CH713530B1 - Escapement, timepiece movement and timepiece. - Google Patents

Abstract

The present invention relates to an escapement whose operation is stable. It provides an escapement (13) comprising an escapement mobile (40) which rotates with the aid of energy transmitted thereto, a chain of anchors (50) in which a plurality of anchors (51, 52 and 55) are coupled to each other so as to be able to move relative to each other, and which are connected in series to each other; rest pallets (62, 63) arranged to come into engagement with and to disengage from an escapement wheel (42) of the escape wheel set (40), and impulse pallets (60, 61) arranged to come into contact with the escape wheel (42) in the absence of mutual engagement of the escape wheel (42) with the rest pallets (62, 63). The chain of anchors (50) is actuated to individually rotate each of the anchors (51, 52, 55) based on the rotation of a balance spring (30). The rest paddles (62, 63) and the impulse paddles (60, 61) respectively form part of at least one or more anchors among the plurality of anchors. Of the plurality of anchors, one anchor (52) is located at one end of the anchor chain (50), has a pivot restricting portion (85), and is pivotally restricted by this restricting section (85). in order to limit the displacement of each anchor (51, 52, 55) of the chain of anchors (50) during an engagement of the rest pallets (62, 63) and the escapement wheel (42).

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 anchor escapement which is most often used in conventional mechanical timepieces, this escapement is designed to reduce slippage of the ends of the escapement wheel set 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 achieved.

[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 use both direct impact and indirect impact.

[0006] The balance-spring is a timepiece component constituting a regulating device and it is required to perform an alternating (oscillation) movement according to a predetermined oscillation cycle. Therefore, in general, a pivot of the sprung balance is formed extremely thin in order to suppress any deterioration in amplitude of the sprung balance due to friction etc. Therefore, when the pivot of the sprung balance is impacted from the outside, it is likely to be deformed or broken. It is conceivable that the precision will deteriorate as a result, and that the balance-spring will stop working.

[0007] Therefore, in order to prevent any deformation, breakage, or the like of the pivot of the sprung balance due to an impact from outside, a bearing resistant to vibration and shock is adopted as the bearing of the sprung balance. . When the sprung balance is impacted, the vibration and shock resistant bearing axially holds the sprung balance while allowing it to move both in the axial direction and in the radial direction. Therefore, the vibration and shock resistant bearing absorbs or reduces the impact applied to the sprung balance pivot and guarantees its shock resistance.

[0008] When the balance-spring is carried axially by the oscillation-resistant bearing as described above, when energy is transmitted from the escapement to the balance-spring, the balance-spring moves more or less according to the axial direction and in the radial direction. At this time, in the case of the direct impact type escapement, due to the operation of the escapement, the level of engagement between the end of the escapement wheel set and an impulse pallet on the balance-spring is often set at approximately several tens of micrometers. Therefore, at the time of the start of the impact and at the end of the impact, the level of engagement decreases further.

[0009] Consequently, when energy is transmitted directly from the escapement wheel set to the balance-spring, if the balance-spring moves, for example, in the radial direction under the action of the oscillation-resistant bearing, it is likely that the distance between the centers of the escapement wheel and the balance-spring will change, and the engagement of the end of the escapement wheel with the balance wheel's impulse pallet will become unstable or, in the worst case case, the end of the escapement wheel disengages from the sprung balance impulse pallet. Therefore, inconveniences can easily arise in that it is difficult to ensure stable operation of the escapement; moreover, the escapement wheel rotates before the balance-spring and it is difficult to transmit energy to the balance-spring.

[0010] In particular, when the escapement wheel set rotates before the sprung balance, the rotation of the escapement wheel set cannot be stopped by a lever resting pallet depending on a mutual phase relationship between the mobile escapement and anchor. It is also likely that a sudden change in frequency is caused, for example, and that the timepiece suddenly starts to move forward.

[0011] On the other hand, in the case of an escapement of the indirect impact type which indirectly transmits the energy of the escapement wheel set to the balance-spring, even when the balance-spring moves, for example, in the radial direction under the action of the oscillation-resistant bearing, inconveniences arise less easily because, as in the crab lever escapement, a safety measure is sometimes provided to allow the lever and the balance-spring to return to the same relative position that those elements were in before they moved.

[0012] For example, patent document 1 (JP-A-2008-268209) discloses an escapement of the indirect impact type comprising a first anchor and a second anchor arranged in such a way that they can come into engagement with a moving part. exhaust and get out. The inconveniences explained above appear less easily in this escapement either. In such an escapement, the first lever is capable of rotating according to the rotation of a balance-spring. The first anchor comprises a first resting pallet and a second resting pallet capable of coming into engagement with one end of the escapement wheel set, and of disengaging therefrom, and comprises a first impulse pallet capable of coming into contact with the end of the escapement mobile. The second anchor allows rotation based on the pivoting of the first anchor. The second anchor comprises a second impulse pallet capable of coming into contact with the end of the escape wheel set.

[0013] In an escapement whose configuration corresponds to that of patent document 1 described above, for example, in the state where the first rest pallet is engaged with the end of the escapement wheel set (which corresponds to a state in which the rotation of the escapement wheel set is stopped), when the first anchor is pushed by a plate pin of the balance-spring - acting as a pulse pin - and rotates on the basis of the rotation of the balance-spring , the first rest pallet emerges from the end of the escape wheel set. Consequently, since the first rest pallet and the end of the escapement wheel set are no longer in mutual engagement, the escapement wheel set begins to rotate using the energy supplied by a gear train .

[0014] Immediately afterwards, the second anchor pivots following the rotation of the first anchor. The second impulse pallet encroaches on the path traveled by the end of the escapement wheel set during its rotation. Consequently, the end of the escape wheel set, which begins its rotation, comes into contact (in collision) with the second impulse pallet. Thus, it is possible to indirectly transmit the energy, which is transmitted to the escapement wheel set, to the balance-spring via the second lever and the first lever, and it is possible to supply rotational energy to the balance-spring.

[0015] Then, when the first anchor and the second anchor rotate further, the second pallet at rest encroaches on the path of rotation taken by the end of the escapement wheel set while the second impulse pallet emerges from the end of the escape wheel. As a result, the end of the escape wheel set comes into engagement with the second rest pallet, and the rotation of the escape wheel set stops.

[0016] Then, the sprung balance continues to rotate by inertia and the plate pin separates from the first anchor. When the rotational energy of the balance-spring is fully stored in a hairspring, the balance-spring stops instantly, and then begins to rotate in the opposite direction using the rotational energy stored in the hairspring.

[0017] Then, the first anchor is pushed again by the balance-spring plate pin and thus caused to rotate in the opposite direction on the basis of the rotation of the balance-spring. The second rest pallet emerges from the end of the escape wheel set. Consequently, since the second rest pallet and the end of the escapement wheel set are no longer in mutual engagement, the escapement wheel set restarts its rotation using the energy of the gear train.

[0018]Immediately afterwards, the second anchor rotates in the opposite direction according to the pivoting of the first anchor, and the first impulse pallet encroaches on the path of rotation taken by the end of the escapement wheel set. Consequently, the end of the escape wheel set, which begins its rotational movement, comes into contact (in collision) with the first impulse pallet. Thus, as explained above, it is possible to indirectly transmit the energy, which is transmitted to the escapement wheel set, to the balance-spring via the first lever. It is possible to supply rotational energy to the balance-spring.

[0019] Subsequently, when the first anchor and the second anchor rotate further, the first rest pallet encroaches on the rotation path taken by the end of the escapement wheel set, while the first impulse pallet emerges from the end of the escapement mobile. Consequently, the end of the escapement wheel set engages with the first rest pallet, and the rotation of the escapement wheel set stops. Then the series of cycles explained above is repeated.

[0020] However, in a conventional escapement, when a stop pin (a limiting pin) is provided to stop the rotation of the escapement wheel set, the latter is arranged to come into contact with the first lever. Consequently, when the first resting pallet or the second resting pallet engages with the end of the escapement wheel set, the first anchor comes into contact with the stop pin, and the pivoting stops. However, during the time that the stop pin and the first anchor are in contact (i.e., during a free oscillation of the balance-spring), the second anchor is not mechanically positioned and found in a free state.

[0021] This is why, for example, when a disturbance occurs while the balance-spring oscillates freely, it is likely that the second lever oscillates due to a backlash generated at the level of an engagement part of the first anchor and the second anchor. The operation of the escapement thus easily becomes unstable due to an involuntary oscillation of the second lever.

SUMMARY OF THE INVENTION

The present invention has been conceived in view of such circumstances, and an object of the present invention is to provide an escapement, a timepiece movement, and a timepiece which are operationally stable. (1) The escapement according to the present invention is defined by claim 1.

According to the present invention, it is possible to respectively rotate each of the anchors forming the chain of anchors on the basis of the rotation (an alternating rotation, according to a reciprocating movement) of the balance-spring. Consequently, it is possible to bring the rest pallet into engagement with the escape wheel to stop the rotation of the escape wheel set, or to disengage the rest pallet, which is engaged with the escape wheel, of the escape wheel and thus release the stop of the escape wheel set. Consequently, it is possible to control the rotation of the escapement wheel set with a constant oscillation corresponding to that of the balance-spring. Since the anchors rotate respectively based on the rotation of the balance-spring, it is possible to induce the impulse pallet to come into contact (collide) with the escape wheel. Consequently, it is possible to indirectly transmit the energy, which is transmitted to the escapement wheel set, to the balance-spring via the anchor chain, and to supply rotational energy to the balance-spring.

[0024] In this way, it is possible to indirectly transmit the energy, which is transmitted to the escapement wheel set, to the balance-spring. It is possible to control the rotation of the escapement wheel set with a constant oscillation corresponding to that of the balance-spring.

[0025] In particular, during the engagement of the rest pallet with the escape wheel, the pivoting restriction part can prevent the anchor located at the end of the chain of anchors from rotating further. Therefore, it is possible to restrict the movement of the entire chain of anchors. It is possible to bring the entire plurality of anchors into a state of immobilization by stopping the rotation of the escape wheel set. Therefore, for example, even if a disturbance occurs while the rotation of the escapement wheel stops and the balance-spring oscillates freely, it is possible to prevent any flutter or vibration of the pallet chain. . Thus, it is possible to guarantee operational stability for the escapement.

[0026] In the case where the escapement is according to claim 2, since the engagement of the rest pallet with the escape wheel and the restriction of the pivoting of the anchor by the pivoting restriction part can be carried out on both sides of the chain of anchors, it is possible to restrict all pivoting of the plurality of anchors. Therefore, as a result, it is possible to restrain the movement of the entire chain of anchors more securely.

[0027] In the case where the escapement is according to claim 3, it is possible to arrange, in respectively optimal configurations for impact and stopping, the anchor to which the impulse pallet is attached and the anchor to which the resting pallet is attached. Therefore, it is possible to respectively determine, for example, an operating angle for the anchor provided with the impulse paddle and an operating angle for the anchor provided with the resting paddle respectively at optimum values by taking account of impact action and stopping action. Therefore, it is possible to improve the power transmission efficiency. The escapement can be configured as an escapement with fewer operating errors. In addition, it is possible to respectively set the inter-central distance between the center of rotation of the escapement wheel set and the center of pivoting of the lever to which the impulse pallet is attached, and an inter-central distance between the center of rotation of the escapement wheel set and the center of pivoting of the anchor to which the resting pallet is attached at optimum distances taking into account the impact action and the stopping action. Therefore, unlike a conventional escapement in which the impulse pallet and the rest pallet are incorporated into a single common lever, it is possible to prevent any increase in the energy required to release the mobile stop from exhaust, which leads to improved power transmission efficiency. (4) The slewing restriction part can restrict slewing by coming into contact with a limiter.

[0028] In this case, for example, a limiting pin or a section delimited by stops generally used in a mechanical timepiece can be used as a limiter. Movement of the entire chain of anchors can be restricted through a simple architecture to bring the pivot restrictor portion into contact with the limiter. Therefore, it is easy to achieve simplified configuration, weight reduction, and cost reduction. (5) The timepiece movement according to the present invention comprises: the escapement; a regulating device comprising the balance-spring; and a gear train arranged to transmit energy to the escape wheel set. (6) The timepiece according to the present invention comprises: the timepiece movement; and a needle arranged to rotate at a rotational speed adjusted by the escapement and the regulating device.

[0029] In this case, since the timepiece movement and the timepiece include an operationally stable escapement, it is possible to realize a timepiece movement and a timepiece which are excellent in terms of operation, exhibit fewer running errors, and exhibit high performance.

According to the present invention, it is possible to produce an escapement, a timepiece movement, and a timepiece which are operationally stable.

