CH713529B1 - Escapement, timepiece 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 set (40) rotating by power transmitted thereto, an impulse transmission device (52) and a stop device (54) coupled together to each other but which can move relative to each other, in order to be able to pivot according to the rotation of a balance-spring (30). The stop device (54) is formed by at least one or more anchors (53) and comprises resting pallets (62, 63), capable of engaging with and disengaging from an escapement wheel (42) of the escape wheel set (40). The impulse transmission device (52) is formed by at least one or more anchors (51), and comprises a first impulse pallet (60) which can be brought into contact with the escape wheel (42) in the absence of mutual engagement of the latter with the rest pallet (62, 63). A second impulse pallet (61) which can be brought into contact with the escapement wheel (42) in the absence of contact with the first impulse pallet (60) is fixed to the balance-spring (30) .

Description

BACKGROUND OF THE INVENTION

1. Field of the invention

The present invention relates to an escapement, a timepiece movement, and a timepiece.

2. Description of prior art

[0002] In general, a mechanical timepiece includes an escapement which transmits energy to drive a balance-spring in rotation according to a back-and-forth movement, and controls a gear train with constant oscillation using the regular alternating rotation of the balance-spring. Exhausts of this type have been worked out in a conventional way, for example, while being improved several times. Currently, various types of exhausts are offered.

[0003] For example, as an escapement having high efficiency and high durability, the escapement from a natural escapement invented by Breguet is known. Escapements of this type have the characteristic that the escapement includes two escapement mobiles formed respectively by a wheel and a pinion, and alternately carries out a direct impact and an indirect impact via an anchor on a balance-spring from the two escapement wheels (i.e. wheel & pinion) to transmit energy to the balance-spring.

[0004] In particular, unlike a crab-shaped lever escapement which is most often used in conventional mechanical timepieces, this escapement is designed to reduce slippage of the ends of the escapement mobile during impact. . This eliminates the wear of the ends of the escapement mobile and improves its durability. When the direct impact is made on the balance-spring, it is possible to transmit the impact from the escapement wheel set to the balance-spring without passing through other components of the timepiece. Therefore, an improvement in efficiency is realized.

[0005] Furthermore, when the escapements are roughly classified by concentrating on the power transmission systems from the escapement mobile (that is to say the wheel and the escapement pinion) to the balance-spring, escapements are mainly roughly classified into a direct impact type for the direct transmission of energy from the escapement wheel set to the balance-spring, and an indirect impact type for the transmission of energy indirectly from the escapement wheel to the balance-spring via other components of the timepiece such as an anchor. Also known are escapements which jointly use both the direct impact and the indirect impact.

[0006] As an escapement which simultaneously uses both a direct impact and an indirect impact, the so-called Coaxial escapement, which is widely used (a coaxial escapement) is conventionally known, including an escapement mobile (i.e. i.e. an escapement wheel and pinion) having a double-layered structure in which two escapement 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. 0018796 - or non-patent scientific literature document 1 - George Daniels, „WATCHMAKING ( Edition 2011 updated)“, Philip Wilson Publishers Ltd., June 15, 2011, p. 238 to p.252).

[0007] The coaxial escapement comprises an escape wheel (that is to say an escape wheel & pinion) having a double-layer structure in which a first escape wheel and a second escape wheel escapement with a larger diameter than the first escape wheel are superimposed on the same axis, an anchor provided with a first impulse pallet, a first rest pallet, and a second rest pallet, and which can be rotated based on the rotation of a balance-spring, as well as a second impulse pallet fixed to the balance-spring.

[0008] The first impulse pallet may be brought into contact with one end of the first escape wheel depending on the direction of pivoting of the lever. The second impulse pallet may be brought into contact with one end of the second escape wheel depending on the rotation of the balance-spring. The first pallet rest and the second pallet rest can respectively engage with and disengage from the end of the second wheel according to the direction of pivoting of the anchor.

[0009] With the coaxial escapement configured in this way, the first pallet rest and the second pallet rest engage with and alternately disengage from the second escapement wheel in the direction of pivoting of the lever. Consequently, it is possible to control the rotation of the escape wheel set. The first impulse pallet comes into contact (in collision) with the end of the first escape wheel according to the direction of pivoting of the lever. Consequently, it is possible to indirectly transmit the energy, which is transmitted to the escapement wheel (that is to say the wheel and the escapement pinion), to the balance-spring via the lever. It is possible to supply rotational energy to the balance-spring. Furthermore, the second impulse pallet comes into contact (collides) with the end of the second escape wheel according to the rotation of the balance spring. Consequently, it is possible to directly transmit the energy, which is transmitted to the escapement mobile (that is to say the wheel and the escapement pinion), to the balance-spring. It is possible to supply rotational energy to the balance-spring.

[0010] Consequently, it is possible to transmit the energy which is transmitted to the escape wheel set (that is to say the wheel and the escape pinion), to the sprung balance wheel by alternately performing a transmission of indirect power and direct power transmission.

[0011] Further, patent document 1 and non-patent literature document 1 also disclose an escapement which jointly uses both direct impact and indirect impact using an escapement mobile (i.e. an escapement wheel and pinion) having a single layer structure rather than an escape wheel set having a double layer structure.

In this escapement, a first pallet rest and a second pallet rest can engage with and respectively disengage from an escapement wheel. Furthermore, a first impulse pallet and a second impulse pallet may be brought into contact with the same escape wheel.

[0013] However, in the conventional coaxial escapement, since the escapement wheel has a double-layered structure, the inertia of the entire escapement wheel (i.e. wheel and pinion exhaust) is large and the dynamic efficiency can easily deteriorate. It is necessary to assemble the escape wheel set by performing a phase focusing on the first escape wheel and the second escape wheel. Therefore, assembly tolerances may occur. Even though the escapement is affected by assembly tolerances, operational reliability needs to be guaranteed for the escapement. Therefore, a spacing link between the first escapement wheel and the second escapement wheel and the pallets must be ensured rather broadly taking into account the assembly tolerances. Therefore, as a result, the power transmission efficiency may easily degrade.

[0014] When an escape wheel set (that is to say the wheel and the escape pinion) having a single-layer structure is used, it is necessary to engage the first rest pallet and the second pallet rest with the escapement wheel, and to disengage the first pallet rest and the second pallet rest from this common escapement wheel. It is necessary to bring the first impulse pallet into contact with the common escapement wheel. However, since the first resting pallet, the second resting pallet, and the first impulse pallet are incorporated into the same anchor, in order to properly engage the pallets with the escape wheel and disengage the pallets from the escapement wheel, or put the pallets in contact with the escapement wheel, it is necessary to dissociate a pivoting center of the lever from the end of the escapement wheel, by spacing the latter by a fixed distance in the radial direction of the escape wheel.

[0015] However, for example, when focusing on the stopping action, since the pivot point of the anchor is farther from the end of the escape wheel, the sliding distance of the the end of the escape wheel sliding on the rest pallet increases until it is disengaged from the rest pallet. Therefore, the energy required for the release of the escape wheel stopper increases, which causes a deterioration in the energy transmission efficiency.

[0016] Further, since the first resting paddle, the second resting paddle, and the first impulse paddle are incorporated into a common anchor, the anchor cannot be operationally used at respectively optimum working angles for impact and stoppage, which causes deterioration in power transmission efficiency.

SUMMARY OF THE INVENTION

[0017] The present invention has been devised in view of such circumstances, and an object of the present invention is to provide an escapement, a timepiece movement, and a timepiece which are excellent in efficiency. of power transmission.

(1) An escapement according to the present invention is defined by claim 1.

[0019] According to the present invention, it is possible to respectively pivot, on the basis of the rotation (alternating rotation, according to a reciprocating movement) of the sprung balance, the impulse transmission device and the stop device coupled to each other while remaining movable relative to each other. By pivoting the impulse transmission device, it is possible to cause the movement of the first impulse pallet so that it comes into contact (collision) with the escape wheel. Consequently, it is possible to transmit energy, which is transmitted to the escapement wheel set, indirectly to the balance-spring via the impulse transmission device. It is thus possible to supply rotational energy to the balance-spring. Since the second impulse pallet is fixed to the balance-spring, when the balance-spring rotates, it is possible to cause the movement of the second impulse pallet so that it comes into contact (in collision ) with the escape wheel. Consequently, it is possible to transmit the energy, which is transmitted to the escapement wheel set, directly to the balance-spring via the second impulse pallet. It is thus possible to supply rotational energy to the spiral balance. In addition, when the stop device pivots, it is possible to bring the resting pallet into engagement with the escapement wheel to stop the rotation of the escapement mobile, or disengage the resting pallet into engagement with the wheel escape wheel from the escape wheel, and releasing the stop of the escape mobile.

[0020] In this way, it is possible to transmit the energy, which is transmitted to the escapement mobile, to the balance-spring 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 escapement wheel set with a constant oscillation corresponding to the balance-spring.

[0021] In particular, unlike the conventional escapement in which the impulse pallet and the rest pallet are incorporated in a common lever, the impulse transmission device comprises only the impulse pallet (the first pallet of 'impulse) and the stop device comprises only the rest pallet. Therefore, it is possible to respectively freely design and dispose, with fewer restrictions, of the relative positions of the impulse transmission device and the stop device with respect to the escapement wheel set. It is possible to arrange the impulse transmission device and the arresting device in optimum configurations respectively for the impact and the arrest.

