CH713529A2 - Exhaust, watch movement and timepiece. - Google Patents

Abstract

The present invention seeks to obtain an exhaust which is excellent in energy transmission efficiency. An escapement (13) is provided which includes an escapement wheel (40) rotating with energy transmitted thereto, an impact anchor unit (52) and a stop anchor unit (54) coupled to each other but which can move relative to each other, in order to be able to rotate according to the rotation of a balance spring (30). The stop anchor unit (54) is formed by at least one or more anchors (53) and includes stop palettes (62, 63), engageable with and disengaged from a drive wheel. exhaust (42) of the escape wheel (40). The impact anchor unit (52) is formed by at least one or more anchors (51), and includes a first impact pallet (60) engageable with the escape wheel ( 42) in the absence of mutual engagement of the latter with the stopping pallet (62, 63). A second impact pallet (61) which can be brought into contact with the escape wheel (42) in the absence of contact with the first impact pallet (60) is attached to the balance spring (30). .

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 mainly roughly classified into a type of direct impact 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 mobile escapement to the sprung balance via other components of the timepiece such as an anchor. Exhaustions are also known which jointly use both direct and indirect impacts.

As an exhaust that simultaneously uses both a direct impact and an indirect impact, conventionally known so-called coaxial exhaust (a coaxial escapement) including an exhaust mobile (ie a wheel and an escape pinion) having a double layer structure in which two escape wheels are superimposed on the same axis. For example, the escapement represented by George Daniels is known as described in, for example, patent document 1 - European Patent Application No. 0 018 796 - or the document of the non-patent scientific literature 1 - George Daniels, " WATCHMAKING (2011 Edition update), "Philip Wilson Publishers Ltd., June 15, 2011, p. 238 to p.252).

[0007] The coaxial escapement comprises an escapement wheel (that is to say a wheel & an exhaust pinion) having a double layer structure in which a first escape wheel and a second wheel are provided. exhaust of a larger diameter than the first escape wheel are superimposed on the same axis, an anchor provided with a first impact pallet, a first stop pallet, and a second pallet stopping, and which can be rotated on the basis of the rotation of a sprung balance, and a second impact pallet attached to the sprung balance.

The first impact paddle may be brought into contact with an end of the first escape wheel depending on the direction of pivoting of the anchor. The second impact pallet may be made to come into contact with one end of the second escape wheel as a function of the rotation of the balance spring. The first stop pallet and the second stop pallet can respectively engage with and disengage from the end of the second wheel in the direction of pivoting of the anchor.

With the Coaxial escapement configured in this way, the first stop pallet and the second stop pallet engage with and alternately emerge from the second escape wheel in the direction of pivoting of the anchor . Therefore, it is possible to control the rotation of the escape wheel. The first impact pallet comes into contact (in collision) with the end of the first escape wheel in the direction of pivoting of the anchor. Therefore, it is possible to indirectly transmit the energy, which is transmitted to the escape wheel (that is to say the wheel and the escape pinion), to the sprung balance via the anchor. It is possible to provide rotational energy to the sprung balance. In addition, the second impact pallet contacts (collides) with the end of the second escape wheel according to the rotation of the sprung balance. Therefore, it is possible to directly transmit the energy, which is transmitted to the escape wheel (that is to say the wheel and the exhaust pinion), to the sprung balance. It is possible to provide rotational energy to the sprung balance.

Therefore, it is possible to transmit the energy that is transmitted to the escape wheel (that is to say the wheel and the exhaust pinion), the sprung balance by alternately performing a transmission of indirect power and direct power transmission.

In addition, the patent document 1 and the document of the non-patent literature 1 also disclose an escapement which jointly uses both a direct impact and an indirect impact using an escape mobile (i.e. a wheel and an escape pinion) having a single layer structure rather than an escapement vehicle having a double layer structure.

In this exhaust, a first stop pallet and a second stop pallet can engage with and respectively disengage from an escape wheel. In addition, a first impact paddle and a second impact paddle may be brought into contact with the same escape wheel.

However, in the conventional coaxial escapement, since the escapement mobile has a double layer structure, the inertia of the entire mobile exhaust (that is to say, the wheel and the pinion). exhaust) is large and the dynamic efficiency can easily be degraded. It is necessary to assemble the escape wheel by performing a phase focusing on the first escape wheel and the second escape wheel. Therefore, assembly tolerances can occur. Even though the exhaust is affected by assembly tolerances, operational reliability needs to be guaranteed for the exhaust. Therefore, a spacing link between the first escape wheel and the second escape wheel and the pallets must be provided rather broadly taking into account the assembly tolerances. As a result, it follows that the efficiency of energy transmission can easily be degraded.

When using an exhaust mobile (that is to say the wheel and the exhaust pinion) having a single-layer structure, it is necessary to engage the first pallet stop and the second stop pallet with the escape wheel, and to disengage the first stop pallet and the second stop pallet of this common escape wheel. It is necessary to bring the first impact pallet in contact with the common escape wheel. However, since the first stop pallet, the second stop pallet, and the first impact paddle are incorporated in the same anchor, in order to properly engage the paddles with the escape wheel and to clear the paddles. pallets of the escape wheel, or put the pallets in contact with the escape wheel, it is necessary to dissociate a pivot center of the anchor of the end of the escape wheel, by spacing the latter a fixed distance in the radial direction of the escape wheel.

However, for example, when focusing on the stopping action, as the pivot point of the anchor is further away from the end of the escape wheel, the sliding distance of the The end of the escape wheel sliding on the stop pallet increases until it is released from the stop pallet. As a result, the energy required to release the escape wheel stopping increases, which causes a deterioration of the energy transmission efficiency.

In addition, since the first stop pallet, the second stop pallet, and the first impact paddle are incorporated in a common anchor, the anchor can not be used operationally at working angles respectively. optimal for impact and shutdown, causing a deterioration in power transmission efficiency.

SUMMARY OF THE INVENTION

The present invention has been designed 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 efficiency. power transmission.

[0018] (1) An exhaust according to the present invention comprises: an escape wheel (that is to say a wheel and an exhaust pinion) which rotates thanks to the energy transmitted to it, as well as an impact anchor unit and a stop anchor unit coupled to each other while remaining movable relative to each other so as to pivot on the basis of the rotation of a balance-spring. The stopping anchor unit is formed by at least one or more anchors and includes a stopping pallet engageable with, and respectively disengaging from, an escape wheel of the escape wheel. The impact anchor unit is formed by at least one or more anchors and comprises a first impact pallet which can be brought into contact with the escape wheel in the absence of engagement of the latter with the stop pallet. A second impact pallet, which may be brought into contact with the escape wheel in the absence of contact of the latter with the first impact pallet, is fixed to the balance spring.

