102) rotate in the same direction of rotation as that of the escape wheel (40), the other stop anchor rotates in the opposite direction to that of the rotation of the escape wheel (40). 6. Movement (10) of timepiece (1) comprising: an exhaust (13, 100, 130, 140, 150) according to one of claims 1 to 5; a speed controller (14) including the sprung balance (30); and a gear train (12) that transmits energy to the escape wheel (40). 7. Timepiece (1) comprising: the movement (10) of timepiece (1) according to claim 6; and a needle which rotates at a speed of rotation adjusted by the exhaust (13) and the speed regulator (14).