[0022] Therefore, for example, it is possible to respectively determine an anchor working angle for the impulse transmission device and an anchor working angle for the arresting device as being equal to optimum angles taking into account the impact action and the stopping action. Therefore, it is possible to improve the power transmission efficiency. It is possible to realize an escapement having fewer operating errors.

[0023] In addition, it is possible to respectively determine an inter-central distance between the center of rotation of the escape wheel set (that is to say the wheel and the escape pinion) and the pivot point for the impulse transmission device and an inter-central distance between the center of rotation of the escapement wheel set and a pivot point for the stop device as being equal to optimum distances taking into account the action of impact and stopping action. Therefore, unlike a conventional escapement in which the impulse pallet and the rest pallet are incorporated in a common pallet, it is possible to prevent the energy required to release the mobile stop from increasing. exhaust, thus leading to improved power transmission efficiency.

[0024] In the case where the escapement is according to claim 2, the impulse transmission device may be formed by an anchor, that is to say, the impulse transmission anchor. The stop device can 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 locking anchor, it is possible to alternately bring the two rest pallets into engagement with the escape wheel, and to disengage them from the escape wheel according to the direction of pivoting of the anchor d 'stop. It is thus possible to appropriately control the rotation of the escapement wheel according to a constant oscillation corresponding to that of the balance-spring.

(3) A timepiece movement according to the present invention is defined by claim 3.

[0026] (4) A timepiece according to the present invention is defined by claim 4.

[0027] In this case, since the proposed timepiece movement and timepiece include an escapement which is excellent in power transmission efficiency and exhibits less operating error, it It is possible to produce a timepiece movement and a timepiece which exhibits reduced variations in rate and demonstrates high performance.

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

BRIEF DESCRIPTION OF DRAWINGS

Figure 1 is an exterior view of a timepiece representing a first embodiment according to the present invention. Figure 2 is a plan view of a movement shown in Figure 1. Figure 3 is a perspective view of a double plate of a balance-spring shown in Figure 2. Figure 4 is a view in plan of an escapement shown in Fig. 2. Fig. 5 is a cross-sectional view of the escapement taken along a line A-B shown in Fig. 4. Fig. 6 is a cross-sectional view of the escapement taken along a line A-C shown in Fig. 4. Fig. 7 is an explanatory diagram of the operation of the escapement and is a diagram showing a state in which a first rest pallet begins to disengage from a gear of escapement starting from the state shown in Fig. 4. Fig. 8 is an explanatory diagram of the operation of the escapement and is a diagram showing a state in which the first rest pallet is completely disengaged from the escapement gear starting from the state shown in Figure 7 and then the gear exhaust comes into contact with a first impulse pallet. Figure 9 is an explanatory diagram of the operation of the escapement and is a diagram showing a state in which the first impulse pallet is completely disengaged from the escapement gear starting from the state shown in Figure 8 and , then the escapement gear comes into contact with a second rest pallet. Figure 10 is an explanatory diagram of the operation of the escapement and is a diagram showing a state in which an impulse transmission anchor comes into contact with a limiting pin and consequently the escapement gear and the second pallet of rest are engaged starting 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 plate pin moves in the direction of the impulse transmission anchor starting from the state represented in FIG. 10. FIG. 12 is a diagram explaining the operation of the escapement and is a diagram representing a state in which the second rest pallet is completely disengaged from the escapement gear starting from the state shown in Fig. 11. Fig. 13 is an explanatory diagram of the operation of the escapement and is a diagram showing a state in which the escapement gear escapement comes into contact with a second impulse vane starting from the state shown in FIG. 12. FIG. 14 is an explanatory diagram of the operation of the escapement and is a diagram representing a state in which the second impulse vane impulse is completely released from the escapement gear starting from the state shown in Fig. 13. Fig. 15 is an explanatory diagram of the operation of the escapement and is a diagram showing a state in which the gear escapement comes into contact with the first rest pallet starting from the state shown in Fig. 14, and the impulse transmission anchor comes into contact with the limiting pin and consequently the escapement gear and the first rest 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 escapement wheel set, a pivot point of a stopper anchor, and an angle retraction of the escapement mobile. Fig. 17 is a diagram for explaining an optimum configuration for impact and is a diagram showing a relationship between the escapement gear of the escapement wheel set and the first impulse vane which are in contact with each other. 'other. Figure 18 is a plan view of an escapement according to a second embodiment of the present invention. Figure 19 is a plan view of the escapement changed from a state shown in Figure 18 to a state in which the escapement gear and the second rest pallet are in mutual engagement. Figure 20 is a plan view of an escapement according to a variant of the second embodiment of the present invention.

DESCRIPTION OF EMBODIMENTS

(First embodiment)

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 drawings, component scales are changed as needed to meet the need to show components in visually recognizable sizes.

(Basic configuration of the timepiece)

[0031] Generally, a part body including a control part of a timepiece is referred to as being a “movement”. The condition of a completed product obtained by attaching a dial and a hand to the movement and housing the movement in a timepiece case is referred to as the “whole” of the timepiece.

Among the two sides of the plate 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 being the „rear side“ of the movement. Of the two sides of the plate, the side on which a caseback of the timepiece case is present (i.e., a side opposite the dial) is referred to as the "front side". movement.

[0033] Please note that, in the following explanation relating to this embodiment, a direction from the dial towards the bottom of the case is defined as upward (upward) and the opposite direction is defined as downward (towards the bottom).

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

As illustrated in Figure 2, the movement 10 includes a plate 11 forming a substrate. Please note that, in Figure 2, part of the components configuring the movement 10 are not illustrated 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 escapement 13 which controls the rotation of the front gear train 12, and a regulating device 14 which regulates the speed of the escapement 13.

[0037] The front gear train 12 mainly comprises a movement barrel 20, a center wheel set 21 (that is to say a wheel and a center pinion), a third wheel set 22 (that is to 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). Movement barrel 20 is supported axially between plate 11 and a barrel bridge, not shown. A barrel spring, not shown (constituting a source of energy) is housed inside the movement barrel 20. A ratchet wheel 24 rotates, thanks to which the spring can be wound. Please note that the ratchet wheel 24 rotates following the rotation of a winding stem, not shown, coupled to a crown 25 illustrated in Figure 1.

The center wheel set 21, the third wheel set 22, and the second wheel set 23 are held axially between the plate 11 and a gear train bridge, not shown. When the movement barrel 20 rotates under the impulse of the elastic return force of the spring which has been wound, the center wheel set 21, the third wheel set 22, and the seconds wheel set 23 are driven in rotation according to this order on the basis of barrel rotation.

[0039] In other words, the center mobile 21 meshes with the movement barrel 20 and rotates based on the rotation of the movement barrel 20. Please note that, when the center mobile 21 rotates, a barrel pinion not shown also rotates based on this rotation. The minute hand 6 shown in Figure 1 is attached to the barrel pinion. The minute hand 6 displays the current minute („minute“) according to the rotation of the barrel pinion. The minute hand 6 performs a complete revolution at a speed of rotation regulated by the escapement 13 and the regulating device 14, that is to say, in one hour.

[0040] When the center mobile 21 rotates, a minute wheel, not shown, rotates on the basis of this rotation. Further, a not shown hour wheel rotates based on the rotation of the minute wheel. Please note that the minute wheel and the hour wheel are timepiece components forming the front gear train 12. The hour hand 5 shown in Figure 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 speed of rotation regulated by the escapement 13 and the regulating device 14, for example, in twelve hours.

The third mobile 22 meshes with the center mobile 21 and rotates based on the rotation of the center mobile 21. The seconds mobile 23 meshes with the third mobile 22 and rotates based on the rotation of the third mobile 22. The seconds hand 7 represented in FIG. 1 is fixed to the seconds wheel 23. The seconds hand 7 displays the current second (“second”) according to the rotation of the seconds wheel 23. The hand seconds 7 performs a complete revolution at a speed of rotation regulated by the escapement 13 and the regulating device 14, for example, in one minute.

[0042] An escape wheel 40 as explained below meshes with the seconds wheel 23 via an escape pinion 41. Consequently, the energy of the spring housed in the movement barrel 20 is transmitted to the wheel escapement wheel 40 essentially via the center wheel set 21, the third wheel set 22, and the seconds wheel set 23. Consequently, the escape wheel set 40 rotates around an axis of rotation O2.

The regulating device 14 mainly comprises a balance-spring 30.

The balance-spring 30 includes a balance shaft 31, a balance wheel 32, and a spiral spring, not shown. The balance-spring 30 is held axially between the plate 11 and a balance bridge, not shown. The balance-spring 30 rotates according to rotary movements back and forth (that is to say rotates in the normal direction and in the opposite direction) around the axis of rotation O1 with an amplitude (that is to say an angle of oscillation) constant, corresponding to the output torque of the movement barrel 20 using the hairspring as a source of energy.

[0045] Tapered tenons 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 balance wheel 32 is formed from a single piece mounted on the outside and fixed to the balance shaft 31. An internal end of the hairspring is fixed to the balance shaft 31 via a ferrule, not shown.