According to the present invention, it is possible to rotate respectively, on the basis of the rotation (alternating rotation, in a back-and-forth movement) of the sprung balance, the impact anchor unit. and the stop anchor unit coupled to each other while remaining movable relative to each other. By pivoting the impact anchor unit, it is possible to cause the first impact pallet to move so that it comes into contact (collide) with the escape wheel. Therefore, it is possible to transmit energy, which is transmitted to the escape wheel, indirectly to the sprung balance via the impact anchor unit. It is thus possible to provide rotational energy to the sprung balance. Since the second impact pallet is fixed to the sprung balance, when the sprung balance rotates, it is possible to cause the displacement of the second impact pallet so that it is brought into contact (collided ) with the escape wheel. Therefore, it is possible to transmit the energy, which is transmitted to the mobile escape directly to the sprung balance via the second impact pallet. It is thus possible to provide rotational energy to the sprung balance. In addition, when the stopping anchor unit is pivoted, it is possible to bring the stopping pallet into engagement with the escape wheel to stop the rotation of the mover, or to disengage the pallet from stopping in engagement with the escape wheel from the escape wheel, and releasing the stop of the escape wheel.

In this way, it is possible to transmit the energy, which is transmitted to the mobile escapement, the sprung balance while performing alternately (by switching) a direct transmission of energy and an indirect transmission of energy . It is possible to control the rotation of the escape wheel with a constant oscillation corresponding to the sprung balance.

In particular, unlike the conventional escapement in which the impact pallet and the stopping pallet are incorporated in a common anchor, the impact anchor unit comprises only the impact pallet (the first impact pallet) and the stop anchor unit includes only the stop pallet. Therefore, it is possible to freely design respectively and have, with fewer restrictions, the relative positions of the impact anchor unit and the stopping anchor unit relative to the escape wheel. It is possible to arrange the impact anchor unit and the stop anchor unit in optimal configurations for impact and stopping, respectively.

Therefore, for example, it is possible to respectively determine an angle of work of the anchor for the impact anchor unit and a working angle of the anchor for the anchor unit. stopping as being equal to optimal angles taking into account the impact action and the stopping action. Therefore, it is possible to improve the energy transmission efficiency. It is possible to make an exhaust with fewer operating errors.

In addition, it is possible to respectively determine an inter-central distance between the center of rotation of the mobile escapement (that is to say the wheel and the exhaust pinion) and the pivot point for the impact anchor unit and an inter-center distance between the center of rotation of the escape wheel and a pivot point for the stop anchor unit as being equal to optimal distances taking into account of the impact action and the stop action. Consequently, unlike a conventional escapement in which the impact pallet and the stopping pallet are incorporated in a common anchor, it is possible to prevent the increase of the energy required to release the stopping of the mobile. exhaust, thus leading to an improvement in power transmission efficiency.

[0024] (2) The impact anchor unit may include an impact anchor comprising the first impact pallet. The stop anchor unit may comprise a stop anchor comprising a pair of stop pallets and which are coupled to the impact anchor while remaining movable relative thereto. The two stopping pallets may be brought alternately into engagement with the escape wheel and disengaged therefrom in the pivoting direction of the stopping anchor.

In this case, the impact anchor unit may be formed by an anchor, that is to say, the impact anchor. The stop anchor unit may be formed by an anchor, i.e., the stop anchor. Therefore, it is possible to form the exhaust in a simple configuration. Even with a single stop anchor, it is possible to alternately bring the two stop pallets into engagement with the escape wheel, and to release them from the escape wheel in the direction of pivoting of the anchor stop. It is thus possible to appropriately control the rotation of the escapement mobile according to a constant oscillation corresponding to that of the balance spring.

[0026] (3) A timepiece movement according to the present invention comprises: the escapement; a speed regulator comprising the balance spring; and a gear train that transmits energy to the escape wheel.

[0027] (4) A timepiece according to the present invention comprises: the timepiece movement; and a needle that rotates at a speed of rotation adjusted by the exhaust and the speed regulator.

In this case, since the timepiece movement and the timepiece proposed include an exhaust which is excellent in terms of energy transmission efficiency and shows less error in operation, it It is possible to make a timepiece movement and a timepiece that has reduced walking distances and shows a high performance.

According to the present invention, it is possible to produce an escapement, a timepiece movement, and a timepiece that are excellent in energy transmission efficiency.

BRIEF DESCRIPTION OF THE DRAWINGS

[0030]

Fig. 1 is an exterior view 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 stop pallet begins to disengage from an escape gear starting from the state shown 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 is completely disengaged from the escape gear from the state shown in FIG. 7, and then the escape gear comes into contact with a first impact pallet.

Fig. 9 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which the first impact pallet is completely disengaged from the escape gear from the state shown in FIG. 8 and then the escape gear comes into contact with a second stop pallet.

Fig. 10 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which an impact anchor contacts a limiting pin and therefore the escape gear and the second stop pallet are engaged from the state shown in fig. 9.

Fig. 11 is an explanatory diagram of the operation of the escapement and is a diagram showing a state in which a plateau pin moves in the direction of the impact anchor starting from the state shown in FIG. 10.

Fig. 12 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which the second stopping pallet is completely disengaged from the escape gear from the state shown in FIG. 11.

Fig. 13 is an explanatory diagram of the operation of the exhaust and is a diagram showing a state in which the escape gear comes into contact with a second impact pallet from the state shown 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 impact pallet is completely disengaged from the exhaust gear from the state shown 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 escape gear comes into contact with the first stop pallet from the state shown in FIG. 14, and the impact anchor comes into contact with the limiting pin and therefore the escape gear and the first stop pallet are in mutual engagement.

Fig. 16 is a diagram for explaining an optimal configuration for stopping and is a diagram showing a relationship between a center of rotation of an escape wheel, a pivot point of a stopping anchor, and a retracting angle. of the mobile escape.

Fig. 17 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. 18 is a plan view of an exhaust according to a second embodiment of the present invention.

Fig. 19 is a plan view of the exhaust passed from a state shown in FIG. 18 to a state in which the escape gear and the second stop pallet are in mutual engagement.

Fig. 20 is a plan view of an exhaust according to a variant of the second embodiment of the present invention.

DESCRIPTION OF THE EMBODIMENTS

(First Embodiment) [0032] A first embodiment according to the present invention is explained below with reference to the drawings. It may be noted that, in this embodiment, the mechanical timepiece is explained by way of example for a timepiece. In the drawings, the scales of the components are changed as needed to meet the need to show the components in visually recognizable sizes.

[0033] (Basic configuration of the timepiece) Generally, reference is made to a part body including a control portion of a timepiece as 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, one 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., a side opposite the dial) as the "front side" some movement.

Please note that, in the following explanation of this embodiment, a direction from the dial toward the bottom of the case is defined as upward (upward) and the opposite direction is defined as descending (towards). 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 second 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 rotates, through which the spring can be raised. 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 movable 21.1e center mobile third 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 mobile center 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 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 exhaust mobile 40 as explained below meshes with the seconds mobile 23 via an exhaust pinion 41. Therefore, the energy of the spring housed in the motion cylinder 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 sprung balance 30 includes 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 rocker wheel 32, four arms 33 are arranged at an interval of 90 degrees 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 externally and fixed to the balance shaft 31 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 performs movements of rotary and reciprocating around the axis of rotation 01 following those of the sprung balance 30, and engages with and reciprocally come off 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.