BRIEF DESCRIPTION OF DRAWINGS

Figure 1 is a view from the outside 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 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 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 resting pallet has disengaged from the escapement gear since the state shown in Figure 7. Figure 9 is an explanatory diagram of the f operation of the escapement and is a diagram showing a state in which the escapement gear is in contact with a first impulse vane from the state shown in Fig. 8. Fig. 10 is an explanatory diagram of the operation of the escapement and is a diagram showing a state in which the first impulse vane has disengaged from the escapement gear from the state shown in Fig. 9. Fig. 11 is an explanatory diagram of the operation of the escapement. escapement and is a diagram showing a state in which the escapement gear starts to come into contact with a second rest pallet from the state shown in Fig. 10. Fig. 12 is an explanatory diagram of the operation of the escapement and is a diagram showing a state in which a restrictor lever comes into contact with a restrictor pin from the state shown in Fig. 11, and in which the escapement gear and the second pallet of r epos are in mutual socket. Fig. 13 is an explanatory diagram of the operation of the escapement and is a diagram showing a state in which a chainring peg moves to a first impact anchor from the state shown in Fig. 12. Fig. 14 is a explanatory diagram of the operation of the escapement and is a diagram showing a state in which the second rest pallet begins to disengage from the escapement gear 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 second rest pallet has disengaged from the escapement gear from the state shown in Fig. 14. Fig. 16 is an explanatory diagram of the operation of the escapement and is a diagram showing a state in which the escapement gear is in contact with the second impulse vane from the state shown in Fig. 15. Fig. 17 is an explanatory diagram of the f operation of the escapement and is a diagram showing a state in which the second impulse vane has disengaged from the escapement gear from the state shown in Fig. 16. Fig. 18 is an explanatory diagram of the operation of the escapement and is a diagram showing a state in which the escapement gear starts to come into contact with the first stopper escapement stone from the state shown in Fig. 17. Fig. 19 is a diagram explanatory of the operation of the escapement and is a diagram showing a state in which the restriction lever comes into contact with the limiting pin from the state shown in Fig. 18 and the escapement gear and the first rest pallet are in mutual contact. Fig. 20 is a diagram for explaining an optimum configuration for stopping and is a diagram showing a relationship among a rotation center of an escapement wheel set, a pivoting center of a stop anchor, and an angle retraction of the escapement mobile. Fig. 21 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. Fig. 22 is a plan view of an exhaust representing a second embodiment according to the present invention. Fig. 23 is a plan view of an escapement representing a third embodiment according to the present invention. Figure 24 is a plan view of the escapement passing from a state illustrated in Figure 23 to a state in which the escapement gear and the second rest pallet are in mutual engagement. Fig. 25 is a plan view of an escapement representing a fourth embodiment according to the present invention. Figure 26 is a plan view of the escapement passing from a state shown in Figure 25 to a state in which the escapement gear and the second rest pallet are in mutual engagement. Fig. 27 is a plan view of an escapement representing a fifth embodiment according to the present invention. Figure 28 is a plan view of the escapement passing from a state shown in Figure 27 to a state in which the escapement gear and the second rest pallet are in mutual engagement. FIG. 29 is a perspective view of a double plate of a hair-spring balance illustrated in FIG. 27. FIG. 30 is a plan view of an escapement representing a sixth embodiment according to the present invention. Fig. 31 is a plan view of the escapement changing from a state shown in Fig. 30 to a state in which a first escapement gear and the second rest pallet are in mutual engagement.

DESCRIPTION OF EMBODIMENTS

First embodiment

A first embodiment according to the present invention is detailed below with reference to the drawings. It may be noted that, in this embodiment, the mechanical timepiece is given by way of example for a timepiece. In drawings, component scales are adjusted as needed to meet the need to show components in visually recognizable sizes.

Basic configuration of the timepiece

[0033] 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, the 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., the side opposite the dial) is referred to as the "front side". some movement.

[0035] Please note that, in the following explanation relating to this embodiment, the direction from the dial towards the bottom of the case is defined as upward (upward) and the opposite direction is defined as 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.

[0039] 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 mobile second 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, thanks to which the spring can be wound, is capable of being driven in rotation. 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.

[0041] 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.

[0042] 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 attached 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.

[0044] 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 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 02.

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

The balance-spring 30 comprises 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 01 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.

[0047] 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.

A double annular plate 35 is mounted outside the balance shaft 31, and fixed thereto 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.

The tray pin 38 has a semicircular shape in plan view and is formed such that it extends downward from the large tray 36. The tray pin 38 performs rotational movements. back and forth around the axis of rotation 01 following those of the balance-spring 30, and comes into engagement with and reciprocally emerges from a fork 74, as explained below, halfway in the movement rotation.

[0052] 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.

[0053] 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 shown primarily for the sake of clarity of the drawings.

Exhaust Setup

As shown in Figure 4, the escapement 13 comprises 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, a chain of anchors 50, a first impulse pallet (the impulse pallet according to the present invention) 60 and a second impulse pallet (the impulse pallet according to the present invention) 61, a first resting pallet (the resting pallet according to the present invention) 62 and a second resting pallet (the resting pallet according to the present invention) 63, and a lever restrictor (the limiter according to the present invention) 85 which restricts the movement of the entire chain of anchors while the first resting pallet 62 and the second resting pallet 63 are engaged with the escapement wheel 42 as explained below.

[0055] 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.

[0056] The escapement wheel set 40 (that is to say the wheel and the escape pinion) is formed according to a single-layer structure including the escape wheel set 41 which meshes with the seconds wheel set 23 and the 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.

[0058] 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 02 thanks to the energy transmitted from by the seconds mobile 23 via the escapement pinion 41.

[0059] Please note that, in Figure 4, the direction of rotation clockwise around the axis of rotation 02 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. Further, reference is made to the rotational path R drawn by the tip of the escapement gear toothing 43 during the rotation of the escapement wheel set 40 as simply being the rotational path R followed by the escapement wheel set. 40.

[0060] 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.

[0061] 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).

[0062] 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.

[0063] The chain of anchors 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 such that it individually rotates (oscillates) the plurality of anchors based on the alternating rotation of the balance spring 30 back and forth.

[0064] Specifically, the chain of anchors 50 includes an impact anchor unit 53 comprising a first impact anchor 51 and a second impact anchor 52, as well as a stop anchor unit 56 including a stop anchor 55. The impact anchor unit 53 and the stop anchor unit 56 are coupled to each other while being movable relative to each other. 'other.

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

[0066] Please note that the impact anchor unit 53 and the stop anchor unit 56 need only be formed by at least one or more anchors. According to this embodiment, as explained above, the impact anchor unit 53 is formed by two anchors, and the stop anchor unit 54 is formed by a single anchor.

The first 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 energy transmission pallets, passing that which has been transmitted to the escapement wheel set 40 to the balance-spring 30. Among the first impulse pallet 60 and the second impulse pallet 61, it is the first impulse paddle 60 which is attached to the impact anchor 51; the second impulse paddle 61 is attached to the second impulse transmission anchor 52.

[0068] 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 paddles to both stop escapement 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 55.

[0069] Please note that the first impulse pallet 60 and the second impulse pallet 61 come into contact with the escapement 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 pallet of impulse 60 and the second impulse paddle 61. The paddles are formed of an artificial gemstone such as a ruby, like the platter peg 38.

[0070] In the following, the impact anchor 51 is explained in detail.

[0071] As shown in Figures 4 to 6, the first impact anchor 51 is arranged between the escapement wheel set 40 and the balance shaft 31 in a plan view, and comprises an anchor pin 70, which is a rotating shaft, an anchor body 71, and an anchor arm 72. The first impact anchor 51 rotates around a pivot axis 03 based on the alternating rotation of the balance-spring 30.

[0072] 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). In the example illustrated in the figure, the anchor pin 70 is arranged so that it is located on a center line connecting the axis of rotation 02 of the escapement wheel set 40 and the axis of rotation O1 of the sprung balance according to a plan view. The anchor pin 70 is driven out and fixed permanently in a base of the anchor body 71, for example, from the top downwards (plate side 11) and fixed integrally to a base of the anchor body 71.

[0073] The anchor body 71 and the anchor arm 72 are integrally formed in a tabular form, for example, by electrofusion or via the MEMS technique. The anchor body 71 and the anchor arm 72 are arranged above the escapement wheel set 40.

[0074] 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 anchor arm 72 as required. In the example shown in the figure, pluralities of lightening holes are formed in the anchor body 71.

The anchor body 71 is designed so that it extends from the base, to which the anchor pin 70 is fixed, in the direction of the balance-spring 30 in the radial direction of the anchor shaft 70. A pair of horns 73 arranged side by side in the circumferential direction of the pivot shaft 03 are provided at the distal end of the anchor body 71. The inside of the horns 73 s opens in the direction of the balance shaft 31, and is designed to form 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 engagement with these last and get out of it.

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 beyond the horns 73 towards the balance shaft 31. In the state where the plate pin 38 is disengaged from the fork 74, the distal end of the dart 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.

[0078] 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 chain of anchors 50 is released under the influence of such disturbance, it is possible to put the distal end of the stinger 75 in first place in contact with the outer circumferential surface of the small plate 37. Consequently, it is possible to suppress the displacement of the impact anchor 51 due to the disturbance. It is thus possible to prevent the entire chain of anchors 50 from being released from its stopped state. Please note that the anchor chain stop 50 is explained in detail below.

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

[0080] The first impulse vane 60 is maintained in a state in which it projects farther towards the escapement mobile 40 than the first holding part of the vane 76. A side surface facing the second direction of rotation M2 in a projection part of the first impulse pallet 60 is designed to form 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 in contact.

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

[0082] The anchor arm 72 is designed such that it extends from the base of the anchor body 71 in the direction of the second direction of rotation M2. An engagement fork 78 having a fork shape whose legs extend in the circumferential direction of the rotation axis 03 is formed at the distal end of the anchor arm 72.

[0083] The impact anchor 51 configured in this way pivots on the basis of the rotation of the balance-spring 30 as explained above.

[0084] Specifically, the first impact anchor 51 is driven in rotation around the pivot axis 03 in the direction opposite to that of the rotation of the balance-spring 30 by the plate pin 38, which moves together with 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 first impact anchor 51. Consequently, it is possible to induce the working surface 43a of the escape gear toothing 43 of the escape wheel 42 to come into contact (collide) with the first impact surface 60a of the first impulse paddle 60.

The second impact anchor 52 is explained in detail below.

[0086] The second impact anchor 52 is arranged further in the second direction of rotation M2 with respect to the first impact anchor 51 according to a plan view, and comprises an anchor axis 80, which is a rotary shaft , and an anchor body 81. The second impact anchor 52 rotates about a rotation axis 04 in a direction opposite to that of the first impact anchor 51 based on the rotation of the first impact anchor d impact 51.

[0087] The anchor pin 80 is arranged coaxially with the axis of rotation 04 and is supported axially between the plate 11 and the gear train bridge, not shown. The anchor pin 80 is driven, for example, from below, and is integrally fixed to the anchor body 81.

[0088] The anchor body 81 is formed into a tabular shape, for example, by electrofusion or via the MEMS technique. In the example shown in the figure, the anchor body 81 is formed so as to extend along the circumferential direction of the escapement wheel set 40. It should be noted that a weight reduction of the body of anchor 81 can be made by providing a lightening hole or a thin part in the anchor body 81 if necessary.

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

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

[0091] Consequently, the first impact anchor 51 and the second impact anchor 52 are coupled to each other in such a way that they can move relative to each other, and they rotate in opposite directions to each other.

[0092] At the circumferential end 81b of the anchor body 81, a second vane holding section 83 is provided; it protrudes in the direction of the escapement wheel set 40. The second pallet holding section 83 is open towards the escapement wheel set 40 and holds the second impulse wheel set 61 using this opening.

[0093] The second impulse vane 61 is maintained in a state in which the second impulse vane 61 projects more in the direction of the escapement wheel set 40 with respect to the second vane holding section 83. A side surface facing the second direction of rotation M2 at a projecting part of the second impulse vane 61 is formed as a second impact surface 61a, with which the working surface 43a of the escapement gear 43 in the escape wheel 42 comes into contact.

[0094] As explained above, the second impact anchor 52 configured in this way pivots around the axis of rotation 04 based on the pivoting of the first impact anchor 51, which rotates according to the alternating rotation of the balance-spring 30. At this moment, the second impulse pallet 61 repeats a movement of encroachment on the path of rotation R of the escapement wheel set 40, and of retraction with respect to the latter following the pivoting of the second impact anchor 52. Therefore, it is possible to induce the working surface 43a of the escape gear 43 of the escape wheel 42 to come into contact (collide) with the second surface d impact 61a of the second impulse pallet 61.

[0095] In particular, the first impact anchor 51 and the second impact anchor 52 are coupled in such a way that they rotate in opposite directions. Therefore, when an impact anchor of the first impact anchor 51 and the second impact anchor 52 rotate in the same direction as that of rotation of the escapement wheel set 40, the other impact anchor rotates in the direction opposite to that of rotation of the escapement wheel set 40. Consequently, the second impulse pallet 61 disengages from the escapement wheel set 40 when the first impulse wheel set 60 comes into contact with the escape wheel 42. The second impulse pallet 61 comes into contact with the escape wheel 40 when the first impulse pallet 60 emerges from the escape wheel 42.

[0096] It should be noted that, according to this embodiment, the first impact anchor 51 and the second impact anchor 52 are coupled so as to rotate in opposite pivoting directions. However, the first impact anchor 51 and the second impact anchor 52 are not limited to such a configuration and could be coupled so as to rotate in the same direction.

In the following, the stop anchor 55 is described in detail.