Please note that, in the example shown in this figure, in the balance wheel 32, four arms 33 are arranged at an interval of 90 degrees centering on the axis of rotation O1. However, the number, arrangement, and shape of the arms 33 are not limited to those of this example and can be changed freely.

[0047] A double annular plate 35 is mounted on the outside and fixed to the balance shaft 31 as shown in Figure 3.

The double plate 35 includes a large plate 36 and a small plate 37 located below (on the side of the plate 11) of the large plate 36. A plate peg 38 formed of an artificial gemstone such as a ruby is, for example, driven into a large plate 36 and permanently fixed in the latter.

[0049] Tray peg 38 has a semi-circular shape in plan view and is formed such that it extends downward from large tray 36. Tray peg 38 performs rotational movements. back and forth around the axis of rotation O1 following those of the balance-spring 30, and comes into engagement with and reciprocally disengages from a fork 74, as explained below, halfway in the movement rotation.

[0050] The small plate 37 has a smaller diameter than the diameter of the large plate 36. In the small plate 37, a recess 39 takes the form of a crescent moon-shaped notch facing inward in the direction radial is arranged in a position corresponding to that of the chainring pin 38. The recesses 39 function as an escape section which prevents a dart 75 - as explained below - from coming into contact with the small chainring 37 when the fork 74 and chainring pin 38 are in mutual engagement.

[0051] Please note that in the drawings other than Figure 3, the small plate 37 and the plate peg 38 of the double plate 35 are mainly shown for the sake of clarity of the drawings.

(Exhaust Setup)

As shown in Figure 4, the escapement 13 includes the double plate 35 as explained above, the escapement mobile 40 (that is to say the wheel & the escapement pinion) which is driven in rotation thanks to the energy transmitted from the mainspring of the barrel, an anchor chain 50, a first impulse pallet 60 and a second impulse pallet 61, and a first rest pallet 62 and a second rest pallet 63.

[0053] Please note that the double plate 35 is a component forming part of both the balance-spring 30 and the regulating device 14 as explained above, and is also a component forming part of the escapement 13.

[0054] The escapement wheel set 40 (that is to say the wheel and the escapement pinion) is formed according to a single-layer structure including the escapement wheel set 41 which meshes with the second wheel set 23 and a escapement wheel 42 comprising a plurality of escapement gear teeth 43. The escapement wheel set 40 is held axially between the plate 11 and the gear train bridge (not shown). Please note that in drawings other than Figure 2, the escapement pinion 41 is not shown.

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

[0056] According to this embodiment, an example is explained in which the escapement wheel set 40, seen in a plan view of the movement 10 from the front side, as shown in Figure 4, rotates clockwise. a watch around the axis of rotation O2 thanks to the energy transmitted from the second mobile 23 via the escapement pinion 41.

Please note that, in Figure 4, the direction of rotation clockwise around the axis of rotation O2 is referred to as constituting the first direction of rotation M1, and refers to the opposite direction as constituting the second direction of rotation M2. Furthermore, reference is made to the path of rotation R drawn by the tip of the escapement gear teeth 43 during the rotation of the escapement wheel set 40 as being simply the path of rotation R of the escapement wheel 42 .

[0058] In the escapement gear toothing 43, the side surface facing the first direction of rotation M1 is shaped as a working surface 43a which comes into contact with the first impulse pallet 60 and the second impulse pallet. impulse 61, and with which the first pallet rest 62 and the second pallet rest 63 come into engagement.

[0059] Please note that the escape wheel set 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 wheel set 40 include electrofusion, a LIGA process incorporating an optical method such as a photolithography technique, DRIE, and metal powder injection molding (MIM).

[0060] However, the material and the manufacturing method for the escape wheel set 40 are not limited to the case explained below and can be modified according to need. A reduction in the weight of the escapement wheel set 40 can be achieved by making a lightening hole or by arranging a thinner portion in the escapement wheel set 40 as required, in proportions which do not affect performance, rigidity, etc of the escapement wheel set 40. In the example shown in the figure, a plurality of lightening holes is made in the escapement wheel set 40.

[0061] The anchor chain 50 is configured such that it couples a plurality of anchors together, 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 rotate (oscillate) the plurality of anchors based on the reciprocating rotation of the sprung balance 30 back and forth.

[0062] Specifically, the anchor chain 50 comprises an impulse transmission device 52 comprising an impulse transmission anchor 51 and a stopper device 54 comprising a stopper anchor 53. The pulse 52 and stopper 54 are coupled to each other while being movable relative to each other. In other words, the impulse transmission anchor 51 and the stop anchor 53 are coupled to each other, but able to move relative to each other. Consequently, the impulse transmission anchor 51 and the stop anchor 53 are coupled so as to be connected in series one after the other.

[0063] Please note that the impulse transmission device 52 and the stop device 54 need only be formed by at least one or more anchors. According to this embodiment, as explained above, each of the units of the impulse transmission anchor 52 and the stopper 54 is formed by an anchor.

The first impulse pallet 60 and the second impulse pallet 61 can be caused to come into contact with the working surface 43a of the escapement gear toothing 43 of the escapement wheel 42, and are configured as pallets for transmitting energy, passing that which has been transmitted to the escapement wheel set 40 to the balance-spring 30.

Among the first impulse paddle 60 and the second impulse paddle 61, it is the first impulse paddle 60 which is attached to the impulse transmission anchor 51 and the second impulse paddle 61 is attached to the double plate 35 fixed to the balance-spring 30.

The first rest pallet 62 and the second rest pallet 63 can come into engagement with and disengage from the working surface 43a of the escapement gear teeth 43 of the escapement wheel 42, and are arranged like pallets to stop the escape wheel set 40 and release it from its stop state. Each of the first rest pallet 62 and second rest pallet 63 are attached to the stop anchor 53.

[0067] Please note that the first impulse pallet 60 and the second impulse pallet 61 come into contact with the escape wheel 42 in the absence of engagement of the first rest pallet 62 and the second pallet of rest 63. The first rest pallet 62 and the second rest pallet 63 engage, that is to say come into engagement with the escapement wheel 42 in the absence of contact of the first impulse pallet 60 and the second impulse paddle 61. The paddles are formed from an artificial gemstone such as a ruby, like the platter peg 38.

[0068] In the following, the pulse transmission anchor 51 is explained in detail.

As shown in Figures 4 to 6, the impulse transmission anchor 51 comprises an anchor axis 70, which is a pivoting shaft, an anchor body 71, and an anchor arm 72. The impulse transmission anchor 51 rotates around a pivot axis O3 based on the alternating rotation of the balance-spring 30.

[0070] The anchor pin 70 is arranged coaxially with respect to the pivot pin 03, and is held axially between the plate 11 and the gear train bridge (not shown). The anchor pin 70 is driven out and permanently fixed in a base of the anchor body 71, for example, from the top (plate 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 escapement wheel set 40.

[0072] Please note that, as for the escapement wheel set 40, a reduction in the weight of the anchor body 71 and of the anchor arm 72 can be achieved by making lightening holes or thinner portions in the body anchor 71 and the anchor arm 72 as the case may be. In the example shown in the figure, pluralities of lightening holes are formed in the anchor body 71.

[0073] The anchor body 71 is designed so that it extends from the base, to which the anchor pin 70 is fixed, in the direction of the second direction of rotation M2, i.e. that is, towards the balance-spring 30. A pair of horns 73 arranged side by side in the circumferential direction of the pivot axis O3 are provided at the distal end of the anchor body 71. The interior of the horns 73 opens in the direction of the balance shaft 31, and is designed like 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 say, to engage) and to free oneself from them.

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

The dart 75 is attached to the distal end of the anchor body 71 from above by, for example, driving in or the like. The stinger 75 is located between the pair of horns 73 (i.e., located inside the fork 74) in plan view and extends so as to project farther than the horns 73 towards the balance shaft 31. Please note that the pin 75 is fixed in such a way that it is located below the plate peg 38, but above the escapement wheel set 40.

[0076] In the state where the plate pin 38 is disengaged from the fork 74, the distal end of the stinger 75 faces a part excluding the recess 39 of the outer circumferential surface of the small plate 37 with a slight play in the radial direction. In the state where the plate pin 38 is engaged in the fork 74, the distal end of the stinger 75 is housed in the recess 39.

[0077] Note that when the chainring peg 38 is disengaged from the yoke 74, the distal end of the dart 75 faces the outer circumferential surface of the small chainring 37 with a small gap in the radial direction. Therefore, for example, even if a disturbance occurs during the free oscillation of the balance-spring 30, and the stoppage of the entire 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 plate 37. Consequently, it is possible to suppress the displacement of the impulse transmission anchor 51 due to the disturbance. It is thus possible to prevent the release of the entire anchor chain 50 from its stopped state. Please note that the 50 anchor chain stop is explained in detail below.

A first pallet holding part 76 is arranged in the base of the anchor body 71 to project towards the escapement wheel set 40. The first pallet holding part 76 is open in the direction of the escapement wheel set 40 and holds the first impulse paddle 60 using this opening.