[0054] 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) [0056] As shown in FIG. 4, the exhaust 13 comprises the double plate 35 as explained above, the escapement wheel 40 (that is to say the wheel & the exhaust pinion) which is rotated by means of the energy transmitted from the mainspring of the barrel, an anchor chain 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.

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 in a single-layer structure including the exhaust pinion 41 which meshes with the second mobile 23 and the exhaust 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, viewed in 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 second mobile 23 via the exhaust pinion 41.

[0061] Please note that on lafig. 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 teeth 43 during the rotation of the escapement wheel 40 as simply being the rotation path R of the escape wheel 42 .

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 anchor chain 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 anchor chain 50 moves to individually pivot (oscillate) 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 comprises an impact anchor unit 52 comprising an impact anchor 51 and a stop anchor unit 54 including a stop anchor 53. impact anchor 52 and stop anchor unit 54 are coupled to each other while being movable relative to each other. In other words, the impact anchor 51 and the stop anchor 53 are coupled to each other, but can move relative to each other. Therefore, the impact anchor 51 and the stop anchor 53 are coupled so as to be serially connected one after the other.

[0067] Please note that the impact anchor unit 52 and the stop anchor unit 54 must only be formed by at least one or more anchors. According to this embodiment, as explained above, each of the units among the impact anchor 52 and the stop anchor unit 54 is formed by an 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 mobile 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 and the second impact pallet 61 is attached to the double plate 35 attached to the spring balance 30.

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 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 53.

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 pad 62 and the second paddle 63. The first stop pallet 62 and the second stop pallet 63 engage, that is to say engage with the escape wheel 42 in the absence of contact of the first impact pallet 60 and 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 impact anchor 51 includes an anchor shaft 70, which is a pivoting shaft, an anchor body 71, and an anchor arm 72. The impact anchor 51 rotates around 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). The anchor pin 70 is driven away and fixed in a base of the anchor body 71, for example, from the top (platinum side 11).

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

[0076] Please note that, as for the escapement wheel 40, a reduction in the weight of the anchor body 71 and the anchor arm 72 can be achieved by making lightening holes or refined portions in the body. anchor 71 and the anchor arm 72 as appropriate. 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, towards the second direction of rotation M2, that is, that is, towards the balance spring 30. A pair of horns 73 arranged 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 horns 73 open towards the balance shaft 31, and is designed as the fork 74 in which the plate pin 38, moving according to the alternating rotation of the balance spring 30, is housed so as to come into taken (that is, to engage) and disengage from 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 plan view and extends to project further than the horns 73. to the balance shaft 31. Please note that the stinger 75 is fixed so that it is located below the plate pin 38, but above the escapement wheel 40.

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 collar 37 with a slight play 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.

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 balance spring 30, and that the stop of the entirety of the anchor chain 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 release of the entire anchor chain 50 from its shutdown 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 to project towards the escapement wheel 40. 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 the first impact pallet 60 extends lower than the anchor body 71 to reach a height equivalent to that of the escape wheel 42. Accordingly, the first impact pad 60 may engage (collide) with the escape gear teeth 43. In addition, the first impact pad 60 is held in a state in which the first paddle 60 is projected further towards the escapement wheel 40 than the first holding portion of the pallet 76. A side surface facing the second direction of rotation M2 in a projection portion of the first impact pallet 60 is designed as 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 into contact.

The anchor arm 72 is designed such that it extends from the base of the anchor body 71 towards the first direction of rotation M1. A downwardly extending engagement pin 77 is attached to the distal end of the anchor arm 72 by driving or the like. The engagement pin 77 is formed in, for example, a columnar hollow form. The lower end of the engagement pin 77 engages inside an engagement fork 92 of the stop anchor 53 explained below.

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

Specifically, the 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 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 pallet 61 is explained below in detail.

As illustrated in FIGS. 3 and 4, the second impact pallet 61 is attached to the small flange 37 of the double plate 35. Specifically, the second impact pallet 61 is held by a second pallet holding portion 80 arranged in the small flange 37. The second pallet holding portion 80 is disposed in a more clockwise position with respect to the axis of rotation 01 in a predetermined phase with respect to the lunar recess 39 (see Fig. 4). and is open towards the escape wheel 40. The second impact pallet 61 is held by the second pallet holding portion 80 using this opening.

The second impact pallet 61 is maintained in a state in which the second impact pallet 61 projects further than the outer circumferential surface of the small flange 37 towards the escapement wheel 40. A side surface forming clockwise rotation of the axis of rotation 01 in a projection portion of the second impact pallet 61 is designed to form a second impact surface 61a with which a working surface of the toothing exhaust gear 43 of the escape wheel 42 comes into contact.

[0090] Please note that a predetermined spacing is provided in the direction of the axis of rotation 01 between the second impact pad 61 and the plateau pin 38. The stinger 75 can approach the lunar recess 39 through this spacing.

Please note that the arrangement of the second impact pallet 61 is not limited to an attachment to the small flange 37; the latter could be attached, for example, to the large flange 36 or to the balance wheel 32 in the double plate 35. The attachment position of the second impact pallet 61 can be changed according to, for example, relative positioning. with the escape wheel 42. In any case, the second impact pallet 61 must only be attached to the balance spring 30.

The second impact pallet 61 attached to the sprung balance 30 as explained above repeats forward and backward movements relative to the rotation path R of the escape wheel 42 as a function of the rotation of the As a result, it is possible to cause the working surface 43a of the toothing of the escape gear 43 of the escape wheel 42 to come into contact (in collision) with the second surface of the impact 61a of the second impact pallet 61.

Please note that, as explained above, the direction of rotation of the sprung balance 30 and the pivoting direction of the impact anchor 51 are configured to be opposite. Consequently, the second impact pallet 61 emerges from the escape wheel 42 when the first impact pallet 60 comes into contact with the escape wheel 42, and vice versa: the second impact pallet 61 comes into contact with the escape wheel 42 when the first impact pallet 60 emerges from the escape wheel 42.

The stop anchor 53 is explained in detail below.

As shown in FIGS. 4 to 6, the stop anchor 53 is disposed further along the first direction of rotation M1 than the impact anchor 51 in a plan view and includes an anchor axis 90, which is a pivoting shaft, and an anchor body 91. The stop anchor 53 pivots about a pivot axis 04 in a direction opposite to that of pivoting the impact anchor 51, based on the rotation of the impact anchor 51.

The anchor axis 90 is disposed coaxially with the pivot axis 04 and is 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 permanently fixed to the anchor body 91.