[0098] The stop anchor 55 is arranged more in the first direction of rotation M1 than the first impact anchor 51 according to a plan view, and it comprises an anchor axis 90, which is a rotating shaft, and an anchor body 91. The stopper anchor 55 rotates about a rotation axis 05 in the direction opposite to that of pivoting of the first impact anchor 51 based on the rotation of the first impact anchor impact 51.

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

The anchor body 91 is formed, for example, by electrofusion or using 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. It should be noted that the weight of the body can be reduced by anchor 91 by providing a relief hole or a thin part in the anchor body 91 if necessary.

[0101] The anchor pin 90 is fixed to the central part of the anchor body 91. It should be noted that the anchor body 91 is arranged in an equivalent position to the anchor body 71 of the first anchor impact 51. In other words, the anchor body 91 of the stop anchor 55 is arranged above the escapement wheel set 40.

[0102] Consequently, the relative positioning in height between the first impact anchor 51, the second impact anchor 52, the stop anchor 55, and the escapement wheel set 40 is as follows: the wheel set d escapement 40 is located in the bottom layer closest to the plate 11, the anchor body 71 of the first impact anchor 51 and the anchor body 91 of the stop anchor 55 are located at the above the escapement mobile 40, and the anchor body 81 of the second impact anchor 52 is located above the anchor body 71 and the anchor body 91.

[0103] 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 05 is formed at a circumferential end 91a located in the second direction of rotation M2. The engagement plate 77 of the first impact anchor 51 is engaged inside the engagement fork 92. The outer circumferential surface of the engagement plate 77 and the inner surface of the engagement fork 92 are slidably engaged with each other. Therefore, the first impact anchor 51 and the stopper anchor 55 are coupled to each other in a way that can move relative to each other, and they rotate in directions opposite to each other.

[0104] 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 mobile of exhaust 40. The third pallet holding part 93 holds the first resting pallet 62 using this opening.

[0105] The first pallet rest 62 is maintained in a state in which it protrudes farther in the direction of the escapement mobile 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.

[0106] 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.

[0107] At a circumferential end 91b located in the first direction of rotation M1 in the anchor body 91, a fourth pallet holding part 94 open towards the escapement wheel set 40 is provided. The fourth pallet holding part 94 holds the second resting pallet 63 using this opening.

[0108] The second pallet rest 63 is maintained in a state in which it protrudes farther towards the escape wheel set 40 than the fourth pallet retaining part 94. A side surface facing the second direction of rotation M2 in a projection part of the second resting pallet 63 constitutes a second engagement surface 63a with which the working surface 43a of the toothing of the escapement gear 43 in the escapement wheel 42 engages. Please note that the second home paddle 63 functions as a paddle commonly referred to as an output paddle.

[0109] 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.

[0110] As explained above, the stop anchor 55 configured in this way rotates around the pivot axis 05 based on the pivoting of the first impact anchor 51, which rotates on the basis of the alternating rotation of 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 escapement wheel set 40 and retract below the latter according to the direction of pivoting of the stop anchor 55.

[0111] Consequently, it is possible to put the working surface 43a of the escapement gear teeth 43 of the escapement wheel 42 into mutual engagement with the first engagement surface 62a of the first rest pallet. 62 and the second engagement surface 63a of the second rest pallet 63.

[0112] In particular, the first pallet rest 62 and the second pallet rest 63 are arranged on either side of the pivot axis 05. Consequently, the second pallet rest 63 emerges from the mobile of escapement 40 when the first resting pallet 62 engages with the escape wheel set 40. The second resting pallet 63 engages with the escapement wheel 42 when the first resting pallet 62 disengages from the escapement wheel. exhaust 42.

[0113] As explained above, the anchor chain 50 is formed by coupling the first impact anchor 51, the second impact anchor 52, and the stop anchor 55 so that they are connected to each other in series. The anchors 51, 52 and 55 are moved such that they individually pivot based on the alternating rotation of the sprung balance 30. In other words, the first impact anchor 51 rotates in the opposite direction to that of rotation of the balance-spring 30. The second impact anchor 52 and the stop anchor 55 respectively rotate in the opposite direction to that of the first impact anchor 51.

[0114] Please note that the second impact anchor 52 and the stop anchor 55 are equivalent to an anchor located at the end of the anchor chain 50. The restriction lever 85 explained above is formed in one piece in the second impact anchor 52. Consequently, the first rest pallet 62 and the second rest pallet 63 are attached to an anchor (the stop anchor 55) located on the opposite side of the chain of anchors 50 with respect to an anchor (the second impact anchor 52) to which the restriction lever 85 is attached.

[0115] When the first rest pallet 62 and the second rest pallet 63 engage with the escapement wheel 42 of the escapement wheel set 40, the restriction lever 85 positions the second impact anchor 52 to restrict the displacement of the entire chain of anchors 50.

[0116] Specifically, the restriction lever 85 is formed so as to project from the circumferential end 81b of the pallet body 81 in a direction away from the escapement wheel set 40. The restriction lever 85 is capable of restrict the pivoting of the second impact anchor 52 and to position the second impact anchor 52 by coming into contact with limiting pins (the limiter according to the present invention) 86 and 87 arranged on both sides on both sides other of the restriction lever 85.

[0117] A pair of limiting pins 86 and 87 are fixed so as to protrude, for example, from the plate 11 upwards. One limit pin 86 is arranged such that it is located further in the second direction of rotation M2 with respect to the restriction lever 85. The other limit pin 87 is arranged such that it is located further in the first direction of rotation M1 relative to the restriction lever 85.

When the first rest pallet 62 comes into engagement with the escapement wheel 42 of the escapement wheel set 40, the restriction lever 85 is brought into contact with the limitation pin 86 located in the second direction of rotation M2 and positions the second impact anchor 52. When the second rest pallet 63 comes into engagement with the escapement wheel 42 of the escapement wheel set 40, the restriction lever 85 is brought into contact with the limitation pin 87 located in the first direction of rotation M1 and positions the second impact anchor 52.

Exhaust Operation

In what follows, the operation of an escapement 13 configured according to the preceding explanations is explained.

[0120] Please note that, in the following explanations, at the start of operation as shown in Figure 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 restriction lever 85 is in contact with the limitation pin 86, defining the positioning of the second impulse transmission anchor 52. Consequently, the rotation of the escapement 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 operation of the escapement 13 according to the alternating rotation of the balance-spring 30 is explained sequentially from such an operating state.

[0122] 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 first impact anchor 51 via the plate peg 38.

[0123] 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 of the balance-spring 30 to the first impact lever 51.

[0124] Therefore, as shown in Figure 7, the entire complete anchor chain 50 moves such that the first impact anchor 51, the second impact anchor 52 and respectively the anchor stops 55 swivel.

[0125] In other words, the first impact anchor 51 rotates counterclockwise around the pivot axis 03, the second impact anchor 52 rotates clockwise around the pivot axis 04, and the stop anchor 55 rotates clockwise around the pivot axis 05.

[0126] When the second impact anchor 52 pivots, the restriction lever 85 separates from the limiting pin 86. When the stop anchor 55 pivots, the first rest pallet 62 moves in a direction allowing the release of escapement wheel 40 (a direction of retraction with respect to an incursion inside the path of rotation R of escapement wheel 40) by sliding on working surface 43a of escapement gear 43.

As illustrated in Figure 8, the first rest pallet 62 moves to a position slightly deviating from the path of rotation R of the exhaust wheel set 40. It is then possible to separate the first rest pallet 62 from the escapement gear toothing 43 and to disengage 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.

[0128] 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, as illustrated in FIG. 8, thanks to the energy transmitted via the front gear train 12.

[0129] 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.

[0130] When the first rest pallet 62 moves in the direction of disengagement with respect to the escape wheel set 40 according to the direction of pivoting of the stop anchor 55, as illustrated in FIGS. 7 and 8, the first impulse pallet 60 encroaches on the rotation path R of the escape wheel set 40 depending on the pivoting of the first impact lever 51.

[0131] Nevertheless, since, as explained above, the escapement wheel retracts instantaneously via the first impulse pallet 62, and rotates in the second direction of rotation M2, at that moment, the escapement gear teeth 43 and the first rest pallet 62 are brought into contact.

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

[0133] Consequently, it is possible to transmit the rotational force of the escapement wheel set 40 to the first impact 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 pin 38 comes into contact with the plate pin 38 and engages with the latter. Consequently, it is possible to indirectly transmit the energy, which is transmitted to the escapement wheel 40, to the balance-spring 30 via the first impact anchor 51. It is possible to continue to rotate the first impact anchor impact 51 so that it follows the plateau peg 38.

[0134] By indirectly transmitting the energy, which is transmitted to the escapement wheel set 40, to the balance-spring 30 via the first impact lever 51 in this way, it is possible to supply rotational energy to the balance-spring 30.

[0135] 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 and slides on the first impact surface 60a. The first impulse pallet 60 moves gradually in the direction of disengagement of the escapement wheel set 40 (the direction retracting from an encroachment inside the rotation path R of the escapement wheel set 40) depending on the direction pivoting of the first impact anchor 51.

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

[0137] When the first impulse pallet 60 moves in the direction of disengagement with respect to the escape wheel set 40 according to the direction of pivoting of the first impact anchor 51, as illustrated in FIG. 10, the second rest pallet 63 moves forward until it encroaches on the path of rotation R of the escapement wheel set 40 following the pivoting of the stop anchor 55 in the clockwise direction.

[0138] Immediately after the first impulse pallet 60 has moved into a position away from the path of rotation R of the escapement wheel set 40, as shown in FIG. 11, 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 set 40.

[0139] At this time, the restriction lever 85 moves towards the other restriction pin 87 in accordance with the pivoting of the second impact anchor 52 in the clockwise direction. However, at this point, the restriction lever 85 is configured not to be in contact with the other limitation pin 87. Therefore, the stop anchor 55, the second impact anchor 52 and the first anchor impact 51 respectively rotate slightly while the escapement gear teeth 43, and the second rest pallet 63 remain in contact.

[0140] As shown in Figure 12, when the restriction lever 85 comes into contact with the other limitation pin 87, the second impact anchor 52 cannot perform any 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 that is to say of mutual influence. Consequently, the rotation of escape wheel set 40 stops.

[0141] Then, the plate pin 38 emerges from the inside of the fork 74 and separates from the first impact anchor 51 following the rotation of the balance-spring 30 in the clockwise direction. Then, balance-spring 30 continues to rotate clockwise by inertia. The 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.

[0142] Thus, as shown in Figure 13, the plate pin 38 begins a movement to approach the first impact anchor 51 following the rotation of the balance-spring 30 in the clockwise direction.

As shown in Fig. 14, when chainring pin 38 advances inwardly of fork 74 of first impact anchor 51, chainring pin 38 contacts and engages the inner surface horns 73 located further downstream in the direction of progression of the chainring pin at the level of the internal surface of the fork 74, and exerts a pressure against the fork 74 in the counter-clockwise direction. Consequently, the energy of the hairspring is transmitted to the impact lever 51 via the plate peg 38.

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

When the second impact anchor 52 rotates, the restriction lever 85 separates from the other limiting pin 87. When the stopper anchor 55 rotates, the second rest pallet 63 moves in the direction release of escapement wheel 40 (the direction of retraction with respect to the path of rotation R of escapement wheel 40) to slide on working surface 43a of escapement gear 43. As shown in FIG. 15 , the second resting pallet 63 moves to a position slightly deviating from the path of rotation R of the escapement wheel set 40. Then, it is possible to separate the second resting pallet 63 from the escapement gear 43 and to disengage from the second rest pallet 63 of the escapement gear 43. Consequently, it is possible to release the escapement wheel set 40 from its stop state.

Like the first pallet rest 62, the second pallet rest 63 has an angle of incidence. Consequently, as shown in Figure 14, after instantaneous retraction in the second direction of rotation M2, the escape wheel set 40 continues its rotation in the first direction of rotation M1, as shown in Figure 15, thanks to the energy transmitted by the gear train 12 before.

[0147] When the second rest pallet 63 moves in the direction of disengagement of the escapement mobile 40 following the pivoting of the stop anchor 55, as shown in Figure 14 and Figure 15, the second pallet impulse 61 encroaches on the path of rotation R of the escapement wheel set 40 following the anti-clockwise pivoting of the second impact lever 52.

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

As shown in Figure 16, when the retracted escape wheel set 40 begins its rotation in the first direction of rotation M1, the working surface 43a of the escape gear 43 comes into contact (collides) with the second impact surface 61a of the second impulse pallet 61 which encroaches on the rotation path R of the escape wheel set 40.

[0150] Consequently, it is possible to transmit the rotational force of the escapement wheel set 40 to the first impact anchor 51 via the second impact anchor 52. The internal surface of the lugs 73 located further downstream than the chainring peg 38 with respect to the direction of advancement of the latter inside the fork 74 comes into contact with the chainring peg 38 and engages with the latter. 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 second impact anchor 52 and the first impact anchor 51. It is possible to make continuously rotate the first impact anchor 51 so that it follows the chainring peg 38.

