CH715093B1 - Combination of an escapement and a sprung balance, timepiece movement and timepiece. - Google Patents

Abstract

The present invention relates to the combination of a half-direct/half-indirect impact type escapement and a sprung balance (30). The exhaust excels in torque transmission efficiency (exhaust efficiency). The escapement (13) comprises an escapement mobile (60), which rotates around a first axis (O1) using transmitted energy, and a control element (70), which allows the mobile to rotate and stops. the escapement (60) on the basis of the rotation of said sprung balance (30), which performs an alternating rotation in a first direction of rotation and a second direction of rotation, which are opposite to each other, around a second axis (O2). The escape wheel (60) directly transmits the energy transmitted to the sprung balance (30) when the sprung balance (30) rotates in the first direction of rotation and indirectly transmits the energy transmitted to the sprung balance (30) via the control element (70) when the sprung balance (30) rotates in the second direction of rotation, and the control element (70) controls the rotation of the escapement wheel (60) in such a way that a first angle of rotational action (θ1) in the context of the direct transmission of energy from the escape wheel (60) to the sprung balance (30) differs from a second angle of rotational action (θ2) in the framework of the indirect transmission of energy from the escapement mobile (60) to the sprung balance (30). The control element (70) controls the rotation of the escapement wheel (60) in such a way that the first rotational action angle (θ1) is greater than the second rotational action angle (θ2).

Description

BACKGROUND OF THE INVENTION

1. Field of the invention

[0001] The present invention relates to the combination of an escapement and a sprung balance, as well as to a timepiece movement and a timepiece.

2. Description of the prior art

[0002] Generally, a mechanical timepiece includes an escapement which transmits energy causing the sprung balance to perform an alternating rotation and controls the gear train on the basis of a fixed frequency using regular alternating rotation of the sprung balance. An exhaust of this type has progressed through repeated improvements and other changes, and a variety of exhaust types are now offered.

[0003] As a traditional escapement for mechanical timepieces, the Swiss anchor escapement is very widely used.

[0004] The Swiss anchor escapement mainly comprises an escapement mobile, a double plate arranged on the sprung balance, and an anchor which can pivot on the basis of the alternating rotation of the sprung balance and includes a pallet of inlet and an outlet pallet which can engage with the teeth of the exhaust mobile and then free itself therefrom. The entry vane and the exit vane are configured to be alternately engaged with and released from the teeth of the escapement mobile in response to the pivoting movement of the anchor.

[0005] The Swiss anchor escapement, in which the entry pallet and the exit pallet alternately engage with the teeth of the escapement mobile then release themselves in response to the pivoting movement of the anchor , can not only control the rotation of the escapement wheel, but also indirectly transmit the energy transmitted to the escapement wheel to the balance spring via the anchor to provide rotational energy (torque) to the balance spring.

[0006] It is, however, generally known that a Swiss lever escapement has a low transmission efficiency (escapement efficiency) with which the torque is transmitted from the escapement wheel to the sprung balance via the anchor, and therefore, there are opportunities for improvement in torque transmission efficiency.

[0007] To improve transmission efficiency in terms of torque, for example, a Swiss anchor escapement is known in which the angle of rotational action of the escapement mobile at the time of contact between the teeth of the escapement mobile escapement and the entry pallet and the angle of rotational action of the escapement mobile at the moment of contact between the teeth of the escapement mobile and the outlet pallet are configured not to be uniform (see Swiss patent No . 570,644 (patent document 1), for example).

[0008] In this case, the supply balance between the quantity of torque transmitted from the input pallet to the sprung balance via the anchor and the quantity of torque transmitted from the output pallet to the sprung balance via the anchor can be adjusted to be optimal, whereby the torque transmission efficiency can be improved.

[0009] As another example, there is, for example, a known Swiss anchor escapement which comprises an escape wheel having a two-stage structure in which a first escape wheel and a second escape wheel are superimposed in coaxially one on the other, and in which the entry vane is encouraged to come into contact with the teeth of the first escape wheel, and the exit vane is encouraged to come into contact with the teeth of the the second escape wheel (see Japanese patent No. 4,894,051 - patent document 2 - and published European patent application No. 1,914,605 - patent document 3 - for example).

[0010] In this case, since the combination between the entry vane and the first escape wheel, and the combination between the exit vane and the second escape wheel can be designed separately, the angle of action rotational force of the escape wheel at the time of contact between the teeth of the first escape wheel and the input pallet, and the angle of rotational action of the escape wheel at the time of contact between the teeth of the second Exhaust wheel and output vane can be adjusted not to be uniform, thereby improving torque transmission efficiency, as in the case described above.

[0011] As yet another example, there is known, for example, a Swiss lever escapement which comprises an escapement mobile having first escapement teeth and second escapement teeth configured so as to be offset from each other in the direction of thickness and in which the entry vane is induced to come into contact with any of the first escape teeth and the exit vane is induced to come into contact with any any of the second escapement teeth (see Japanese Patent Publication No. 2018-48958 - patent document 4 - for example).

[0012] In this case, since the first escapement teeth and the second escapement teeth can be designed separately, the angle of rotational action of the escapement mobile at the moment of contact between the first escapement teeth and the entry vane, and the angle of rotational action of the exhaust mobile at the moment of contact between the second escape teeth and the exit vane can be adjusted so as not to be uniform, and the efficiency torque transmission can thus also be improved, as in the cases described above.

[0013] The variety of types of Swiss anchor escapement described above, each consist, however, of what is called an indirect impact type escapement, where the torque is transmitted from the escapement mobile to the sprung balance via the pallet. The torque transmission efficiency is therefore insufficient, and there is still room for improvement in terms of torque transmission efficiency.

[0014] As an escapement having a higher torque transmission efficiency than that of a Swiss lever escapement, we know, for example, the coaxial escapement comprising an escapement mobile having a two-level structure in which two escape wheels are arranged coaxially and superimposed one on the other (see the European patent application published under No. 0,018,796 - patent document 5 - for example).

[0015] A coaxial escapement comprises a first impact vane, an anchor provided with a first stop vane and a second stop vane, and a second impact vane fixed to the sprung balance. The first impact vane is configured so that it can be brought into contact with a first escape wheel in response to pivotal movement of the anchor. The second impact vane is configured so that it can be brought into contact with a second escape wheel in response to the rotation of the balance spring. The first stop vane and the second stop vane are configured to be alternately engaged with and disengaged from the second escape wheel in response to pivotal movement of the anchor.

[0016] The coaxial escapement thus configured, in which the first stop pallet and the second stop pallet alternately engage with the second escape wheel and are released from it in response to the pivoting movement of the anchor, can control the rotation of the escape mobile. In addition, since the first impact vane comes into contact (collision) with the first escape wheel in response to the pivoting movement of the anchor, the energy transmitted to the escape wheel can be transmitted indirectly to the balance wheel. -spring via the anchor, which allows a replenishment of torque from the sprung balance. Furthermore, since the second impact vane comes into contact (collision) with the tip of any tooth of the second escape wheel in response to the rotation of the balance spring, the energy transmitted to the mobile d The escapement can be directly transmitted to the sprung balance, which allows replenishment of the sprung balance with torque.

[0017] The coaxial exhaust is therefore qualified as a half-direct/half-indirect impact type exhaust, where indirect energy transmission via the anchor and direct energy transmission via no anchor are carried out alternately. to transmit the energy transmitted to the escapement mobile to the sprung balance, (that is to say an escapement using a direct impact and an indirect impact). The coaxial escapement is therefore considered to be an escapement having a higher torque transmission efficiency (exhaust efficiency) than that of the Swiss lever escapement.

However, even the half-direct/half-indirect impact type exhaust represented by the coaxial exhausts of the prior arts described above, could have even further improved torque transmission efficiency, and there are still possibilities of 'improvement.

SUMMARY OF THE INVENTION

[0019] According to the present application, the combination of a half-direct/half-indirect impact type escapement and a sprung balance, a timepiece movement, and a timepiece is provided. which excels in torque transmission efficiency (exhaust efficiency).

[0020] (1) Claim 1 defines the combination of an escapement and a sprung balance.

[0021] The escapement of the association according to claim 1 allows the energy, that is to say the rotary energy transmitted to the escapement mobile, to be directly transmitted to the sprung balance, allowing a transmission of energy (torque) to the sprung balance when the sprung balance rotates in the first direction of rotation. The escapement of the association according to claim 1 further allows the energy transmitted to the escapement mobile to be transmitted indirectly to the sprung balance via the control element, allowing the transmission of torque to the sprung balance, when the balance spring rotates in the second direction of rotation.

[0022] The direct torque transmission and the indirect torque transmission can therefore be carried out alternatively, in a switchable manner, to allow a replenishment of torque from the sprung balance, and the rotation of the escapement wheel can be controlled to take a fixed oscillation frequency corresponding to that of the sprung balance. In other words, a half-direct/half-indirect impact type escapement can be produced, thanks to which the torque transmission efficiency can be increased compared to a Swiss lever escapement according to the prior art, which is an escapement with indirect type.

[0023] In particular, the rotation of the escape wheel is controlled by the control element such that the first angle of rotational action of the escape wheel which directly transmits the energy transmitted to the sprung balance when the sprung balance rotates in the first direction of rotation and the second angle of rotational action of the escapement wheel which indirectly transmits the energy transmitted to the sprung balance when the sprung balance rotates in the second direction of rotation are not equal , but differ from each other (that is, are unequal to each other). The quantity of torque transmitted directly to the sprung balance and the quantity of torque transmitted indirectly to the sprung balance can therefore be adjusted in such a way that an optimal supply balance is achieved between these two transmission modes. As a result, the torque transmission efficiency (exhaust efficiency) can be increased.

[0024] Furthermore, since it is not necessary to arrange the escapement mobile, the sprung balance, and the control element in such a way that the first angle of rotational action and the second angle of rotational action are intentionally defined so as to be equal to each other, the escapement mobile, the sprung balance, and the control element can be freely designed, arranged and arranged with few constraints. The escapement can therefore be optimized in terms of layout, and the resulting escapement has only a small amount of operating error and excels in time measurement accuracy (i.e., exhibits deviations low walking speeds).

[0025] According to claim 1, the control element controls the rotation of the escapement wheel in such a way that the first angle of rotational action is greater than the second angle of rotational action.

[0026] When the control element controls the rotation of the escapement mobile in such a way that the first angle of rotational action is greater than the second angle of rotational action, the proportion of direct torque transmission of the mobile d The escapement of the sprung balance during alternate movement of the sprung balance can be greater than that of indirect torque transmission, and thus the torque transmission efficiency can be easily increased further.

[0027] (2) The sprung balance can be equipped with a contact pallet configured to be brought into contact with the escape teeth of the escape wheel. The control element may include an anchor that includes a first vane and a second vane configured to be engaged with and disengaged from escapement teeth, and that pivots based on rotation of the sprung balance. When the sprung balance rotates in the first direction of rotation, the engagement between any of the escapement teeth and the first pallet is released, and after another escapement tooth comes into contact with the escapement pallet. contact, another of the escape teeth can come into engagement with the second pallet, and when the sprung balance rotates in the second direction of rotation, the engagement between any escape tooth and the second pallet can be released, and after the escapement tooth slides along and moves relative to a sliding surface formed on the second vane, another of the escapement teeth can engage with the first palette.

In this case, when the sprung balance rotates in the first direction of rotation, the anchor pivots accordingly, and the engagement between any escapement tooth and the first pallet is released. The stopped escape mobile can therefore be released. Another of the escape teeth of the escape wheel having started to rotate is therefore allowed to come into contact (collision) with the contact pallet, whereby the torque can be transmitted directly from the escape wheel to the balance wheel. -spiral via the contact paddle. Since another of the escapement teeth engages with the second pallet after the direct transmission of torque, the rotation of the escapement wheel can be stopped.

Then, when the sprung balance rotates in the second direction of rotation, the anchor pivots accordingly, and the engagement between any of the escapement teeth and the second pallet is released. The escape mobile which is stopped can therefore be released. The escape tooth of the escape wheel which has started its rotation then slides along the sliding surface of the second pallet and moves relative to it. The torque can therefore be transmitted from the escapement mobile to the second pallet, and the torque can also be transmitted indirectly to the sprung balance via the pallet. After the indirect transmission of torque, that is to say, after the escape tooth separates from the second vane, another of the escape teeth comes into engagement with the first vane, whereby the rotation of the mobile exhaust can be stopped.

[0030] As described above, the contact paddle and the anchor, which includes the first paddle and the second paddle, can be used to alternately perform direct torque transmission and indirect torque transmission via reciprocating movement of the sprung balance, allowing the replenishment of the sprung balance with torque from the escapement mobile. In particular, since a simple configuration using only the anchor allows stable and accurate operation of the escapement, the exhaust can be configured to excel in torque transmission efficiency with the simplified configuration and action performance. stable guaranteed.

[0031] (3) The escape wheel may have a two-layer structure including a first escape wheel having first escape teeth forming the escape teeth, and a second escape wheel which is arranged in superimposed manner above the first escape wheel in the axial direction of the first axis, and has second escape teeth forming the escape teeth. At least the contact vane may be configured to be brought into contact with the first escapement teeth, and at least the second vane may be configured to be engaged with and released from the second escapement teeth .

[0032] In this case, the first escape wheel can be arranged such that the first escape teeth are each in contact with the contact pallet, and the second escape wheel can be arranged such that the second escape teeth are each in contact with the second pallet. Since the second pallet can thus be designed, for example, without being affected by the height position of the contact pallet, an increase in length of the second pallet in the direction of the first axis can, for example, be avoided, and the design flexibility can thus be improved. The size and weight of the second pallet can therefore, for example, be reduced, the moment of inertia of the anchor reduced accordingly. The torque transmission efficiency can therefore be further improved in indirect torque transmission to the sprung balance via the pallet.

[0033] Furthermore, the two-layer escape wheel allows, for example, a reduction in the distance along which each of the escape teeth (first escape teeth and second escape teeth) slides when of one oscillation cycle of the sprung balance, whereby the amount of wear due to sliding can be reduced.

[0034] Furthermore, the first escape wheel and the second escape wheel can be designed separately from each other. For example, it is easy to make the first escape teeth and the second escape teeth take different shapes adapted to each of them, and the first escape wheel and the second escape wheel can have different diameters, or take any other type of optimal configuration leading to additional improvement in terms of torque transmission efficiency.

[0035] (4) The sprung balance can be equipped with a first contact pallet configured so as to be able to be brought into contact with the escape teeth of the escapement wheel. The control element may include an anchor unit which is formed from a plurality of anchors and pivots based on the rotation of the sprung balance. The anchor unit may include a second contact vane configured to be brought into contact with the escapement teeth, and a first vane and a second vane configured to be engaged with and released from escapement teeth. these. When the sprung balance rotates in the first direction of rotation, the engagement between one of the escape teeth and the first pallet can be released, and after another of the escape teeth comes into contact with the first contact pallet, another of the escape teeth can come into engagement with the second pallet; when the sprung balance rotates in the second direction of rotation, the engagement between one of the escape teeth and the second pallet can be released, and after another of the escape teeth comes into contact with the second contact pallet, another of the escape teeth can come into engagement with the first pallet.

[0036] In this case, when the sprung balance rotates in the first direction of rotation, the anchor unit pivots accordingly, and the engagement between one of the escapement teeth and the first pallet is released. The escape mobile, stopped at this moment, can therefore be released. Another of the escapement teeth of the escapement wheel having started to rotate is therefore allowed to come into contact (collision) with the first contact vane, whereby the torque can be transmitted directly from the escapement wheel to the sprung balance via the first contact paddle. Since another of the escapement teeth engages with the second vane after the direct transmission of torque, the rotation of the escapement wheel can be stopped.

[0037] Then, when the sprung balance rotates in the second direction of rotation, the anchor unit pivots accordingly, and the engagement between one of the escapement teeth and the second pallet is released. The escape mobile, stopped at this moment, can therefore be released. Another escape tooth of the escape wheel having started to rotate is therefore allowed to come into contact (collision) with the second contact pallet, whereby the torque can be transmitted indirectly from the escape wheel to the balance wheel. -spiral via the second contact paddle and the anchor unit. After the indirect transmission of torque, another of the escapement teeth comes into engagement with the first pallet, which makes it possible to stop the rotation of the escapement mobile.

[0038] As described above, the first contact vane, the second contact vane, and the anchor unit, which includes the first vane and the second vane, can be used to alternately perform direct torque transmission and the indirect transmission of torque during an alternating movement of the sprung balance, which thus makes it possible to carry out a transmission of the energy transmitted to the escapement mobile to replenish the sprung balance in terms of torque. Particularly, since a simple configuration using only the anchor unit allows stable and exact operation of the exhaust, the exhaust can be configured to excel in torque transmission efficiency with a simplified configuration and guaranteed performance in terms of operation.

[0039] (5) The control element can control the rotation of the escapement wheel in such a way that the ratio between the first angle of rotational action and a predetermined angle of rotational action corresponding to the sum of the first angle d The rotational action and the second angle of rotational action by which the escapement mobile rotates during an alternating movement of the sprung balance is greater than 50%, but smaller than 75%.

[0040] In this case, since the ratio between the first angle of rotational action and the predetermined angle of rotational action is greater than 50%, the proportion of direct transmission of torque from the escapement wheel to the balance wheel- spiral can be larger than indirect torque transmission, and the torque transmission efficiency can thus be increased.

[0041] In addition to the above, adjusting the ratio between the first rotational action angle and the predetermined rotational action angle so that it is smaller than 75% makes it possible to avoid a situation in which the angle of rotational action via which the escape wheel rotates when the sprung balance rotates in the second direction of rotation (second angle of rotational action) is, for example, an excessively small angle of action. An angle of action which allows, for example, the anchor to act correctly can therefore be guaranteed, and the escapement can thus be reliable enough to operate stably. The anchor can therefore operate correctly, with excellent torque transmission efficiency maintained over time, and thus the escapement can be reliable enough to exhibit stable performance in terms of operation.