The anchor body 91 has a tabular shape obtained, for example, by electrofusion or via 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. Please note that, according to the example shown in the figure, a plurality of lightening holes are made in the anchor body 91.

The anchor pin 90 is attached to the central portion of the anchor body 91. Please note that the anchor body 91 is disposed below the anchor body 71 of the impact anchor 51 and arranged on the same plane as the escape wheel 40.

Consequently, the relative heights of the impact anchor 51, the stop anchor 53, and the escape wheel 40 are as follows: the escape wheel 40 and the anchor body 91 of the stop anchor 53 are located in a lower layer, the closest to the plate 11, and the anchor body 71 of the impact anchor 51 is located above the escape wheel 40 and of the anchor body 91.

However, the anchor body 91 of the stop anchor 53 may be disposed below the anchor body 71 of the impact anchor 51 and above the escape wheel 40. In this case, like the first impact pallet 60, the first stop pallet 62 and the second stop pallet 63 must only extend further down than the anchor body 91 so that they reach a height equivalent to that of the escape wheel 42.

A fork 92 having a forked shape projecting towards the second direction of rotation M2 and bifurcating in the circumferential direction of the pivot axis 04 is formed at a circumferential end 91a located in the second direction of rotation M2 in the anchor body 91. The engagement pin 77 of the impact anchor 51 penetrates inside the engagement fork 92. The outer circumferential surface of the engagement pin 77 and the internal surface of the engagement fork 92 are slidably engaged with each other. Therefore, the impact anchor 51 and the stop anchor 53 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 portion between the anchor pin 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 side. 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 lateral 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 pad 62 is fixed such that the first engagement surface 62a engages with the work 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 is provided a fourth pallet holding portion 94, open towards the escapement wheel 40. The fourth holding part pallet 94 holds the second stopping pallet 63 using this opening.

The second stopping pallet 63 is maintained in a state in which it projects further to 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, that is to say, comes into mutual engagement. Note that the second stopping pallet 63 functions as a pallet commonly referred to as an output pallet.

[0107] Please 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 work surface 43a of the toothed portion 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 53 configured in this manner rotates about the pivot axis 04 on the basis of the pivoting of the impact anchor 51, which rotates 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 escape wheel 42 and retract below the latter in the direction of pivoting of the stop anchor 53.

Therefore, it is possible to engage the working 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 04. Consequently, the second stop pallet 63 is disengaged from the escape wheel 42 when the first stop pallet 62 engages with the escape wheel 42. The second stop pallet 63 engages with the escape wheel 42 when the first stop pallet 62 emerges from the escape wheel 42.

As explained above, the anchor chain 50 is formed by coupling the impact anchor 51 to the stop anchor 53, so that they are connected in series to each other. following each other. The anchors 51 and 53 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 impact anchor 51 rotates in the opposite direction to that of the rotation of the balance. -spiral 30, and the stop anchor 53 rotates in the opposite direction to that of the impact anchor 51.

In this embodiment, both the impact anchor 51 and the stop anchor 53 are equivalent to an anchor located at the coupling end of the anchor chain 50. In the impact anchor 51 is arranged a restriction section. The restriction section positions the impact anchor 51 and limits the movement of the entire anchor chain 50 when the first stop pallet 62 and the second stop pallet 63 engage a wheel. exhaust 42 of the escape wheel 40.

In the impact anchor 51, an external lateral surface 100 located on the opposite side to the lateral surface facing the escape wheel 40 in the anchor body 71 comes into contact with a first limiting pin 102. arranged further along the first direction of rotation M1 with respect to the anchor axis 70 and acting as a restriction section limiting the pivoting of the impact anchor 51 and positioning the impact anchor 51.

Similarly, in the impact anchor 51, an outer lateral surface 101 located on the opposite side to the lateral surface facing the escape wheel 40 in the anchor arm 72 comes into contact with the other pin. limitation device 103 arranged further along the second direction of rotation M2 with respect to the anchor axis 70 and which acts as a restriction section limiting the pivoting of the impact anchor 51 and positioning the impact anchor 51 .

A pair of limiting pins 102 and 103 is, for example, fixed so that they protrude upwards from the plate 11.

When the first stop pallet 62 engages with the escape gear teeth 43 of the escape wheel 42, the outer lateral surface 100 of the anchor body 71 comes into contact with the locking pin. 102 and positions the impact anchor 51. When the second stop pallet 63 engages with the escape gear teeth 43 of the escape wheel 42, the outer lateral surface 101 of the exhaust arm 43 anchor 72 comes into contact with the other limiting pin 103 and positions the impact anchor 51.

[0117] (Operation of the exhaust) In the following, we explain the operation of an exhaust 13 configured as detailed above.

Please note that, in the following explanations, at the beginning of the 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 outer lateral surface 100 of the impact anchor 51 comes into contact with the limiting pin 102 defining its positioning. 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 first impact pallet 60 has already advanced beyond the rotation path R of the escape wheel 42. However, a spacing is provided between the first impact surface 60a of the first impact pallet 60 and the work surface 43a of the escape gear 43. The escape gear teeth 43 are configured not to be in contact with the first impact pallet 60.

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 impact anchor 51 via the plate pin 38.

[0123] Please note that the small collar 37 and the stinger 75 are not allowed to come 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 impact anchor 51.

[0124] Therefore, as shown in FIG. 7, the entire complete anchor chain 50 moves so that the impact anchor 51 and the stop anchor 53 are pivoted. In other words, the impact anchor 51 rotates counterclockwise around the pivot axis 03 and the stop anchor 53 rotates clockwise around the pivot axis 04.

When the impact anchor 51 pivots, the outer lateral surface 100 of the impact anchor 51 separates from the limiting pin 102. When the stop anchor 53 pivots, the first pallet of stop 62 moves in a direction away from the escape wheel 42 (a direction of retraction relative to an insertion within the rotational path R of the escape wheel 42) by sliding on the surface of work 43a of the escape gear 43.

The first stop pallet 62 moves to a position slightly diverging from the rotation path R of the escape wheel 42. It is then possible to separate the first stop pallet 62 from the toothing of FIG. escape gear 43 and disengage from the first stop pallet 62 from the escape gear 43. Therefore, it is possible to release the escape wheel 40 from its stopped 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 shown in FIG. 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 escapement wheel 40 resumes its rotation in the first direction of rotation M1 thanks to the energy transmitted via the front gear 12.

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

As shown in FIG. 8, when the retracted exhaust wheel 40 resumes its rotation in the first direction of rotation M1, the working surface 43a of the escape gear teeth 43 is brought into contact (in collision) with the first surface of impact 60a of the first impact pallet 60 which has already impeded on the rotation path R of the escape wheel 42.