[0151] By indirectly transmitting the energy, which is transmitted to the escapement wheel set 40, to the balance-spring 30 via the second impact anchor 52 and the first impact anchor 51 in this way, it is possible to provide a rotational energy to the balance-spring 30.

[0152] When the escapement gear 43 comes into contact with the second impulse pallet 61 as explained above, the escapement gear 43 rotates in the first direction of rotation M1 and slides on the second surface of impact 61a. The second impulse pallet 61 moves gradually in the direction of disengagement of the escapement wheel set 40 (the direction of retraction of the path of rotation R of the escapement wheel set 40) following the pivoting of the second impact anchor 52.

[0153] As illustrated in FIG. 17, when the second impulse pallet 61 moves to reach a position slightly deviating from the path of rotation R of the escapement wheel set 40, the indirect impact on the balance-spring 30 explained above ends.

[0154] When the second impulse pallet 61 moves in the direction of disengagement of the escapement wheel set 40 following the pivoting of the second impact anchor 52, as shown in FIG. 17, the first rest pallet 62 comes encroach on the path of rotation R of the escapement wheel set 40 following the anti-clockwise pivoting of the stop anchor 55.

[0155] Immediately afterwards, the second impulse pallet 61 moves into a position deviating from the path of rotation R of the escapement wheel set 40, as shown in FIG. 18, and the working surface 43a of the gear escapement 43 comes into contact with the first engagement surface 62a of the first rest pallet 62, which encroaches on the path of rotation R of the escapement wheel set 40.

[0156] At this point, the restriction lever 85 moves towards a limitation pin 86 following counter-clockwise pivoting of the second impact anchor 52. However, at At this point, the restriction lever 85 is positioned such that it is not in contact with a limiter pin 86.

[0157] Consequently, the stop anchor 55, the first impact anchor 51, and respectively the second impact anchor 52 rotate slightly while the escapement gear 43 and the first rest pallet 62 remain in touch. As shown in Figure 19, when the restriction lever 85 comes into contact with a limit pin 86, the second impact anchor 52 can no longer rotate and position itself. Consequently, the movement of the entire chain of anchors 50 is limited and the escapement gear 43 and the first rest pallet 62 come into a state of mutual engagement. Consequently, the rotation of escape wheel set 40 stops.

[0158] Then, by repeating the operation explained above according to the alternating rotation of the balance-spring 30, the escapement 13 engages and disengages repeatedly from the escapement gear 43, and the first pallet of rest 62 as well as the second rest pallet 63 carry out an indirect transmission of energy to the balance-spring 30 by using the contact of the escapement gear 43 with the first impulse pallet 60 and the second impulse pallet 61 .

[0159] Consequently, it is possible to ensure that the escapement 13 operates like an escapement 13 of the type whose impact is often qualified as an indirect impact. It is possible to guarantee stable operation and stable transmission of energy compared to the case where the energy is directly transmitted to the balance-spring 30.

[0160] In particular, with an escapement 13 according to this embodiment, when the escapement gear 43 comes into engagement with the first rest pallet 62 or the second rest pallet 63, and the rotation of the mobile escapement 40 is stopped, that is to say when the plate pin 38 disengages from the fork 74 and the balance-spring 30 oscillates freely, the restriction lever 85 is brought into contact with any of the pairs limit pins 86 and 87. Consequently, it is possible to restrict the pivoting of the second impact anchor 52 located at the end of the chain of anchors 50 and to position the second impact anchor 52. is thus possible to limit the movement of the entire chain of anchors 50.

[0161] More specifically, during the duration of the engagement of the escapement gear 43 with the first pallet of rest 62, or during the duration of the engagement of the escapement gear 43 with the second pallet of rest 63, it is possible to position the second impact anchor 52 located at the end of the chain of anchors 50 through the contact of the restriction lever 85 with the pair of limiting pins 86 and 87. Thus, it It is possible to prevent the second impact anchor 52 from rotating further.

[0162] In particular, it is possible to carry out, on both sides of the chain of anchors 50, an engagement of the first rest pallet 62 and of the second rest pallet 63 with the escapement gear. 43, and to restrict the pivoting of the second impact anchor 52 via the restriction lever 85. Consequently, it is possible to restrict all the pivotings of a plurality of anchors (in the case of this mode embodiment, three anchors, that is to say, the first impact anchor 51, the second impact anchor 52, and the stop anchor 55) starting from the stop anchor 55 attached to the first rest pallet 62 and the second rest pallet 63, up to the second impact anchor 52 located at the end of the chain of anchors 50. Consequently, it is possible to restrict the movement of any the chain of anchors 50.

[0163] Consequently, when the escapement gear 43 and the first rest pallet 62 or the second rest pallet 63 come into mutual engagement, it is possible to put the first impact anchor 51, the second impact anchor impact 52, and the stop anchor 55 in a state of immobilization while stopping the rotation of the escapement wheel set 40. Therefore, for example, even if a disturbance occurs while the rotation of the escape wheel set escapement 40 is stopped and the balance-spring 30 oscillates freely, it is possible to prevent the chain of anchors 50 from undulating by having flutter or from vibrating. Therefore, it is possible to operate the escapement 13 stably.

It is possible to use the limiting pins 86 and 87, which are generally used in a mechanical timepiece, as a limiter. It is possible to restrict the movement of the entire chain of anchors 50 with a simple configuration to bring the restriction lever 85 into contact with the limiting pins 86 and 87. Therefore, it is easy to achieve a simplification of the architecture of the mechanism, a reduction in weight, as well as a reduction in costs.

[0165] Furthermore, in the escapement 13 according to this embodiment, unlike a conventional escapement in which the impulse pallet and the rest pallet are incorporated in a common lever, the first impact lever 51 and the second impact anchor 52 include the first impulse paddle 60 and the second impulse paddle 61 respectively, and the stop anchor 55 includes the first rest paddle 62 and the second rest paddle 63. In other words, the first impulse pallet 60 and the second impulse pallet 61 are attached to a different anchor from an anchor to which the first rest pallet 62 and the second rest pallet 63 are attached.

[0166] Therefore, it is possible to freely design and respectively dispose, with less restriction, a relative position of the impact anchor unit 53 (the first impact anchor 51 and the second impact anchor 51). impact 52) with respect to the escapement wheel set 40 and a relative position of the stop anchor unit 56 (the stop anchor 55) with respect to the escape wheel set 40. It is possible to arrange the impact anchor unit 53 and stop anchor unit 56 in optimum configurations for impact and stop respectively.

[0167] The stop anchor 55 is arranged, according to this embodiment, based on a design concept explained below.

[0168] FIG. 20 illustrates a relationship between the center of rotation (that is to say, the axis of rotation O2) of the escapement wheel set 40, the center of pivoting (that is to say, the axis of rotation O5) of the stop anchor 55, and the angle of retraction of the escapement wheel set 40.

[0169] It should be noted that, in FIG. 20, the escape wheel set 40 is not illustrated. However, the path of rotation R followed by the end of escapement gear 43 is illustrated. Consequently, the path of rotation R corresponds to the external diameter of the escapement wheel set 40.

[0170] Moreover, FIG. 20 represents a case where the center of pivoting of the stop anchor 55 is arranged in a position spaced by a distance L1 from that of the path of rotation R of the escapement wheel set 40 and a case where the center of pivoting of the stop anchor 55 is arranged in a position separated by a distance L2, longer than the distance L1, from the path of rotation R of the escapement wheel set 40.

[0171] In both cases, the first rest pallet 62 moves, according to the pivoting of the stop anchor 55, between an engagement position X1 where the escapement gear 43 comes into engagement with the first resting pallet 62, and a disengagement position X2, where the first resting pallet 62 moves to a position deviating from the path of rotation R of the escapement wheel set 40, and is disengaged from the escapement gear 43 .

[0172] The angle between a linear segment connecting the first engagement surface 62a of the first resting pallet 62 to the center of pivoting of the stop anchor 55 and a direction normal with respect to the first engagement surface α1 is the angle of incidence α1. The pivot angle of stop anchor 55 required as first resting paddle 62 moves from engagement position X1 to disengagement position X2 is considered to be a working angle (or a release) α2. Furthermore, reference is made to the angle of retraction α3 as being that corresponding to the angle of retraction of the escapement wheel set 40 involved in the movement of the first rest pallet 62 between the engagement position X1 and the position clearance X2.

In the above conditions, it is explained how the distance between the center of pivoting of the stop anchor 55 and the path of rotation R of the escapement wheel set 40 affects the angle of retraction α3 when the working angle α2 is fixed at a predetermined value.

[0174] As shown in Fig. 20, when the stopper anchor 55 rotates through the same working angle α2 respectively in a state in which the pivoting center of the stopper anchor 55 is spaced by a distance L2 with respect to the path of rotation R of the escapement wheel set 40, and in a state in which the center of pivoting of the stop anchor 55 is spaced by a distance L1 with respect to the path of rotation R of the wheel set d exhaust 40, it is possible to define a smaller retraction angle α3 in the case of a distance L1 than for a distance L2. In other words, it is possible to define a smaller retraction angle α3 when the center of pivoting of the stop anchor 55 is closer to the path of rotation R.

[0175] 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 55 as close as possible to the rotation path R of the escapement wheel set. 40. It is possible to reduce the energy required to release the escapement wheel set 40 from its stop state (that is to say, the energy required to return the retracted escape wheel set 40 to its original direction of rotation).

[0176] It should be noted that in Figure 20 the explanation is focused on the first rest paddle 62. However, the same reasoning applies to the second rest paddle 63. Therefore, an optimal configuration for the stop is to put the center of pivoting of the stop anchor 55 as close as possible to the path of rotation R of the escapement wheel set 40 (that is to say, the outer diameter of the escape wheel set 40).

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

[0178] It is also possible to, for example, design the working angle of the stop anchor 55 as being equal to an optimum angle. Thus, it is easy to improve the power transmission efficiency.

[0179] The first impact anchor 51 and the second impact anchor 52 are, according to this embodiment, arranged based on a design concept explained below.

Fig. 21 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. 21, 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.

[0181] 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 contact, is determined, for example, by the number of teeth of the escape wheel 42. The working angle a5, which is a pivot angle of the impact anchor 51 required between the start of contact of the escapement gear teeth 43 and the first pulse pallet 60 to the end of the contact, is determined on the basis of the working angle α4 of the escapement wheel set 40.

[0182] When energy is efficiently 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 gear 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 .

[0183] 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 with 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 O2) of the mobile d escapement 40 and the center of pivot (i.e., pivot axis O3) of impact 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 impact anchor 51 and the high point P0 of the gear.

In this case, the ratio between the distance L3 between the center of rotation of the escapement wheel 40 and the high point P0 of the gear, and the distance L4 between the center of pivoting of the lever impact 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 impact lever 51. In other words, the distance L3, distance L4, working angle α4 and working angle α5 substantially satisfy the mathematical relationship (L3/L4)≡(α5/α4).

[0186] Consequently, such a design constitutes an optimal configuration for impact. It should be noted that the same applies to the second impulse paddle 61 and the second impact anchor 52.

[0187] Consequently, according to this embodiment, it is possible to respectively arrange the first impact anchor 51 and the second impact anchor 52 in optimal configurations for the impact. Therefore, in the two impact levers, it is possible to efficiently transmit the energy, which is transmitted to the escapement wheel set 40, to the sprung balance 30. It is also possible, for example, to design the angles of work of the first impact anchor 51 and the second impact anchor 52 at optimum values. It is easier to improve the power transmission efficiency.

[0188] As explained above, with the escapement 13 in this embodiment, when the balance-spring 30 oscillates freely, it is possible to restrict the movement of the entire chain of anchors 50 by using the restriction lever 85. Therefore, even if a disturbance occurs during the free oscillation of the balance spring 30, it is possible to prevent the anchor chain 50 from waving fluttering or vibrating. Therefore, it is possible to operate the escapement 13 stably.

[0189] It is possible to produce a design optimized for impact and stopping. The escapement can be configured as an escapement excellent in power transmission efficiency and having fewer operating errors.

[0190] The first pulse pallet 60 and the second pulse pallet 61 come into contact with the first rest pallet 62, and the second rest pallet 63 comes into engagement with the working surface 43a of the gear d escapement 43. Therefore, it is possible to form the escapement wheel set 40 in a single layer structure. Therefore, it is possible to prevent any increase in the inertia of the escapement wheel set 40. Thus, it is also possible to improve the power transmission efficiency.

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

Second embodiment

A second embodiment according to the present invention is explained with reference to the drawings. It should be noted that, in this second embodiment, the same parts as the components in the first embodiment are indicated by the same reference numerals and signs and an explanation relating to these parts will not be repeated.

[0193] In the first embodiment, the stop anchor unit is formed by a single anchor. However, in the second embodiment, the stop anchor unit is formed by two anchors.

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

[0195] Consequently, the chain of anchors 105 is formed, according to this embodiment, by four anchors, that is to say, the first impact anchor 51, the second impact anchor 52, the first stop anchor 102, and the second stop anchor 103.

[0196] The first detent anchor 102 and the second detent anchor 103 are respectively coupled to the impact anchor unit 53 so as to be able to move with respect thereto. In the example shown in the figure, the first stop anchor 102 is coupled to the first impact anchor 51. The second stop anchor 103 is coupled to the second impact anchor 52. The first pallet rest 62 is attached to the first stop anchor 102. The second rest pallet 63 is attached to the second stop anchor 103.