[0042] (6) The control element can control the rotation of the escapement wheel in such a way that the ratio between the first rotational action angle and the predetermined rotational action angle is greater than 50% but smaller than 56%.

[0043] In this case, since the ratio between the first rotational action angle and the predetermined rotational action angle is greater than 50% but smaller than 56%, too great an angular difference between the first angle d The rotational action and the second angle of rotational action can be further avoided thanks to the fact that the proportion of direct transmission of torque from the escapement wheel to the sprung balance is greater than the indirect transmission of torque. Undesirable change of angle for needle movement can therefore be avoided, and the angle of needle movement can thus be approximately uniform.

[0044] (7) The number of escape teeth of the escape wheel can be at least equal to two.

[0045] In this case, the escapement mobile can be configured to have at least two escapement teeth, whereby the angle between the adjacent escapement teeth relative to each other in the circumferential direction can be big. The escape wheel thus configured allows an increase in each of the first rotational action angles, according to which the escape wheel rotates as part of the direct transmission of torque to the sprung balance, and the second rotational action angle , according to which the escapement mobile rotates as part of the indirect torque transmission to the sprung balance. The torque transmission efficiency can therefore be further improved.

[0046] A reduction in the number of escapement teeth allows an increase in each of the first and second rotational action angles, whereby the torque transmission efficiency can be increased.

[0047] (8) The escape teeth of the escape wheel can be eight in number.

[0048] In this case, since the number of escapement teeth is eight, a situation in which the first and second rotational angles of action each take, for example, an excessively large value can be avoided. Therefore, the anchor can be designed to, for example, be compact, and the anchor does not need to pivot to a large extent. The exhaust can therefore be reliable enough to act even more stably.

[0049] (9) According to claim 9, a timepiece movement comprises the combination of the escapement and the sprung balance according to claim 1, a regulator comprising the sprung balance, and a gear train which transmits energy to the exhaust mobile.

[0050] (10) According to claim 10, a timepiece comprises the timepiece movement described above, and a display hand which rotates at a rotational speed adjusted by the escapement and the regulator .

[0051] In this case, the timepiece movement and the timepiece, each of which includes the escapement defined in claim 1, which not only excels in terms of torque transmission efficiency but has only a small amount of operation error and excels in time measurement accuracy, can similarly exhibit high performance with excellent time measurement accuracy. In particular, since the escapement excels in torque transmission efficiency, the oscillation angle of the sprung balance is, for example, easily maintained at a high value, whereby the timepiece movement and the part watchmaking are unlikely to be affected, for example, by external disturbances.

[0052] According to the invention described in the present patent application, it is thus possible to provide an escapement, a timepiece movement, and a timepiece which each excel in torque transmission efficiency (escapement efficiency ).

BRIEF DESCRIPTION OF THE DRAWINGS

[0053] Figure 1 is an external view of a timepiece illustrating a first embodiment of the invention. Figure 2 is a plan view of a movement shown in Figure 1. Figure 3 is a perspective view of an exhaust shown in Figure 2 and seen from the front. Figure 4 is a perspective view of the exhaust shown in Figure 3 and seen from the rear. Figure 5 is a perspective view of a double plate shown in Figure 4. Figure 6 is a plan view of the escapement shown in Figure 3. Figure 7 is a plan view of a wheel d The exhaust shown in Figure 6. Figure 8 describes the operation of the escapement and shows the transition from the state shown in Figure 6 to a state in which an input vane begins to move away from one tooth exhaust. Figure 9 describes the operation of the escapement and shows the transition from the state shown in Figure 8 to a state in which another escapement tooth comes into contact with a contact paddle. Figure 10 describes the operation of the escapement and shows the transition from the state shown in Figure 9 to a state in which another escapement tooth engages an output vane. Figure 11 describes the operation of the escapement and shows the transition from the state shown in Figure 10 to a state in which the impulse pin begins rotation in the reverse direction. Figure 12 describes the operation of the escapement and shows the transition from the state shown in Figure 11 to a state in which the engagement between the escapement tooth and the output vane is released. Figure 13 describes the operation of the escapement and shows the transition from the state shown in Figure 12 to a state in which the escapement tooth slides along a sliding surface of the output vane. Figure 14 describes the operation of the escapement and shows the transition from the state shown in Figure 13 to a state in which another escapement tooth engages the input vane. Figure 15 represents the relationship between the predetermined rotational action angle according to which an escapement wheel rotates during reciprocating movement of a sprung balance, and a first rotational action angle of the escapement wheel which directly transmits torque to the sprung balance. Figure 16 represents the relationship between the predetermined rotational action angle, according to which the escapement wheel rotates during reciprocating movement of the sprung balance, and a second rotational action angle of the escapement wheel which transmits indirectly the torque to the sprung balance. Figure 17 is a perspective view of an exhaust representing a second embodiment according to the invention and seen from the front. Figure 18 is a perspective view of the exhaust shown in Figure 17 and seen from the rear. Figure 19 is a plan view of a first escape wheel shown in Figure 17. Figure 20 is a plan view of the escapement shown in Figure 17. Figure 21 is a plan view of a second escape wheel shown in Figure 17. Figure 22 describes the operation of the escapement and shows the transition from the state shown in Figure 20 to a state in which a first escape tooth comes into contact with the contact palette. Figure 23 describes the operation of the escapement and shows the transition from the state shown in Figure 22 to a state in which a second escapement tooth comes into contact with the outlet vane. Figure 24 describes the operation of the escapement and shows the transition from the state shown in Figure 23 to a state in which the impulse pin begins to rotate in the opposite direction. Figure 25 describes the operation of the escapement and shows the transition from the state shown in Figure 24 to a state in which the second escapement tooth slides along the sliding surface of the output vane. Figure 26 describes the operation of the escapement and shows the transition from the state shown in Figure 25 to a state in which another first escapement tooth engages the input vane. Figure 27 represents the relationship between the predetermined rotational action angle, according to which the escapement wheel rotates during reciprocating movement of the sprung balance, and the first rotational action angle of the escapement wheel which transmits directly couple the sprung balance. Figure 28 represents the relationship between the predetermined rotational action angle, according to which the escapement wheel rotates during reciprocating movement of the sprung balance, and the second rotational action angle of the escapement wheel which transmits indirectly the torque to the sprung balance. Figure 29 is a perspective view of an exhaust representing a third embodiment according to the invention, seen from the front. Figure 30 is a perspective view of the exhaust shown in Figure 29 and seen from the rear. Figure 31 is a plan view of the exhaust shown in Figure 29. Figure 32 describes the operation of the exhaust and shows the transition from the state shown in Figure 31 to a state in which a first vane d The stop begins to move away from an exhaust tooth. Figure 33 describes the operation of the escapement and shows the transition from the state shown in Figure 32 to a state in which another escapement tooth comes into contact with a first contact paddle. Figure 34 describes the operation of the escapement and shows the transition from the state shown in Figure 33 to a state in which another escapement tooth comes into contact with a second stop pallet. Figure 35 describes the operation of the escapement and shows the transition from the state shown in Figure 34 to a state in which the impulse pin begins to rotate in the opposite direction. Figure 36 describes the operation of the escapement and shows the transition from the state shown in Figure 35 to a state in which the engagement between the escapement tooth and the second stopping pallet is released. Figure 37 describes the operation of the escapement and shows the transition from the state shown in Figure 36 to a state in which another escapement tooth comes into contact with a second contact vane. Figure 38 describes the operation of the escapement and shows the transition from the state shown in Figure 37 to a state in which another escapement tooth comes into contact with the first stop pallet. Figure 39 represents the relationship between the predetermined rotational action angle, according to which the escapement wheel rotates during reciprocating movement of the sprung balance, and the first rotational action angle of the escapement wheel which transmits directly couple the sprung balance. Figure 40 represents the relationship between the predetermined rotational action angle, by which the escapement wheel rotates during reciprocating movement of the sprung balance, and the second rotational action angle of the escapement wheel which transmits indirectly the torque to the sprung balance. Figure 41 shows the relationship between the number of escapement teeth and the amount of torque transmitted. Figure 42 shows the relationship between the ratio of a first rotational action angle to a predetermined rotational action angle and the amount of torque transmitted.

DESCRIPTION OF THE EMBODIMENTS

(First embodiment)

[0054] A first embodiment according to the invention will be described below with reference to the drawings. The present embodiment will be described with reference to a case where a mechanical timepiece is presented as an example of a timepiece.

(Basic configuration of the timepiece)

[0055] In general, the mechanical part including a driving part of a timepiece is referred to as the "movement." The movement to which a dial and hands are attached is placed in a part housing timepiece to form a complete product, which is referred to as a “complete unit” of the timepiece. A platen which forms a substrate of the timepiece has two sides, and the glass side of the timepiece case (i.e., the dial side) is referred to as the „ rear side“ of the movement. Of these two sides of the plate, we refer to the back side of the timepiece case (i.e., the side opposite the dial) as the “front side” of the movement.

To describe the present embodiment, the following definitions will be used: the direction extending from the dial towards the caseback constitutes an ascending direction; and the opposite direction constitutes a downward direction.

[0057] A complete unit of a timepiece 1 according to the present embodiment comprises the following components in a timepiece case formed of a case base - which is not shown - and a plate of glass 2: a movement (timepiece movement according to the invention) 10; a dial 3 having marks indicating at least information relating to the time; and display hands 4 including an hour hand 5, a minute hand 6, and a second hand 7, as illustrated in Figure 1.

The movement 10 comprises a plate 11, which forms a substrate, as illustrated in Figure 2. Figure 2 is a plan view of the movement 10 seen from the front. Furthermore, in Figure 2, part of the components which form the movement 10 is deliberately omitted to facilitate the illustration.

The following components are provided at the front of the plate 11: a front cog (gear train according to the invention) 12; an exhaust 13, which controls the rotation of the front cog 12; and a regulator 14, which adjusts the speed of the exhaust 13.

The front gear 12 essentially comprises a movement barrel 20, a center mobile 21, a third mobile 22, and a second mobile 23. The movement barrel 20 is supported by a shaft in the space between the plate 11 and a barrel bridge which is not shown and contains a mainspring (power source) which is not shown. The mainspring is wound when a ratchet wheel 24 turns. The ratchet wheel 24 rotates via a winding gear - which is not shown - when a winding stem - which is also not shown and connected to a crown 25 shown in Figure 1 - is rotated.

The center wheel 21, the third wheel 22, and the second wheel 23 are each supported by a shaft in the space between the plate 11 and a gear train bridge which is not shown. When an elastic return force produced by the mainspring wound on itself when it is wound acts on the movement barrel 20, and consequently the movement barrel 20 rotates, the center mobile 21, the third mobile 22, and the second mobile 23 rotate sequentially based on the rotation of the movement barrel 20.

In other words, the center mobile 21 is engaged with the movement barrel 20 and rotates on the basis of the rotation of the movement barrel 20. When the center mobile 21 rotates, a roadway - which is not shown - rotates based on the rotation of the center mobile 21. The minute hand 6 shown in Figure 1 is fixed to the roadway, and the rotation of the roadway allows the minute hand 6 to display the current minutes. The minute hand 6 rotates at a rotation speed adjusted by the escapement 13 and the regulator 14, that is to say, makes a complete rotation in one hour.

[0063] When the center wheel 21 rotates, a minute wheel - which is not shown - turns on the basis of the rotation of the center wheel 21, and an hour wheel - which is not shown - turns then based on the rotation of the minute wheel. The minute wheel and the hour wheel are components of the timepiece which form the front gear 12. The hour hand 5 shown in Figure 1 is attached to the hour wheel, and the rotation of the wheel hour allows the hour hand 5 to display the current time. The hour hand 5 rotates at a rotation speed adjusted by the escapement 13 and the regulator 14, and completes, for example, one complete rotation in 12 hours.

The third mobile 22 is engaged with the center mobile 21 and rotates on the basis of the rotation of the central mobile 21. The second mobile 23 is engaged with the third mobile 22 and rotates on the basis of the rotation of the third mobile 22. The seconds hand 7 shown in Figure 1 is fixed to the second mobile 23, and the seconds hand 7 is supposed to display the current seconds on the basis of the rotation of the second mobile 23. The hand seconds 7 rotates at a rotation speed adjusted by the escapement 13 and the regulator 14 and performs, for example, one rotation in one minute.

An escapement wheel 60, which will be described later, is engaged with the second wheel 23 via an escapement pinion 61. The energy (rotational energy) of the mainspring housed in the barrel of the movement 20 is therefore transmitted to the exhaust mobile 60 mainly via the center mobile 21, the third mobile 22, and the second mobile 23. The exhaust mobile 60 therefore rotates around a first axis O1.

The regulator 14 mainly includes a sprung balance 30.

The sprung balance 30 comprises a balance shaft 31, a balance wheel 32, and a spiral spring which is not shown, and the sprung balance 3 is supported by a shaft in the space between the plate 11 and a balance bridge which is not shown, as illustrated in Figures 3 and 4. The sprung balance 30, which operates under the action of an energy source which is constituted by the balance spring, performs a alternating rotation (rotation towards the front and in the opposite direction) around a second axis O2 at a regular amplitude (angle of oscillation) according to the torque delivered at the output of the barrel of movement 20.

[0068] Specifically, the sprung balance 30 rotates alternately in a first direction of rotation M1 and a second direction of rotation M2, which are opposite, around the second axis O2, as shown in Figure 3. In the present embodiment, according to a plan view seen from the side facing the front side of the movement 10, the direction in which the sprung balance 30 rotates counterclockwise around the second axis O2 is called the first direction of rotation M1, and the direction in which the sprung balance 30 turns clockwise is called the second direction of rotation M2.

[0069] An upper pivot 31a and a lower pivot 31b, which are each conical, are formed at the axially opposite ends of the balance shaft 31, as shown in Figures 3 and 4. The balance shaft 31 is supported by the shaft in the space between the plate 11 and the balance bridge via the upper pivot 31a and the lower pivot 31b. The balance wheel 32 is externally adjusted and integrally fixed to the balance shaft 31, and the internal end of the balance spring is fixed to the balance shaft 31 via a ferrule which is not shown.

[0070] In the example shown in Figures 3 and 4, the balance wheel 32 is formed of four arms 33 extending radially outwards from the second axis O2, and which are arranged at intervals of 90 degrees ; nevertheless the number, arrangement, and shape of the arms 33 are not limited to the configuration described above, and can be changed freely.

[0071] A double annular plate 35, which is not only a component of the sprung balance 30 but also a component of the escapement 13, is adjusted externally and fixed to the balance shaft 31, and arranged coaxially with the second axis O2.

The double plate 35 is composed, for example, of a metallic material or of a material having a crystalline orientation, such as silicon single crystal. Examples of manufacturing processes for the double platen 35 may include electroforming, a LIGA process, which adopts an optical approach, such as photolithography technology, DRIE, and metal powder injection molding (MIM). The manufacturing method is not limited to any of the methods described above, and the double plate 35 can be formed using any other method.

[0073] The double plate 35 includes a large collar 36, which is arranged at the height corresponding to the exhaust mobile 60, and a small collar 37, which is integrated with the large collar 36 and arranged below the large collar 36 (on the side facing the plate 11), as illustrated in Figures 3 to 6.

[0074] The large collar 36 has a through hole 38, which passes through the large collar 36 in the ascending/descending direction, and a slot 39, which has a U shape so as to extend in the radial direction and open outwards in the radial direction.

[0075] The through hole 38 has a flat surface facing outwards in the radial direction, and has a semi-circular shape having an inner surface in the form of a convex arc in the radial direction, when viewed along the axial direction of the second axis O2. An impulse peg 40, which is formed on an artificial gemstone made of, for example, ruby, is driven into the through hole 38 to be fixed there. A contact paddle 50, which will be described later, is fixed in slot 39.

[0076] The impulse pin 40, corresponding to the shape of the through hole 38, has a flat surface facing outwards in the radial direction and has a semi-circular shape having an arcuate surface 42 convex inside in the radial direction according to the view in the plan. The impulse pin 40 is formed so as to extend outwards beyond the large collar 36. The impulse pin 40 thus configured is arranged to be brought into contact with an anchor 71, which will be described further far and is arranged below the exhaust mobile 60.

[0077] The impulse pin 40 performs an alternating rotation around the second axis O2, in association with the sprung balance 30 and engages with a fork 81, which will be described later, so that it can then be released in the course of the alternating rotation.

[0078] The small collar 37 is formed so as to be radially smaller than the large collar 36. A crescent-shaped portion 43, which is recessed inwardly in the radial direction to form a curved surface, is arranged in a part of the small collar 37 which is the portion facing radially and corresponding to the impulse pin 40. The part in the shape of a crescent moon 43 functions as a clearance which prevents a dart 82, which will be described later, to come into contact with the small collar 37 when the fork 81, which will be described later, engages with the impulse pin 40. A portion of the external circumferential surface of the small collar 37, which is the portion excluding the crescent moon-shaped portion 43 is configured such that the stinger 82 can be brought into contact and adjustable along the portion.

(Exhaust setup)

[0079] The escapement 13 includes the double plate 35 described above, the contact pallet 50 provided on the sprung balance 30, the escapement mobile 60, which rotates using the energy transmitted from the mainspring via the front gear 12, and a control element 70, which rotates and stops the escapement mobile 60 on the basis of the rotation of the sprung balance 30, as shown in Figures 3 and 4.

[0080] In the description which follows, we simply refer to the energy transmitted to the exhaust wheel 60 as corresponding to the torque in certain cases.

(Contact palette)

[0081] The contact pallet 50 is a pallet configured to be brought into contact with escapement teeth 63 of the escapement wheel 60 and to transmit the torque transmitted to the escapement wheel 60 to the sprung balance 30. The teeth exhaust 63 will be described later. The contact pallet 50 is fixed to the large collar 36 of the double plate 35.