The first impulse pallet 60 is maintained in a state in which the first impulse pallet 60 extends lower than the pallet body 71 to reach a height equivalent to that of the escapement wheel 42 Therefore, the first impulse vane 60 may come into contact (collide) with the escapement gear teeth 43. Further, the first impulse vane 60 is maintained in a state in which the first impulse vane impulse 60 projects further towards the escapement wheel set 40 than the first holding part of the pallet 76. A side surface facing the second direction of rotation M2 in a projection part of the first impulse pallet 60 is designed to constitute a first impact surface 60a with which the working surface 43a of the toothing of the escapement gear 43 of the escapement wheel 42 comes into contact.

[0080] The anchor arm 72 is designed such that it extends from the base of the anchor body 71 in the direction of 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 in or the like. The engagement pin 77 is formed in, for example, a hollow columnar shape. The lower end of the engagement pin 77 engages inside an engagement fork 92 of the stop anchor 53 explained below.

[0081] The impulse transmission anchor 51 configured in this way pivots on the basis of the rotation of the balance-spring 30 as explained above.

[0082] Specifically, the impulse transmission anchor 51 is driven in rotation around the pivot axis O3 in the direction opposite to that of the rotation of the balance-spring 30 by the plate pin 38, which moves together with the alternating rotation of the balance-spring 30. At this moment, the first impulse pallet 60 repeats advance and retract movements with respect to the path of rotation R of the escape wheel 42 according to the direction of pivoting of the impulse transmission anchor 51. Consequently, it is possible to induce the working surface 43a of the escapement gear teeth 43 of the escapement wheel 42 to come into contact ( in collision) with the first impact surface 60a of the first impulse paddle 60.

The second impulse pallet 61 is explained below in detail.

As illustrated in Figures 3 and 4, the second impulse pallet 61 is attached to the small plate 37 of the double plate 35. Specifically, the second impulse pallet 61 is held by a second pallet holding part 80 arranged in the small plate 37. The second pallet holding part 80 is arranged in a position more offset in the direction of clockwise with respect to the axis of rotation O1 according to a predetermined phase with respect to the recess 39 ( see Figure 4) and is open towards the escape wheel set 40. The second impulse pallet 61 is held by the second pallet holding part 80 using this opening.

The second impulse vane 61 is maintained in a state in which the second impulse vane 61 projects further than the outer circumferential surface of the small plate 37 towards the escapement wheel set 40. A side surface facing clockwise from the axis of rotation O1 in a projection part of the second impulse vane 61 is designed to form a second impact surface 61a with which a working surface of the toothing of escape gear 43 of escape wheel 42 comes into contact.

[0086] Please note that a predetermined spacing is ensured in the direction of the axis of rotation O1 between the second pulse pallet 61 and the plate peg 38. The dart 75 can approach the recess 39 through this spacing.

[0087] Please note that the arrangement of the second impulse pallet 61 is not limited to an attachment to the small plate 37; the latter could be attached, for example, to the large plate 36 or to the balance wheel 32 in the double plate 35. The attachment position of the second impulse pallet 61 can be changed according, for example, to the relative positioning with the escapement wheel 42. In any case, the second impulse pallet 61 need only be attached to the balance-spring 30.

[0088] The second impulse pallet 61 attached to the balance-spring 30 as explained above repeats forward and backward movements with respect to the path of rotation R of the escape wheel 42 as a function of the rotation of the balance-spring 30. Consequently, it is possible to induce the working surface 43a of the toothing of the escapement gear 43 of the escapement wheel 42 to come into contact (collide) with the second surface d impact 61a of the second impulse pallet 61.

[0089] Please note that, as explained above, the direction of rotation of the balance-spring 30 and the direction of pivoting of the impulse transmission anchor 51 are configured to be opposite. Consequently, the second impulse pallet 61 disengages from the escapement wheel 42 when the first impulse pallet 60 comes into contact with the escapement wheel 42, and vice versa: the second impulse pallet 61 comes into contact with the escapement wheel 42 when the first impulse pallet 60 disengages from the escapement wheel 42.

The stop anchor 53 is explained in detail below.

[0091] As shown in Figures 4 to 6, the stop anchor 53 is arranged further, following the first direction of rotation M1, than the impulse transmission anchor 51 according to a plan view and comprises an anchor axis 90, which is a pivoting shaft, and an anchor body 91. The stop anchor 53 pivots around a pivot axis O4 in a direction opposite to that of pivoting of the anchor of impulse transmission 51, based on the rotation of the impulse transmission anchor 51.

The anchor pin 90 is arranged coaxially with the pivot pin O4 and is held axially between the plate 11 and the gear train bridge (not shown). The anchor pin 90 is driven out, for example, from below, and fixed permanently 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 set 40. Please note that, according to the example shown in the figure, a plurality of lightening holes are made in the anchor body 91.

[0094] The anchor pin 90 is fixed to the central part of the anchor body 91. Please note that the anchor body 91 is arranged below the anchor body 71 of the transmission anchor. impulse 51 and placed on the same plane as the escape wheel set 40.

[0095] Consequently, the relative heights of the impulse transmission anchor 51, the stop anchor 53, and the escapement wheel set 40 are as follows: the escapement wheel set 40 and the body of anchor 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 impulse transmission anchor 51 is located above the mobile d escapement 40 and anchor body 91.

[0096] However, the anchor body 91 of the stop anchor 53 can be arranged below the anchor body 71 of the impulse transmission anchor 51 and above the escapement mobile 40. In this case, like the first impulse vane 60, the first rest vane 62 and the second rest vane 63 need only extend farther downward than the anchor body 91 such that they reach a height equivalent to that of the escape wheel 42.

[0097] An engagement fork 92 having a forked shape projecting in the direction of the second direction of rotation M2 and bifurcating in the circumferential direction of the pivot axis O4 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 impulse transmission anchor 51 penetrates inside the engagement fork 92. The outer circumferential surface of the engagement pin 77 and the inner surface of the engagement fork 92 are slidably engaged with each other. Therefore, the impulse transmission anchor 51 and the stopper anchor 53 are coupled to each other in a way that can move relative to each other, and they rotate in opposite directions to each other.

[0098] In a part located between the anchor axis 90 and the engagement fork 92 in the anchor body 91, a third pallet holding part 93 is provided, which is open towards the side of the mobile exhaust 40. The third pallet holding part 93 holds the first resting pallet 62 using this opening.

The first pallet rest 62 is maintained in a state in which it projects farther in the direction of the escape wheel set 40 than the third pallet holding part 93. A side surface facing the second direction of rotation M2 in a projecting part of the first resting pallet 62 forms a first engagement surface 62a, with which the working surface 43a of the escape gear toothing 43 of the escape wheel 42 engages, c is to say comes into mutual engagement. Please note that the first rest paddle 62 functions as a paddle commonly referred to as an entry paddle.

[0100] Please note that the first rest pallet 62 is fixed such that the first engagement surface 62a engages with the working surface 43a of the escape gear toothing 43 in a state where the first rest pallet 62 forms a predetermined angle of incidence therewith.

[0101] At a circumferential end 91b located in the first direction of rotation M1 in the anchor body 91 is provided a fourth pallet holding part 94, open in the direction of the escapement mobile 40. The fourth holding part paddle 94 holds the second paddle rest 63 using this opening.

[0102] The second pallet rest 63 is maintained in a state in which it projects further towards the escape wheel set 40 than the fourth pallet holding part 94. A side surface facing the second direction of rotation M2 in a projecting part of the second resting 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, it that is to say comes into mutual engagement. Please note that the second home paddle 63 functions as a paddle commonly referred to as an output paddle.

[0103] Please note that, like the first rest paddle 62, the second rest paddle 63 is fixed such that the second engagement surface 63a engages with the working surface 43a of the gear tooth d exhaust 43 in a state where the second pallet rest 63 forms a predetermined angle of incidence therewith.

[0104] As explained above, the stop anchor 53 configured in this way rotates around the pivot axis O4 based on the pivoting of the impulse transmission anchor 51, which itself rotates on the base of the alternating rotation of the balance-spring 30. At this moment, the first pallet rest 62 and the second pallet rest 63 advance beyond the path of rotation R of the escape wheel 42 and retract below the latter according to the direction of pivoting of the stop anchor 53.

[0105] Consequently, it is possible to put the working surface 43a of the escapement gear toothing 43 of the escapement wheel 42 into mutual engagement with the first engagement surface 62a of the first rest pallet. 62, or the second engagement surface 63a of the second rest pallet 63.

[0106] In particular, the first pallet rest 62 and the second pallet rest 63 are arranged on either side of the pivot axis O4. Consequently, the second rest pallet 63 disengages from the escape wheel 42 when the first rest pallet 62 engages with the escape wheel 42. The second rest pallet 63 engages with the escape wheel. escapement 42 when the first pallet rest 62 emerges from the escapement wheel 42.

[0107] As explained above, the anchor chain 50 is formed by coupling the impulse transmission anchor 51 to the stopper anchor 53, such that they are connected in series with each other. following the other. The anchors 51 and 53 are moved such that they individually rotate based on the alternating rotation of the balance-spring 30. In other words, the impulse transmission anchor 51 rotates in the opposite direction to that of rotation. balance-spring 30, and stop anchor 53 rotates in the opposite direction to that of impulse transmission anchor 51.