Therefore, it is possible to transmit the rotational force of the escapement wheel 40 to the impact anchor 51. The inner surface of the horns 73 on the inner surface of the fork 74 located upstream of the direction of progression of the plate pin 38 comes into contact and engages with the plate pin 38. Therefore, it is possible to indirectly transmit the energy, which is transmitted to the escape wheel 40, to the balance spring 30 via the impact anchor 51. It is possible to continue to rotate the 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 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 is 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 to slide. on the first impact surface 60a. The first impact pallet 60 moves gradually in the release direction of the escape wheel 42 (the retracting direction due to an encroachment within the rotation path R of the escape wheel 42) depending on the pivoting direction of the impact anchor 51.

When the first impact pallet 60 moves to reach a position slightly deviating from the rotation path R of the escape wheel 42, the indirect impact on the balance spring 30 explained above ends. .

When the first impact pallet 60 moves in the direction of clearance relative to the escape wheel 42 as a function of the pivoting direction of the impact anchor 51, the second stopping pallet 63 s advance to encroach on the rotational path R of the escape wheel 42 following the pivoting of the stop anchor 53 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 escape wheel 42, as shown in FIG. 9, 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 wheel exhaust 42.

At this time, the impact anchor 51 moves to the other limiting pin 103 in accordance with the pivoting of the impact anchor 51 in the counterclockwise direction. However, at this point, the impact anchor 51 is configured not to be in contact with the other limiting pin 103. Therefore, the impact anchor 51 and the stop anchor 53 rotate. slightly while the escape gear teeth 43 and the second stop pallet 63 remain in contact.

As shown in FIG. 10, when the outer lateral surface 101 of the impact anchor 51 comes into contact with the other limiting pin 103, the impact anchor 51 can not perform any 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 to say of mutual engagement. Therefore, the rotation of the escape wheel 40 stops. The anchor chain 50 enters a stopped state.

Then, the plate pin 38 disengages from the inside of the fork 74 and separates from the 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. A 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.

Thus, as shown in FIG. 11, the plateau pin 38 begins a movement to approach the impact anchor 51 following the rotation of the balance spring 30 in the direction of clockwise.

As shown in FIG. 12, when the plate pin 38 moves inwardly of the fork 74 of the 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 on the inner surface of the fork 74 and exerts a pressure against the fork 74 in the opposite direction of clockwise. 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 impact anchor 51 and the stop anchor 53 are pivoted. In other words, the impact anchor 51 rotates clockwise around the pivot axis 03 and the stop anchor 53 rotates counterclockwise around the pivot axis 04.

[0142] Please note that, after the spring balance 30 has begun to rotate counterclockwise, the second impact pad 61 is gradually approaching the rotation path R of the wheel. Exhaust 42. At a given time, when the plate pin 38 exerts pressure against the fork 74 counterclockwise, as shown in FIG. 12, the second impact pallet 61 encroaches on the rotation path R of the escape wheel 42.

However, at the stage where the second stopping pallet 63 and the escape gear teeth 43 are in mutual engagement and the outer lateral surface 101 of the impact anchor 51 is in contact with the other pin limiting 103, a spacing is ensured between the second impact surface 61a of the second impact pad 61 and the working surface 43a of the escape gear 43. Therefore, the teeth of the gear exhaust 43 is configured not to be in contact with the second impact pallet 61.

When the impact anchor 51 rotates, the outer lateral surface 101 in the impact anchor 51 dissociates from the other limiting pin 103. When the stop anchor 53 pivots, the second pallet stop 63 moves in the disengagement direction with respect to the escape wheel 42 (the retraction direction with respect to an encroachment on the rotation path R of the escape wheel 42) to slide on the surface of 43a of the escape gear 43. The second stop pallet 63 moves to the position slightly deviating from the rotation path R of the escape wheel 42. Thus, it is possible to release the second pallet stopping 63 of the escape wheel 42 and disengaging the second stopping pallet 63 of the escape gear 43. Therefore, it is possible to perform a release of the stopping state of the mobile exhaust 40.

Like the first stop pallet 62, the second stop pallet 63 has an angle of incidence. Therefore, as illustrated in FIG. 12, after an instantaneous retraction movement in the second direction of rotation M2, the escapement wheel 40 continues its rotation in the first direction of rotation M1 under the impulse of the energy transmitted via the front gear train 12.

As illustrated in FIG. 13, when the retracted exhaust wheel 40 resumes its rotation in the first direction of rotation M1, the working surface 43a of the escape gear teeth 43 comes into contact (in collision) with the second impact surface 61a of the second impact pallet 61 which encroaches on the rotation path R of the escape wheel 42.

Therefore, it is possible to directly transmit the rotational force of the escapement wheel 40 to the sprung balance 30 via the second impact pallet 61. It is possible to provide a rotational energy to the sprung balance 30. , and to continuously rotate the impact anchor 51 to follow the plateau pin 38.

When the escape gear teeth 43 comes into contact with the second impact pad 61 as explained above, the escape gear teeth 43 rotate in the first direction of rotation M1 to slide on the second impact surface 61a. The second impact pallet 61 moves gradually in the disengagement direction with respect to the escape wheel 42 (the direction of retractation with respect to an encroachment on the rotational path R of the escape wheel 42 ) following the rotation of the sprung balance 30.

As shown on lafig. 14, when the second impact pallet 61 moves to reach a position slightly deviating from the rotation path R of the escape wheel 42, the direct impact on the balance-spring 30 as explained herein above is finished.

When the second impact pallet 61 moves in the disengagement direction with respect to the escape wheel 42 following the rotation of the balance spring 30, the first stop pallet 62 advances to encroach on the rotation path R of the escape wheel 42 following the pivoting, in the counterclockwise direction, of the stop anchor 53.

Immediately after the second impact pallet 61 has moved into a position deviating from the rotation path R of the escape wheel 42, the working surface 43a of the gearing of the escape gear 43 is brought into contact with the first engagement surface 62a of the first stop pallet 62, which has advanced to encroach on the rotation path R of the escape wheel 42. At this time, the The impact anchor 51 moves toward the limiting pin 102 by pivoting clockwise. However, at this point, the impact anchor 51 is configured not to be in contact with the limiting pin 102. Therefore, the impact anchor 51 and the stop anchor 53 turn slightly then that the escape gear teeth 43 and the first stop pallet 62 remain in contact.

As illustrated in FIG. 15, when the outer lateral surface 100 of the impact anchor 51 comes into contact with the limiting pin 102, the impact anchor 51 can no longer rotate further and is thus positioned. Therefore, any movement of the entire anchor chain 50 is prevented and the escape gear teeth 43 and the first stop pallet 62 enter a engaged state, i.e. mutual influence. Therefore, the rotation of the escape wheel 40 stops. The anchor chain 50 enters a stopped state.

Then, by repeating the operating operations explained above according to the alternating rotation of the sprung balance 30, the exhaust 13 comes, repeatedly, to engage the first stopping pallet 62 and the second stopping pallet 63 with the toothing of the escape gear 43, and respectively disengage them from the latter, and carries out a transmission of the energy of the sprung balance 30 using the contact of the gear teeth of Exhaust 43 with the first impact pallet 60 and the second impact pallet 61. In particular, it is possible to transmit the energy, which is transmitted to the escapement wheel 40, to the balance-spring 30 by alternately performing ( by switching) an indirect power transmission performed using the first impact pallet 60 and an indirect power transmission performed using the second impact pallet 61.