[0082] Specifically, the contact paddle 50 is inserted from the outside in the radial direction into the slot 39 formed in the large collar 36 and is fixed there, for example, with an adhesive. The contact paddle 50 is formed from an artificial gemstone consisting of, for example, ruby, as is the impulse peg 40. The contact paddle 50 has a rectangular plate shape extending in the radial direction of the large collar 36 and has a front end which projects outwardly in the radial direction beyond the outer circumferential edge of the large collar 36.

[0083] The side surface of the front end of the contact pallet 50, which is the side surface located furthest downstream in the second direction of rotation M2, is a flat surface extending in the radial direction and forms a contact surface 51, with which a working surface 63a of each of the escapement teeth 63 is brought into contact, as shown in Figure 6. The front end of the contact vane 50 further has an inclined surface 52 making facing the positive side in the first direction of rotation M1.

The contact pallet 50 is fixed in the slot 39 so as not to project outwards beyond the large collar 36. The contact pallet 50 thus fixed does not come into contact with the anchor 71 , which will be described later.

The contact pallet 50 fixed to the sprung balance 30 as described above repeats an incursion into the rotational trajectory R of the escape wheel 64, which will be described later, and a retraction out of it d 'one when the sprung balance 30 turns. The working surface 63a of each of the escapement teeth 63 of the escapement wheel 64 is therefore allowed to come into contact (collision) with the contact surface 51 of the contact vane 50. The contact of the surface working 63a of one of the escapement teeth 63 with the contact surface 51 of the contact pallet 50 allows transmission of energy from the escapement mobile 60 to the contact pallet 50.

(Mobile exhaust)

[0086] The exhaust wheel 60 comprises an exhaust shaft 62, around which the exhaust pinion 61, which engages with the second wheel 23, is formed, and the escape wheel 64, which is integrally fixed to the exhaust shaft 62, for example, under the action of a driving force and has a plurality of exhaust teeth 63, as shown in Figures 3, 4, and 6.

[0087] The present embodiment is described with reference to a case where the number of exhaust teeth 63 is 8, and the number of teeth of the exhaust pinion 61 is 10, but these numbers of teeth d The exhaust 63 and the teeth of the exhaust pinion 61 should not be considered essential, and can be changed if necessary depending on the needs.

[0088] The present embodiment will further be described with reference to a case where the escapement mobile 60 rotates clockwise around the first axis O1 according to a plan view of the movement 10 taken from the front, as shown in Figure 6 when the torque transmitted from the second mobile 23 via the exhaust pinion 61 acts on the exhaust mobile 60.

[0089] For the escapement wheel, the direction of rotation clockwise around the first axis O1 is called the clockwise direction M3, and the direction opposite the clockwise direction An M3 mount is called a counterclockwise M4. In addition, the rotation envelope R, which is drawn by the tip of each escapement tooth 63 when the escapement wheel 60 rotates, is simply called the rotational trajectory R of the escapement wheel 64.

[0090] An upper pivot 62a and a lower pivot 62b, which are each conical, are formed at the axially opposite ends of the exhaust shaft 62, as shown in Figures 3 and 4. The exhaust mobile 60 is supported by the shaft in the space between the plate 11 and the gear bridge - which is not shown - via the upper pivot 62a and the lower pivot 62b.

[0091] The escape wheel 64 is made up, for example, of a metallic material or of a material having a crystalline orientation, such as silicon single crystal, like the double plate 35, as shown in Figures 6 and 7. Examples of manufacturing processes for the escape wheel 64 may include electroforming, a LIGA process, which adopts an optical approach, such as photolithography technology, DRIE, and metal powder injection molding ( MIM). The manufacturing method is not limited to any of the methods described above, and the escape wheel 64 may be formed using any other manufacturing method.

[0092] The escape wheel 64 includes an annular hub 65, which has an insertion hole 65a formed in a central portion of the hub 65 and is combined with the exhaust shaft 62 via the insertion hole 65a, for example, via a drive, as well as four first spokes 66, which extend outwards from the hub 65 in the radial direction and are arranged at regular intervals in the circumferential direction, and four second spokes 67, which extend outward from the hub 65 in the radial direction and are arranged at regular intervals in the circumferential direction. The hub 65, the first spokes 66, and the second spokes 67 are integrated with each other in the escape wheel 64.

The first spokes 66 and the second spokes 67 are formed to be arranged alternately in the circumferential direction and to have the same radial length. The first spokes 66 and the second spokes 67 have a conical shape tapering outward in the radial direction, and a front end of each of the first spokes 66 and the second spokes 67 has a slightly curved shape in the direction of clockwise direction. an M3 watch. The curved front ends act as escapement teeth 63.

[0094] The escapement mobile 60 according to the present embodiment therefore has eight escapement teeth 63. A lateral surface of each of the escapement teeth 63, that is to say the lateral surface oriented positively in clockwise direction M3, forms the working surface 63a, which is brought into contact with the contact pallet 50 and engages with an input pallet (first pallet according to the invention) 72 and a pallet outlet (second pallet according to the invention) 73, which will be described later.

[0095] The base (root) of each of the first rays 66 has a circumferential shape wider than the base of each of the second rays 67. The base of each of the first rays is perforated 66 by a first aperture hole 68 having a elliptical shape elongated in the radial direction in plan view. The base end of each of the second spokes 67 is perforated by a second perforation hole 69 having a triangular shape in the plan view.

[0096] The weight of the exhaust mobile 60 is reduced mainly by the first opening holes 68 and the second opening holes 69, but this is not essential; other perforation holes could also be provided, as well as thinner portions and any other types of portions, to the extent that the additional perforations or the finer portions do not affect the performance, the rigidity , or other factors of the exhaust mobile 60.

[0097] The escapement mobile 60 configured as described above is responsible for the direct transmission of the torque which was transmitted to it to the sprung balance 30 when the sprung balance 30 rotates in the first direction of rotation M1 and a indirect transmission of the torque transmitted to the sprung balance 30 via the control element 70 when the sprung balance 30 rotates in the second direction of rotation M2.

(Control element)

[0098] The control element 70 comprises the anchor 71, which pivots around a third axis O3 on the basis of the rotation of the sprung balance 30, as shown in Figures 3, 4 and 6, and which controls the rotation of the exhaust mobile 60, that is to say, controls the starting and stopping of the rotation of the exhaust mobile 60.

The anchor 71 comprises the inlet pallet 72 and the outlet pallet 73 configured to be alternately engaged with the escapement teeth 63. The anchor 71 further comprises a shaft 75, which constitutes an axis of rotation for the pivoting movement, and the body of the anchor 78, which includes two anchor arms 76 and 77.

[0100] The shaft 75 is arranged coaxially with respect to the third axis O3. An upper pivot 75a and a lower pivot 75b, which are each conical, are formed at the axially opposite ends of the shaft 75. The shaft 75 is supported in the space between the plate 11 and an anchor bridge which does not is not represented via the upper pivot 75a and the lower pivot 75b.

[0101] A flange 75c, which is larger than the shaft 75 in terms of diameter, is formed integrally with a central portion in the axial direction of the shaft 75. The anchor body 78 is integrally fixed to the shaft 75, for example, via a drive, with the anchor body 78 placed on the collar 75c.

[0102] The anchor body 78 has a plate shape, for example, using electroforming or MEMS technology and is arranged below the exhaust mobile 60 and the large collar 36 of the double plate 35. The body anchor 78 can be provided, depending on the case, with an opening, a thinner portion, or any other portion allowing a reduction in weight, as in the case of the escapement mobile 60. In the example shown in Figures 3, 4 and 6, a plurality of openings are formed in the anchor body 78.

[0103] A connecting segment 79 of the anchor body 78, which is the portion where the two anchor arms 67 and 77 are connected to each other, has an insertion hole for fixing the shaft 75. Insertion of the shaft 75 into the insertion hole, for example, via a drive, allows the anchor body 78 to be integrally attached to the shaft 75 with the anchor body 78 placed on the 75c collar.

[0104] One of the anchor arms or the anchor arm 76 is arranged so as to extend from the connecting segment 79, to which the shaft 75 is fixed, in a counterclockwise direction M4 , which is opposite to the direction in which the escapement mobile 60 rotates, that is to say, towards the sprung balance 30. The other anchor arm or the anchor arm 77 is arranged to extend from the connecting segment 79, to which the shaft 75 is fixed, in the clockwise direction M3, which is the direction in which the exhaust mobile 60 rotates.

[0105] The front end of the anchor arm 76 is provided with a pair of horns 80 arranged side by side in the circumferential direction around the third axis O3. The interior of the horns 80 opens towards the balance shaft 31 and forms the fork 81, which can receive the impulse pin 40, which moves when the sprung balance 30 performs its alternating rotation, engaging inside it to then escape from it.

[0106] Furthermore, the dart 82 is fixed to the front end of the anchor arm 76.

[0107] The dart 82 is thus inserted from below into the front end of the anchor arm 76, for example, via a chase to be integrally fixed to the anchor arm 76, but this is not imperative. For example, stinger 82 may instead be attached to the forward end of anchor arm 76, for example, using adhesive or caulking.

[0108] The stinger 82 is located between the pair of horns 80 (that is to say, in the fork 81) in the plan view and thus extends to project slightly beyond the horns 80 towards the balance shaft 31. The dart 82 is located below the impulse pin 40 and fixed to be at the same height level as the small collar 37.

[0109] In the state where the impulse pin 40 has moved out of the fork 81, the front end of the stinger 82 faces, in the radial direction, and via a slight spacing, a portion of the external circumferential surface of the small collar 37 which is the portion excluding the part in the shape of a crescent moon 43, while in the state in which the impulse pin 40 engages with the fork 81, the front end of the dart 82 is housed in the crescent moon-shaped part 43.

[0110] When the impulse pin 40 has moved out of the fork 81, the front end of the dart 82 faces the external circumferential surface of the small collar 37, with a slight spacing between them, and the end front of the dart 82 is thus authorized to come first into contact with the external circumferential surface of the small collar 37 even, for example, in the case where a disturbance occurs during the free oscillation of the sprung balance 30 and where the anchor 71 arrested at that time would be released due to the disruption. It is therefore possible to prevent any movement of the anchor 71 due to a disturbance, and thus an untimely release of the stopped anchor 71 can be avoided. The anchor 71 will be described later in detail in its stopped state.

[0111] Furthermore, a stone fixing orifice 83 for fixing the input pallet 72 is formed in the anchor arm 76, specifically, in a position offset relative to the stinger 82 towards the shaft 75 The stone fixing hole 83 is thus formed so as to pass through the anchor arm 76 in the front/rear direction relative to the plate. The input pallet 72 is a pallet which is configured to be engaged with and released from the working surface 63a of each of the escape teeth 63 of the escape wheel 64 to stop the mobile exhaust 60, and release the exhaust mobile 60 when it is stopped.

[0112] The entry pallet 72 is formed of an artificial precious stone consisting, for example, of ruby, such as the impulse pin 40 is, and fixed in the fixing hole of the stone 83, for example, via a chase, or glued and fixed inside, for example, using an adhesive. The inlet pallet 72 has a rectangular column shape extending upwards beyond the anchor arm 76, and is fixed to be aligned in height with the exhaust mobile 60.

[0113] A side surface of the inlet pallet 72 which is the side surface facing the ends of the spokes of the exhaust wheel 60 in the counterclockwise direction M4, which is opposite to the direction in which the exhaust mobile 60 rotates, forms the engagement surface 72a, with which the working surface 63a of each of the escape teeth 63 of the escape wheel 64 comes into engagement.

[0114] A slot 85 for fixing the outlet pallet 73 is formed at a front end of the other anchor arm 77. The slot 85 is formed so as to pass through the anchor arm 77 of top to bottom and opens towards the exhaust mobile 60. The exit pallet 73 is not only a pallet which is configured to engage with the working surface 63a of each of the escape teeth 63 of the escape wheel 64 and free itself from it, and which stops the escape mobile 60, then releases the escape mobile 60 when it is stopped, but constitutes a pallet which transmits the energy supplied to the mobile d escapement 60 to sprung balance 30 via anchor 71.

[0115] The output pallet 73 is formed of an artificial precious stone consisting, for example, of ruby, like the impulse pin 40, and is fixed in the slot 85, for example, via a chase, or glued and fixed inside, for example, using adhesive. The outlet pallet 73 has the shape of a rectangular plate extending along the slot 85, and is fixed so as to project beyond the anchor arm 77 towards the exhaust mobile 60. Furthermore, the outlet pallet 73 is formed so as to extend upwards beyond the anchor arm 77, and fixed so as to be aligned in height with the escapement mobile 60.

[0116] The front end of the outlet pallet 73 has an engagement surface 73a and a sliding surface 73b formed so as to face the spokes of the exhaust wheel 60 in a counterclockwise direction. M4, which is opposite the direction in which the escapement mobile 60 rotates.

[0117] The engagement surface 73a is a flat surface extending along the slot 85, and the working surface 63a of each of the escapement teeth 63 of the escapement wheel 64 is configured to engage with the engagement surface 73a.

[0118] The sliding surface 73b is an inclined surface offset relative to the engagement surface 73a in the direction of the exhaust wheel 60, and arranged so as to extend in the direction of clockwise M3, which is the direction in which the escapement mobile 60 rotates, that is to say, arranged so as to approach the escapement mobile 60 as one moves away from the slot and following the clockwise direction M3, and the escapement teeth 63 are configured to slide along the sliding surface 73b.

[0119] Specifically, the escapement teeth 63 of the escapement wheel 60 are each configured to slide along the sliding surface 73b after engagement with the escapement tooth 63 when the engagement surface 73a is released. The sliding movement of the working surface 63a of each of the escapement teeth 63 along the sliding surface 73b transmits the torque of the escapement mobile 60 towards the output pallet 73.

[0120] The anchor 71 configured as described above pivots around the third axis O3 on the basis of the rotation of the sprung balance 30, as described above.

[0121] Specifically, the impulse pin 40, which moves when the sprung balance 30 performs its alternating rotation, causes the anchor 71 to pivot around the third axis O3 in the direction opposite to that in which the sprung balance 30 turns. During this process, the entry vane 72 and the exit vane 73 alternately repeat an incursion into the rotational trajectory R of the escape wheel 64 and a retraction outside of it in response to the pivoting movement of the anchor 71. The working surface 63a of each of the escape teeth 63 of the escape wheel 64 is therefore authorized to come into engagement with the engagement surface 72a of the entry pallet 72, with the surface d engagement 73a of the output pallet 73.

[0122] In particular, since the inlet pallet 72 and the outlet pallet 73 are arranged so as to sandwich the third axis O3, when one of the escape teeth 63 comes into engagement with the pallet inlet 72, the outlet pallet 73 disengages from another exhaust tooth 63, while when one of the escape teeth 63 comes into engagement with the outlet pallet 73, the inlet pallet 72 disengages from another escape tooth 63.

[0123] More specifically, when the sprung balance 30 rotates in the first direction of rotation M1, and after the engagement between one of the escapement teeth 63 and the input pallet 72 is released, and another escape tooth 63 comes into contact with the contact pallet 50, another escape tooth 63 comes into engagement with the output pallet 73. When the sprung balance 30 turns in the second direction of rotation M2, and after the engagement between one of the escapement teeth 63 and the outlet pallet 73 is released, and the escapement tooth 63 slides along the sliding surface 73b of the outlet pallet 73 and moves relative to this, another escape tooth 63 engages with the input pallet 72. This point will be described in detail later.

[0124] The escapement 13 further comprises a first limitation pin 90 and a second limitation pin 91, which position the anchor 71 when the entry pallet 72 and the exit pallet 73 come into engagement with the escape wheel 64 of the escape wheel 60.

[0125] The first limitation pin 90 is arranged on the side opposite the escapement mobile 60 with respect to the anchor arm 76. The second limitation pin 91 is arranged on the side opposite the escapement mobile 60 with respect to the other anchor arm 77. The first limiting pin 90 and the second limiting pin 91 are, for example, fixed so as to project upwards relative to the plate 11 and each reaches a height position aligned with the level of the anchor body 78.

[0126] Since the first limiting pin 90 and the second limiting pin 91 are arranged as described above, an outer side surface 76a of the anchor arm 76, which is the outer side surface located on the side opposite the surface external side facing the exhaust mobile 60, can be brought into contact with the first limiting pin 90. The first limiting pin 90 can prevent a pivoting movement of the anchor 71, but positions the anchor 71. similarly, an external side surface 77a of the other anchor arm 77, which is the external side surface located on the opposite side of the external side surface facing the exhaust mobile 60, can be brought into contact with the second limiting pin 91. The second limiting pin 91 can thus prevent a pivoting movement of the anchor 71, but positions the anchor 71.

[0127] The entry pallet 72 described above is fixed to the anchor arm 76 in such a way that the engagement surface 72a having a predetermined angle of incidence of pulling comes into engagement with the working surface 63a of each of the escape teeth 63.

[0128] Furthermore, taking into consideration the following definition: the first straight line L1 is an imaginary line which connects the third axis O3 of the shaft 75 towards the tip of one of the escapement teeth 63; and the second straight line L2 is an imaginary line perpendicular to the first straight line L1, the input pallet 72 is fixed to the anchor arm 76 in such a way that engagement with the surface 72a of the input pallet 72 is carried out according to an inclination relative to the second straight line L2 corresponding to a predetermined angle α oriented in the direction of clockwise M3, which is the direction in which the escapement mobile 60 rotates, when the surface of engagement 72a of the input pallet 72 engages with the working surface 63a of the exhaust tooth 63, as shown in Figure 6. The predetermined angle a varies, for example, from approximately 11° to 16 °.

[0129] Since the engagement with the surface 72a of the input pallet 72 is carried out at an inclination corresponding to the predetermined angle a with respect to the second straight line L2, as described above, the rotational torque produced by the exhaust mobile 60 causes a torque to act on the input pallet 72, when one of the escape teeth 63 engages with the input pallet 72, in such a way that the entry pallet 72 is pulled towards the escapement mobile 60. The engagement between each of the escapement teeth 63 and the entry pallet 72 can therefore be stabilized, and thanks to this, any shift or Any other change in the position where the inlet vane 72 engages the escape tooth 63 due to, for example, a disturbance, can be avoided. Adjusting the angle of incidence of pulling can therefore avoid a situation in which the pivoting movement of the anchor 71 causes, due to a disturbance, for example the small collar 37 and the dart 82 to be brought in mutual contact, causing abnormal operation which prevents the free oscillation of the sprung balance 30.