[0197] The first stop anchor 102 is arranged further in the first direction of rotation M1 with respect to the first impact anchor 51 in a plan view, and it comprises an anchor axis 110, which is a shaft rotatable, and an anchor body 111. The first stop anchor 102 rotates around an axis of rotation 06 in the direction opposite to that of the pivoting of the first impact anchor 51, based on the rotation of the first impact anchor 51.

[0298] The anchor pin 110 is held axially between the plate 11 and the gear train bridge (not shown) and driven out for example from the bottom to be fixed integrally to the anchor body 111 and form only a single one-piece piece.

The anchor body 111 is arranged so as to extend along the circumferential direction of the escapement wheel set 40. The anchor pin 110 is fixed to a circumferential end 111a of the anchor body 111 located in the first direction of rotation M1. It should be noted that the anchor body 111 is arranged at a height equivalent to that of the anchor body 71 of the first impact anchor 51, and arranged above the escape wheel set 40 located in the layer of the bottom.

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

[0201] The third pallet holding section 93 opening in the direction of the escapement mobile 40 is arranged in the central part of the anchor body 111. The third pallet holding section 93 holds the first resting pallet 62 using this opening.

[0202] The second stop anchor 103 is arranged further in the second direction of rotation M2 with respect to the second impact anchor 52 according to a plan view, and comprises an anchor axis 120, which is a rotary shaft , and an anchor body 121. The second stop anchor 103 rotates around an axis of rotation 07 in the direction opposite to that of the pivoting of the second impact anchor 52 on the basis of the rotation of the second impact anchor 52.

[0203] The anchor pin 120 is held axially between the plate 11 and the gear train bridge (not shown) and is driven into the anchor body 121 from, for example, the bottom so as to be fixed integrally to the latter by forming a single piece.

[0204] The anchor body 121 is formed so that it extends along the circumferential direction of the escapement wheel set 40. The anchor pin 120 is fixed to the central part of the escapement body. anchor 121. It should be noted that the anchor body 121 is arranged in a position equivalent to that of the anchor body 81 of the second impact anchor 52, and is arranged above the escapement mobile 40 .

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

[0206] The second detent anchor 103 configured in this way is coupled to the second impact anchor 52 through a gear using a toothed sector.

[0207] In other words, a plurality of teeth 125 is provided at the level of the circumferential end 81b to which the second impulse pallet 61 is attached in the second impact anchor 52. Teeth 126 meshing with the teeth 125 of the second impact anchor 52 are formed at a circumferential end 121b of the second stop anchor 103 located in the first direction of rotation M1, so as to correspond to the teeth 125.

[0208] Consequently, the second impact anchor 52 and the second stop anchor 103 are coupled to each other so as to be able to move relative to each other, and rotate in opposite directions to each other.

[0209] It should be noted that, in this embodiment, the first detent anchor 102 and the second detent anchor 103 rotate in opposite directions with respect to each other. However, the first stop anchor 102 and the second stop anchor 103 are not limited to such a configuration and could be coupled so as to rotate in the same direction as each other.

[0210] A limiting pin 86 is arranged so as to be able to come into contact with an external lateral surface 121c located on the opposite side with respect to the second rest pallet 63 at the level of the circumferential end 121a of the second anchor. stopper 103. The other limiting pin 87 is arranged so as to be able to come into contact with an outer side surface 111c located on the opposite side with respect to the first resting pallet 62 in the central part of the first stop anchor 102 .

[0211] When the escapement gear 43 and the first rest pallet 62 are in mutual engagement, the outer side surface 121c of the second stop anchor 103 comes into contact with the limiting pin 86 and positions the second anchor. stopper 103. On the other hand, when the escapement gear 43 and the second rest pallet 63 are in mutual engagement, the outer side surface 111c of the first stopper anchor 102 comes into contact with the another limit pin 87 and positions the first stop anchor 102.

[0212] It should be noted that the first stop anchor 102 and the second stop anchor 103 are equivalent to the anchor located at the end of the chain of anchors 105.

[0213] Therefore, the outer side surface 121c is arranged on the second stop anchor 103, and it is located at the end of the chain of anchors 105. The outer side surface 121c functions as a part of pivot restriction which positions the second stop anchor 103 and restricts the movement of the entire chain of anchors 105 during the duration of engagement between the escapement gear 43 and the first rest pallet 62.

[0214] It should be noted that the second stop anchor 103 provided with the external lateral surface 121c is equivalent to a different anchor from the first stop anchor 102 provided with the first rest pallet 62 engaged with the gear. escapement gear 43 for the duration of the engagement between the escapement gear 43 and the first rest pallet 62. Accordingly, the first rest pallet 62 is attached to an anchor (the first stop anchor 102) located on the opposite side of the chain of anchors 105 with respect to an anchor (the second stop anchor 103) provided with the outer side surface 121c.

[0215] Similarly, the outer side surface 111c is arranged over the first stop anchor 102 located at the end of the chain of anchors 105. The outer side surface 111c functions as a pivot restriction portion which positions the first stop anchor 102 and restricts the movement of the entire chain of anchors 105 for the duration of the engagement between the escapement gear 43 and the second rest pallet 63.

[0216] It should be noted that the first stop anchor 102 provided with the external lateral surface 111c is equivalent to an anchor different from the second stop anchor 103 equipped with the second rest pallet 63 engaged with the gear. escapement gear 43 for the duration of the engagement between the escapement gear 43 and the second rest pallet 63. Therefore, the second rest pallet 63 is attached to an anchor (the second stop anchor 103) located on the opposite side of the chain of anchors 105 with respect to an anchor (the first stop anchor 102) provided with the outer side surface 111c.

Exhaust Operation

As in the first embodiment, the escapement 100 according to this embodiment configured as explained above can alternately and repeatedly engage between the escapement gear 43 and the first rest 62, and a clearance between these; the second rest pallet 63 can carry out an indirect transmission of energy to the balance-spring 30 by using the contact of the escapement gear 43 with the first impulse pallet 60 and the second impulse pallet 61.

[0218] The outer side surfaces 111c and 121c respectively coming into contact with the limiting pins 86 and 87 are arranged on the first stopper anchor 102 and the second stopper anchor 103, equivalent to the end of the chain. anchors 105. Consequently, when the escapement gear 43 is in mesh with the first rest pallet 62 or the second rest pallet 63, and the rotation of the escapement mobile 40 is stopped, it is possible to restrict the movement of the entire chain of anchors 105.

[0219] In other words, it is possible to achieve, on both sides of the chain of anchors 105, the engagement of the first rest pallet 62 with the escapement gear 43, and the restriction of the pivoting of the second stop anchor 103 thanks to the contact of the limiting pin 86 with the outer side surface 121c of the second stop anchor 103. Similarly, it is possible to realize, on both sides of the chain of anchors 105, the engagement of the second rest pallet 63 with the escapement gear 43 and the restriction of the pivoting of the first stopper anchor 102 thanks to the contact of the limiting pin 87 with the outer lateral surface 111c of the first anchor of stop 102. Therefore, it is possible to restrict the movement of the entire chain of anchors 105.

Thus, even if a disturbance occurs while the sprung balance 30 oscillates freely, it is possible to prevent the chain of anchors 105 from undulating by exhibiting flutter or vibrating. Therefore, it is possible to operate the escapement 100 stably.

[0221] Consequently, with an escapement 100 according to this embodiment, it is possible to perform the same actions and to obtain the same results as in the first embodiment.

Third embodiment

A third embodiment according to the present invention is explained below with reference to the drawings. It should be noted that, in this third embodiment, the same parts as the components of the first embodiment are indicated by the same signs and reference numerals, and no explanation will be given again as to these elements.

[0223] In the first embodiment, the first impact anchor 51 rotates to follow the plate pin 38 of the balance-spring 30. However, in the third embodiment, the second impact anchor 52 is configured to turn following the plate pin 38 of the balance-spring 30.

[0224] As shown in Figures 23 and 24, in an escapement 130 according to this embodiment, the pairs of lugs 73 defining the fork 74 are formed in one piece with the second impact anchor 52 at the end circumferential 81b. It should be noted that, in this embodiment, the position of the balance-spring 30 is different from that of the first embodiment depending on the position of the fork 74.

Exhaust Operation

The escapement 130 thus configured according to this embodiment differs from the first embodiment only in that the second impact lever 52 is driven in rotation first by the plate pin 38 of the balance-spring 30. The anchors can be rotated as in the first embodiment.

[0226] In other words, with an escapement 130 according to this embodiment, it is also possible to alternately and repeatedly engage the escapement gear 43 with the first rest pallet 62 and the second pallet. of rest 63, and their mutual disengagement, as well as effecting an indirect transmission of energy to the balance-spring 30 by using the contact of the escapement gear 43 with the first impulse pallet 60 and the second pallet impulse 61. Furthermore, when the sprung balance 30 oscillates freely, it is possible to restrict the movement of the entire chain of anchors 50 by using the restriction lever 85. Therefore, even if a disturbance occurs during the free oscillation of balance-spring 30, it is possible to prevent any form of uncontrolled undulation or any floating of the chain of anchors 50 and to prevent it from vibrating. Therefore, it is possible to operate the escapement 130 stably.

[0227] In particular, the second impact anchor 52 located at the level of the end of the chain of anchors 50 is configured to rotate following the plate pin 38 of the sprung balance 30. Consequently, it is possible to arrange the balance-spring 30 and the escapement wheel set 40 in close positions compared to the first embodiment.

[0228] Consequently, for example, when an escapement 130 according to this embodiment is applied to a Tourbillon, it is possible to contribute to a reduction in size of a cage on which a mechanism including the escapement 130 would be mounted. . Consequently, it is possible to produce an escapement 130 particularly suitable for a Tourbillon.

Fourth Embodiment

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

[0230] In the first embodiment, the first impact anchor 51 rotates following the plate pin 38 of the balance-spring 30. However, in the fourth embodiment, the stop anchor 55 is configured to turn following the plate pin 38 of the balance-spring 30.

As shown in Figure 25 and Figure 26, in an escapement 140 according to this embodiment, the pair of horns 73 defining the fork 74 is formed in one piece at a circumferential end 91b of the lever stopper 55. It should be noted that in this embodiment, the position of the balance-spring 30 differs from that of the first embodiment depending on the position of the fork 74.

[0232] The engagement plate 77 of the first impact anchor 51 is formed by a pair of elastic sections 141. Each of the elastic sections of the pair of elastic sections 141 respectively has a semicircular shape in a plan view. . As indicated by arrows shown in Fig. 25, a force is applied to the elastic sections 141 outwardly so that they move apart from each other.

[0233] Therefore, the engagement plate 77 of the first impact anchor 51 and the engagement fork 92 of the stopper anchor 55 are coupled to each other in a state in which the outer circumferential surfaces of the pair of resilient sections 141 are held in compression against the inner surface of the engagement fork 92.

[0234] Furthermore, the engagement fork 78 of the first impact anchor 51 is configured such that it can hold the engagement pin 82 of the second impact anchor 52. In other words, a section curve 142 is formed in a section at the base of the engagement fork 78. As indicated by an arrow shown in Figure 25, this has the consequence that the distal end of this leg of the fork tends to approach the other branch of the fork by pivoting at the level of the curved section 142.

[0235] Therefore, the engagement pin 82 of the second impact anchor 52 and the engagement fork 78 of the first impact anchor 51 are coupled to each other in a state in which the inner surface of engagement fork 78 is held in compression against the outer circumferential surface of engagement pin 82.

Exhaust Operation

[0236] In this embodiment, the escapement 140 configured as indicated above differs from that of the first embodiment only in that the stop anchor 55 is driven in rotation first by the plate pin 38 of the balance-spring 30. The anchors can otherwise pivot as in the first embodiment.

In other words, with the escapement 140 according to this embodiment, it is also possible to alternately engage the escapement gear 43 with the first rest pallet 62 and the second rest pallet 63, then to disengage it from the latter, and this repeatedly, and to effect an indirect transmission of energy to the balance-spring 30 by using the contact of the escapement gear 43 with the first impulse pallet 60 and the second impulse pallet 61. Furthermore, when the balance-spring 30 oscillates freely, it is possible to restrict the movement of the entire chain of anchors 50 by using the restriction lever 85. Consequently, even if a disturbance then occurs that the balance-spring 30 oscillates freely, it is possible to prevent the chain of anchors 50 from undulating in an uncontrolled manner having flutter or vibrating. Therefore, it is possible to operate the escapement 140 stably.

In particular, with an escapement 140 according to this embodiment, as in the context of the third embodiment, it is possible to arrange the balance-spring 30 and the escapement wheel set 40 in close positions compared to the first embodiment. Consequently, it is possible to produce an escapement 140 which is particularly suitable for a Tourbillon.

[0239] Furthermore, the engagement plate 77 of the first impact anchor 51 and the engagement fork 92 of the stopper anchor 55 are here coupled to each other in a state in which the outer circumferential surfaces of the pair of elastic sections 141 are held in compression against the inner surface of the engagement fork 92. Therefore, it is possible to prevent the formation of any gap between the engagement plate 77 and the engagement fork 92. Thus, it is possible to couple the first impact anchor 51 to the stop anchor 55 with less jolts.