Therefore, it is possible to encourage the exhaust 13 to function as an exhaust 13 of the type of those described as semi-direct impact, which simultaneously use the direct impact and the indirect impact. It is thus possible to ensure stable operation and energy transmission.

In particular, with the escapement 13 according to the embodiment described, unlike a conventional escapement in which the impact pallet and the stopping pallet are incorporated in a common anchor, the impact anchor 51 comprises the first impact pallet 60, while the stop anchor 53 comprises the first stop pallet 62 and the second stop pallet 63.

Therefore, it is possible to freely design and respectively dispose, with less restriction, the relative position of the impact anchor unit 52 (the impact anchor 51) relative to the mobile of Exhaust 40 and the relative position of the stop anchor unit 54 (the stop anchor 53) relative to the escape wheel 40. It is thus possible to arrange the impact anchor unit. 52 and the stop anchor unit 54 in respectively optimal planes for impact and stopping.

In the following, we explain an operating relationship between the stop anchor 53 and the escape wheel 40.

[0158] FIG. 16 shows 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 pivot axis 04) of the stop anchor 53, and the retracting angle of the escape wheel 40.

[0159] Please note that in fig. 16, the escape wheel 40 is not illustrated. However, the rotation path R drawn by the tip of the escape gear teeth 43 is illustrated. Consequently, the rotation path R corresponds to the external diameter of the escape wheel 42.

[0601] Moreover, FIG. 16 represents a first case where the center of pivoting of the stop anchor 53 is disposed in a position remote from a distance L1 with respect to the rotation path R of the escape wheel 42, and a second case where the center of pivoting of the stop anchor 53 is disposed in a position remote by a distance L2, longer than the distance L1, with respect to the rotation path R of the escape wheel 42.

In both cases, the first stop pallet 62 moves, in the direction of pivoting of the stop anchor 53, between an engagement position X1 where the escape gear teeth 43 is engaged with the first stop pad 62, and a release position X2 where the first stop pad 62 moves to a position deviating from the rotation path R of the escape wheel 42, and disengages from the escape gear 43.

The angle between the segment connecting the first engagement surface 62a of the first stop pallet 62 and the pivot center of the stop anchor 53 and a direction normal to the first surface of commitment 62a is considered the angle of incidence a1. The required pivot angle for the stop anchor 53 while the first stop pad 62 moves from the engagement position X1 to the release position X2 is considered as the working angle (or an angle clearance / release) a2. In addition, reference is made to the retracting angle of the escapement wheel 40 involved in the movement of the first stopping pallet 62 from the engagement position X1 to the stowing position X2 as the retracting angle. a3.

Under the conditions defined above, it is explained how the distance between the pivot center of the stop anchor 53 and the rotation path R of the escape wheel 42 affects the retraction angle a3. when the working angle a2 is set to a predetermined value.

As shown in FIG. 16, when the stop anchor 53 rotates the same working angle a2 respectively in a state where the center of pivoting of the stop anchor 53 is spaced a distance L2 from the rotation path R of the wheel d 42, and a state where the center of pivoting of the stop anchor 53 is spaced a distance L1 from the rotation path R of the escape wheel 42, it is possible to define a retraction angle a3 smaller for distance L1 than for distance L2. In other words, it is possible to define the retraction angle a3 as being smaller when the pivot center of the stopping anchor 53 is closer to the rotation path R.

Therefore, it is possible to reduce the retraction angle of the escapement wheel 40 by putting the center of pivoting of the stop anchor 53 as close as possible to the rotation path R of the wheel. Exhaust 42. It is possible to reduce the energy required for the release of the stop of the escapement 40 (that is, the energy required to return the retracted exhaust wheel 40 again in its original direction of rotation).

[0166] Please note that in fig. 16, the explanation focuses on the first stopping pallet 62. However, the same reasoning applies to the second stopping pallet 63. Therefore, an optimal plan for stopping is to bring the center of stopping. pivoting of the stop anchor 53 to be as close as possible to the rotation path R of the escape wheel 42 (i.e., the outer diameter of the escape wheel 42).

In particular, the working angle of the anchor is an extremely important parameter in the operation of the escapement 13. For this purpose, according to this embodiment, a pallet intended for impact is not attached to the stop anchor 53 and only the first stop pallet 62 and the second stop pallet 63, which are pallets for stopping, are attached to the stop anchor 53. it is possible to adjust the working angle a2 of the stop anchor 53 to an optimum angle concentrating only on the stopping action. It is thus possible to arrange the stop anchor 53 so that the center of pivoting of the stop anchor 53 approaches the maximum of the rotation path R of the escapement wheel 42.

Therefore, according to this embodiment, it is possible to reduce the energy required for the release of the escapement 40 from its shutdown state to improve the efficiency of energy transmission and reduce malfunctions.

In what follows, an operating relationship is explained between the impact anchor 51 and the escapement wheel 40.

[0170] FIG. 17 is a diagram showing a relationship between the escape gear teeth 43 of the escape wheel 42 and the first impact pad 60 which are in contact with each other. Please note that in fig. 17, 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 line of contact.

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 power 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.

[0173] 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 and the first impact pallet 60 and a contact point 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 of 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 d 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 oc4 and working angle oc5 substantially satisfy the mathematical relation (L3 / L4) = (α5 / α4).

Therefore, a design respecting these proportions is an optimal arrangement for the impact.

According to this embodiment, no stop pallet is attached to the impact anchor 51, and only the first impact pallet 60, which is a pallet for an impact, is attached to the impact anchor 51. Impact anchor 51. Therefore, it is possible to adjust the working angle of the impact anchor 51 at an optimum angle by focusing only on the impact action. Therefore, it is possible to indirectly efficiently transmit a power, which is transmitted to the escape wheel 40, balance-balance 30.

As explained above, with an exhaust 13 according to the embodiment described, it is possible to achieve a design optimized for impact and stopping. The exhaust 13 can be configured as an exhaust which 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, and respectively the first stop pallet 62 and the second stop pallet 63 engage with the working surface 43a of Thus, it is possible to arrange the escape wheel 40 in a single layer structure, that is to say with a single level of gearing. Therefore, it is possible to prevent any increase in the inertia of the escape wheel 40. Therefore, it is also possible to improve the energy transmission efficiency.

[0180] Furthermore, when the escape gear teeth 43 engage with the first stop pallet 62 or the second stop pallet 63 and the rotation of the escape wheel 40 is stopped, that is to say, when the plate pin 38 disengages from the fork 74 and the balance spring 30 oscillates freely, the impact anchor 51 is brought into contact with one or the other pair of pairs. limiting pins 102 and 103 using the outer side surfaces 100 and 101. Therefore, it is possible to position the impact anchor 51 located at the coupling end of the anchor chain 50. It is possible to restrict moving the entire anchor chain 50.