[0130] The output pallet 73 is also fixed to the anchor arm 77 in such a way that the engagement surface 73a having a predetermined angle of incidence of pulling comes into engagement with the working surface 63a of each of the teeth d exhaust 63, as is the inlet pallet 72.

[0131] Furthermore, the output pallet 73 is fixed to the anchor arm 77 in such a way that the engagement surface 73a of the output pallet 73 is inclined relative to the second straight line L2 at a predetermined angle α in the clockwise direction M3, which is the direction in which the exhaust mobile 60 rotates, when the engagement surface 73a of the output pallet 73 comes into engagement with the working surface 63a of the one of the escapement teeth 63 (see Figure 10). The predetermined angle α varies, for example, from approximately 11° to 16°.

[0132] Since the engagement surface 73a of the outlet pallet 73 is inclined at the predetermined angle α relative to the second straight line L2, as described above, the rotary torque produced by the escapement mobile 60 causes the action of a torque on the output pallet 73, when one of the escapement teeth 63 engages with the output pallet 73, such that the output pallet 73 is pulled towards the mobile d exhaust 60. The engagement between each of the escapement teeth 63 and the exit vane 73 can therefore be stabilized, to the extent that a shift or any other change in the position where the exit vane 73 comes engaged with the escape tooth 63 due, for example, to a disturbance, can be avoided. An adjustment of the angle of incidence of pulling can therefore avoid finding oneself in a situation in which a pivoting movement of the anchor 71 induces, due to a disturbance, for example the small collar 37 and the stinger 82 to be brought into mutual contact to cause abnormal operation which prevents the free oscillation of the sprung balance 30.

[0133] In the escapement 13 configured as described above, the rotation of the escapement mobile 60 is controlled in such a way that a first rotational action angle θ1 (see Figures 15 and 16) of the exhaust mobile escapement 60 which directly transmits the torque to the sprung balance 30 and a second rotational action angle θ2 (see Figures 15 and 16) of the escapement mobile 60 which indirectly transmits the torque to the sprung balance 30 differ from one of the other.

[0134] Specifically, the rotation of the escape wheel 60 is controlled in such a way by the control element 70, which includes the anchor 71, that the first angle of rotational action θ1 is greater than the second rotational action angle θ2. This point will be described in detail later.

(Exhaust operation)

[0135] In what follows, we will describe the operation of the exhaust 13 configured as described above.

[0136] In a start-of-operation state in the description which follows, the working surface 63a of one of the escapement teeth 63 engages with the engagement surface 72a of the inlet pallet 72, and the external lateral surface 77a of the other anchor arm 77 is in contact with the second limiting pin 92 to position the anchor 71, as shown in Figure 6. The rotation of the escapement mobile 60 is therefore stopped . Furthermore, the free oscillation of the sprung balance 30 has moved the impulse pin 40 in the first direction of rotation M1, and the impulse pin 40 has entered the fork 81. The contact pallet 50 has retracted outside the rotational trajectory R of the escape wheel 64.

[0137] The operation of the escapement 13 in response to the alternating rotation of the sprung balance 30 will be described sequentially from the start of operation state described above.

[0138] When the rotational energy (power) accumulated in the hairspring causes the hairspring balance 30 to rotate further in the first direction of rotation M1 starting from the state shown in FIG. 6, the impulse pin 40 comes in contact and engages with an internal surface of the fork 81, which is the internal surface facing the horn 80 located on the side towards which the impulse pin 40 moves, and the impulse pin 40 acts on the fork 81 in the first direction of rotation M1. The energy of the hairspring is therefore transmitted to the anchor 71 via the impulse pin 40.

[0139] When the impulse pin 40 is engaged with the fork 81, the part in the shape of a crescent moon 43 arranged in the small collar 37 prevents the small collar 37 and the dart 82 from coming into contact with one another. with the other. The energy of the sprung balance 30 can therefore be efficiently transmitted to the anchor 71.

[0140] Consequently, the anchor 71 pivots clockwise around the third axis O3, and the external lateral surface 77a of the anchor arm 77 separates from the second limiting pin 91, as shown in Figure 8. In addition, the pivoting movement of the anchor 71 moves the entry pallet 72 in a direction away from the escape wheel 64 (direction in which the entry pallet 72 retracts in outside the rotational trajectory R of the escape wheel 64).

[0141] The movement of the entry pallet 72 towards a position slightly outside the rotational trajectory R of the escape wheel 64 can thus cause the entry pallet 72 to move away from each other. exhaust teeth 63, in order to release the engagement between the entry pallet 72 and the exhaust tooth 63. The stopped exhaust mobile 60 can therefore be released.

[0142] When the engagement between one of the escapement teeth 63 and the entry pallet 72 is released, the escapement mobile 60 retracts for an instant not in the direction of clockwise M3 , which is the main direction in which the escapement mobile 60 rotates, but in the counterclockwise direction M4, which is opposite to the clockwise direction M3. After this retraction for an instant, the torque transmitted via the front gear train 12 restarts the rotation of the exhaust mobile 60 in the clockwise direction M3.

[0143] The retraction of the exhaust mobile 60 for an instant described above allows more reliable engagement with the front gear train 12, whereby the front gear train 12 can operate stably, particularly reliable.

[0144] When the escapement mobile 60 restarts clockwise rotation M3, the working surface 63a of another escapement tooth 63 comes into contact (collision) with the contact surface 51 of the contact pallet 50 which has penetrated inside the rotational trajectory R of the escape wheel 64 in response to the rotation of the sprung balance 30 in the first direction of rotation M1, as shown in Figure 9 Consequently, the torque transmitted to the escapement mobile 60 can be transmitted directly to the sprung balance 30 via the contact pallet 50 and the double plate 35, and the anchor 71 is thus authorized to pivot continuously to follow the impulse pin 40. The direct transmission mentioned above of the torque transmitted to the escapement mobile 60 to the sprung balance 30 allows a replenishment of torque from the sprung balance 30.

[0145] When any of the escapement teeth 63 comes into contact with the contact paddle 50 as described above, the escapement tooth 63 rotates clockwise M3 while sliding the along the contact surface 51, and the contact vane 50 moves gradually in a direction away from the escape wheel 64 (direction in which the contact vane 50 retracts outside the rotational trajectory R of the escape wheel 64) when the sprung balance 30 turns. Furthermore, when the rotation of the sprung balance 30 moves the contact pallet 50 in the direction away from the escape wheel 64, the pivoting movement of the anchor 71 in the direction of the clocks of a watch causes the start of the incursion movement of the output pallet 73 inside the rotational trajectory R of the escape wheel 64.

[0146] Then, when the contact vane 50 moves to a position outside the rotational trajectory R of the escape wheel 64, the working surface 63a of another escape tooth 63 comes into contact with the engagement surface 73a of the output pallet 73, which has penetrated inside the rotational trajectory R of the escape wheel 64, as shown in Figure 10.

[0147] At the time of initial contact, the anchor 71 moves towards the first limiting pin 90 when it pivots clockwise, and is not in contact with the first limiting pin 90. The anchor 71 therefore pivots slightly while the escape tooth 63 remains in contact with the output pallet 73. Then, when the external lateral surface 76a of the anchor arm 76 comes into contact with the first pin of limitation 90, the anchor 71 no longer pivots and remains in this position. The escapement tooth 63 therefore engages with the output pallet 73. The rotation of the escapement mobile 60 is therefore stopped, and the anchor 71 is stopped. Figure 10 shows the state in which the outer side surface 76a of the anchor arm 76 is in contact with the first limiting pin 90.

[0148] At this time, the direct transmission of torque to the sprung balance 30 ends.

[0149] Then, the impulse pin 40 moves away from the inside of the fork 81 and separates from the anchor 71 when the sprung balance 30 rotates in the first direction of rotation M1. Later, the inertia of the sprung balance 30 allows it to continue to rotate in the first direction of rotation M1, and the rotational energy of the sprung balance 30 is accumulated in the spiral spring. Then, when all the rotating energy is accumulated in the hairspring, the hairspring balance 30 stops rotating in the first direction of rotation M1, remains stationary for a moment, and then begins to rotate in the second direction of rotation M2, which is opposite to the first direction of rotation M1, on the basis of the rotary energy accumulated in the hairspring.

[0150] The impulse pin 40 therefore begins to move again towards the anchor 71 to approach it when the sprung balance 30 turns in the second direction of rotation M2.

[0151] Then, when the impulse pin 40 penetrates inside the fork 81 of the anchor 71, the impulse pin 40 comes into contact and engages with an internal surface of the fork 81 which is the internal surface facing the horn 80 located on the side towards which the impulse pin 40 moves, and acts on the fork 81 in the second direction of rotation M2. The energy of the hairspring is therefore transmitted to the anchor 71 via the impulse pin 40.

[0152] Consequently, the anchor 71 pivots counterclockwise around the third axis O3, and the external lateral surface 76a of the anchor arm 71 separates from the first limiting pin 90, as shown in Figure 12. In addition, the pivoting movement of the anchor 71 moves the output pallet 73 in a direction away from the escape wheel 64 (direction in which the output pallet 73 retracts outwards of the rotational trajectory R of escape wheel 64). The movement of the engagement surface 73a of the output pallet 73 towards a position slightly outside the rotational trajectory R of the escape wheel 64 makes it possible to release the engagement between the engagement surface 73a and the escape tooth 63. The escape wheel 60, which was stopped, can therefore be released.

[0153] Since the exit pallet 73, which has an angle of incidence of pulling, just like the inlet pallet 72, the exhaust mobile 60 resumes its clockwise rotation M3 on the basis of the energy transmitted via the front cog 12 after retracting counterclockwise M4 for an instant. Then, when the escapement mobile 60 restarts its clockwise rotation M3, the escapement mobile 60 rotates in the clockwise direction M3, while the tooth of exhaust 63 slides along the sliding surface 73b of the outlet pallet 73 and moves relatively relative to the latter, as shown in Figure 13. Consequently, the torque transmitted to the exhaust mobile 60 can be transmitted to the anchor 71 via the output pallet 73, and an internal surface of the fork 81, which is the internal surface facing the horn 80 located on the side opposite to the direction in which the impulse pin 40 moves , comes into contact and engages with the impulse pin 40.

[0154] Consequently, the torque transmitted to the escapement wheel 60 can be transmitted indirectly to the sprung balance 30 via the anchor 71, and the anchor 71 is thus allowed to pivot continuously to follow the impulse pin. 40. The indirect transmission mentioned above of the torque transmitted to the escapement mobile 60 to the sprung balance 30 allows a replenishment of the sprung balance 30 in terms of torque.

[0155] Then, when the pivoting movement of the anchor 71 moves the output pallet 73 towards a position outside the rotational trajectory R of the escape wheel 64, the working surface 63a of another tooth d The exhaust 63 comes into contact with the engagement surface 72a of the input pallet 72 having penetrated inside the rotational trajectory R of the escape wheel 64, as shown in Figure 14.

[0156] During initial contact, the anchor 71 moves towards the second limiting pin 91 when it pivots counterclockwise and is not in contact with the second limiting pin 91. The anchor 71 therefore pivots slightly while the escapement tooth 63 and the inlet vane 72 remain in mutual contact. Then, when the external lateral surface 77a of the other anchor arm 77 comes into contact with the second limiting pin 91, the anchor 71 no longer pivots and remains in this position. The escapement tooth 63 therefore engages with the entry pallet 72. The rotation of the escapement mobile 60 is therefore stopped, and the anchor 71 is stopped. Figure 14 represents the state in which the external side surface 77a of the anchor arm 77 is in contact with the second limiting pin 91.

[0157] At this time, the indirect transmission of torque to the sprung balance 30 ends.

[0158] Then, the escapement 13 repeats the operation described above when the sprung balance 30 performs its alternating rotation. Therefore, the contact paddle 50 and the anchor 71, which includes the input paddle 72 and the output paddle 73, can be used to alternately (switchably) perform direct torque transmission and indirect transmission of torque during the alternating movement, that is to say back and forth, of the sprung balance 30, allowing a replenishment of the sprung balance 30 in terms of torque with the torque transmitted to the escapement mobile 60, and a control of the rotation of the escapement mobile 60 according to a fixed oscillation corresponding to that of the sprung balance 30.

[0159] In other words, the exhaust 13 is allowed to operate as a half-direct/half-indirect impact type exhaust using direct impact and indirect impact, thanks to which the torque transmission efficiency can be increased. increased compared to a Swiss anchor escapement of the prior art, which is an indirect impact type escapement.

[0160] In particular, in the escapement 13 according to the present embodiment, the rotation of the escapement mobile 60 is controlled by the control element 70 so that the first angle of rotational action θ1 of the mobile escapement 60 which directly transmits the torque transmitted to the sprung balance 30 when the sprung balance 30 rotates in the first direction of rotation M1 and the second rotational angle of action θ2 of the escapement wheel 60 which indirectly transmits the torque transmitted to the balance -spring 30 when the sprung balance 30 rotates in the second direction of rotation M2 are not equal to each other but differ from each other (that is to say are unequal l 'to each other), as illustrated in Figures 15 and 16.

[0161] Specifically, the rotation of the escapement mobile 60 is controlled so that the first rotational action angle θ1 is greater than the second rotational action angle θ2.

[0162] More specifically, the rotation of the escape wheel 60 is controlled so that the ratio between the first rotational action angle θ1 and a predetermined rotational action angle θ3, by which the escape wheel 60 rotates following an alternating movement of the sprung balance 30, i.e. greater than 50% but smaller than 75%.

[0163] According to the present embodiment, the rotation of the escapement mobile 60 is controlled such that the ratio between the first rotational action angle θ1 and the predetermined rotational action angle θ3, by which the mobile escapement 60 rotates following an alternating movement of the sprung balance 30, is approximately 66.7%.

[0164] Control of the rotation of the escapement mobile 60 is described in detail in the following.

[0165] In the operation described above, the escapement wheel 60 rotates by an amount corresponding to one tooth during an alternating movement of the sprung balance 30. The escapement wheel 60, which has eight teeth d The escapement 63, rotates 45 degrees around the first axis O1 during an alternating movement of the sprung balance 30, that is to say when it has carried out its back and forth movement once. The predetermined rotational action angle θ3, by which the escapement mobile 60 rotates in a reciprocating movement of the sprung balance 30, is therefore 45 degrees, as shown in Figure 15.

[0166] The escape wheel 60 then rotates, during the period extending between the state shown in Figure 6 (state in which the working surface 63a of the escape tooth 63 engages with a surface 10 (state in which the working surface 63a of the exhaust tooth 63 engages with an engagement surface 73a of the exit pallet 73) while the sprung balance 30 rotates in the first direction of rotation M1. The torque is transmitted directly to the sprung balance 30 during this period.

[0167] The angle at which the escape wheel 60 rotates from the state shown in Figure 6, shown by a long dotted line and a short double dotted line in the state shown in Figure 10, drawn in line full, corresponds to the first rotational action angle θ1, illustrated in Figure 15, and is 30 degrees according to the present embodiment.

[0168] The escape wheel 60 continues to rotate further during the period extending between the state shown in FIG. 11 (state in which a working surface 63a of the escape tooth 63 comes into engagement with a surface engagement surface 73a of the outlet pallet 73) and the state shown in Figure 14 (state in which the working surface 63a of the escapement tooth 63 engages with the engagement surface 72a of the outlet pallet input 72) while the sprung balance 30 rotates in the second direction of rotation M2. The torque is then transmitted indirectly to the sprung balance 30 during this period.

[0169] The angle at which the escape wheel 60 rotates from the state shown in Figure 11, shown by a long dotted line followed by a short double dotted line, to the state shown in Figure 14 drawn in solid lines, corresponds to the second rotational action angle θ2, illustrated in Figure 16, and is 15 degrees according to the present embodiment.

[0170] The sum of the first rotational action angle θ1 and the second rotational action angle θ2 corresponds to the predetermined rotational action angle θ3.

[0171] Consequently, according to the present embodiment, the ratio between the first rotational action angle θ1 (30 degrees) and the predetermined rotational action angle θ3 (45 degrees), according to which the escape wheel 60 rotates during an alternating movement of the sprung balance 30, is set at approximately 66.7%, as described above.

[0172] In the exhaust 13 according to the present embodiment, where the first rotational action angle θ1 and the second rotational action angle θ2 differ from each other (that is to say they are unequal to each other), the quantity of torque transmitted directly to the sprung balance 30 and the quantity of torque transmitted indirectly to the sprung balance 30 can be adjusted such that a balance of Optimal supply between the two is obtained. As a result, the torque transmission efficiency (exhaust efficiency) can be increased.

[0173] Furthermore, since it is not necessary to arrange the escapement mobile 60, the sprung balance 30, and the anchor 71 in such a way that the first angle of rotational action θ1 and the second angle rotational action θ2 are intentionally adjusted so as to be equal to each other, the escapement mobile 60, the sprung balance 30, and the anchor 71 can be designed and arranged freely, and arranged in front take into account few constraints. The escapement 13 can therefore be optimized in terms of layout, and the resulting escapement has only a small amount of operating errors and excels in terms of time measurement accuracy (has small rate deviations).

[0174] In particular, since the first rotational action angle θ1 is greater than the second rotational action angle θ2, the proportion of direct transmission of torque from the escapement wheel 60 to the sprung balance 30 during a alternating movement of the sprung balance 30 can be greater than the indirect torque transmission, whereby the torque transmission efficiency can be further easily increased.