[0108] Please note that, in this embodiment, both the impulse transmission anchor 51 and the stopper anchor 53 are equivalent to an anchor located at the coupling end of the chain. anchor 50. In the impulse transmission anchor 51 is arranged a restriction section. The restriction section positions the impulse transmission anchor 51 and limits the movement of the entire anchor chain 50 when the first resting paddle 62 and the second resting paddle 63 engage a wheel. escapement 42 of escape wheel set 40.

[0109] In the impulse transmission anchor 51, an external lateral surface 100 located on the side opposite to the lateral surface facing the escapement wheel set 40 in the anchor body 71 comes into contact with a first pin of limitation 102 arranged further along the 1<er>direction of rotation M1 with respect to the anchor axis 70 and which acts as a restriction section limiting the pivoting of the impulse transmission anchor 51 and positioning the anchor impulse transmission 51.

[0110] Similarly, in the impulse transmission anchor 51, an external lateral surface 101 located on the side opposite the lateral surface facing the escapement wheel 40 in the anchor arm 72 comes into contact with another limiting pin 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 impulse transmission anchor 51 and positioning the anchor of impulse transmission 51.

[0111] A pair of limiting pins 102 and 103 is, for example, fixed in such a way that they protrude upwards from the plate 11.

[0112] When the first rest pallet 62 comes into engagement with the escapement gear teeth 43 of the escapement wheel 42, the outer side surface 100 of the anchor body 71 comes into contact with the limiting pin. 102 and positions the impulse transmission anchor 51. When the second rest pallet 63 comes into engagement with the escapement gear toothing 43 of the escapement wheel 42, the outer lateral surface 101 of the arm of anchor 72 comes into contact with the other limiting pin 103 and positions the impulse transmitting anchor 51.

(Exhaust operation)

In what follows, the operation of an escapement 13 configured as detailed above is explained.

[0114] Please note that, in the following explanations, at the start of the operation as represented in FIG. 4, the working surface 43a of the escapement gear teeth 43 is in mesh with the first engagement surface. 62a of the first rest pallet 62 and the outer side surface 100 of the impulse transmission anchor 51 comes into contact with the limiting pin 102 defining its positioning. Consequently, the rotation of escape wheel set 40 is stopped. In addition, the plate pin 38 moves clockwise according to the free oscillation of the balance-spring 30 and advances towards the inside of the fork 74.

The first impulse pallet 60 has already advanced beyond the rotational path R of the escapement wheel 42. However, a spacing is ensured between the first impact surface 60a of the first impulse pallet 60 and the working surface 43a of the escapement gear 43. The escapement gear teeth 43 are configured not to be in contact with the first impulse pallet 60.

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

[0117] When the balance-spring 30 continues to rotate clockwise thanks to the rotational energy (power) stored in the balance-spring from the state represented in FIG. 38 comes into contact and engages with the internal surface of the horns 73 located in the direction of its progression at the level of the internal surface of the fork 74, and comes to bear against the fork 74 in the direction of clockwise . Consequently, the energy of the hairspring is transmitted to the impulse transmission lever 51 via the chainring peg 38.

[0118] Please note that the small chainring 37 and the stinger 75 are not brought into contact with each other during the engagement of the fork 74 with the chainring pin 38. Consequently, it is possible to effectively transmit the energy from the balance-spring 30 to the impulse transmission lever 51.

[0119] Consequently, as shown in Figure 7, the entire complete anchor chain 50 moves so that the impulse transmission anchor 51 and the stop anchor 53 respectively pivot. In other words, the impulse transmission anchor 51 rotates counterclockwise around the pivot axis O3, and the stopper anchor 53 rotates clockwise around of pivot axis O4.

[0120] When the impulse transmission anchor 51 pivots, the outer side surface 100 of the impulse transmission anchor 51 separates from the limiting pin 102. When the stop anchor 53 pivots, the first rest pallet 62 moves in a direction away from the escapement wheel 42 (a direction of retraction with respect to an insertion inside the rotational path R of the escapement wheel 42) by sliding on the working surface 43a of the escapement gear 43.

The first rest pallet 62 moves to a position slightly deviating from the path of rotation R of the escape wheel 42. It is then possible to separate the first rest pallet 62 from the gear teeth d escapement 43 and disengage from the first rest pallet 62 from the escapement gear 43. Consequently, it is possible to release the escapement wheel set 40 from its stop state.

[0122] Moreover, when the escapement gear teeth 43 and the first rest pallet 62 are no longer in mutual engagement, due to the angle of incidence of the first rest pallet 62, as shown in Figure 7, the escape wheel set 40 instantly retracts in the second direction of rotation M2 (counterclockwise) rather than the first direction of rotation M1 (clockwise ), which is the original direction of rotation. After the instantaneous retraction, the escapement wheel set 40 resumes its rotation in the first direction of rotation M1 thanks to the energy transmitted via the front gear train 12.

[0123] Thanks to the instantaneous retraction of the escapement wheel set 40 in this way, it is possible to ensure more secure engagement with the front gear train 12. It is thus possible to operate the front gear train 12 stably and with high reliability.

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

[0125] Consequently, it is possible to transmit the rotational force of the escapement wheel set 40 to the impulse transmission lever 51. The internal surface of the horns 73 on the internal surface of the fork 74 located upstream of the direction of progression of the plate peg 38 comes into contact and engages with the plate peg 38. Consequently, it is possible to indirectly transmit the energy, which is transmitted to the escapement wheel set 40, to the balance-spring 30 via the impulse transmission anchor 51. It is possible to continue to rotate the impulse transmission anchor 51 so that it follows the chainring peg 38.

[0126] By indirectly transmitting the energy, which is transmitted to the escapement wheel set 40, to the balance-spring 30 via the impulse transmission anchor 51 in this way, it is possible to supply rotational energy to the balance - hairspring 30.

[0127] When the escapement gear toothing 43 is brought into contact with the first impulse pallet 60 as explained above, the escapement gear toothing 43 rotates according to the first direction of rotation M1 to slide on the first impact surface 60a. The first impulse pallet 60 moves gradually in the direction of release of the escapement wheel 42 (the direction of retraction following an encroachment inside the rotational path R of the escapement wheel 42) depending of the direction of pivoting of the impulse transmission anchor 51.

[0128] When the first impulse pallet 60 moves to reach a position slightly deviating from the path of rotation R of the escapement wheel 42, the indirect impact on the balance-spring 30 explained above ends .

[0129] When the first impulse pallet 60 moves in the direction of disengagement with respect to the escapement wheel 42 according to the direction of pivoting of the impulse transmission anchor 51, the second rest pallet 63 moves forward until it encroaches on the path of rotation R of the escape wheel 42 following the pivoting of the stop anchor 53 in the direction of clockwise.

[0130] Immediately after the first impulse pallet 60 has moved to a position away from the path of rotation R of the escapement wheel 42, as shown in FIG. 9, the working surface 43a of the toothing of the escapement gear 43 is brought into contact with the second engagement surface 63a of the second rest pallet 63 which encroaches on the path of rotation R of the escapement wheel 42.

[0131] At this time, the impulse transmission anchor 51 moves to the other limiting pin 103 in accordance with the rotation of the impulse transmission anchor 51 counterclockwise. show. However, at this point, the impulse transmission anchor 51 is configured not to be in contact with the other limiting pin 103. Therefore, the impulse transmission anchor 51 and respectively the anchor of stopper 53 rotate slightly while escapement gear teeth 43 and second rest pallet 63 remain in contact.

As shown in Figure 10, when the outer side surface 101 of the impulse transmission anchor 51 comes into contact with the other limiting pin 103, the impulse transmission anchor 51 cannot perform additional rotational movement and is thus positioned. Consequently, the movement of the entire anchor chain 50 is restricted and the escapement gear teeth 43 and the second rest pallet 63 are caused to be in an engaged state, that is i.e. of mutual taking. Consequently, the rotation of escape wheel set 40 stops. The anchor chain 50 enters a stopped state.

[0133] Then, the plate pin 38 emerges from the inside of the fork 74 and separates from the impulse transmission lever 51 following the rotation of the balance-spring 30 in the clockwise direction. show. Then, balance-spring 30 continues to rotate clockwise by inertia. A rotational energy of balance-spring 30 is stored in the balance-spring. When all the rotational energy is stored in the hairspring, the balance-spring 30 stops its clockwise rotation, comes to a standstill for a moment, and a counter-clockwise rotation A watch then begins under the impetus of the rotational energy stored in the hairspring.

[0134] Thus, as shown in Figure 11, the plate pin 38 begins a movement to approach the impulse transmission anchor 51 following the rotation of the balance-spring 30 in the clockwise direction. show.

[0135] As shown in Figure 12, when the plate pin 38 advances inwardly of the fork 74 of the impulse transmission anchor 51, the plate pin 38 comes into contact and engages with the internal surface of the horns 73 located further downstream in the direction of progression of the chainring peg on the level of the internal surface of the fork 74 and exerts a pressure against the fork 74 in the counterclockwise direction. Consequently, the energy of the hairspring is transmitted to the impulse transmission lever 51 via the chainring peg 38.