Therefore, for example, even if some disturbance is introduced while the spring balance 30 oscillates freely, it is possible to prevent the anchor chain 50 undulates or oscillates. Therefore, it is possible to operate the exhaust 13 stably.

In addition, since the exhaust 13 in this embodiment is of the type called semi-direct impact, it is possible to have the sprung balance 30 and the exhaust 40 in positions close to the one of the other. Therefore, for example, when the exhaust 13 according to this embodiment is applied to a vortex, it is possible to contribute to a size reduction of the cage on which a mechanism including the exhaust 13 is mounted. Therefore, it is possible to make an exhaust 13 particularly suitable for a vortex.

With a movement 10 and a timepiece 1 according to the embodiment above, since the movement 10 and the timepiece 1 include the exhaust 13 explained above which is excellent in transmission efficiency of energy and has less operating error, therefore, the movement 10 and the timepiece 1 are a movement and a timepiece with less error of deviation and a very high performance.

[0184] (Second Embodiment) [0185] In the following, a second embodiment according to the present invention is explained with reference to the drawings. Note that in this second embodiment, the same parts as the components of the first embodiment are indicated by the same numbers and reference signs, and no explanation of these parts will be provided again.

In the first embodiment, the impact anchor 51 is positioned using the pair of limiting pins 102 and 103; however, in the second embodiment, the impact anchor 51 is positioned using a single limiting pin. In addition, in the first embodiment, the stop anchor 53 is disposed below the impact anchor 51. However, in the second embodiment, the impact anchor 51 and the stop anchor 53 are configured to be arranged on the same plane.

As shown in FIGS. 18 and 19, in the escapement 110 according to this embodiment, a positioning hole 112, through which a limiting pin 111 is inserted, is formed in the impact anchor 51.

In the impact anchor 51, a coupling piece 113 which couples the anchor body 71 and the first pallet holding portion 76 is integrally formed between the anchor body 71 and the first holding portion 71. The positioning hole 112 is formed in the coupling piece 113.

Specifically, the positioning hole 112 passes through the coupling piece 113 in the thickness direction of the coupling piece 113 and has an arcuate shape in a plan view extending along the pivoting direction of the coupling member 113. impact anchor 51 (i.e. the pivoting direction about the pivot axis 03). The length (the circumferential length) of the positioning hole 112 along the circumferential direction of the pivot axis 03 corresponds to a pivot angle (a working angle) in which the impact anchor 51 rotates between a state of rotation. wherein the first stop pallet 62 and the escape gear teeth 43 of the escape wheel 42 are mutually engaged, and a state in which the second stop pallet 63 and the tooth gear of exhaust 43 of the escape wheel 42 are mutually engaged.

[0190] The limiting pin 111 is disposed in the positioning hole 112 explained above. The limiting pin 111 is fixed to the plate 11 and inserted through the positioning hole 112 from the bottom. In this case, the other circumferential surface of the limiting pin 111 is in sliding contact with the inner circumferential surface of the positioning hole 112. Therefore, the limiting pin 111 moves in the positioning hole 112 and relatively to the to the latter according to the pivoting of the impact anchor 51.

At this time, since the length of the positioning hole 112 along the circumferential direction corresponds to the pivot angle of the impact anchor 51, as shown in FIG. 18, when the first stop pallet 62 and the escape gear teeth 43 engage each other, the limiting pin 111 is brought into contact with a first inner circumferential surface 112a located on the side of the first pallet impact 60 in the inner circumferential surface of the positioning hole 112. Therefore, the impact anchor 51 is positioned by the limiting pin 111.

As shown in FIG. 19, when the second stop pallet 63 and the escape gear teeth 43 engage each other, the limiting pin 111 is brought into contact with a second inner circumferential surface 112b located on the side of the anchor body 71 on the inner circumferential surface of the positioning hole 112. Therefore, the impact fork 51 is positioned by the limiting pin 111.

Therefore, even with a single limiting pin 111, it is possible to position the impact anchor 51. Note that the first inner circumferential surface 112a and the second inner circumferential surface 112b in the positioning hole 112 operate as a restriction section which contacts the limiting pin 111 to position the impact anchor 51 and limit the range of motion of the entire anchor chain 50.

[0194] Please note that, according to this embodiment, since the impact anchor 51 and the stop anchor 53 are arranged in the same plane, the first stop pallet 62 and the second stop pallet 63 are maintained in a state in which the first stop pallet 62 and the second stop pallet 63 extend further down than the anchor body 91 to reach a position of height equivalent to that of the wheel. 42. Therefore, the first stop pallet 62 and the second stop pallet 63 can engage with and respectively disengage from the escape gear 43.

[0195] An engagement plate 115 taking a circular shape in a plan view is arranged at the distal end of the anchor arm 72 in the impact anchor 51 instead of the engagement pin 77.

The engagement plate 115 is formed by a pair of elastic sections 116. The pair of elastic sections 116 is formed by semicircular sections respectively in plan view, and each of the sections being induced to separate from each other. the other as indicated by the arrows visible in fig. 18 and 19.

In the state where the engagement plate 115 is engaged on the inner side of the engagement fork 92, the anchor body 91 of the stop anchor 53 is disposed on the same plane relative to the anchor body 71, and the anchor arm 72 of the impact anchor 51. The outer circumferential surface of the engagement plate 115 and the inner surface of the engagement fork 92 are mutually engaged with one another. with each other in a sliding way. Therefore, the impact anchor 51 and the stop anchor 53 are coupled to each other while being able to move relative to each other, and rotate in opposite directions. one of the other in a state in which the impact anchor 51 and the stop anchor 53 are disposed in the same plane.

In particular, the engagement plate 115 of the impact anchor 51 and the engagement fork 92 of the stop anchor 53 are coupled to each other in a state in which the outer circumferential surfaces of the pair of elastic sections 116 are held in compression against the inner surface of the engagement fork 92.

[0199] (Operation of the exhaust) [0200] With an escapement 110 according to this embodiment configured in this way, it is possible to perform the same action and obtain the same effects as the action performed and the effects obtained by through the first embodiment.

[0201] In other words, with the exhaust 110 according to this embodiment, it is possible to repeatedly engage and alternate clearance of the escape gear teeth 43 with the first stop pallet 62 and the second stopping pallet 63. It is possible to transmit the energy, which has been transmitted to the escape wheel 40, to the sprung balance 30 while alternately performing an indirect energy transmission performed using the first pallet impact 60, and indirect energy transmission performed using the second impact pallet 61.