[0175] Furthermore, in the present embodiment, the ratio between the first rotational action angle θ1 and the predetermined rotational action angle θ3 is set at 66.7%, which is smaller than 75%, allows avoid finding yourself in a situation in which the angle of rotational action according to which the escapement wheel 60 rotates when the sprung balance 30 rotates in the second direction of rotation M2 (second angle of rotational action θ2) is , for example, an excessively small angle of action. An angle of action which allows, for example, the anchor 71 to operate correctly can therefore be ensured, whereby the escapement 13 can be reliable by ensuring that it operates stably.

[0176] The anchor 71 can therefore operate correctly with excellent torque transmission efficiency maintained over time, and thanks to which the exhaust 13 can be reliable by presenting stable operating performance.

[0177] Furthermore, since the number of escapement teeth 63 is equal to 8, a situation in which the first rotational action angle θ1 and the second rotational action angle θ2 each have, for example, an excessively high value. large can be avoided. Therefore, the anchor 71 can be designed such that, for example, it can be compact, and the anchor 71 does not need to pivot with large amplitude movements. The exhaust 13 can therefore be reliable and act even more stably.

[0178] As described above, the exhaust 13 according to the present embodiment not only excels in terms of torque transmission efficiency, but has only a small amount of operating error and excels in terms of time measurement accuracy.

[0179] Furthermore, the movement 10 and the timepiece 1 according to the present embodiment, which each include the escapement 13 described above, also each have high performance and excellent precision in terms of measuring the time. In particular, since the movement 10 and the timepiece 1 each include the escapement 13 which excels in terms of torque transmission efficiency, the angle of oscillation of the sprung balance 30 is, for example, easily maintained to a value corresponding to a large amplitude, thanks to which the movement 10 and the timepiece 1 are unlikely to be affected, for example, by a disturbance.

(Second embodiment)

[0180] In the following, we will describe a second embodiment according to the invention with reference to the drawings. In this second embodiment, the same components as those of the first embodiment bearing the same reference numbers will not be described.

[0181] While the escape wheel 60 has a single-layer structure in the first embodiment, the escape wheel has a two-layer structure in the second embodiment.

[0182] The exhaust 100 according to this present embodiment comprises an exhaust mobile 101, which has a two-layer structure comprising the exhaust shaft 62, around which the exhaust pinion 61, which meshes with the second mobile 23, is formed, a first escape wheel 110, and a second escape wheel 120, which is superimposed on the first escape wheel 110 in the axial direction of the first axis 01, as shown in Figures 17 and 18.

[0183] The first escape wheel 110 has the same configuration as that of the escape wheel 64 of the first embodiment and will therefore not be described in detail.

[0184] According to the present embodiment, we refer to the escapement teeth 63 of the first embodiment as constituting the first escapement teeth 111, as illustrated in Figure 19. The rotation envelope R1, which is drawn by the tip of each of the first escapement teeth 111 when the escapement wheel 101 rotates, is simply called the rotational trajectory R1 of the first escapement wheel 110.

[0185] The side surface of each of the first escapement teeth 111 which is the side surface located furthest downstream in the clockwise direction M3, forms a first working surface 111a, which comes into contact with the contact pallet 50 and engaged with the input pallet 72.

[0186] The second escape wheel 120 is integrally fixed to the exhaust shaft 62, for example, via a chase, like the first escape wheel 110, and the second escape wheel 120 is arranged under the first escape wheel 110, as illustrated in Figures 17, 18 and 20. The second escape wheel 120 has a plurality of second escape teeth 121 and has a smaller shape than the first escape wheel 110 in terms of diameter.

[0187] The number of second escapement teeth 121 is equal to 8, like the number of first escapement teeth 111. The rotation envelope R2, which is drawn by the tip of each of the second escapement teeth 121 when the escape wheel 101 rotates, the rotational trajectory R2 of the second escape wheel 120 is simply called.

[0188] The second escape wheel 120 is made, for example, of a metallic material or of a material having a crystalline orientation, such as a single crystal of silicon. Examples of manufacturing processes for the second escape wheel 120 may include electroforming, a LIGA process, which adopts an optical approach, such as photolithography technology, DRIE, and metal powder injection molding (MIM ). The manufacturing method, however, is not limited to any of the methods described above, and the second escape wheel 120 may be formed using any other manufacturing method.

[0189] The second escape wheel 120 comprises an annular hub 122, which has an insertion hole 122a formed at a central portion of the hub 122 and is combined with the exhaust shaft 62 via the hole d insertion 122a, for example, via a drive, as well as four third spokes 123, which extend radially outwards from the hub 122 and are arranged at regular intervals in the circumferential direction, and four fourth spokes 124, which extend radially outward from the hub 122 and are arranged at regular intervals in the circumferential direction. The hub 122, the third spokes 123, and the fourth spokes 124 are mutually integrated with each other in the second escape wheel 120, as shown in Figure 21.

[0190] The third spokes 123 and the fourth spokes 124 are formed so as to be arranged alternately in the circumferential direction, and they have the same radial length. The third spokes 123 and the fourth spokes 124 are shaped to be tapered with tapering as one moves outward in the radial direction, and the forward end of each of the third spokes 123 and of the fourth spokes 124 has a slightly curved shape in the direction of clockwise M3. The curved front ends act as second escapement teeth 121.

[0191] The second escape wheel 120 according to the present embodiment therefore has 8 second escape teeth 121. The lateral surface of each of the second escape teeth 121, which is slightly inclined inwards relative to clockwise M3, forms a second working surface 121 a, which is brought into contact with the outlet pallet 73.

[0192] The second escapement teeth 121 have the shape of the escapement teeth of a Swiss anchor escapement, and are intended to exert an impact force on the exit pallet 73 via the lateral surfaces slightly inclined towards the inside relative to clockwise M3 (second working surfaces 121 a) in order to transmit energy to the anchor 71.

[0193] The base of each of the third rays 123 has a circumferential shape wider than the base of each of the fourth rays 124. The base of each of the third rays 123 is provided with a third aperture 125 having an elongated elliptical shape in the radial direction in plan view. The base of each of the fourth rays 124 is provided with a fourth opening 126 having a triangular shape in a plan view.

[0194] The third openings 125 are configured to be identical to the first openings 68 formed in the first escape wheel 110 and have the same size as those of the first openings 68.

[0195] The weight of the second escape wheel 120 is reduced mainly by the third openings 125 and the fourth openings 126, but this is not essential, and other openings could be provided elsewhere and finer portions or any other type of portion may be provided to the extent that the additional openings or thinner portions do not affect the performance, rigidity, or other factors of the second escape wheel 120.

[0196] The second escape wheel 120 configured as described above is arranged in layers on the first escape wheel 110 such that their mutual phases coincide, as illustrated in Figures 18 and 20. In other words, the second escape wheel 120 is superimposed on the first escape wheel 110 and fixed to the escape shaft 62 such that the bases of the third spokes 123 and the fourth spokes 124 of the second escape wheel 120 are superimposed on the lower side of the base ends of the first spokes 66 and the second spokes 67 of the first escape wheel 110.

[0197] In particular, since the third openings 125 are configured to be identical to the first openings 68 formed in the first escape wheel 110 and have the same size as those of the first openings 68, the fact of aligning the first openings 68 and the third apertures 125 in the circumferential direction allows the first escape wheel 110 and the second escape wheel 120 to be easily and correctly aligned with each other in terms of phase.

[0198] The front end of each of the third spokes 123 and the fourth spokes 124 of the second escape wheel 120 is curved clockwise M3 relative to the front end of each of the first spokes 66 and second spokes 67 of the first escape wheel 110. The phase of the second escape teeth 121 is therefore offset relative to the phase of the first escape teeth 111.

[0199] Since the escape wheel 101 has a two-layer structure including the first escape wheel 110 and the second escape wheel 120 as described above, the outlet pallet 73 is arranged so as to project towards the exhaust mobile 101 more pronouncedly than in the first embodiment, but projects upwards less significantly than in the first embodiment.

(Exhaust operation)

[0200] The exhaust 100 according to the present embodiment configured as described above can also provide the same operating features as those provided in the first embodiment. The operation of the exhaust 100 according to the present embodiment will be described briefly below.

[0201] In a start-of-operation state, the first working surface 111a of one of the first exhaust teeth 111 engages with the engagement surface 72a of the inlet pallet 72, and the external lateral surface 77a of the other anchor arm 77 is in contact with the second limiting pin 92 to position the anchor 71, as shown in Figure 20. The rotation of the escapement mobile 101 is therefore stopped. In addition, the free oscillation of the sprung balance 30 has moved the impulse pin 40 in the first direction of rotation M1, and the impulse pin 40 has entered the fork 81. The contact paddle 50 has retracted outside the rotational trajectory R1 of the first escape wheel 110.

[0202] The operation of the escapement 100 in response to the alternating rotation of the sprung balance 30 will be described sequentially starting from the start of operation state described above.

[0203] When the sprung balance 30 rotates in the first direction of rotation M1 from the state shown in Figure 20, the impulse pin 40 comes into contact and engages with the internal surface of the fork 81, and the impulse pin 40 acts in compression on the fork 81 in the first direction of rotation M1. The energy of the hairspring is therefore transmitted to the anchor 71 via the impulse pin 40.

[0204] Consequently, the anchor 71 pivots clockwise around the third axis O3, and the external lateral surface 77a of the other anchor arm 77 separates from the second limiting pin 91 Furthermore, the pivoting movement of the anchor 71 moves the entry pallet 72 in a direction away from the first escape wheel 110 (direction in which the entry pallet 72 moves away from the first escape wheel 110). retracts outside the rotational trajectory R1 of the first escape wheel 110). The movement of the input pallet 72 towards a position slightly outside the rotational trajectory R1 of the first escape wheel 110 can then cause the input pallet 72 to disengage from one of the first teeth d exhaust 111 in order to release the engagement between the entry pallet 72 and the first escapement tooth 111. The escapement mobile 101, which was stopped, can therefore be released.

[0205] When the escapement mobile 101 resumes its clockwise rotation M3, the first working surface 111a of another first escapement tooth 111 comes into contact (in collision) with the surface contact 51 of the contact pallet 50 having penetrated inside the rotational trajectory R1 of the first escape wheel 110 when the sprung balance 30 rotates in the first direction of rotation M1, as shown in Figure 22.

[0206] The torque transmitted to the escape wheel 101 can therefore be transmitted directly to the sprung balance 30 via the contact pallet 50 and the double plate 35. The direct transmission of the torque transmitted to the escape wheel 101 to the sprung balance 30 therefore allows a replenishment of the sprung balance 30 in terms of torque.

[0207] When one of the first escapement teeth 111 comes into contact with the contact pallet 50 as described above, the first escapement tooth 111 rotates clockwise M3 while sliding along the contact surface 51, and the contact vane 50 gradually moves in a direction away from the first escape wheel 110 (direction in which the contact vane 50 retracts away from the rotational trajectory R1 of the first escape wheel 110) when the sprung balance 30 turns. Furthermore, when the rotation of the sprung balance 30 moves the contact vane 50 towards the first escape wheel 110, the pivoting movement of the anchor 71 in the clockwise direction causes the incursion of the output pallet 73 inside the rotational trajectory R2 of the second escape wheel 120.

[0208] Then, when the contact pallet 50 moves to a position outside the rotational trajectory R1 of the first escapement wheel 110, the second working surface 121a of another second escapement tooth 121 comes into play. contact with the engagement surface 73a of the output pallet 73 which has penetrated inside the rotational trajectory R2 of the second escape wheel 120, as shown in Figure 23.

[0209] In an initial contact step, the anchor 71 moves towards the first limiting pin 90 while it pivots clockwise and is not in contact with the first limiting pin 90. The anchor 71 therefore pivots slightly while the second escapement tooth 121 remains in contact with the output pallet 73. Then, when the external lateral surface 76a of the anchor arm 76 comes into contact with the first pin limitation 90, the anchor 71 no longer pivots and keeps its position. The second escapement tooth 121 therefore engages with the output pallet 73. The rotation of the escapement mobile 101 is therefore stopped, and the anchor 71 is stopped. Figure 23 represents the state in which the external side surface 76a of the anchor arm 76 is in contact with the first limiting pin 90.

[0210] At this time, the direct transmission of torque to the sprung balance 30 ends.

[0211] Then, the impulse pin 40 moves away from the inside of the fork 81 and separates from the anchor 71 while the sprung balance 30 rotates in the first direction of rotation M1. Then, the inertia of the sprung balance 30 allows it to continue to rotate in the first direction of rotation M1, and the rotational energy of the sprung balance 30 accumulates in the balance spring. Then, when all the rotating energy is accumulated in the hairspring, the hairspring balance 30 stops rotating in the first direction of rotation M1, remains in a stationary position for a moment, and begins to rotate in the second direction of rotation M2, which is opposite to the first direction of rotation M1, on the basis of the rotary energy accumulated in the hairspring.

[0212] The impulse pin 40 therefore begins to move again towards the anchor 71 and approaches the latter while the sprung balance 30 rotates in the second direction of rotation M2.

[0213] Then, when the impulse pin 40 penetrates inside the fork 81 of the anchor 71, the impulse pin 40 comes into contact and engages with the internal surface of the fork 81, and acts in compression on the fork 81 in the second direction of rotation M2, as shown in Figure 24. The energy of the hairspring is therefore transmitted to the anchor 71 via the impulse pin 40.

[0214] Consequently, the anchor 71 pivots counterclockwise around the third axis O3, and the external lateral surface 76a of the anchor arm 71 separates from the first limiting pin 90. By elsewhere, the pivoting movement of the anchor 71 moves the output pallet 73 in a direction away from the second escape wheel 120 (direction in which the output pallet 73 retracts outside the rotational trajectory R2 of the second escape wheel 120). The movement of the engagement surface 73a of the output pallet 73 towards a position slightly outside the rotational trajectory R2 of the second escape wheel 120 allows engagement between the engagement surface 73a and the second tooth exhaust 121 to be released. The exhaust mobile 101, which was stopped, can therefore be released.

[0215] Then, when the escapement wheel 101 restarts its clockwise rotation M3, the escapement wheel 101 rotates in the clockwise direction M3, while the second tooth d The exhaust 121 slides along the sliding surface 73b of the outlet pallet 73 and moves relative to the latter, as illustrated in Figure 25. Consequently, the torque transmitted to the exhaust mobile 101 can be transmitted to the anchor 71 via the output pallet 73. Consequently, the torque transmitted to the escapement mobile 101 can be transmitted indirectly to the sprung balance 30 via the anchor 71, and the indirect transmission of the torque allows the replenishment of the balance spiral 30 in couple.

[0216] Then, when the pivoting movement of the anchor 71 moves the output pallet 73 towards a position located outside the rotational trajectory R2 of the second escape wheel 120, the first working surface 111a of a another first escape tooth 111 comes into contact with the engagement surface 72a of the input vane 72 which has penetrated inside the rotational trajectory R1 of the first escape wheel 110, as shown in the figure 26.

[0217] At the time of initial contact, the anchor 71 moves towards the second limiting pin 91 while it pivots counterclockwise and is not in contact with the second limiting pin 91. The anchor 71 therefore pivots slightly while the first escapement tooth 111 and the entry vane 72 remain in mutual contact. Then, when the external lateral surface 77a of the anchor arm 77 comes into contact with the second limiting pin 91, the anchor 71 no longer pivots and remains in this latter position. The first escapement tooth 111 therefore engages with the input pallet 72. The rotation of the escapement mobile 101 is therefore stopped, and the anchor 71 is stopped. Figure 26 represents the state in which the external side surface 77a of the anchor arm 77 is in contact with the second limiting pin 91.

[0218] At this time, the indirect transmission of torque to the sprung balance 30 ends.

[0219] As described above, the escapement 100 according to the present embodiment thus also alternately performs a direct transmission of torque and an indirect transmission of indirect torque during an alternating movement of the sprung balance 30 in order to transmit the torque transmitted to the escape wheel 101 to the sprung balance 30 to replenish the sprung balance 30 with torque.

[0220] Furthermore, also in the present embodiment, the rotation of the escapement wheel 101 is controlled such that the ratio between the first rotational action angle θ1 and the predetermined rotational action angle θ3, according to which the escapement mobile 101 rotates during an alternating movement of the sprung balance 30, is greater than 50%, but smaller than 75%, as shown in Figures 27 and 28.

[0221] Specifically, the rotation of the escape wheel 101 is controlled such that the ratio between the first rotational action angle θ1 and the predetermined rotational action angle θ3, according to which the escape wheel 101 rotates during an alternating movement of the sprung balance 30, is approximately 66.7%.

[0222] Control of the rotation of the exhaust wheel 101 is described in detail in the following.

[0223] In the operation described above, the escapement wheel 101 rotates by an amount corresponding to an angular sector corresponding to the spacing between two consecutive teeth during an alternating movement of the sprung balance 30. predetermined rotational action angle θ3, according to which the escapement mobile 101 rotates during an alternating movement of the sprung balance 30, is therefore 45 degrees, as shown in Figures 27 and 28.

[0224] The escapement mobile 101 rotates during the period corresponding to the transition between the state shown in Figure 20 (state in which the first working surface 111a of the first escapement tooth 111 is engaged with a surface engagement surface 72a of input pallet 72) in the state shown in Figure 23 (state in which the second working surface 121a of second escapement tooth 121 is engaged with the engagement surface 73a of the pallet output 73) when the sprung balance 30 rotates in the first direction of rotation M1. The torque is transmitted directly to the sprung balance 30 during this period.

[0225] The angle at which the exhaust wheel 101 rotates when passing from the state shown in Figure 20 - shown by a long dotted line followed by a short double dotted line - to the state shown in the figure 23, drawn in solid lines, corresponds to the first rotational action angle θ1, shown in Figure 27, and is 30 degrees according to the present embodiment.

[0226] The escapement wheel 101 continues to rotate during the period corresponding to the transition between the state shown in Figure 24 (state in which the second working surface 121a of the second escapement tooth 121 is engaged with the engagement surface 73a of the output pallet 73) in the state shown in Figure 26 (state in which the first working surface 111 has first escapement tooth 111 is engaged with the engagement surface 72a of input pallet 72) while the sprung balance 30 rotates in the second direction of rotation M2. The torque is transmitted indirectly to the sprung balance 30 during this period.