The entire anchor chain 50 is then moved again so that the impulse transmission anchor 51 and respectively the stop anchor 53 pivot. In other words, the impulse transmission anchor 51 rotates clockwise around the pivot axis O3 and the stopper anchor 53 rotates counterclockwise around of pivot axis O4.

[0137] Please note that, after the sprung balance 30 has started its rotation in the counterclockwise direction, the second impulse pallet 61 gradually approaches the rotation path R of the wheel. escapement 42. At a given moment, when the plate pin 38 exerts pressure against the fork 74 in the counterclockwise direction, as shown in Figure 12, the second impulse pallet 61 comes to encroach on the rotation path R of the escape wheel 42.

[0138] However, at the stage where the second rest pallet 63 and the escapement gear teeth 43 are in mutual engagement and the outer side surface 101 of the impulse transmission anchor 51 is in contact with the another limit pin 103, spacing is provided between the second impact surface 61a of the second impulse vane 61 and the working surface 43a of the escapement gear 43. Accordingly, the toothing of the gear exhaust 43 is configured not to be in contact with the second impulse pallet 61.

[0139] When the impulse transmission anchor 51 rotates, the outer side surface 101 in the impulse transmission anchor 51 separates from the other limiting pin 103. When the stopper anchor 53 rotates , the second rest pallet 63 moves in the disengagement direction with respect to the escapement wheel 42 (the direction of retraction with respect to an encroachment on the rotation path R of the escapement wheel 42) to slide on the working surface 43a of the escapement gear 43. The second rest pallet 63 moves to the position deviating slightly from the path of rotation R of the escapement wheel 42. Thus, it is possible to release the second rest pallet 63 of the escapement wheel 42 and to disengage the second rest pallet 63 from the escapement gear 43. Consequently, it is possible to perform a release from the stop state of the mobile exhaust 40.

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

[0141] As illustrated in FIG. 13, when the retracted escape wheel set 40 resumes its rotation in the first direction of rotation M1, the working surface 43a of the escape gear toothing 43 comes into contact (in collision ) with the second impact surface 61a of the second impulse pallet 61 which encroaches on the path of rotation R of the escapement wheel 42.

[0142] Consequently, it is possible to directly transmit the rotational force of the escapement wheel set 40 to the balance-spring 30 via the second impulse pallet 61. It is possible to supply rotational energy to the balance-spring 30 , and to continuously rotate the impulse transmission anchor 51 to follow the chainring peg 38.

[0143] When the escapement gear toothing 43 comes into contact with the second impulse pallet 61 as explained above, the escapement gear toothing 43 rotates in the first direction of rotation M1 to slide on the second impact surface 61a. The second impulse pallet 61 moves gradually in the direction of disengagement from the escapement wheel 42 (the direction of retraction with respect to an encroachment on the rotation path R of the escapement wheel 42 ) by following the rotation of the balance-spring 30.

As shown in Figure 14, when the second impulse pallet 61 moves until it reaches a position slightly deviating from the path of rotation R of the escape wheel 42, the direct impact on the balance -hairspring 30 as explained above is finished.

[0145] When the second impulse pallet 61 moves in the direction of disengagement relative to the escapement wheel 42 following the rotation of the balance-spring 30, the first rest pallet 62 advances to encroach on the path of rotation R of the escape wheel 42 following the pivoting, counterclockwise, of the stop anchor 53.

[0146] Immediately after the second impulse pallet 61 has moved into a position deviating from the path of rotation R of the escapement wheel 42, the working surface 43a of the toothing of the escapement gear 43 is brought into contact with the first engagement surface 62a of the first rest pallet 62, which has advanced until it encroaches on the path of rotation R of the escape wheel 42. At this moment, the impulse transmission anchor 51 moves towards the limiting pin 102 by rotating clockwise. However, at this point, the impulse transmission anchor 51 is configured not to be in contact with the limiting pin 102. Therefore, the impulse transmission anchor 51 and respectively the stop anchor 53 rotate slightly while the escapement gear teeth 43 and the first rest pallet 62 remain in contact.

[0147] As shown in Figure 15, when the outer side surface 100 of the impulse transmission anchor 51 comes into contact with the limiting pin 102, the impulse transmission anchor 51 cannot rotate any further. and is so positioned. Consequently, any displacement of the entire anchor chain 50 is prevented and the escapement gear teeth 43 and the first rest pallet 62 enter an engaged state, that is to say mutual influence. Consequently, the rotation of escape wheel set 40 stops. The anchor chain 50 enters a stopped state.

[0148] Then, by repeating the operating operations explained above according to the alternating rotation of the balance-spring 30, the escapement 13 comes, repeatedly, to engage the first rest pallet 62 and the second pallet of rest 63 with the toothing of the escapement gear 43, and respectively release them from the latter, and transmits the energy of the balance-spring 30 by using the contact of the toothing of the escapement gear 43 with first impulse pallet 60 and second impulse pallet 61. ) an indirect power transmission performed using the first impulse vane 60 and an indirect power transmission performed using the second impulse vane 61.

Consequently, it is possible to induce the escapement 13 to function as an escapement 13 of the type of those qualified as semi-direct impact, which simultaneously use the direct impact and the indirect impact. It is thus possible to ensure stable operation and power transmission.

[0150] In particular, with the escapement 13 according to the embodiment described, unlike a conventional escapement in which the impulse pallet and the rest pallet are incorporated in a common anchor, the impulse transmission anchor 51 includes the first impulse paddle 60, while the stop anchor 53 includes the first rest paddle 62 and the second rest paddle 63.

[0151] Consequently, it is possible to freely design and respectively arrange, with less restriction, the relative position of the impulse transmission device 52 (the impulse transmission anchor 51) with respect to the escapement mobile 40 and the relative position of the stop device 54 (the stop anchor 53) with respect to the escapement wheel set 40. It is thus possible to arrange the impulse transmission device 52 and the stop device 54 in respectively optimal planes for an impact and a stop.

[0152] In the following, an operating relationship between the stop anchor 53 and the escapement wheel set 40 is explained.

[0153] FIG. 16 represents a relationship between the center of rotation (that is to say, the axis of rotation 02) of the escapement wheel set 40, the center of pivoting (that is to say, the pivot axis 04) of the stop anchor 53, and the angle of retraction of the escapement wheel set 40.

[0154] Please note that, in Figure 16, the escape wheel set 40 is not illustrated. However, the path of rotation R drawn by the tip of the escapement gear teeth 43 is illustrated. Therefore, the path of rotation R corresponds to the outer diameter of the escapement wheel 42.

[0155]Furthermore, FIG. 16 represents a first case where the center of pivoting of the stop anchor 53 is arranged in a position remote by a distance L1 from the path of rotation R of the escape wheel. 42, and a second case where the center of pivoting of the stop anchor 53 is arranged in a position far from a distance L2, longer than the distance L1, with respect to the rotation path R of the wheel. exhaust 42.

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

[0157] The angle between the segment connecting the first engagement surface 62a of the first rest pallet 62 and the center of pivoting of the stop anchor 53 and a direction normal with respect to the first engagement surface θ2a is taken as the angle of incidence α1. The pivot angle required for the stop anchor 53 while the first resting paddle 62 moves from the engagement position X1 to the disengagement position X2 is considered the working angle (or a clearance/release) α2. In addition, reference is made to the retraction angle of the escape wheel set 40 involved in the movement of the first rest pallet 62 from the engagement position X1 to the disengagement position X2 as being the retraction angle α3 .

[0158] Under the conditions defined above, it is explained how the distance between the center of pivoting of the stop anchor 53 and the path of rotation R of the escape wheel 42 affects the angle of retraction α3 when the working angle α2 is fixed at a predetermined value.

[0159] As shown in Figure 16, when the stopper anchor 53 rotates through the same working angle α2 respectively in a state where the center of pivoting of the stopper anchor 53 is away by a distance L2 from the rotation path R of the escape wheel 42, and a state where the center of pivoting of the stop anchor 53 is separated by a distance L1 from the rotation path R of the escape wheel 42, it is possible to define a smaller retraction angle α3 for distance L1 than for distance L2. In other words, it is possible to define the angle of retraction α3 as being smaller when the center of pivoting of the stop anchor 53 is closer to the path of rotation R.

[0160] Consequently, it is possible to reduce the angle of retraction of the escapement wheel set 40 by placing the center of pivoting of the stop anchor 53 as close as possible to the path of rotation R of the wheel. escapement 42. It is possible to reduce the energy required for the release of the stoppage of the escapement wheel set 40 (i.e., the energy required to return the retracted escape wheel set 40 again in its original direction of rotation).

[0161] Please note that, in Figure 16, the explanation focuses on the first resting pallet 62. However, the same reasoning applies to the second resting pallet 63. Therefore, an optimal plan for the stop is to bring the center of pivoting of the stop anchor 53 to be as close as possible to the path of rotation R of the escapement wheel 42 (i.e. the outer diameter of the wheel d exhaust 42).

[0162] 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 stopper anchor 53 and only the first rest pallet 62 and the second rest pallet 63, which are stopper pallets, are attached to the stopper anchor 53. Therefore, it It is possible to adjust the working angle α2 of the stop anchor 53 to an optimum angle focusing only on the stop action. It is thus possible to arrange the stop anchor 53 such that the center of pivoting of the stop anchor 53 comes as close as possible to the path of rotation R of the escapement wheel 42.