As shown in FIG. 18, when the escape gear teeth 43 and the first stop pad 62 are in mutual engagement, the first inner circumferential surface 112a of the positioning hole 112 comes into contact with the limiting pin 111 and the anchor impact 51 is thus positioned. As shown in FIG. 19, when the escape gear teeth 43 and the second stop pallet 63 are in mutual engagement, the second inner circumferential surface 112b of the positioning hole 112 comes into contact with the limiting pin 111 and the anchor impact 51 is thus positioned.

In all cases, the impact anchor 51 is an anchor equivalent to the coupling end of the anchor chain 50. Therefore, when the escape gear teeth 43 are in mutual engagement with each other. with the first stop pallet 62 or the second stop pallet 63, and that the rotation of the escape wheel 40 is stopped, it is possible to limit the displacement of the entire anchor chain 50.

Therefore, according to this embodiment also, for example, even if some disturbance occurs when the sprung balance 30 oscillates freely, it is possible to prevent the anchor chain 50 does not wave or oscillates. Therefore, it is possible to operate the exhaust 110 stably.

In particular, in contrast to the first embodiment, only a limiting pin 111 must be provided and the limiting pin 111 may be arranged in a plane corresponding to that of the impact anchor 51. It is possible to dispense with or effectively utilize the space occupied by the pair of limiting pins 102 and 103 of the first embodiment.

In addition, the engagement plate 115 of the impact anchor 51 and the engagement fork 92 of the stop anchor 53 are coupled to each other in a state in which the outer circumferential surface of the pair of elastic sections 116 are held in compression against the inner surface of the engagement fork 92. Therefore, it is possible to prevent the formation of a gap between the engagement plate 115 and the As a result, it is possible to couple the impact anchor 51 and the stop anchor 53 to each other with fewer jerks.

Therefore, it is possible to effectively prevent the occurrence of jerks or backlash between the impact anchor 51 and the stop anchor 53. It is possible to rotate the anchor impact 51 and stop anchor 53 with a good mutual reaction. Therefore, it is possible to operate the escapement 110 smoothly. It is thus possible to further improve operational performance.

[0208] Please note that, according to the second embodiment, the impact anchor 51 and the stop anchor 53 are coupled while being able to move relative to each other via the engagement of the engagement plate 115 with the engagement fork 92. However, the coupling of the impact anchor 51 with the stop anchor 53 is not limited to such a case. The impact anchor 51 and the stop anchor 53 may also be coupled, for example, through a tooth section gear.

For example, in the exhaust 120 shown in FIG. 20, in the first pallet holding portion 76 in the impact anchor 51, a plurality of teeth 121 arranged along the pivot direction of the impact anchor 51 is formed in the first direction of rotation M1. . At the circumferential end 91b of the anchor body 91 of the stop anchor 53, in place of the engagement fork 92 according to the second embodiment, a plurality of teeth 122 which mesh with the teeth 121 of the impact anchor 51 is formed to correspond to the teeth 121. Therefore, the impact anchor 51 is coupled to the stop anchor 53 by meshing the toothed sections 121 and 122.

With an escapement 120 configured in this way, it is possible to perform the same actions and obtain the same effects as those achieved and those obtained through the second embodiment.

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 modifica

Claims (4)

Embodiments of the proposed embodiments include, for example, alternative embodiments and modifications readily adopted by those skilled in the art, substantially identical embodiments and modifications to the proposed embodiments and their variants, as well as embodiments and modifications within the scope of the doctrine of equivalents. For example, in the embodiments described, the proposed configuration for transmitting the energy of the motor spring 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 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 stop 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 formed of other brittle materials and metal materials such as iron-based alloys. Furthermore, the pallets may be formed of a semiconductor material such as silicon and formed integrally with the anchor integrally by a semiconductor manufacturing 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. In the embodiments described, the impact anchor unit is formed by a single anchor. However, the impact anchor unit is not limited to such a case. For example, the impact anchor unit could be formed, for example, by two or more anchors. The first impact pallet may be attached to any of the two or more anchors. [0216] Similarly, in the embodiments described, the stop anchor unit is formed by a single anchor. However, the stop anchor unit is not limited to such a case. The stop anchor unit could be formed, for example, by two or more anchors. The stopping pallets could be respectively attached to two anchors chosen from the two or more anchors. In addition, in the embodiments described, the use of an escapement mobile according to a single-layer structure is given as an example. However, the escape mobile is not limited to such a case. For example, an escape wheel having a double layer structure in which a first escape wheel and a second escape wheel overlap on the same axis could be adopted. The escape mobile could thus have a configuration similar to that of the exhaust called Coaxial. [0218] Even in such a case, according to this embodiment, the impact anchor comprises the first impact pallet and the stop anchor comprises the first stop pallet and the second stop pallet. Therefore, it is possible to respectively dispose the impact anchor and the stop anchor relative to the escapement of the double layer structure so that the impact action and the action of stopping are carried out optimally. For example, the first impact pallet attached to the impact anchor and the second impact pallet attached to the sprung balance can be configured so that they can come into contact with the escape gear of the first escape wheel. The first stop pallet and the second stop pallet attached to the stop pallet may be configured so that it can engage with and respectively disengage from the second wheel exhaust gear. exhaust. Therefore, for example, it is possible to perform the same actions and obtain the same effects as those achieved and respectively those obtained via the first embodiment. However, when the escapement mobile according to a single-layer structure is adopted, as in the embodiments described, it is possible to prevent any increase in the inertia of the escapement mobile with respect to a double structure. layer. Therefore, it is easy to improve the energy transmission efficiency. claims An exhaust (13) comprising: an escapement wheel (40) which rotates due to energy transmitted thereto; and an impact anchor unit (52) and a stop anchor unit (54) coupled to each other while remaining movable relative to each other to pivot on the base of the rotation of a sprung balance (30), wherein the stopping anchor unit (54) is formed by at least one or more anchors and comprises a stopping pallet engageable with and disengage from an escape wheel (42) of the escape wheel (40), the impact anchor unit (52) is formed by at least one or more anchors and includes a first impact pallet (60) can be brought into contact with the escape wheel (42) in the absence of engagement of the latter with the stop pallet, and a second impact pallet (61), which can be brought to come into contact with the escape wheel (42) in the absence of contact of the latter with the first impact pallet (60), and which is fixed e to the sprung balance (30). An exhaust (13) according to claim 1, wherein the impact anchor unit (52) comprises an impact anchor (51) having the first impact pallet (60), the stop anchor (54) includes a stop anchor (53) having a pair of stopping vanes coupled to, but movable relative to, the impact anchor (51), and both stopping vanes are alternately engaged and disengaged from the escape wheel (42) in the pivoting direction of the stopping anchor (53). 3. Movement (10) of timepiece comprising: the exhaust (13) according to claim 1 or 2; a speed controller (14) including the sprung balance (30); and a gear train (12) that transmits energy to the escape wheel (40). 4. Timepiece (1) comprising: the movement (10) of a timepiece according to claim 3; and a needle (4) which rotates at a speed of rotation adjusted by the exhaust (13) and the speed regulator (14).