[0227] The angle at which the escape wheel 101 rotates when passing from the state shown in Figure 24, shown by the long dotted line followed by a short double dotted line, to the state shown in the figure 26, drawn in solid lines, corresponds to the second rotational action angle θ2, shown in Figure 28, and is 15 degrees in the present embodiment.

[0228] Consequently, also in the present embodiment, the ratio between the first rotational action angle θ1 (30 degrees) and the predetermined rotational action angle θ3 (45 degrees), according to which the mobile of escapement 101 rotates during an alternating movement of the sprung balance 30, is set at approximately 66.7%. The exhaust 100 according to the present embodiment can therefore also have the same operating characteristics as those provided by the exhaust 13 according to the first embodiment.

[0229] Furthermore, in the escapement 100 according to the present embodiment, the first escapement wheel 110 can be arranged such that the first escapement teeth 111 can each be brought into contact with the contact pallet 50, and the second escape wheel 120 can be arranged in such a way that the second escape teeth 121 can each be brought into contact with the output pallet 73. Since the output pallet 73 can thus be designed, for example , without being affected by the height position of the contact paddle 50, an increase in the length of the output paddle 73 upwards or downwards can be avoided, and the design flexibility can be improved accordingly . The weight of the output pallet 73 can therefore be reduced, and consequently the moment of inertia of the anchor 71 can also be reduced. The torque transmission efficiency can therefore be further improved for the indirect transmission of torque to the sprung balance 30 via the anchor 71.

[0230] Furthermore, the first escape wheel 110 and the second escape wheel 120 can be designed separately from each other. For example, the first escapement teeth 111 and the second escapement teeth 121 can therefore take different shapes adapted for each of them, the first escapement wheel 110 and the second escapement wheel 120 can be formed in such a way. so that they have different diameters, or any other types of optimal design leading to yet further improvements in torque transmission efficiency can be easily achieved.

(Third embodiment)

[0231] In the following, we will describe a third embodiment according to the invention with reference to the drawings. In this third embodiment, the same components as those of the first embodiment bear the same reference numbers and will not be described.

[0232] While the control element 70 comprises an anchor 71 in the first embodiment, the control element 70 comprises, in the third embodiment, an anchor unit formed of a plurality of anchors .

[0233] Furthermore, while the large collar 36 and the small collar 37 are integrated with each other in the double plate 35, and the impulse pin 40 and the contact pallet 50 are fixed to the large collar 36 in the first embodiment, in the third embodiment, the double plate comprises a large collar and a small collar formed separately from each other, the impulse pin is fixed to the large collar, and a first contact paddle is attached to the small collar.

[0234] The escapement 130 comprises a double plate 140 fixed to the balance shaft 31, a first contact pallet 150 arranged on the sprung balance 30, an escapement mobile 160, which rotates using the transmitted energy from the mainspring of the barrel, and the control element 70, which lets it rotate and stops the escapement wheel 160 on the basis of the rotation of the sprung balance 30, as shown in Figures 29 to 31.

[0235] The present embodiment will be described with reference to a case where the escapement mobile 160 rotates counterclockwise around the first axis O1 according to a plan view of the movement 10 seen from the 'Before. Furthermore, according to the present embodiment, in correspondence with the direction in which the escapement mobile 160 rotates, the direction in which the sprung balance 30 rotates clockwise around the second axis O2 is called the first direction of rotation M1, and the direction in which the sprung balance 30 turns counterclockwise is called the second direction of rotation M2.

(Double tray)

[0236] The double plate 140 is provided with a large collar 141 and a small collar 142, which are components formed separately from each other. The large collar 141 has a disc shape having an insertion hole which is not shown, which is arranged at a central part of the large collar 141, and through which the balance shaft 31 is inserted, and the large collar 141 is arranged coaxially with respect to the second axis O2 and under the balance wheel 32. A through hole 143 for fixing the impulse pin 40 is formed in a portion of the large collar 141 which is the portion located radially to the exterior of the main body of the small collar 142b, which will be described later. The impulse pin 40 is fixed in the through hole 143, for example, via a drive.

[0237] The impulse pin 40 is formed so as to extend downwards beyond the large collar 141, but being located above the main body of the small collar 142b.

[0238] The crescent-shaped part 43, which has an inward recess in the radial direction so as to form a curved surface, is arranged at a portion of the outer circumferential edge of the large collar 141 which is the portion located outside the impulse pin 40 in the radial direction. A plurality of openings are formed in the large collar 141 in order to provide weight reduction.

[0239] Finer portions or other portions can be formed in place of the apertures, and finer portions or other portions can be added elsewhere in addition to the apertures.

[0240] The small collar 142 has a multi-stage shape arranged coaxially with respect to the second axis O2, and is arranged below the large collar 141. Specifically, the small collar 142 is configured to take a multi-stage shape including an insertion portion, which is not shown, but is the uppermost part, a flange 142a, which is arranged below the insertion portion and has a diameter larger than that of the portion d insertion, a connecting part which is not shown but is arranged below the collar 142a and has a diameter smaller than the collar 142a, and the main body of the small collar 142b, which is arranged below the connecting part and has a diameter larger than that of the connecting part and the flange 142a.

[0241] The small collar 142 further has an insertion hole which is not shown but passes through the entire small collar 142 in the direction from bottom to top. The small collar 142 is fitted externally on the balance shaft 31 and fixed thereto, while the balance shaft 31 is inserted into the insertion hole. The small collar 142 is therefore integrally attached to the balance shaft 31.

[0242] Furthermore, the small collar 142 is configured such that the insertion part is inserted from below into the insertion hole formed in the large collar 141, and inserted into the insertion hole while the collar 142a is in contact with the lower side of the large collar 141 and combined with the balance shaft 31. The large collar 141 is therefore integrally secured to the small collar 142, and is furthermore integrally secured to the balance shaft 31 via the small collar 142.

[0243] The large collar 141 and the small collar 142, which are formed separately from each other, are therefore both integrally secured to the balance shaft 31. In addition, a slot 144 , which divides the small collar main body 142b according to a diameter, is arranged in the small collar main body 142b. The slot 144 does not necessarily take the shape described above. For example, slot 144 may be formed in a "U" shape which opens outward in the radial direction, as in the first embodiment. The first contact paddle 150 is then fixed in the slot 144.

(First contact palette)

[0244] The first contact pallet 150 is a pallet configured to be brought into contact with escapement teeth 161 of the escapement wheel 160, and transmit the torque transmitted to the escapement wheel 160 to the sprung balance 30. escapement teeth 161 will be described later.

[0245] The first contact pallet 150 is inserted radially from the outside into the slot 144 formed in the main body of the small collar 142b and fixed inside it, for example, using a adhesive. The first contact paddle 150 is made of an artificial precious stone, for example ruby, like the impulse peg 40. The first contact paddle 150 has a rectangular plate shape extending in the radial direction of the main body of the small collar 142b and has a front end which projects outward in the radial direction beyond the outer circumferential edge of the main body of the small collar 142b.

[0246] The lateral surface of the first contact pallet 150 which is the most downstream lateral surface in the second direction of rotation M2 is a flat surface extending radially to form a first contact surface 151, with which a surface working 161a of each of the escapement teeth 161, which will be described later, can be brought into contact. In addition, the front end of the first contact pallet 150 has an inclined surface 152 located downstream of the first contact surface 151 moving in the first direction of rotation M1.

[0247] Since the first contact paddle 150 is attached to the main body of the small collar 142b, which is located below the impulse pin 40, any contact between the first contact paddle 150 and the anchor unit 170, which will be described later, is avoided.

[0248] When the sprung balance 30 rotates, the first contact pallet 150 fixed to the sprung balance 30 via the double plate 140, as described above, repeats an incursion movement inside the rotational trajectory R of the escape wheel 162, which will be described later, then retraction outside this trajectory. The working surface 161a of each of the escape teeth 161 of the escape wheel 162 is therefore allowed to come into contact (collision) with the first contact surface 151 of the first contact vane 150.

[0249] The contact between the working surface 161a of one of the escapement teeth 161 and the first contact surface 151 of the first contact pallet 150 allows transmission of the energy of the escapement mobile 160 towards the first contact palette 150.

(Mobile exhaust)

[0250] The exhaust wheel 160 comprises the exhaust shaft 62, around which the exhaust pinion 61, which engages with the second wheel 23, is formed, and the escape wheel 162, which is integrally fixed to the exhaust shaft 62, for example, via a chase, and which has a plurality of exhaust teeth 161.

[0251] The present embodiment is described with reference to a case where the number of escapement teeth 161 is 8, as in the first embodiment; such a number is however absolutely not essential, and this number of escapement teeth 161 can be adjusted appropriately according to needs.

[0252] Furthermore, according to the present embodiment, the rotation envelope of the escapement wheel R, which is drawn by the tip of each of the escapement teeth 161 when the escapement wheel 160 rotates, is simply called the rotational trajectory R of the escape wheel 162.

[0253] The escape wheel 162 is made, for example, of a metallic material or of a material having a crystalline orientation, such as a single crystal of silicon. Examples of a method of manufacturing the escape wheel 162 may include electroforming, a LIGA process, which adopts an optical approach, such as photolithography technology, DRIE, and metal powder injection molding ( MIM). The manufacturing method is not limited to any of the methods described above, however, and the escape wheel 162 could also be formed using another manufacturing method.

[0254] The escape wheel 162 includes an annular hub 164, which has an insertion hole which is not shown but is arranged in a central portion of the hub 164, and is secured to the escape shaft 62 via the insertion hole, for example, via a drive, and eight spokes 165, which extend outward from the hub 164 in the radial direction and are arranged at regular intervals in the circumferential direction, and the hub 164 and the spokes 165 are mutually integrated with each other on the escape wheel 162.

[0255] The spokes 165 have a conical shape tapering outwards as one moves away from the center in the radial direction, and the front end of each of the spokes 165 has a shape slightly curved in counterclockwise M4, with the degree of curvature also increasing as one moves outward in the radial direction. The curved front ends act as escapement teeth 161.

[0256] The lateral surface of each of the escapement teeth 161 which is the lateral surface located furthest downstream in the counterclockwise direction M4 forms the working surface 161 a, which comes into contact with the first contact pallet 150 and a second contact pallet 200, which will be described later, and engages with a first stop pallet (first pallet according to the invention) 210 and a second stop pallet (second pallet according to the invention) invention) 220, which will be described later.

[0257] The spokes 165 each have an opening 166 of triangular shape in a plan view. The weight of the escapement mobile 160 is reduced mainly by the openings 166, but this is not absolutely essential, and other openings could be formed elsewhere and thinner portions or other portions can be provided in the to the extent that the additional openings or the thinner portions do not affect the performance, rigidity, or other factors of the escapement mobile 160.

[0258] The escapement mobile 160 configured as described above is responsible for the direct transmission of the torque which was transmitted to it to the sprung balance 30 when the sprung balance 30 rotates in the first direction of rotation M1, and for the indirect transmission of the torque which was transmitted to the sprung balance 30 via the control element 70 when the sprung balance 30 rotates in the second direction of rotation M2. The exhaust mobile 160 is arranged in a height position aligned with that of the main body of the small collar 142 and the first contact pallet 150.

(Control element)

[0259] The control element 70 comprises an anchor unit 170, which is formed from a plurality of anchors 180 and 190, and pivots based on the rotation of the sprung balance 30. It controls the rotation of the exhaust mobile 160, that is to say, controls the starting and stopping of the rotation of the exhaust mobile 160.

[0260] The anchor unit 170 according to the present embodiment comprises a first anchor 180 and a second anchor 190. The first anchor 180 and the second anchor 190 are linked to each other so as to be able to move relative to each other, and are connected in series one behind the other along the same line. The anchor unit 170 is then moved based on the alternating rotation of the sprung balance 30 so as to cause the first anchor 180 to pivot and the second anchor 190 to pivot separately from each other.

[0261] The anchor unit 170 further comprises the second contact pallet 200, which is configured to be able to be brought into contact with the escapement teeth 161, as well as the first stop pallet 210 and the second pallet stop 220, which are configured to be able to engage with the escapement teeth 161 and free themselves from them.

[0262] The second contact vane 200 is a vane arranged to transmit the torque which was transmitted to the escape wheel 160 to the sprung balance 3 via the anchor unit 170, and is fixed to the first anchor 180.

[0263] The first stopping pallet 210 and the second stopping pallet 220 are each a pallet intended to stop the escape wheel 160, then release the escape wheel 160 when it is stopped and are each fixed to the second anchor 190.

[0264] In the following, the first anchor 180 will be described in detail.

[0265] The first anchor 180 comprises a first anchor shaft 181, which is a pivot axis, and a first anchor body 182; it pivots around a fourth axis line O4 on the basis of the alternating rotation of the sprung balance 30.

[0266] The first anchor shaft 181 is arranged coaxially with respect to the fourth axis O4. An upper pivot 181a and a lower pivot 181b, which are each conical, are formed at the axially opposite ends of the first anchor shaft 181. The first anchor shaft 181 is supported in the space between the plate 11 and the bridge anchor which is not shown via the upper pivot 181a and the lower pivot 181b.

[0267] A collar 181 c, which is wider than the first anchor shaft 181 in terms of diameter, is formed in one piece with a central portion of the first anchor shaft 181 facing the 'rotation axis. The body of the first anchor 182 is integrally fixed to the first anchor shaft 181, for example, via a drive with the body of the first anchor 182 placed on the collar 181c.

[0268] The body of the first anchor 182 has a plate shape produced, for example, using electroforming or MEMS technology and is arranged between the large collar 141 and the small collar 142. In other words, the body of the first anchor 182 is arranged above the escapement mobile 160. The body of the first anchor 182 can be provided, depending on the needs, with an opening, a thinner portion, or another portion in order to give a reduction in weight, as in the case of the escapement mobile 160. In the example shown in Figures 29, 30 and 31, several openings are formed in the body of the first anchor 182.

[0269] The body of the first anchor 182 includes a first anchor arm 183, which is formed so as to extend towards the sprung balance 30 starting from the part at which the first anchor shaft 181 is fixed, a second anchor arm 184, which is formed so as to extend from the part to which the first anchor shaft 181 is attached towards the second anchor 190, and a third anchor arm 185, which is formed so as to extend from the part to which the first anchor shaft 181 is fixed towards the escapement mobile 160, and is located between the first anchor arm 183 and the second anchor arm 184.

[0270] The front end of the first anchor arm 183 is provided with a pair of horns 80 arranged side by side in the circumferential direction around the fourth axis O4. The interior of the horns 80 opens towards the balance shaft 31 and forms the fork 81, which receives the impulse pin 40, which moves when the sprung balance 30 performs its alternating rotation. During this alternating rotation, the impulse pin 40 can engage in the fork 81, then disengage from it.

[0271] Furthermore, the dart 82 is fixed to the front end of the first anchor arm 183.

[0272] The stinger 82 is inserted into the front end of the first anchor arm 183, according to the present embodiment, from above, for example, via a chase so as to be integrally fixed to the first anchor arm 183, but this is not absolutely necessary. For example, the stinger 82 could instead be attached to the front end of the first anchor arm 183, for example, using an adhesive or caulking.

[0273] The dart 82 is fixed in a position offset relative to the fork 81 towards the first anchor shaft 181 in a plan view, and fixed so as to be aligned in height with respect to the large collar 141.

[0274] In the state where the impulse pin 40 is released and moved away from the fork 81, the front end of the stinger 82 faces, in the radial direction and via a slight spacing, a part of the circumferential surface external of the large collar 141, which is the complementary part to that in the shape of a crescent moon 43, that is to say forming the entire rest of the periphery, while in the state where the impulse pin 40 is in taken with the fork 81, the front end of the dart 82 is located in the crescent-shaped part 43.

[0275] When the impulse pin 40 has emerged from the fork 81 and moved away from it, the front end of the dart 82 faces the external circumferential surface of the large collar 141 with a slight spacing between them, which allows the front end of the dart 82 to come into contact first and foremost with the external circumferential surface of the large collar 141 even, for example, in the case where a disturbance takes place during the free oscillation of the sprung balance 30 and that the anchor unit 170, then stopped, is released due to the disturbance. A movement of the anchor unit 170 due to a disturbance can therefore be avoided, since any release of the stopped anchor unit 170 can be avoided. The anchor unit 170 will be described in detail later in its stopped state.

[0276] An engagement fork with two branches 186, which bifurcates in the circumferential direction around the fourth axis O4, is formed at the front end of the second anchor arm 184. A slot 187 for fixing the second pallet contact 200 is formed at the front end of the third anchor arm 185. The slot 187 is arranged so as to pass through the third anchor arm 185 in the direction going from top to bottom, and s opens towards the exhaust mobile 160.

[0277] The second contact pallet 200 is formed by an artificial precious stone consisting, for example, of ruby, like the first contact pallet 150, and fixed in the slot 187, for example, via a chase, or glued and fixed in this, for example, using an adhesive. The second contact pallet 200 has the shape of a rectangular plate extending along the slot 187, and is fixed so as to project from the third anchor arm 185 towards the escapement mobile 160. In addition, the second contact pallet 200 is formed so as to extend downwards beyond the third anchor arm 185, and is fixed so as to be aligned in height with the escapement mobile 160.

[0278] The side surface of the front end of the second contact pallet 200 which is the side surface located furthest downstream in the clockwise direction M3, which is opposite to the direction in which the mobile of exhaust 160 rotates, is a flat surface along the slot 187 and forms a second contact surface 201, with which the working surface 161a of each of the escapement teeth 161 is allowed to come into contact (collide). The front end of the second contact pallet 200 furthermore has a second inclined surface 202 located further downstream in the counterclockwise direction M4, which is the direction in which the escapement mobile 160 rotates.

[0279] The first anchor 180 configured as described above rotates based on the rotation of the sprung balance 30, as described above.