[0240] Similarly, the engagement pin 82 of the second impact anchor 52 and the engagement fork 78 of the first impact anchor 51 are coupled to each other in a state in which the surface inside of the engagement fork 78 is held in compression against the outer circumferential surface of the engagement pin 82. Therefore, it is possible to prevent the formation of any gap between the engagement pin 82 and the engagement fork. engagement 78. Consequently, it is possible to couple the second impact anchor 52 to the first impact anchor 51 with less jerking.

[0241] Therefore, it is possible to effectively prevent the occurrence of jerks and backlashes between the first impact anchor 51 and the stopper anchor 55, and between the first impact anchor 51 and the second impact anchor 52. It is thus possible to rotate the first impact anchor 51, the second impact anchor 52, and the stopper anchor 55 with good mutual reaction. Thus, it is possible to operate the exhaust 140 more smoothly, and further improve operational performance.

Fifth Embodiment

In the following, a fifth embodiment according to the present invention is explained with reference to the drawings. It should be noted that, in the fifth embodiment, the same parts as the components of the first embodiment are indicated by the same reference numerals and signs, and no explanation concerning them will be repeated.

In the first embodiment, the escapement is an escapement qualified as an escapement of the indirect impact type which indirectly transmits energy to the balance-spring 30. However, in the fifth embodiment, the escapement The escapement is configured as an escapement qualified as an escapement of the semi-direct impact type which simultaneously uses a direct transmission of energy and an indirect transmission of energy to the balance-spring 30.

[0244] As shown in Figure 27 and Figure 28, an escapement 150 according to this embodiment includes a chain of anchors 155 having an impact anchor unit 152 including an impact anchor 151 and an impact anchor stop anchor 154 including a stop anchor 153.

[0245] The impact anchor unit 152 and the stop anchor unit 154 are coupled to each other in such a way that they can move relative to each other. In other words, the impact anchor 151 and the stop anchor 153 are coupled to each other in such a way that they can move relative to each other. Consequently, the impact anchor 151 and the stop anchor 153 are coupled so as to be connected in series one after the other.

[0246] It should be noted that the impact anchor unit 152 and the stop anchor unit 154 need only be formed by one or more anchors. In this embodiment, the impact anchor unit 152 and the stop anchor unit 154 are respectively constituted by a single anchor.

In this embodiment, among the first impulse paddle 60 and the second impulse paddle 61, it is the first impulse paddle 60 which is attached to the impact anchor 151, and the second impulse pallet 61 is attached to the double plate 35 fixed to the balance-spring 30. The first resting pallet 62 and the second resting pallet 63 are attached to the stop anchor 153.

In the following, the impact anchor 151 is described in detail.

[0249] The impact anchor 151 comprises an anchor pin 160, which is a rotatable shaft, and an anchor body 161; it pivots around an axis of rotation 08 on the basis of the alternating rotation of the balance-spring 30.

[0250] The anchor pin 160 is arranged coaxially with respect to the axis of rotation 08 and is held axially between the plate 11 and the gear train bridge (not shown). The anchor pin 160 is driven out, for example, from the bottom (the plate side 11), and fixed to a base of the anchor body 161 so as to no longer form a single piece with the latter.

The anchor body 161 is formed, for example, by electrofusion or thanks to the MEMS technique, and is placed above the escapement wheel set 40. It should be noted that, like the escapement wheel set 40 , weight reduction of the anchor body 161 can be achieved by making a lightening hole or a thin part in the anchor body 161 as required. In the example shown in the figure, a plurality of lightening holes is formed in the anchor body 161.

[0252] The anchor body 161 is arranged in a shape such that it extends from the base, to which the anchor pin 160 is fixed, towards the second direction of rotation M2, i.e. say, towards the balance-spring 30. The pair of horns 73 and the dart 75 arranged side by side in the circumferential direction of the axis of rotation 08 are arranged at the level of the distal end of the anchor body 161.

[0253] It should be noted that the dart 75 is fixed so as to be located below the plate pin 38, and located above the escapement wheel set 40.

The first pallet holding section 76 is arranged at the base of the anchor body 161 so that it protrudes in the direction of the escapement wheel set 40. The first impulse pallet 60 is held by the first pallet holding section 76.

[0255] It should be noted that the first impulse pallet 60 is maintained in a state in which it extends further downward relative to the anchor body 161 to reach a position of height equivalent to that at the wheel of escapement 42. Therefore, the first impulse vane 60 may come into contact (collide) with the escapement gear 43.

[0256] In the first paddle holding section 76, a plurality of teeth 162 arranged along the pivot direction of the impact anchor 151 are formed in the first rotation direction M1. A coupling piece 163 which connects the anchor body 161 to the first paddle holding section 76 is integrally formed between the anchor body 161 and the first paddle holding section 76. A positioning hole 165, through which a limiter pin (the limiter according to the present invention) 164 is inserted, is formed in the coupling part 163.

[0257] The positioning hole 165 is explained in detail below.

[0258] The impact anchor 151 configured in this way so that it rotates based on the rotation of the balance-spring 30 as explained above.

[0259] Specifically, the impact anchor 151 is driven in rotation around the axis of rotation 08 in the opposite direction to that of rotation of the balance-spring 30 by the plate pin 38 which moves according to the alternating rotation of the balance-spring 30. At that moment, the first impulse pallet 60 comes to encroach on the path of rotation R of the escapement wheel 42 by going beyond the latter, then retracts, according to the pivoting of the impact anchor 151. Therefore, it is possible to cause the working surface 43a of the escape gear 43 of the escape wheel 42 to come into contact (collide) with the first impact surface 60a of the first impulse paddle 60.

[0260] The second impulse pallet 61 is explained below.

[0261] As shown in Figure 27 and Figure 29, the second impulse pallet 61 is attached to the small collar 37 of the double plate 35. Specifically, the second impulse pallet 61 is carried by a second holding section of pallet 170 formed in the small collar 37. In Fig. 27, the second pallet holding section 170 is arranged in a clockwise position offset by a predetermined phase from the recess 39 around the axis of rotation O1, and it opens onto the escape wheel set 40. The second impulse pallet 61 is carried by the second pallet holding section 170 using this opening. The second impulse pallet 61 is maintained in a state in which it projects more towards the escapement wheel set 40 than the outer circumferential surface of the small collar 37. It should be noted that a side surface facing clockwise of a clock around the axis of rotation 01 in a projecting part of the second impulse pallet 61 is formed to constitute the second impact surface 61a with which the working surface of the escapement gear 43 in escape wheel 42 is brought into contact.

[0262] It should be noted that a predetermined spacing is ensured in the direction of the axis of rotation O1 between the second impulse pallet 61 and the plate peg 38. The dart 75 approaches the recess 39 through of this spacing.

The second impulse pallet 61 is not limited to an attachment to the small collar 37; it could be attached, for example, to the large plate 36 or to the balance wheel 32. The position of attachment and fixing of the second impulse pallet 61 can be changed according, for example, to its relative position with respect to the escape wheel 42. In all cases, the second impulse pallet 61 need only be attached to the balance-spring 30.

The second impulse pallet 61 attached to the sprung balance 30 as explained above encroaches beyond the path of rotation R of the escape wheel 42, and retracts from it according to the rotation of the balance-spring 30. Consequently, it is possible to cause the working surface 43a of the escapement gear 43 of the escapement wheel 42 to come into contact (collide) with the second surface of impact 61a of the second impulse paddle 61.

It should be noted that, as explained above, the direction of rotation of balance-spring 30 and the direction of pivoting of impact anchor 151 are 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 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 153 is explained in detail below.

As shown in Figs. 27 and 28, the stop anchor 153 according to this embodiment has the same configuration as that of the first embodiment; it thus comprises an anchor pin 90 and an anchor body 91. The stop anchor 153 according to this embodiment is arranged more in the first direction of rotation M1 with respect to the impact anchor 151 according to a plan view. The stop anchor 153 rotates around a rotation axis 09 in a direction opposite to that of the pivoting of the impact anchor 151 based on the rotation of the impact anchor 151.

[0268] It should be noted that the anchor body 91 of the stop anchor 153 is arranged on the same plane as the anchor body 161 of the impact anchor 151 and arranged above the mobile exhaust 40.

[0269] Consequently, the relative arrangement in height between the impact anchor 151, the stop anchor 153, and the escapement wheel set 40 is as follows: the escape wheel set 40 is located in the layer of the bottom closest to the plate 11, and the anchor body 161 of the impact anchor 151 and the anchor body 91 of the stop anchor 153 are located above the escapement wheel set 40.

[0270] As explained above, the anchor body 91 of the stop anchor 153 is arranged above the escapement wheel set 40. Consequently, like the first impulse pallet 60, the first pallet rest 62 and the second rest pallet 63 are maintained in a state in which they extend further downward relative to the pallet body 91 to reach a position of height equivalent to that of the escapement wheel 42. Thus, the first rest pallet 62 and the second rest pallet 63 can engage and disengage from the escapement gear 43.

[0271] At the circumferential end 91a of the anchor body 91, a plurality of teeth 171 meshing with the teeth 162 of the impact anchor 151 is formed in place of the engagement fork 92 of the first embodiment. Therefore, the impact anchor 151 and the stopper anchor 153 are coupled to each other through the mutual gearing of the teeth 162 and 171. Therefore, the impact anchor 151 and the stopper anchor 153 are coupled to each other in a moveable manner relative to each other, and rotate in opposite directions relative to each other.

As explained above, the chain of anchors 155 is formed by the coupling of the impact anchor 151 and the stop anchor 153 connected in series one after the other. The anchors 151 and 153 move to rotate individually based on the alternating rotation of the balance-spring 30. In other words, the impact anchor 151 rotates in the opposite direction to that of rotation of the balance-spring 30. The stop anchor 153 rotates in the opposite direction to that of the pivoting of the impact anchor 151.

The positioning hole 165 detailed above is explained in detail.

[0274] The positioning hole 165 passes right through the coupling piece 163 in the thickness direction, and has an arcuate shape in a plan view extending along the direction of pivoting of the anchor. impact 151 (i.e., a direction rotating around the axis of rotation 08). The length (circumferential length) of the positioning hole 165 along the circumferential direction of the rotation axis 08 corresponds to a swing angle (a working angle) of the impact anchor 151 swinging between a state in which the first rest pallet 62 and the escape gear 43 of the escape wheel 42 are in mutual engagement, and a state in which the second rest pallet 63 and the escape gear 43 of the escape wheel exhaust 42 are in mutual engagement.

Limit pin 164 is disposed in positioning hole 165. Limit pin 164 is attached to platen 11 and inserted through positioning hole 165 from below. In this case, the outer circumferential surface of the limiting pin 164 is in sliding contact with the inner circumferential surface of the positioning hole 165. Consequently, the limiting pin 164 moves relatively with respect to the positioning hole 165 and the inside the latter according to the pivoting of the impact anchor 151.

[0276] At this time, the length of the positioning hole 165 along the circumferential direction corresponds to the swing angle of the impact anchor 151. Therefore, as shown in Fig. 27, when the first rest vane 62 and the escapement gear 43 are brought into mutual engagement, a first inner circumferential surface 165a located on the first impulse vane 60 at the inner circumferential surface of the positioning hole 165 comes into contact with the limit pin 164. Therefore, the impact anchor 151 is positioned by the limit pin 164.

[0277] As shown in Figure 28, when the second rest pallet 63 and the escapement gear 43 are in mutual engagement, a second internal circumferential surface 165b located on the anchor body 161 at the level of the circumferential surface internal of the positioning hole 165 comes into contact with the limiting pin 164. Therefore, the impact anchor 151 is positioned by the limiting pin 164.

[0278] Therefore, the impact anchor 151 can be positioned even by a single limiting pin 164. It should be noted that the first inner circumferential surface 165a and the second inner circumferential surface 165b of the positioning hole 165 function as a pivoting restriction part which is brought into contact with the limiting pin 164 to restrict the pivoting of the impact anchor 151 and restrict the movement of the entire chain of anchors 155.

[0279] It should be noted that the impact anchor 151 and the stop anchor 153 are equivalent to an anchor located at the end of the chain of anchors 155. Therefore, the first resting pallet 62 and the second resting pallet 63 are attached to an anchor (the stop anchor 153) located on the opposite side of the chain of anchors 155 with respect to an anchor (the impact anchor 151) in which the first inner circumferential surface 165a and the second inner circumferential surface 165b are arranged.

Exhaust Operation

[0280] With an escapement 150 configured as explained above corresponding to this embodiment, as in the context of the first embodiment, it is possible to alternately effect engagement of the escapement gear 43 with the first pallet rest 62 and the second pallet rest 63, and a disengagement thereof relative to these pallets, all repeatedly. Furthermore, it is possible to carry out an indirect transmission of energy to the balance-spring 30 by using the contact of the escapement gear 43 with the first impulse pallet 60 and the second impulse pallet 61.