[0163] Consequently, according to this embodiment, it is possible to reduce the energy necessary for the release of the escapement mobile 40 from its stop state to improve the efficiency of the transmission of energy and reduce the operating errors.

In the following, an operating relationship between the impulse transmission anchor 51 and the escapement wheel set 40 is explained.

Fig. 17 is a diagram showing a relationship between the escapement gear teeth 43 of the escapement wheel 42 and the first impulse vane 60 which are in contact with each other. Note that in Fig. 17, it is assumed that the tip of the escapement gear tooth 43 and the first impulse vane 60 are in contact in a near line of contact state.

[0166] The working angle α4, which is a pivoting angle of the escapement wheel set 40 required between the start of contact of the escapement gear teeth 43 and the first impulse pallet 60 until the end of the contact, is determined, for example, by the number of teeth of the escapement wheel 42. The working angle a5, which is a pivoting angle of the impulse transmission anchor 51 required between the start of the contact of the escapement gear teeth 43 and the first impulse pallet 60 up to the end of the contact, is determined on the basis of the working angle α4 of the escapement wheel set 40.

[0167] When power is effectively transmitted from the escapement wheel set 40 to the first impulse pallet 60 following contact of the escapement gear teeth 43 with the first impulse 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 P0 of the gear between the toothing of the escapement gear 43 and the first impulse pallet 60.

[0168] Please note that the gear high point P0 is equivalent to the intersection of a working line connecting a contact point P1 corresponding to the moment of the start of contact of the toothing of the escapement gear 43 and the first impulse 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 escapement 40 and the pivot center (i.e., pivot axis 03) of impulse transmission anchor 51.

When the transmission of energy to the high point P0 of the gear is taken into account, the ratio between the distance L3 between the center of rotation of the escapement wheel set 40 and the high point P0 d is determined. gear, and a distance L4 between the center of pivoting of the impulse transmission anchor 51 and the high point P0 of the gear.

[0170] In this case, the ratio between the distance L3 between the center of rotation of the escapement wheel set 40 and the high gear point P0, and the distance L4 between the center of pivoting of the transmission anchor pulse 51 and the gear high point P0 is substantially an inverse ratio between that of the working angle α4 of the escapement wheel set 40 and the working angle α5 of the impulse transmission lever 51. In other words, the distance L3, the distance L4, the working angle α4 and the working angle α5 substantially satisfy the mathematical relationship (L3/L4)=(α5/α4).

[0171] Consequently, a design respecting these proportions is an optimal layout for impact.

[0172] According to this embodiment, no rest paddle is attached to the impulse transmission anchor 51, and only the first impulse paddle 60, which is an impact paddle, is attached to the anchor. impulse transmission anchor 51. Therefore, it is possible to adjust the working angle of the impulse transmission anchor 51 to an optimum angle focusing only on the impact action. Consequently, it is possible to effectively indirectly transmit power, which is transmitted to the escapement wheel set 40, to the balance-spring 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 escapement 13 can be configured as an escapement which is excellent in power transmission efficiency, and has fewer operating errors.

[0174] The first pulse pallet 60 and the second pulse pallet 61 come into contact with, and respectively the first rest pallet 62 and the second rest pallet 63 engage with the work surface 43a of the escapement gear 43. Consequently, it is possible to arrange the escapement wheel set 40 according to a single-layer structure, that is to say with a single level of gearing. Consequently, it is possible to prevent any increase in the inertia of the escape wheel set 40. Consequently, it is also possible to improve the efficiency in energy transmission.

[0175] Furthermore, when the escapement gear toothing 43 engages with the first resting pallet 62 or the second resting pallet 63 and the rotation of the escapement mobile 40 is stopped, that is that is to say, when the plate pin 38 disengages from the fork 74 and the sprung balance 30 oscillates freely, the impulse transmission lever 51 is brought into contact with one or the other of the pairs of limit pins 102 and 103 using the outer side surfaces 100 and 101. Therefore, it is possible to position the impulse transmission anchor 51 located at the coupling end of the anchor chain 50. It is possible to restrict the movement of the entire anchor chain 50.

[0176] Therefore, for example, even if some disturbance occurs while the balance-spring 30 oscillates freely, it is possible to prevent the anchor chain 50 from undulating or oscillating. Therefore, it is possible to operate the escapement 13 stably.

Furthermore, since the escapement 13 in this embodiment is of the so-called semi-direct impact type, it is possible to arrange the balance-spring 30 and the escapement wheel set 40 in positions close to each other. one from the other. Consequently, for example, when the escapement 13 according to this embodiment is applied to a tourbillon, it is possible to contribute to a reduction in the size of the cage on which a mechanism including the escapement 13 is mounted. Consequently, it is possible to produce an escapement 13 that is particularly suitable for a tourbillon.

[0178] With a movement 10 and a timepiece 1 according to the above embodiment, since the movement 10 and the timepiece 1 include the escapement 13 explained above which is excellent in transmission efficiency of energy and has less operating error, consequently, the movement 10 and the timepiece 1 are a movement and a timepiece having less rate deviation error and very high performance.

(Second Embodiment)

In the following, a second embodiment according to the present invention is explained with reference to the drawings. Please note that, in this second embodiment, the same parts as the components of the first embodiment are indicated by the same reference numerals and signs, and no explanation of these parts will be given again.

[0180] In the first embodiment, the impulse transmission anchor 51 is positioned using the pair of limiting pins 102 and 103; however, in the second embodiment, the impulse transmission anchor 51 is positioned using a single limit pin. Further, in the first embodiment, the stop anchor 53 is disposed below the impulse transmission anchor 51. However, in the second embodiment, the impulse transmission anchor 51 and stop anchor 53 are configured to be arranged on the same plane.

[0181] 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 transmission anchor. impulse 51.

[0182] In the impulse transmission anchor 51, a coupling part 113 which couples the anchor body 71 and the first paddle holding part 76 is integrally formed between the anchor body 71 and the first part pallet holder 76. The positioning hole 112 is formed in the coupling piece 113.

[0183] Specifically, the positioning hole 112 passes through the coupling part 113 in the thickness direction of the coupling part 113 and has an arcuate shape in a plan view extending along the direction of rotation of the coupling part. the impulse transmission anchor 51 (that is to say the direction of pivoting around the pivot axis 03). The length (the circumferential length) of the positioning hole 112 along the circumferential direction of the pivot axis O3 corresponds to a pivot angle (a working angle) by which the impulse transmission anchor 51 rotates between a state in which the first resting pallet 62 and the escapement gear teeth 43 of the escapement wheel 42 are mutually engaged, and a state in which the second resting pallet 63 and the escapement gear teeth escapement 43 of escape wheel 42 are mutually engaged.

[0184] Limit pin 111 is disposed in positioning hole 112 explained above. Limit pin 111 is attached to platen 11 and inserted through positioning hole 112 from below. 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 within the positioning hole 112 and relatively to the latter according to the pivoting of the impulse transmission anchor 51.

[0185] At this time, since the length of the positioning hole 112 along the circumferential direction corresponds to the swing angle of the impulse transmission anchor 51, as shown in Fig. 18, when the first rest pallet 62 and the escape gear toothing 43 come into mutual engagement, the limiting pin 111 is brought into contact with a first internal circumferential surface 112a located on the side of the first impulse pallet 60 in the surface inner circumferential of the positioning hole 112. Therefore, the impulse transmission anchor 51 is positioned by the limiting pin 111.

As shown in Fig. 19, when the second rest pallet 63 and the escapement gear teeth 43 come into mutual engagement, the limiting pin 111 is brought into contact with a second internal 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.

[0187] Therefore, even with a single limiting pin 111, it is possible to position the impulse transmission anchor 51. Note that the first inner circumferential surface 112a and the second inner circumferential surface 112b in the hole of positioning 112 function as a restrictor section which contacts the limiting pin 111 to position the impulse transmitting anchor 51 and limit the amount of movement of the entire anchor chain 50.

[0188] Please note that, according to this embodiment, since the impulse transmission anchor 51 and the stop anchor 53 are arranged in the same plane, the first rest pallet 62 and the second rest pallet 63 are maintained in a state in which the first resting pallet 62 and the second resting pallet 63 extend further downward than the anchor body 91 to reach a position of height equivalent to that of the steering wheel. escapement 42. Therefore, the first resting pallet 62 and the second resting pallet 63 can engage with and respectively disengage from the escapement gear 43.

[0189] An engagement plate 115 taking a circular shape in plan view is arranged at the distal end of the anchor arm 72 in the impulse transmitting anchor 51 instead of the engagement pin 77 .

[0190] The engagement plate 115 is formed by a pair of elastic sections 116. The pair of elastic sections 116 are formed by respectively semi-circular sections in plan view, and each of the sections being urged to separate from the other as indicated by the arrows visible in Figures 18 and 19.