[0280] Specifically, the impulse pin 40, which moves while the sprung balance 30 performs its alternating rotation, causes the first anchor 180 to pivot around the fourth axis O4 in the direction opposite to that in which the balance -spring 30 turns. In this process, the second contact pallet 200 repeats an incursion inside the rotational trajectory R of the escape wheel 162, then a retraction outside thereof in response to the pivoting movement of the first anchor 180 The working surface 161a of each of the escapement teeth 161 of the escapement wheel 162 is therefore allowed to come into engagement (in collision) with the second contact surface 201 of the second contact vane 200. When the surface working 161a of one of the escapement teeth 161 comes into contact with the second contact surface 201 of the second contact pallet 200, the energy is transmitted from the escapement mobile 160 to the second contact pallet 200 .

[0281] The direction in which the sprung balance 30 rotates is opposite to that in which the first anchor 180 pivots. Consequently, when the working surface 161a of one of the escapement teeth 161 comes into contact with the first contact vane 150, the second contact vane 200 behaves so as to penetrate inside the rotational trajectory R of the escape wheel 162, while at the moment when the working surface 161a of one of the escape teeth 161 comes into contact with the second contact pallet 200, the first contact pallet 150 behaves so as to retract outside the rotational trajectory R of the escape wheel 162.

[0282] In what follows, we will describe the second anchor 190 in detail.

[0283] The second anchor 190 is arranged on the downstream side in the clockwise direction M3, which is opposite to that in which the escapement mobile 160 rotates; it includes a second anchor shaft 191, which is an axis for pivoting movement, and a second anchor body 192. The second anchor 190 pivots based on the rotation of the first anchor 180 about a fifth axis O5 in the direction opposite to that in which the first anchor 180 pivots.

[0284] The second anchor shaft 191 is arranged coaxially with respect to the fifth axis O5. An upper pivot 191a and a lower pivot 191b, which are each conical, are formed at the axially opposite ends of the second anchor shaft 191. The second anchor shaft 191 is supported in the space between the plate 11 and the bridge d anchor - which is not shown - via the upper pivot 191a and the lower pivot 191b.

[0285] A collar 191c, which is larger than the second anchor shaft 191 in terms of diameter, is formed in one piece with the axial central portion of the second anchor shaft 191. The body of the second anchor 192 is integrally fixed to the second anchor shaft 191, for example, via a recess of the body of the second anchor 192 placed on the collar 191c.

[0286] The body of the second anchor 192 has a plate shape produced using, for example, electroforming or MEMS technology and is located below the body of the first anchor 182. In other words, the body of the second anchor 192 is arranged so as to be aligned in height with the escapement mobile 160. The body of second anchor 192 can be provided, depending on the needs, with an opening, with a thinner portion, or with no any other portion in order to obtain a weight reduction, just like the escapement mobile 160. In the example illustrated in Figures 29, 30 and 31, several openings are formed in the body of the second anchor 192.

[0287] The body of the second anchor 192 includes a fourth anchor arm 193, which is formed so as to extend from the portion to which the second anchor shaft 191 is attached toward the body of the first anchor 182 , and a fifth anchor arm 194, which is formed so as to extend from the part to which the second anchor shaft 191 is attached towards the fourth anchor arm 193.

[0288] An engagement pin 195, which extends upwards, is fixed to the front end of the fourth anchor arm 193, for example, via a chase. The engagement pin 195 has a shape, for example, solid cylindrical, and the upper end of the engagement pin 195 penetrates inside the engagement fork 186 of the first anchor 180.

[0289] Since the engagement pin 195 penetrates inside the engagement fork 186, the outer circumferential surface of the engagement pin 195 and the inner surface of the engagement fork 186 engage in a manner sliding relative to each other. The first anchor 180 and the second anchor 190 are connected to each other so as to be able to move relative to each other and can pivot in opposite directions.

[0290] A slot 196 for fixing the first stop pallet 210 is arranged at a part of the fourth anchor arm 193 which is the part between the second anchor shaft 191 and the engagement pin 195. The slot 196 is formed so as to pass through the fourth anchor arm 193 in the direction going from top to bottom and opens towards the escapement mobile 160.

[0291] The first stop pallet 210 is formed by an artificial precious stone consisting, for example, of ruby, like the first contact pallet 150 and the second contact pallet 200, and fixed in the slot 196, for example, via a chase, or glued and fixed therein, for example, with an adhesive. The first stop pallet 210 has the shape of a rectangular plate extending along the slot 196, and is fixed so as to project from the fourth anchor arm 193 towards the escapement mobile 160.

[0292] The lateral surface of the projecting part of the first stopping pallet 210 which is the lateral surface located downstream in the clockwise direction M3, which is opposite to the direction in which the exhaust mobile 160 rotates, forms a first engagement surface 210a, with which the working surface 161a of each of the escapement teeth 161 of the escapement wheel 162 comes into engagement. The first stop pallet 210 functions as entry pallet 72.

[0293] The first stop pallet 210 is fixed in the slot 196 such that the first engagement surface 210a having a predetermined angle of incidence of pulling can engage with the working surface 161a of each of the exhaust teeth 161, like the inlet pallet 72 in the first embodiment.

[0294] A slot 197 for fixing the second stop pallet 220 is arranged on the fifth anchor arm 194. The slot 197 is formed so as to pass through the fifth anchor arm 194 in the direction going upwards. at the bottom and opens towards the exhaust mobile 160.

[0295] The second stop pallet 220 is formed by an artificial precious stone consisting, for example, of ruby, like the first stop pallet 210, and is fixed in the slot 197, for example, via a chase, or glued and fixed therein, for example, with an adhesive. The second stop pallet 220 has the shape of a rectangular plate extending along the slot 197, and is fixed so as to project from the fifth anchor arm 194 towards the escapement mobile 160.

[0296] The lateral surface of the projecting part of the second stop pallet 220 which is the lateral surface located furthest forward in the direction of clockwise M3, which is opposite to that in which the mobile exhaust 160 rotates, forms a second engagement surface 220a, with which the working surface 161a of each of the escapement teeth 161 of the escapement wheel 162 comes into engagement. The second stop pallet 220 functions as exit pallet 73.

[0297] The second stop pallet 220 is fixed in the slot 197 so that the second engagement surface 220a having a predetermined angle of incidence of pulling engages with the working surface 161a of each of the exhaust teeth 161, like the outlet pallet 73 in the first embodiment.

[0298] The second anchor 190 configured as described above pivots around the fifth axis O5 on the basis of the pivoting movement of the first anchor 180, which itself pivots on the basis of the alternating rotation of the sprung balance 30, as described above. In this process, the first stop pallet 210 and the second upper pallet 220 alternately repeat an incursion inside the rotational trajectory R of the escape wheel 162, then a retraction outside it in response to the pivoting movement of the second anchor 190. The working surface 161a of each of the escape teeth 161 of the escape wheel 162 is therefore authorized to come into engagement with the first engagement surface 210a of the first pallet stop 210 or the second engagement surface 220a of the second stop pallet 220.

[0299] In particular, since the first stop pallet 210 and the second stop pallet 220 are arranged so as to sandwich the fifth axis O5, when the first stop pallet 210 comes into engagement with the wheel d exhaust 162, the second stop pallet 220 moves away from it, while on the contrary, when the first stop pallet 210 moves away from the escape wheel 162, the second stop pallet 220 comes into taken with her.

[0300] The anchor unit 170 is configured so that the first anchor 180 and the second anchor 190 are connected to each other in series and so as to be arranged on the same line, and the first anchor 180 and the second anchor 190 are moved on the basis of the alternating rotation of the sprung balance 30 so as to pivot separately from each other. In other words, the first anchor 180 pivots in the direction opposite to that in which the sprung balance 30 rotates, and the second anchor 190 pivots in the direction opposite to that in which the first anchor 180 pivots.

[0301] More specifically, when the sprung balance 30 rotates in the first direction of rotation M1, and after the engagement between one of the escapement teeth 161 and the first stop pallet 210 is released, and that another escapement tooth 161 comes into contact with the first contact pallet 150, another escapement tooth 161 comes into engagement with the second stop pallet 220. When the sprung balance 30 rotates in the second direction of rotation M2, and after the engagement between one of the escapement teeth 161 and the second stop pallet 220 is released, and another escapement tooth 161 has come into contact with the second stop pallet 220. stop 220, another escapement tooth 161 engages with the first stop pallet 210. This point will be described in detail later.

[0302] In the present embodiment, when the first stop pallet 210 and the second stop pallet 220 engage with the escape wheel 162 of the escape wheel 160, a limiting pin 230 is used to restrict any movement of the anchor unit 170 in order to position the anchor unit 170.

[0303] The first limiting pin 230 is arranged on the opposite side of the escapement mobile 60 relative to the first anchor arm 183, and is fixed to the plate 11, for example, so as to project upwards from the plate 11. The first limiting pin 230 is arranged so as to be aligned in height with the body of the first anchor 182.

[0304] When the first stop pallet 210 engages with the escape wheel 162 of the escape wheel 160, the external lateral surface of the first anchor arm 183 which is the external lateral surface 183a located on the opposite side on the external lateral surface facing the exhaust mobile 160 comes into contact with the limiting pin 230.

[0305] A restriction lever 240, which extends from the part to which the first anchor shaft 181 is attached in the direction away from the second anchor arm 184, is formed as part of the body of first anchor 182. When the second stop pallet 220 engages with the escape wheel 162 of the escape wheel 160, the restriction lever 240 is brought into contact with the limitation pin 230.

(Exhaust operation)

[0306] The exhaust 130 according to the present embodiment, configured as described above, can also have the same operating characteristics as those produced in the first embodiment. The operation of the exhaust 130 according to the present embodiment will be described briefly below.

[0307] In a start-of-operation state, the first working surface 111a of any escapement tooth 161 engages with the engagement surface 210a of the first stop pallet 210, and the lateral surface external 183a of the first anchor arm 183 is in contact with the limiting pin 230 to position the entire anchor unit 170, as shown in Figure 31. The rotation of the escapement mobile 160 is therefore stopped. Furthermore, the free oscillation of the sprung balance 30 has moved the impulse pin 40 in the first direction of rotation M1, and the impulse pin 40 has penetrated into the fork 81. The first contact pallet 150 is is retracted outside the rotational trajectory R of the escape wheel 162.

[0308] The operation of the escapement 130 in response to the alternating rotation of the sprung balance 30 will be described sequentially starting from this start of operation state above.

[0309] When the sprung balance 30 continues to rotate in the first direction of rotation M1 from the state shown in FIG. 31 on the basis of the rotary energy (energy) accumulated in the balance spring, the impulse pin 40 acts in compression on the internal surface of the fork 81 in the first direction of rotation M1. The energy of the hairspring is therefore transmitted to the first anchor 180 via the impulse pin 40.

[0310] When the impulse pin 40 engages with the fork 81, the part in the shape of a crescent moon 43 formed in the large collar 141 prevents the large collar 141 and the dart 82 from being brought into contact with each other. one with the other. The energy of the sprung balance 30 can therefore be efficiently transmitted to the first anchor 180.

[0311] Consequently, the entire anchor unit 170 moves so that the first anchor 180 and the second anchor 190 each pivot, as shown in Figure 32. That is to say, the first anchor 180 pivots counterclockwise around the fourth axis O4, while the second anchor 190 pivots clockwise around the fifth axis O5.

[0312] The pivoting movement of the first anchor 180 causes the separation of the external lateral surface 183a of the first anchor arm 183 with respect to the limiting pin 230. Furthermore, the pivoting movement of the second anchor 190 moves the first stop pallet 210 in a direction away from the escape wheel 162 (direction in which the first stop pallet 210 retracts outside the rotational trajectory R of escape wheel 162) .

[0313] The movement of the first stopping pallet 210 towards a position slightly outside the rotational trajectory R of the escape wheel 162 encourages the first stopping pallet 210 to move away from the tooth of exhaust 161, and allows the engagement between the first stop pallet 210 and the escapement tooth 161 to be released. The exhaust mobile 160, which was stopped, can therefore be released.

[0314] When the escapement mobile 160 resumes its rotation in the counterclockwise direction M4, the first working surface 161a of another escapement tooth 161 comes into contact (collision) with the first contact surface 151 of the first contact pallet 150 which has penetrated inside the rotational trajectory R of the escape wheel 162 while the sprung balance 30 rotates in the first direction of rotation M1, as shown in the figure 33.

[0315] The torque transmitted to the escapement wheel 160 can therefore be transmitted directly to the sprung balance 30 via the first contact vane 150 and the double plate 140, allowing a replenishment of torque from the sprung balance 30.

[0316] When any of the escapement teeth 161 comes into contact with the first contact pallet 150 as described above, the escapement tooth 161 rotates counterclockwise M4 while sliding along the first contact surface 151, and the first contact vane 150 gradually moves in a direction away from the escape wheel 162 (direction in which the first contact vane 150 retracts outside the rotational trajectory R of the escape wheel 162) while the sprung balance 30 turns. Furthermore, when the rotation of the sprung balance 30 moves the first contact pallet 150 in a direction away from the escape wheel 162, the pivoting movement of the second anchor 190 causes the incursion of the second pallet d stop 220 inside the rotational trajectory R of the escape wheel 162.

[0317] Then, when the first contact pallet 150 moves towards a position located outside the rotational trajectory R of the escape wheel 162, the working surface 161a of another escapement tooth 161 comes in contact with the second engagement surface 220a of the second stopping pallet 220 which has penetrated inside the rotational trajectory R of the escape wheel 162, as shown in Figure 34.

[0318] During initial contact, the restriction lever 240 moves towards the limitation pin 230 while the first anchor 180 is not in contact with the limitation pin 230. The first anchor 180 and the second anchor 190 pivot therefore slightly while the escapement tooth 161 remains in contact with the second stop pallet 220. Then, when the restriction lever 240 comes into contact with the limitation pin 230, the first anchor 180 and the second anchor 190 no longer rotate and remain positioned like this. The escapement tooth 161 therefore engages with the second stop pallet 220. The rotation of the escapement mobile 160 is therefore stopped, and the entire anchor unit 170 is thus stopped. Figure 34 shows the state in which the restriction lever 240 is in contact with the limitation pin 230.

[0319] At this time, the direct transmission of torque to the sprung balance 30 ends.

[0320] Immediately afterwards, the impulse pin 40 moves away from the inside of the fork 81 and separates from the anchor unit 170 while the sprung balance 30 rotates in the first direction of rotation M1. Subsequently, the inertia of the sprung balance 30 allows it to continue to rotate in the first direction of rotation M1, and the rotational energy of the sprung balance 30 is accumulated in the balance spring. Then, when all the rotational energy is accumulated in the hairspring, the hairspring balance 30 stops rotating in the first direction of rotation M1, maintains a stationary position for a moment, and begins to rotate in the second direction of rotation. rotation M2, which is opposite to the first direction of rotation M1, on the basis of the rotary energy accumulated in the hairspring.

[0321] The impulse pin 40 therefore begins to move again towards the anchor unit 170, or to approach it, while the sprung balance 30 rotates in the second direction of rotation M2 .

[0322] Then, when the impulse pin 40 enters the fork 81 of the anchor unit 170, the impulse pin 40 acts in compression on the internal surface of the fork 81 in the second direction of rotation M2 , as shown in Figure 35. The energy of the hairspring is therefore transmitted to the first anchor 180 via the impulse pin 40.

[0323] Consequently, the entire anchor unit 170 moves such that the first anchor 180 and the second anchor 190 each pivot, as shown in Figure 36. That is, the first anchor 180 pivots clockwise around the fourth axis O4, while the second anchor 190 pivots counterclockwise around the fifth axis O5.

[0324] The pivoting movement of the first anchor 180 causes the restriction lever 240 to separate from the limiting pin 230. Furthermore, the pivoting movement of the second anchor 190 moves the second pallet stop 220 in a direction away from the escape wheel 162 (direction in which the second stop pallet 220 retracts outside the rotational trajectory R of the escape wheel 162).

[0325] The movement of the second engagement surface 220a of the second stopping pallet 220 towards a position located slightly outside the rotational trajectory R of the escape wheel 162 allows engagement between the second engagement surface 220a and the escapement tooth 161 to be released. The exhaust mobile 160, which was stopped, can therefore be released.

[0326] When the escapement mobile 160 restarts its rotation in the counterclockwise direction M4, the first working surface 161a of another escapement tooth 161 comes into contact (collision) with the second contact surface 201 of the second contact pallet 200, which has penetrated inside the rotational trajectory R of the escape wheel 162 while the first anchor 180 pivots, as shown in Figure 37.

[0327] The torque transmitted to the escapement wheel 160 can therefore be transmitted indirectly to the sprung balance 30 via the second contact vane 200 and the first anchor 180, allowing a replenishment of torque from the sprung balance 30.

[0328] When one of the escapement teeth 161 comes into contact with the second contact pallet 200 as described above, the escapement tooth 161 rotates counterclockwise M4 while sliding along the second contact surface 201, and the second contact vane 200 moves gradually in a direction away from the escape wheel 162 (that is to say a direction in which the second vane contact 200 retracts outside the rotational trajectory R of the escape wheel 162) while the first anchor 180 pivots. Furthermore, when the pivoting movement of the first anchor 180 moves the second contact vane 200 in the direction away from the escape wheel 162, the pivoting movement of the second anchor 190 causes the incursion of the first stop pallet 210 inside the rotational trajectory R of the escape wheel 162.

[0329] Then, when the second contact pallet 200 moves to a position located outside the rotational trajectory R of the escape wheel 162, the working surface 161a of another escapement tooth 161 comes in contact with the first engagement surface 210a of the first stopping pallet 210 having penetrated inside the rotational trajectory R of the escape wheel 162, as shown in Figure 38.