[0281] In particular, the first impulse pallet 60 is arranged on the impact anchor 151 and the second impulse pallet 61 is arranged on the balance-spring 30. Consequently, it is possible to indirectly transmit a energy, which is supplied to the entry of the escapement wheel set 40, to the balance-spring 30 via the first impulse pallet 60 and the impact anchor 151. It is possible to transmit the energy directly to the balance- hairspring 30 via the second impulse pallet 61.

[0282] In other words, it is possible to transmit the energy, which was previously transmitted to the escapement wheel 40, to the balance-spring 30 while alternately carrying out (switching) an indirect transmission of energy by using the first pallet pulse 60 and direct energy transmission performed using the second pulse paddle 61.

[0283] Consequently, it is possible to make the escapement 150 operate as an escapement 150 qualified as a semi-direct impact type escapement, which simultaneously uses a direct impact and an indirect impact. Stable operation and power transmission can be guaranteed. In particular, in the case of the escapement 150 with semi-direct impact, since energy can be directly transmitted to the balance-spring 30 by the second impulse pallet 61, it is possible to improve the transmission efficiency. energy compared to an indirect type impact. Therefore, it is desirable to employ such an escapement 150 of the semi-direct impact type.

[0284] Also in the case of this embodiment, unlike a conventional escapement in which the impulse pallet and the rest pallet are incorporated in a common anchor, the impact anchor 151 comprises the first pallet of impulse 60 and stop anchor 153 has the first resting paddle 62 and the second resting paddle 63. Therefore, it is possible to freely design, and respectively arrange the impact anchor unit 152 (the anchor 151) in a position relative to the escapement wheel set 40 and the stop anchor unit 154 (the stop anchor 153) a position relative to the escape wheel set 40 with fewer restrictions. It is possible to arrange the impact anchor unit 152 and the stop anchor unit 154 in respectively optimum configurations for impact and stop.

[0285] As shown in Figure 27, when the escapement gear 43 and the first rest pallet 62 are in mutual engagement, the first inner circumferential surface 165a of the positioning hole 165 comes into contact with the limiting pin 164 and the impact anchor 151 is positioned. As shown in Fig. 28, when the escapement gear 43 and the second rest paddle 63 are in mutual engagement, the second inner circumferential surface 165b of the positioning hole 165 comes into contact with the limit pin 164 and the impact anchor 151 is positioned.

[0286] In both cases, the impact anchor 151 is an equivalent anchor at the end of the chain of anchors 155. Consequently, when the escapement gear 43 is in mesh with the first pallet of rest 62 or the second rest pallet 63, and the rotation of the escapement wheel set 40 is stopped, it is possible to restrict the movement of the entire chain of anchors 155.

[0287] In other words, it is possible to achieve, on both sides of the chain of anchors 155, the engagement of the first rest pallet 62 and the second rest pallet 63 with the escapement gear 43, and to restrict pivoting of the impact anchor 151 by contact of the first inner circumferential surface 165a and the second inner circumferential surface 165b with the limiting pin 164. Accordingly, it is possible to restrict the movement of the entire chain of anchors 155.

[0288] Therefore, in this embodiment also, for example, even if a disturbance occurs while the balance-spring 30 oscillates freely, it is possible to prevent the chain of anchors 155 from undulating by having flutter or vibrate. Thus, it is possible to operate the escapement 150 stably.

[0289] In particular, contrary to the first embodiment, only one limiting pin 164 is sufficient and the limiting pin 164 can be arranged in the plane of the impact anchor 151. Consequently, the space occupied by the pair of limiting pins 86 and 87 according to the first embodiment can be eliminated or effectively used for other elements.

In addition, the escapement 150 according to this embodiment is an escapement usually qualified as an escapement of the semi-direct impact type. Consequently, it is possible to arrange the balance-spring 30 and the escapement wheel set 40 in positions close to each other. Thus, for example, when the escapement 150 according to this embodiment is applied to a Tourbillon, it is possible to contribute to a reduction in the size of the cage in which would be mounted with a mechanism comprising such an escapement 150. Consequently , the escapement 150 can be configured as an escapement particularly suitable for a Tourbillon.

Sixth Embodiment

[0291] In the following, a sixth embodiment according to the present invention is explained with reference to the drawings. It should be noted that, in the sixth embodiment, the same parts as the components of the first embodiment bear the same signs and reference numerals, and no explanation will be repeated for these parts.

[0292] In the first embodiment, the impulse paddle and the rest paddle are attached to the various anchors. However, in the sixth embodiment, the escapement is configured as an escapement in which the first impulse pallet 60, the first resting pallet 62, and the second resting pallet 63 are attached to a common anchor. Furthermore, in the first embodiment, the escape wheel set 40 is made in the form of a single-layer structure. However, in the sixth embodiment, the escape wheel set 40 is made in the form of a double-layer structure.

[0293] As shown in Figure 30 and Figure 31, the escapement 180 according to this embodiment comprises an escapement wheel set 40 having a double-layered structure, and an anchor chain 185 comprising an anchor unit actuator 182 including an actuator anchor 181 and an impact anchor unit 184 including an impact anchor 183.

[0294] The escapement wheel 40 is formed in a double-layer structure comprising the escapement pinion 41 which meshes with the seconds wheel 23, a first escapement wheel 45 including a plurality of first escapement gears 46 , a second escapement wheel 47 including a plurality of second escapement gears 48. The escapement wheel set 40 is axially supported between the plate 11 and the gear train bridge (not shown).

[0295] It should be noted that, in this embodiment, an example is detailed in which the escapement wheel 40 rotates counterclockwise around the axis of rotation 02 thanks to the energy transmitted by the seconds mobile 23 via the escapement pinion 41 according to a plan view in which the movement 10 is seen from the front side, as illustrated in FIG. 30 and FIG. 31. In other words, in this mode of realization, the escape wheel set 40 rotates in the second direction of rotation M2.

[0296] The escapement pinion 41, the first escapement wheel 45, and the second escapement wheel 47 are integrally arranged in a state in which the escapement pinion 41, the first escapement wheel 45 , and the second escapement wheel 47 are arranged on the same axis, i.e., the common axis of rotation 02. The escapement pinion 41 and the second escapement wheel 47 are formed so as to monobloc on the upper side of the first escape wheel 45.

[0297] The number of teeth of the first escapement gear 46 is fixed at eight. However, the number of teeth of the first escapement gear 46 is not limited to such a configuration and can be changed as needed. For example, the first escapement wheel 45 can be a first escapement wheel 45 including a first escapement gear 46 having, for example, six teeth, ten teeth, or twelve teeth.

[0298] It should be noted that reference is simply made to the path of rotation R1 of the first escapement wheel 45 to designate the path of rotation R1 followed by the end of the first escapement gear 46 during the rotation of the exhaust mobile 40.

[0299] The second escapement wheel 47 has a diameter smaller than that of the first escapement wheel 45. The number of teeth of the second escapement gear 48 is fixed at eight, as the number of teeth of the first escapement gear exhaust 46.

[0300] However, the number of teeth of the second escapement gear 48 need only be the same as that of the first escapement gear 46, and thus is not limited to eight either. Thus, when the number of teeth of the first escapement gear 46 is set to, for example, six, ten, or twelve, the number of teeth of the second escapement gear 48 need only be changed according to the number of teeth of the first escapement gear 46.

[0301] The phase of the second escapement wheel 47 is slightly offset around the axis of rotation O2 with respect to the first escapement gear 45. In the example shown in the figure, the phase of the second escapement gear escapement 48 is offset so that the second escapement gear 48 is located further in the second direction of rotation M2 than the first escapement gear 46.

[0302] It should be noted that reference is simply made to the path of rotation R2 of the second escapement wheel 47 to designate the path of rotation R2 traced by the end of the second escapement gear 48 following the rotation of the escapement wheel 40. Since the second escapement wheel 47 is configured in a smaller diameter than that of the first escapement wheel 45 as explained above, the external diameter of the second escapement wheel 47 is smaller than the outer diameter of the first escapement wheel 45. Consequently, the rotation path R2 is located inside the rotation path R1.

[0303] The side surface facing the second direction of rotation M2 in the first escapement gear 46 detailed above is arranged to form a first working surface 46a which comes into contact with the second impulse pallet 61, and with which the first pallet rest 62 and the second pallet rest 63 engage. A side surface facing the second direction of rotation M2 in the second escapement gear 48 explained above is arranged to form a second working surface 48a which comes into contact with the first impulse pallet 60.

[0304] Actuation anchor unit 182 and impact anchor unit 184 are movably coupled to each other. In other words, the actuating anchor 181 and the impact anchor 183 are coupled to each other in such a way that they can move relative to each other. Consequently, the actuating anchor 181 and the impact anchor 183 are coupled so as to be connected in series one after the other.

[0305] It should be noted that the actuation anchor unit 182 and the impact anchor unit 184 need only be formed by at least one or more anchors. In this embodiment, as explained above, the actuation anchor unit 182 and the impact anchor unit 184 are respectively formed by a single anchor.

In this embodiment, among the first impulse paddle 60 and the second impulse paddle 61, it is the first impulse paddle 60 which is attached to the actuation anchor 181; the second impulse pallet 61 is attached to the impact anchor 183. The first rest pallet 62 and the second rest pallet 63 are attached to the actuation anchor 181.

[0307] In the following, the actuating anchor 181 is explained in detail.

[0308] The actuating anchor 181 comprises an anchor pin 190, which is a rotatable shaft, and an anchor body 191; it rotates around an axis of rotation 010 on the basis of the alternating rotation of the balance-spring 30.

[0309] The anchor pin 190 is arranged coaxially with respect to the axis of rotation 010 and held axially between the plate 11 and the gear train bridge (not shown). The anchor pin 190 is driven out, for example, from the bottom, and integrally fixed to the anchor body 191 to form a single, one-piece piece.

The anchor body 191 is produced, for example, by electrofusion or via the MEMS technique. In the example shown in the figure, the anchor body 191 has an arcuate shape in a plan view so as to extend along the circumferential direction of the escapement wheel set 40. It should be noted that A reduction in the weight of the anchor body 191 can be obtained by making a lightening hole or a thin part in the anchor body 191 as required.

[0311] The anchor pin 190 is fixed to the central part of the anchor body 191. The anchor body 191 is placed above the first escapement wheel 45. It should be noted that the body lever 191 can be placed above the second escapement wheel 47 or can be placed in the same plane as the second escapement wheel 47.

The first rest pallet 62 is held, by the third pallet holding section 93, at the level of a circumferential end 191a located in the first direction of rotation M1 of the anchor body 191.

[0313] The first rest pallet 62 is maintained in a state in which the first rest pallet 62 protrudes more towards the escapement wheel set 40 than the third pallet holding section 93. The first rest pallet 62 extends further downward relative to the anchor body 191 to reach a height position equivalent to that of the first escapement wheel 45. Accordingly, the first rest pallet 62 can be brought into engagement with the first escapement gear 46, and disengage from it.

[0314] A side surface facing the first direction of rotation M1 in a protruding part of the first rest pallet 62 is arranged to form the first engagement surface 62a. First working surface 46a of first escapement gear 46 is engageable with first engagement surface 62a.

[0315] In the anchor body 191, the second pallet rest 63 is held, by the fourth pallet holding section 94, at the level of a circumferential end 191b located in the second direction of rotation M2.

[0316] The second rest pallet 63 is maintained in a state in which the second rest pallet 63 protrudes more towards the escapement wheel set 40 than the fourth pallet holding section 94. As the first rest pallet 62, the second rest pallet 63 extends further downward relative to the anchor body 191 to reach a position of height equivalent to that of the first escapement wheel 45. Consequently, the second rest pallet 63 can come into engagement with the first escapement gear 46 and disengage therefrom.

A lateral surface facing the first direction of rotation M1 in a protruding part of the second rest pallet 63 is arranged to form the second engagement surface 63a. The first working surface 46a of the first escapement gear 46 is capable of engaging the second engagement surface 63a.

The first pallet holding section 76 is arranged in the central part to which the anchor pin 190 is fixed to the anchor body 191, and so as to protrude in the direction of the escapement wheel set 40. The first impulse paddle 60 is held by the first paddle holding section 76.

The first impulse vane 60 is maintained in a state in which the first impulse vane 60 protrudes more in the direction of the escapement wheel set 40 with respect to the first vane holding section 76. A side surface facing the first direction of rotation M1 in a projection part of the first impulse pallet 60 is arranged to form the first impact surface 60a with which the second working surface 48a of the second escapement gear 48 comes into contact . It should be noted that the first impulse pallet 60 is configured not to be in contact with the first escapement wheel 45.

[0320] In the example shown in the figure, in order to make possible a contact between the first pulse pallet 60 and the second escapement gear 48, the first pallet holding section 76 protrudes in the direction of the mobile d escapement 40 at a level above the first escapement gear 46.

[0321] However, the first pallet holding section 76 is not limited to such a configuration and could be disposed further outward in the radial direction relative to the first escapement wheel 45. The protrusion level of the first impulse paddle 60 from the first paddle holding section 76 can be increased. Only the first impulse pallet 60 can be located above the first escapement gear 46.