[0191] 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 arranged on the same plane with respect to the anchor body 71, and the anchor arm 72 of the impulse transmission anchor 51. The outer circumferential surface of the engagement plate 115 and the inner surface of the engagement fork 92 are mutually engaged. with each other in a sliding way. Therefore, the impulse transmission anchor 51 and the stopper anchor 53 are coupled to each other while being able to move relative to each other, and rotate in opposite directions. each other in a state in which the impulse transmission anchor 51 and the stopper anchor 53 are arranged in the same plane.

[0192] In particular, the engagement plate 115 of the impulse transmission anchor 51 and the engagement fork 92 of the stopper anchor 53 are coupled to each other in a state in wherein the outer circumferential surfaces of the pair of resilient sections 116 are held in compression against the inner surface of the engagement yoke 92.

(Exhaust Operation)

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 through the first embodiment.

[0194] In other words, with the escapement 110 according to this embodiment, it is possible to repeatedly engage and disengage the escapement gear teeth 43 with the first rest pallet 62 and the second pallet at rest 63. It is possible to transmit the energy, which has been transmitted to the escapement wheel set 40, to the balance-spring 30 while alternatively carrying out an indirect transmission of energy carried out by using the first pallet of pulse 60, and indirect energy transmission performed using the second pulse paddle 61.

[0195] As shown in Figure 18, when the escapement gear teeth 43 and the first rest pallet 62 are in mutual engagement, the first internal circumferential surface 112a of the positioning hole 112 comes into contact with the pin of limitation 111 and the impulse transmission anchor 51 is thus positioned. As shown in Fig. 19, when the escapement gear tooth 43 and the second rest 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 impulse transmission anchor 51 is thus positioned.

[0196] In all cases, the impulse transmission anchor 51 is an equivalent anchor to the coupling end of the anchor chain 50. Consequently, when the escapement gear toothing 43 is in mutual engagement with the first rest pallet 62 or the second rest pallet 63, and that the rotation of the escapement wheel set 40 is stopped, it is possible to limit the movement of the entire anchor chain 50.

[0197] Therefore, according to this embodiment also, for example, even if some disturbance occurs when the balance-spring 30 swings freely, it is possible to prevent the anchor chain 50 from waving and swinging. Therefore, it is possible to operate the escapement 110 stably.

[0198] In particular, contrary to the first embodiment, only one limiting pin 111 need be provided and the limiting pin 111 can be arranged in a plane corresponding to that of the impulse transmission anchor 51. Therefore , it is possible to dispense or efficiently use the space occupied by the pair of limiting pins 102 and 103 of the first embodiment.

[0199] Further, the engagement plate 115 of the impulse transmission anchor 51 and the engagement fork 92 of the stopper anchor 53 are coupled to each other in a state in wherein the outer circumferential surface of the pair of elastic sections 116 are held in compression against the inner surface of the engagement fork 92. Accordingly, it is possible to prevent the formation of a gap between the engagement plate 115 and the engagement fork 92. Therefore, it is possible to couple the impulse transmission anchor 51 and the stopper anchor 53 to each other with less jerking.

[0200] Consequently, it is possible to effectively prevent the occurrence of jolts or backlashes between the impulse transmission anchor 51 and the stopper anchor 53. It is possible to rotate the the impulse transmission anchor 51 and the stop anchor 53 with good mutual reaction. Therefore, it is possible to operate the escapement 110 smoothly. It is thus possible to further improve operational performance.

[0201] Please note that, according to the second embodiment, the impulse transmission 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 impulse transmission anchor 51 with the stopper anchor 53 is not limited to such a case. The impulse transmission anchor 51 and the stop anchor 53 can also be coupled, for example, through a gear of toothed sections.

[0202] For example, in the escapement 120 shown in Fig. 20, in the first pallet holding portion 76 in the impulse transmission anchor 51, a plurality of teeth 121 arranged along the pivot direction of the impulse transmission 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, instead of the engagement fork 92 according to the second embodiment, a plurality of teeth 122 which mesh with the teeth 121 of the impulse transmission anchor 51 is formed to match the teeth 121. Therefore, the impulse transmission anchor 51 is coupled to the stopper anchor 53 by meshing the toothed sections 121 and 122.

[0203] With an escapement 120 configured in this way, it is possible to perform the same actions and obtain the same effects as those performed and those obtained through the second embodiment.

[0204] 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 carried out according to other variants. Various omissions, substitutions, and feature changes could be made to an extent that does not depart from the spirit of the invention. Alternative embodiments and modifications of the proposed embodiments include, for example, alternative embodiments and modifications readily adopted by those skilled in the art, embodiments and modifications substantially identical to the proposed embodiments and to their variants, as well as the embodiments and modifications falling within the framework of the doctrine of equivalents.

[0205] For example, in the embodiments described, the configuration proposed for transmitting the energy of the mainspring housed in the movement barrel to the escapement wheel set is given by way of example. However, the power transmission is not limited to such a case. For example, the energy could be transmitted to the escapement wheel set from a mainspring provided in a component other than the barrel of the movement.

[0206] In the embodiments described, the movement adopted is of the manual winding type to manually wind the mainspring of the barrel using the crown. However, the movement is not limited to such a case. For example, the movement could be a movement of the automatic winding type including a rotor (that is to say an oscillating weight).

[0207] In the described embodiments, an example is detailed in which the paddles such as the impulse paddle and the rest paddle are made of artificial gemstones such as a ruby. However, pallets are not limited to such a case. For example, paddles can be formed from other brittle materials and metal materials such as iron-based alloys. Furthermore, the vanes can be formed from a semiconductor material such as silicon and formed integrally with the anchor in a single piece by a semiconductor fabrication technique such as DeepRIE. In any case, the material, shape, and the like of the paddles can be changed as needed as long as the functions of the paddles can be realized.

[0208] In the embodiments described, the impulse transmission device is formed by a single anchor. However, the pulse transmission device is not limited to such a case. For example, the impulse transmission device could be formed, for example, by two or more anchors. The first impulse paddle can be attached to any of the two or more anchors.

[0209] Similarly, in the embodiments described, the stop device is formed by a single anchor. However, the stopper is not limited to such a case. The stop device could be formed, for example, by two or more anchors. The rest paddles could be respectively attached to two anchors selected from the two or more anchors.

[0210] Furthermore, in the embodiments described, the use of an escape wheel 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 escapement wheel having a double-layered structure in which a first escapement wheel and a second escapement wheel overlap on the same axis could be adopted. The escapement wheel could thus have a configuration close to that of the so-called coaxial escapement.

[0211] Even in such a case, according to this embodiment, the impulse transmission anchor comprises the first impulse pallet and the stop anchor comprises the first rest pallet and the second rest pallet. Consequently, it is possible to arrange respectively the impulse transmission anchor and the stop anchor with respect to the escapement mobile of the double-layered structure in such a way that the impact action and the stopping action are carried out optimally. For example, the first impulse pallet attached to the impulse transmission anchor and the second impulse pallet attached to the balance-spring can be configured so that they can come into contact with the gear of escapement of the first escape wheel. The first resting pallet and the second resting pallet attached to the resting pallet can be configured such that it can engage with and respectively disengage from the escape gear of the second escape wheel .

[0212] Consequently, for example, it is possible to perform the same actions and obtain the same effects as those performed and respectively those obtained via the first embodiment. However, when the escapement wheel set according to a single-layer structure is adopted, as in the described embodiments, it is possible to prevent any increase in the inertia of the escape wheel set compared to a double-layered structure. layer. Therefore, it is easy to improve the power transmission efficiency.

Claims (4)

1. Exhaust (13) comprising: an escape wheel set (40) arranged to rotate by virtue of the energy which is transmitted to it; and an impulse transmission device (52) and a stopper (54) coupled to each other while remaining movable relative to each other to rotate based on the rotation of 'a sprung balance (30), in which the stop device (54) is formed by at least one or more anchors and comprises a resting pallet (62, 63) able to engage with and disengage from an escape wheel (42) of the wheel set exhaust (40), the impulse transmission device (52) is formed by at least one or more anchors and comprises a first impulse pallet (60) capable of coming into contact with the escape wheel (42) in the absence of engagement of the latter with the rest pallet, and the escapement comprising a second impulse pallet (61), intended to be fixed to the balance-spring (30) so as to be able to come into contact with the escape wheel (42) in the absence of contact of the latter with the first impulse pallet (60). 2. Exhaust (13) according to claim 1, wherein the impulse transmission device (52) comprises an impulse transmission anchor (51) comprising the first impulse paddle (60), the stop device (54) comprises a stop anchor (53) comprising the resting paddle (62) and another resting paddle (63), the stop anchor (53) being coupled to the anchor pulse transmission (51), while remaining movable relative thereto, and the two pallets of rest (62, 63) are arranged to be caused to alternately come into engagement and disengage from the escapement wheel (42) according to the direction of pivoting of the stop anchor (53). 3. Timepiece movement (10) comprising: an exhaust (13) according to claim 1 or 2; a speed regulator (14) comprising the balance-spring (30) to which the second impulse pallet (61) is attached; and a gear train (12) which is arranged to transmit energy to the escapement wheel set (40). 4. Timepiece (1) comprising: a timepiece movement (10) according to claim 3; and at least one needle (5, 6, 7) designed to rotate at a rotational speed adjusted by the exhaust (13) and the speed regulator (14).