[0330] Upon initial contact, the first anchor 180 moves toward the limiting pin 230 as it pivots clockwise, but it is not in contact with the limiting pin 230. The first anchor 180 and the second anchor 190 therefore pivot slightly while the escapement tooth 161 remains in contact with the first stop pallet 210. Then, when the external lateral surface 183a of the first anchor 180 comes into contact with the limitation pin 230, the first anchor 180 and the second anchor 190 no longer pivot and remain positioned like this. The escapement tooth 161 therefore engages with the first stop pallet 210. The rotation of the escapement mobile 160 is therefore stopped, and thus the entire anchor unit 170 is stopped. Figure 38 shows the state in which the outer side surface 183a of the first anchor 180 is in contact with the limiting pin 230.

[0331] At this time, the indirect transmission of torque to the sprung balance 30 ends.

[0332] As described above, the escapement 130 according to the present embodiment also alternately performs a direct transmission of torque and an indirect transmission of torque during an alternating movement of the sprung balance 30 in order to transmit the transmitted torque to the escape wheel 160 to the sprung balance 30 and replenish the sprung balance 30 with torque.

[0333] Furthermore, also in the present embodiment, the rotation of the escapement mobile 160 is controlled so that the ratio between the first rotational action angle θ1 and the predetermined rotational action angle θ3 , according to which the escapement mobile 160 rotates following an alternating back-and-forth movement of the sprung balance 30, i.e. greater than 50% but smaller than 75%, as shown in Figures 39 and 40.

[0334] Specifically, the rotation of the escape wheel 160 is controlled so that the ratio between the first rotational action angle θ1 and the predetermined rotational action angle θ3, according to which the escape wheel 160 rotates following an alternating movement of the sprung balance 30, is approximately 55.6%.

[0335] Control of the rotation of the exhaust wheel 160 is described in detail in the following.

[0336] In the operation described above, the escapement wheel 160 rotates by an amount corresponding to one tooth during an alternating back-and-forth movement of the sprung balance 30. The angle of action predetermined rotational θ3, according to which the escapement mobile 160 rotates during an alternating movement of the sprung balance 30, is therefore 45 degrees, as shown in Figures 39 and 40.

[0337] The escapement wheel 160 rotates during the period corresponding to the transition between the state shown in Figure 31 (state in which the working surface 161a of an escapement tooth 161 is engaged with the first surface engagement 210a of the first stop pallet 210) and the state shown in Figure 34 (state in which the working surface 161a of the escapement tooth 161 is engaged with the second engagement surface 220a of the second stop pallet 220) while the sprung balance 30 rotates in the first direction of rotation M1. The torque is then transmitted directly to the sprung balance 30 during this period.

[0338] The angle at which the escape wheel 160 rotates from the state shown in Figure 31, shown by a long dotted line followed by a short double dotted line to the state shown in Figure 34, drawn in solid lines, corresponds to the first rotational action angle θ1, shown in Figure 39, and is 25 degrees according to the present embodiment.

[0339] The escape wheel 160 continues to rotate during the period going from the state shown in Figure 35 (state in which the working surface 161a of an escapement tooth 161 comes into engagement with the second surface d engagement 220a of the second stop pallet 220) in the state shown in Figure 38 (state in which the working surface 161a of an escapement tooth 161 engages with the first engagement surface 210a of the first stop pallet 210) while the sprung balance 30 rotates in the second direction of rotation M2. The torque is transmitted indirectly to the sprung balance 30 during this period.

[0340] The angle at which the escape wheel 160 rotates from the state shown in Figure 35, shown by a long dotted line followed by a short double dotted line to the state shown in Figure 38, drawn in solid lines, corresponds to the second rotational action angle θ2, shown in Figure 40, and is 20 degrees according to the present embodiment.

[0341] Consequently, also in the present embodiment, the ratio between the first rotational action angle θ1 (25 degrees) and the predetermined rotational action angle θ3 (45 degrees), by which the mobile of escapement 160 rotates during an alternating movement of the sprung balance 30, is set at approximately 55.6%. The exhaust 130 according to the present embodiment can therefore have the same operating characteristics as those provided by the exhaust 13 according to the first embodiment.

[0342] Furthermore, in the exhaust 130 according to the present embodiment, the first anchor 180 comprises the first contact pallet 150, and the second anchor 190 comprises the first stop pallet 210 and the second stop pallet 220. The position of the first anchor 180 relative to the escapement mobile 160 and the position of the second anchor 190 relative to the escapement mobile 160 can therefore be arranged freely and carried out under few constraints, the first anchor 180 and the second anchor 190 can be arranged in an optimal arrangement for both impact and arrest. An optimal design leading to further improvement in terms of torque transmission efficiency is therefore easily achieved.

[0343] In the third embodiment described above, the anchor unit 170 is formed of two anchors (first anchor 180 and second anchor 190), this is not absolutely necessary, and it could be formed of three or more anchors.

[0344] In the above, embodiments of the invention have been described which are given by way of example, but are not intended to limit the scope of the invention. The embodiments could be implemented in a variety of other forms, deleting, replacing, or changing certain features to the extent that such deletions, replacements, or changes do not depart from the substance of the invention. The embodiments and variations thereof include, for example, variations that one skilled in the art could easily design, variations substantially identical to one of the embodiments and variations thereof, and shapes equivalent thereto.

[0345] The above embodiments have been described, for example, with reference to a configuration in which the energy produced by the hairspring housed in the movement barrel is transmitted to the escapement mobile by way of example , but this is not essential for the realization of the invention. For example, a mainspring provided in a component other than the movement barrel could transmit energy to the escapement mobile.

[0346] In each of the embodiments described above, a manually wound movement, in which a crown is used to manually wind the mainspring, is given by way of example, but this is not necessary either for the realization of the invention. For example, a self-winding movement including an oscillating weight could also be used.

[0347] The above embodiments have been described, for example, with reference to the case where the pallets are each formed by an artificial precious stone consisting, for example, of ruby, but this is not necessary either for the realization of the invention. For example, the pallets could each be made, for example, of another fragile material or of a metallic material, such as an iron-based alloy. In any case, the material, shape, and other factors of each of the pallets can be appropriately adjusted as needed as long as the aforementioned functionalities of the pallets are realized.

[0348] In each of the embodiments described above, the relative positioning between the components in the direction of the thickness of the timepiece can be modified appropriately to the extent that the escapement action is carried out. For example, in a longitudinal sectional view, the relative positioning between the large collar, the small collar, the escape wheel, the anchor (including an anchor body, an anchor unit, and the like), and other components can be changed as needed, so that they are swapped with each other, and the directions in which the stinger, vanes (such as entry vane and exit vane) , the engagement pin, and other extended components can be correspondingly changed according to the changed positional relationships.

[0349] Furthermore, the first and second embodiments have been described with reference to the case where the large collar and the small collar are integrally formed in the double plate, but this is not necessary either. For example, in the first and second embodiments, a small collar having a crescent-shaped portion and a large collar including a contact paddle and a pulse pin can be configured to form separate components. one from the other and be combined on a double plate, and the crescent moon-shaped part of the small collar can be arranged as part of the balance shaft. In any case, a specific double tray is not necessarily employed, and any variety of other double trays may be employed in each of the embodiments.

[0350] In each of the embodiments described above, the limiting pin can, for example, constitute a certain type of limiting pin; for example, what is called a solid pin arranged as an integral part of the anchor deck. Furthermore, the anchor may, for example, be formed from an anchor body, a vane, a stinger, and other components integrated with each other via a MEMS manufacturing process, such as LIGA and DRIE, or a MIM process. Furthermore, in each of the embodiments described above, steps, such as the second escapement teeth in the second embodiment, can be produced, for example, at the level of the front end of the wheel. 'exhaust.

[0351] Furthermore, the first embodiment has been described with reference to a typical gear train configuration (front cog), for example, and the cog configuration can be changed appropriately in accordance with the request of patent and other factors of the timepiece. For example, a gear train configuration in which an intermediate escape wheel is disposed between the second mobile and the exhaust mobile can be used. In any case, the invention of the present patent application is applicable without being affected by the gear train configuration.

[0352] The above embodiments have each been described with reference to the case where the escapement mobile has eight escapement teeth. The number of teeth is, however, not limited to eight and can be adjusted as required.

[0353] It may however be noted that the greater the number of escapement teeth, the smaller the angle between the escapement teeth adjacent to each other in the circumferential direction. Conversely, the fewer the number of escapement teeth, the greater the angle between the escapement teeth adjacent to each other in the circumferential direction. The reduction in the number of escapement teeth therefore allows an increase in each first angle of rotational action θ1, through which the escape wheel rotates as part of the direct transmission of torque to the sprung balance, and the second angle of rotational action θ2, by which the escapement mobile rotates in the frame the indirect transmission of torque to the sprung balance. The reduction in the number of escapement teeth therefore allows an increase in torque transmission efficiency.

[0354] For example, considering a case where the quantity of torque transmitted to the sprung balance is 1 when the number of escapement teeth is 15, and a reduction in the number of escapement teeth by 10 increases the quantity of torque transmitted by a factor of approximately 1.2 to 1.3, and decreasing the number of escapement teeth to 8 increases the amount of torque transmitted by a factor of approximately 1.4.

[0355] As described above, it is preferable to reduce the number of escapement teeth because the efficiency of transmitting torque to the sprung balance can be increased even further. For example, in a case where the ratio between the first rotational action angle θ1 and the predetermined rotational action angle θ3, by which the escapement wheel rotates during an alternating movement of the sprung balance, is fixed ( around 66.7%, for example); reducing the number of escapement teeth allows an increase in the predetermined rotational action angle θ3 and the first rotational action angle θ1, allowing an additional improvement in terms of torque transmission efficiency.

[0356] It is therefore preferable to reduce the number of escapement teeth in order to achieve high torque transmission efficiency, and the escapement mobile only needs to have at least two escapement teeth according to the 'invention.

[0357] However, a reduction in the number of escapement teeth causes, for example, a tendency to increase the size of the anchor, and it is consequently difficult to arrange the escapement having a larger size on the plate, and the amount of power transmission loss increases undesirably due to an increase in the moment of inertia of the anchor. Therefore, to design a compact anchor and not encourage the anchor to pivot over a large amplitude, it is preferable to provide a certain number of escapement teeth. It is ideal to adjust the number of escapement teeth to 8 in each of the embodiments described above from the point of view of producing an escapement which not only allows a suitable arrangement of the anchor but a stable operation to reduce power transmission losses.

[0358] Furthermore, in the first and second embodiments described above, the rotation of the escape wheel is controlled such that the ratio between the first rotational action angle θ1 and the action angle predetermined rotational θ3, according to which the escape wheel rotates in a reciprocating movement of the sprung balance, is approximately 66.7%, and in the third embodiment described above, the rotation of the escape wheel is controlled by so that the ratio between the first rotational action angle θ1 and the predetermined rotational action angle θ3 is approximately 55.6%, but this is not necessary, and this ratio could be changed appropriately according to needs.

[0359] The increase in the ratio described above allows the proportion of torque transmitted directly from the escape wheel to the sprung balance to be greater than the proportion of torque transmitted indirectly from the escape wheel to the balance wheel. -spiral, preferably conferring high torque transmission efficiency.

[0360] For example, in the first embodiment, considering a case where the quantity of torque transmitted to the sprung balance is 1 when the ratio between the first rotational action angle θ1 and the rotational action angle predetermined θ3 is approximately 66.7%, an increase in the ratio described above to approximately 73.3% (for example, a predetermined rotational action angle θ3 set at 45 degrees, and a first rotational action angle θ1 set at 33 degrees) increases the amount of torque transmitted by a factor of approximately 1.1, as shown in Figure 42. Additionally, increasing the ratio described above to approximately 80.0% (e.g., via a rotational action angle predetermined θ3 of 45 degrees, and a first rotational action angle θ1 of 36 degrees), the quantity of torque transmitted is increased by a factor of approximately 1.2.

[0361] It is therefore preferable to increase the ratio described above in order to increase the torque transmission efficiency.

[0362] However, on the other hand, an increase in the ratio described above generates a tendency to have too large an angular difference between the first rotational action angle θ1 and the second rotational action angle θ2. In this case, for example, the output vane and the second contact vane of the anchor, the escape teeth, and other components are arranged in a narrow space to achieve the indirect impact in each of the modes of achievement described above. It is therefore difficult to ensure stable operation of the exhaust because sufficient clearance between the components described above cannot be achieved.

[0363] Consequently, from the point of view of producing a reliable exhaust which maintains excellent efficiency in terms of torque transmission, allows good operation of the anchor, and presents stable operating performance, the ratio between the first rotational action angle θ1 and the predetermined rotational action angle θ3 is preferably greater than 50% but less than 75%.

[0364] Furthermore, the ratio between the first rotational action angle θ1 and the predetermined rotational action angle θ3 is even more preferably greater than 50% but less than 56%, as in the third embodiment described above.

[0365] In this case, a large angular difference between the first rotational action angle θ1 and the second rotational action angle θ2 can be avoided, and thanks to this, the needle movement angle can be substantially uniform . In this case, for example, the predetermined rotational action angle θ3 can be set at 45 degrees, and the first rotational action angle θ1 can be set at 25 degrees.

[0366] In the escapement according to the invention, however, the first rotational action angle θ1 and the second rotational action angle θ2 only need to differ from each other (rotational action angles not uniforms). Among other conditions, it is further preferable to use the condition that the first rotational action angle θ1 is larger than the second rotational action angle θ2.

Claims (10)

1. Association of an escapement (13,100,130) and a sprung balance (30), the escapement (13,100,130) comprising: an exhaust wheel (60) which rotates around a first axis (O1) using transmission energy; And a control element (70) which allows the escape wheel (60) to rotate and stops on the basis of the rotation of said sprung balance (30), the latter performing an alternating rotation around a second axis (O2) according to a first direction of rotation (M1) and a second direction of rotation (M2) opposite each other, the escape wheel (60) directly transmitting the energy transmitted to the sprung balance (30) when the sprung balance (30) rotates in the first direction of rotation (M1) and indirectly transmitting the energy transmitted to the sprung balance (30) via the control element (70) when the sprung balance (30) rotates in the second direction of rotation (M2), and the control element (70) controlling the rotation of the escapement mobile (60) in such a way that a first angle of rotational action (θ1) traveled within the framework of the direct transmission of the energy of the mobile escapement (60) to the sprung balance (30) differs by a second angle of rotational action (θ2) traveled as part of the indirect transmission of energy from the escapement mobile (60) to the sprung balance (30 ), the control element (70) controlling the rotation of the escapement wheel (60) in such a way that the first rotational action angle (θ1) is greater than the second rotational action angle (θ2). 2. Association according to claim 1, in which the sprung balance (30) is equipped with a contact pallet (50) configured to be brought into contact with escapement teeth (63) of the escapement wheel (60), the control element (70) comprising an anchor (71) which includes an entry vane (72) and an exit vane (73) configured to be engaged with escapement teeth (63) and released from the latter, and which is able to pivot on the basis of the rotation of the sprung balance (30), and when the sprung balance (30) rotates in the first direction of rotation (M1), the engagement between any of the escapement teeth (63) and the input pallet (72) is released, and after another escape tooth (63) comes into contact with the contact pallet (50), another escape tooth (63) comes into engagement with the outlet pallet (73), and when the sprung balance (30) rotates in the second direction of rotation (M2), the engagement between any of the escapement teeth (63) and the output pallet (73) is released, and after the escape tooth (63) slides along a sliding surface formed on the outlet vane (73) and moves relative to the latter, another of the escape teeth (63) comes into engagement with the input palette (72). 3. Association according to claim 2, the exhaust mobile (60) having a two-layer structure comprising a first escape wheel (110) having first so-called escape teeth (111), and a second escape wheel (120) which is arranged superimposed on the first escape wheel (110) in the axial direction of the first axis (O1), and has second so-called escape teeth (121), at least the contact paddle (50) being configured to be able to be brought into contact with the first escapement teeth, and at least the exit vane (73) being configured to be able to be engaged with and released from the second escapement teeth. 4. Association according to claim 1, in which the sprung balance (30) is equipped with a first contact pallet (150) configured so as to be able to be brought into contact with escapement teeth (63) of the escapement wheel (60), the control element (70) comprises an anchor unit (170) which is formed from a plurality of anchors and pivots based on the rotation of the sprung balance (30), the anchor unit (170) comprises a second contact vane (200) configured so as to be able to be brought into contact with the escapement teeth (63), and a first stop vane (210) and a second stop pallet (220) configured so as to be able to be engaged with and released from the escapement teeth (63), when the sprung balance (30) rotates in the first direction of rotation (M1), the engagement between one of the escapement teeth (63) and the first stopping pallet (210) is released, and after another escape tooth (63) comes into contact with the first contact pallet (150), another escape tooth (63) engages with the second stop pallet (220), and when the sprung balance (30) rotates in the second direction of rotation (M2), the engagement between one of the escapement teeth (63) and the second stop pallet (220) is released, and after Another of the escape teeth (63) comes into contact with the second contact vane (200), another of the escape teeth (63) engages with the first stop vane (210). 5. Association according to one of claims 1 to 4, in which the control element (70) controls the rotation of the escapement wheel (60) in such a way that the ratio between the first rotational action angle (θ1) and a predetermined rotational action angle (θ3) corresponding to the sum of said first rotational action angle (θ1) and said second rotational action angle (θ2) according to which the escapement wheel (60) rotates during an alternating movement of the sprung balance (30) is more larger than 50% but smaller than 75%. 6. Association according to claim 5, in which the control element (70) controls the rotation of the escapement wheel (60) in such a way that the ratio between the first rotational action angle (θ1) and the predetermined rotational action angle (θ3) is greater than 50%, but less than 56%. 7. Association according to claim 1, in which the number of escapement teeth (63) of the escapement mobile (60) is at least equal to two. 8. Association according to one of claims 2 to 7, in which the escape teeth (63) of the escapement mobile (60) are eight in number. 9. Timepiece movement (10) comprising: an association (30) according to one of claims 1 to 8; a regulator (14) including said sprung balance (30); And a gear train (12) which transmits the transmission energy to the exhaust mobile (60). 10. Timepiece (1) comprising: a timepiece movement (10) according to claim 9; And a display needle which rotates at a rotation speed adjusted by the exhaust (13) and the regulator (14).