In the central part of the anchor body 191, an anchor arm 192 is arranged so as to extend in the direction of the sprung balance 30. The pair of horns 73 and the dart 75 arranged side by side in the circumferential direction of the axis of rotation 010 are arranged at the distal end of the anchor arm 192.

Furthermore, at the circumferential end 191b of the anchor body 191, an engagement fork 193 having a forked shape extending in the second direction of rotation M2 and bifurcating in the circumferential direction of the axis of rotation 010 is formed in one piece.

[0324] Actuating anchor 181 configured in this way rotates based on the rotation of balance-spring 30 as explained above.

[0325] Specifically, the actuating anchor 181 pivots around the axis of rotation 010 in the opposite direction to that of rotation of the balance-spring 30 by the plate pin 38, which moves following the alternating rotation of the balance-spring 30. At this moment, the first pallet rest 62 and the second pallet rest 63 move forward until they encroach beyond the path of rotation R of the first escapement wheel 45, and retracts from it following the pivoting of the actuating anchor 181.

[0326] Consequently, it is possible to bring the first working surface 46a of the first escapement gear 46 of the first escapement wheel 45 into engagement with the first engagement surface 62a of the first rest pallet 62 or with the second engagement surface 63a of the second rest pallet 63.

[0327] In particular, the first pallet rest 62 and the second pallet rest 63 are arranged on either side of the axis of rotation 010. Consequently, the second pallet rest 63 emerges from the first wheel escapement plate 45 when the first rest pallet 62 comes into engagement with the first escapement wheel 45. The second rest pallet 63 comes into engagement with the first escapement wheel 45 when the first rest pallet 62 disengages from the first escape wheel 45.

[0328] Furthermore, the first impulse pallet 60 alternately repeats an advance to encroach on the path of rotation R2 of the second escape wheel 47, and a retraction with respect thereto according to the pivoting of the lever 181. Therefore, it is possible to make the second working surface 48a of the second escapement gear 48 of the second escapement wheel 47 come into contact (collide) with the first surface of impact 60a of the first impulse paddle 60.

[0329] It should be noted that the first pulse pallet 60 comes into contact with the second escapement gear 48 during the absence of mutual engagement between the first rest pallet 62 and the second rest pallet 63.

[0330] In the following, the impact anchor 183 is explained in detail.

[0331] The impact anchor 183 is arranged further in the second direction of rotation M2 with respect to the actuating anchor 181 in plan view and comprises an anchor axis 200, which is a rotating shaft, and an anchor body 201. The impact anchor 183 rotates about a rotation axis 011 in a direction opposite to that of the pivoting of the actuation anchor 181 based on the rotation of the anchor actuation 181.

The anchor pin 200 is arranged coaxially with respect to the axis of rotation 011 and is held axially between the plate 11 and the gear train bridge (not shown). The anchor pin 200 is driven out, for example, from the bottom, and integrally fixed to the anchor body 201 to form only one single piece.

[0333] The anchor body 201 is produced in the form of a disc according to a plan view, for example by electrofusion or via the MEMS technique, and is arranged in the same plane as the anchor body 191 of the anchor. actuation 181.

In the anchor body 201, an engagement plate 202 is arranged so as to protrude in the first direction of rotation M1. In the example shown in the figure, the engagement plate 202 is made so as to have a thickness equivalent to that of the anchor body 201, and has a circular shape in a plan view.

[0335] The engagement plate 202 is brought into engagement inside the engagement fork 193 of the actuation anchor 181. The outer circumferential surface of the engagement plate 202 and the inner surface of the engagement fork 193 are mutually engaged with each other through sliding contact. Therefore, the actuating anchor 181 and the impact anchor 183 are coupled to each other in such a way that they can move relative to each other and they rotate in opposite directions. each other.

[0336] In the anchor body 201, the second pallet holding section 83 is arranged to protrude in the direction of the escapement wheel set 40. The second impulse pallet 61 is held by the second pallet holding section 83.

The second impulse vane 61 is maintained in a state in which the second impulse vane 61 protrudes more towards the escapement wheel set 40 than the second vane holding section 83. The second impulse vane impulse 61 is maintained in a state in which the second impulse pallet 61 extends further downward relative to the anchor body 201 to reach a position of height equivalent to that of the first escapement wheel 45. Therefore, the second impulse vane 61 may come into contact (collide) with the first escapement gear 46.

[0338] A side surface facing the first direction of rotation M1 in a projecting part of the second impulse pallet 61 is arranged to form a second impact surface 61a with which the first working surface 46a of the first gear exhaust 46 comes into contact.

[0339] As explained above, the impact anchor 183 configured in this way pivots around the axis of rotation 011 based on the pivoting of the actuation anchor 181, which pivots according to the alternating rotation of the balance-spring 30. At this moment, the second impulse pallet 61 advances and encroaches on the path of rotation R of the first escapement wheel 45 and retracts therefrom according to the pivoting of the impact anchor 183. Therefore, it is possible to cause the first working surface 46a of the first escapement gear 46 to come into contact (collide) with the second impact surface 61a of the second pallet impulse 61.

[0340] In particular, the actuating anchor 181 and the impact anchor 183 are coupled in such a way that the directions of pivoting are opposite. Consequently, when an anchor of the actuating anchor 181 and the impact anchor 183 rotate in the same direction as that of rotation of the escapement wheel set 40, the other anchor rotates in the opposite direction to that of rotation of the escape wheel set 40.

[0341] Consequently, the second impulse pallet 61 disengages from the first escapement wheel 45 when the first impulse pallet 60 comes into contact with the second escapement wheel 47. The second impulse pallet 61 comes into contact with the first escapement wheel 45 when the first impulse pallet 60 disengages from the second escapement wheel 47.

[0342] It should be noted that, according to this embodiment, the actuating anchor 181 and the impact anchor 183 are coupled in such a way that the directions of pivoting are opposite. However, actuation anchor 181 and impact anchor 183 are not limited to such a configuration and could be coupled to rotate in the same direction.

[0343] Furthermore, as in the context of the first embodiment, the restriction lever 85 which restricts the movement of the entire chain of anchors 185 for the duration of the engagement between the first pallet rest 62 and the second pallet rest 63 and the first escapement wheel 45 is formed in the anchor body 201. In other words, the restriction lever 85 is located at the end of the chain of anchors 185 and is arranged in an anchor ( that is to say, the impact anchor 183) different from that in which the first rest pallet 62 and the second rest pallet 63 are arranged (that is to say, the anchor of actuation 181).

[0344] The restriction lever 85 is formed such that it extends from the anchor body 201 in a direction opposite to the direction in which the engagement plate 202 projects. The restriction lever 85 comes into contact with the pair of limitation pins 86 and 87 arranged on both sides located on either side of the restriction lever 85 in order to be able to restrict the pivoting of the impact anchor 183, and to position the impact anchor 183.

[0345] A limitation pin 86 is arranged so as to be located more on the side of the escapement mobile 40 than of the restriction lever 85. The other limitation pin 87 is arranged so as to be located more on the side of the balance -hairspring 30 than restriction lever 85.

[0346] When the first rest pallet 62 engages the first escape wheel 45 as shown in Figure 30, the restriction lever 85 comes into contact with a limiting pin 86 to restrict the pivoting of the anchor 183. When the second resting paddle 63 engages the first escapement wheel 45 as shown in Fig. 31, the restrictor lever 85 contacts the other restrictor pin 87 to restrict pivoting. of the impact anchor 183.

[0347] It should be noted that the actuating anchor 181 and the impact anchor 183 are equivalent to an anchor located at the end of the chain of anchors 185. Therefore, the first resting pallet 62 and the second rest paddle 63 are attached to an anchor (the actuating anchor 181) located on the opposite side of the chain of anchors 185 from an anchor (the impact anchor 183) in which the lever restriction 85 is formed.

Exhaust Operation

[0348] With the escapement 180 corresponding to this embodiment and configured as explained above, as in the first embodiment, it is possible to alternately and repeatedly engage the first gear of exhaust 46 with the first pallet rest 62 and the second pallet rest 63, followed by disengagement thereof with the latter. It is possible to carry out an indirect transmission of energy to the balance-spring 30 by using the contact of the second escapement gear 48 with the first impulse pallet 60 and the contact of the first escapement gear 46 with the second pallet. impulse 61.

Consequently, it is possible to ensure that the escapement 180 functions like an escapement 180 of the type of those qualified as indirect impact escapements. It is possible to guarantee a stable operation and a transmission of energy compared to the case where the energy is directly transmitted to the balance-spring 30.

[0350] In the context of this embodiment also, during the engagement of the first escapement gear 46 with the first rest pallet 62 or during the engagement of the first escapement gear 46 with the second rest pallet 63 , it is possible to position the impact anchor 183 located at the end of the chain of anchors 185 according to the contact of the restriction lever 85 with the pair of limiting pins 86 and 87. Therefore, it is possible to prevent the impact anchor 183 from rotating further. Therefore, it is possible to restrict the movement of the entire chain of anchors 185.

[0351] In other words, it is possible to effect, on both sides of the chain of anchors 185, an engagement of the first rest pallet 62 and of the second rest pallet 63 with the first escapement gear. 46, and restriction of pivoting of impact anchor 183 through contact of restriction lever 85 with limit pins 86 and 87. anchors 185.

[0352] Consequently, for example, even if a disturbance occurs when the rotation of the escapement wheel set 40 is stopped and the balance-spring 30 oscillates freely, it is possible to prevent the chain of anchors 185 from flutter or vibrate. Therefore, it is possible to operate the escapement 180 stably.

[0353] 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.

For example, in the embodiments described, the configuration proposed for transmitting the energy from 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.

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).

[0356] In the embodiments described, 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 made of 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.

From the first embodiment to the fourth embodiment, the impact anchor unit is formed by two anchors. However, the impact anchor unit is not limited to such configuration. For example, the impact anchor unit could be configured by, for example, one anchor or three or more anchors. Impulse paddles can be attached to two anchors of the three or more anchors.

[0358] It should be noted that, when the impact anchor unit is formed by a single anchor, for example, the anchor need only be configured to take an arcuate shape extending along the circumferential direction. of the escape wheel set and have a shape such that the two ends in the circumferential direction are located on opposite sides in the radial direction on either side of the escape wheel set. The impulse paddles only have to be attached respectively to the two ends of the anchor.

[0359] By configuring the impact anchor unit in this way, even with the pivoting of only one anchor, it is possible to ensure that the impulse paddles attached to both ends of the impact anchor alternately coming into contact (colliding) with the escape mobile. Therefore, it is possible to perform the same actions and obtain the same effects as those of the first embodiment.

[0360] In the above embodiments, the stop anchor unit is formed by a single anchor or two anchors. However, the stop anchor unit is not limited to such a configuration. The stop anchor unit could be formed, for example, of three or more anchors. The rest paddles can be attached to two anchors of the three or more anchors.

[0361] Further, in the embodiments, an example is given where the limiter pin is used as a limiter. However, the limiter is not limited to such a configuration. A stop boundary section could be arranged on, for example, a plate or a bridge. For example, the restriction lever could be brought into contact with the stop boundary section to restrict movement of the entire chain of anchors.

Claims (6)

1. Exhaust (13) comprising: an escape wheel set (40) arranged to rotate with energy transmitted thereto; an anchor chain (50) in which a plurality of anchors (51, 52, 55) are coupled to each other so as to be movable relative to each other or relative to each other, being connected in series one after the other; a rest pallet (62) able to come into engagement with an escapement wheel (42) of the escapement wheel set (40) and to disengage therefrom; and an impulse pallet (60) able to come into contact with the escapement wheel (42) in the absence of mutual engagement of the escapement wheel (42) with the resting pallet (62), in which the anchor chain (50) is arranged to be actuated to individually rotate the plurality of anchors (51, 52, 55) based on the rotation of a hairspring (30), the rest paddle (62) and the impulse paddle (60) are respectively part of at least one or more anchors among the plurality of anchors (51, 52, 55), and of the plurality of anchors (51, 52, 55), one anchor is located at one end of the chain of anchors (50), has a pivot restricting part (85) and is arranged to be constrained in pivoting by this pivoting restriction part (85) in order to limit the displacement of each anchor of the chain of anchors (50) during the engagement of the rest pallet (62) with the escapement wheel (42). 2. Exhaust (13) according to claim 1, wherein the end at which the anchor is located with the pivoting restriction part (85) is a first end of the chain of anchors, the resting pallet (62 ) forming part of a said anchor located at a second end of the chain of anchors (50), the first end and the second end being opposite ends of the chain of anchors. 3. Exhaust (13) according to claim 1 or 2, wherein the impulse pallet (60) is part of a said anchor different from that of which the rest pallet (62) is part. 4. Exhaust (13) according to one of claims 1 to 3, wherein the pivoting restriction part (85) restricts the pivoting by coming into contact with a limiter (86,87). 5. Movement (10) of timepiece (1) comprising: an exhaust (13) according to one of claims 1 to 4; a regulating device (14) including the balance-spring (30); and a gear train (12) arranged to transmit energy to the escape wheel set (40). 6. Timepiece (1) comprising: a movement (10) of a timepiece (1) according to claim 5; and a needle (5, 6, 7) arranged to rotate at a speed of rotation adjusted by the escapement (13) and the regulating device (14).