CH717089A2 - Exhaust and regulator assembly, timepiece movement and timepiece. - Google Patents

Abstract

The invention relates to an escapement and regulator assembly, a timepiece movement and a timepiece having excellent running time. The assembly (13) comprises a hairspring; a sprung balance (40) which rotates alternately in a first direction of rotation (M1) and in a second direction of rotation (M2) about a first axis (O1); an escapement (14) comprising an anchor (70) which pivots about a second axis (02) and an escapement mobile (60); and a plate (45) which transmits a torque from the escapement (14) to the sprung balance (40). The escapement (14) transmits torque to the sprung balance (40) by means of at least two pulses during one cycle of the sprung balance (40). The balance of spring balance (40) torque is defined as the difference obtained by subtracting the balance spring torque from the torque received by the spring balance (40) from the escapement (14). The plate (45) is provided in such a way that the balance of torque of the sprung balance at the final instant of each pulse of the escapement (14) is identical.

Description

Background of the invention

1. Field of the invention

The present invention relates to an exhaust and adjustment device, a timepiece movement and a timepiece.

2. Description of the related prior art

[0002] A mechanical timepiece generally comprises an escapement which uses regular alternating rotation of a sprung balance to regulate, with constant oscillation, a cog and which transmits power to the sprung balance for its reciprocating rotation. . This type of exhaust has evolved by means of repeated improvements and the like from the related prior art, and different types of exhaust are offered today.

The Swiss lever escapement is widely known as the escapement which occupies a predominant place in mechanical timepieces.

An escapement mainly comprises an escapement mobile, a plate provided on the sprung balance and an anchor which pivots according to the reciprocating rotation of the sprung balance and which comprises an inlet pallet and an outlet pallet which are able to separate from a toothing of the exhaust pinion. The inlet pallet and the outlet pallet separate alternately from the teeth of the escape wheel set when the anchor pivots.

In the Swiss lever escapement, since the inlet pallet and the outlet pallet are alternately engaged with and separated from the teeth of the exhaust mobile while the anchor pivots, the rotation of the mobile exhaust can be controlled, and the torque transmitted to the exhaust mobile can be indirectly transmitted to the sprung balance via the anchor due to a pulse when the teeth of the exhaust mobile is in contact with the pallet. input and a pulse when the teeth of the exhaust mobile is in contact with the output pallet, the sprung balance can thus be supplied with energy.

However, it is generally known that the Swiss lever escapement has a low transmission efficiency of the torque transmitted from the escapement mobile to the sprung balance by the anchor (exhaust efficiency), and there is room for improvements.

[0007] Consequently, in order to improve the torque transmission efficiency, it is known, for example, a Swiss lever escapement having a rotational angle of operation of the exhaust mobile which is not identical between the stage where the teeth of the exhaust mobile is in contact with the input pallet and the step where the teeth of the exhaust mobile are in contact with the output pallet (for example, see the description of the invention of the patent Switzerland No. 570644 (PTL1)).

In this case, the distribution of supply between the amount of transmission of the torque transmitted from the input pallet to the sprung balance via the anchor and the amount of transmission of the torque transmitted from the output pallet to the balance- hairspring by the anchor can be brought to an optimum distribution, and the torque transmission efficiency can be improved.

As another example, there is known a Swiss lever escapement comprising an escapement mobile having a two-stage (two-layer) structure in which a first escape wheel and a second escape wheel are coaxially the one on top of the other, in which an input vane and a toothing of the first escape wheel cooperate with each other, and in which an output vane and a toothing of the second escape wheel cooperate with each other (e.g., see Japanese Patent No. 4894051 (PTL 2) and European Patent Application No. 1914605 (PTL 3)).

In this case, since the combination of the input pallet and the first escape wheel and the combination of the exit pallet and the second escape wheel can be designed independently, as in the case described above, it is possible to ensure that the operating rotational angle of which the escape wheel rotates when the teeth of the first escape wheel is in contact with the input pallet and the operating rotational angle which rotates the exhaust mobile when the teeth of the second escape wheel is in contact with the output pallet are different, and the torque transmission efficiency can be improved.

In addition, as another example, it is known a Swiss lever escapement comprising an exhaust mobile having a first exhaust teeth and a second exhaust teeth offset in the direction of the thickness, and the pallet inlet and the first exhaust toothing cooperate with each other, while the outlet vane and second exhaust toothing cooperate with each other (e.g. see JP-A-2018 -48958 (PTL 4)).

In this case, as the first exhaust teeth and the second exhaust teeth can be designed independently, as in the case described above, we can ensure that the rotational angle of operation which rotates the exhaust mobile when the first exhaust teeth is in contact with the input vane and the operating angle at which the exhaust mobile rotates when the second exhaust teeth is in contact with the output vane are different, and the torque transmission efficiency can be improved.

However, as the various Swiss lever escapements mentioned above are escapements of the type called indirect impulse which transmit the torque from the escapement mobile to the sprung balance via the anchor, the torque transmission efficiency n ' is not enough, and there is still room for improvement.

[0014] Consequently, as an escapement having a higher torque transmission efficiency than the Swiss lever escapement, an escapement called the semi-direct-semi-indirect impulse type is known (G. Daniel coaxial escapement) in which the torque transmitted to the escapement mobile is transmitted to the sprung balance in a manner which alternates an indirect torque transmission via the anchor and a direct torque transmission without passing through the anchor (for example, see the European patent application No. 0018796 (PTL 5) and Japanese Patent No. 6558761 (PTL 6)).

The semi-direct-semi-indirect impulse type escapement comprises an anchor provided with a first impulse vane, as well as a second impulse vane attached to the sprung balance. The first impulse vane and the second impulse vane may alternately come into contact with an escape wheel when the anchor pivots. In the escapement thus configured, as the first impulse paddle comes into contact with the escape wheel when the anchor pivots, the torque transmitted to the escapement mobile can be indirectly transmitted to the sprung balance via the anchor by an impulse when the escape wheel is in contact with the first impulse paddle, and the sprung balance can be replenished with energy. In addition, since the second impulse vane comes into contact with a tooth of the escape wheel when the sprung balance rotates, the torque transmitted to the escapement mobile can be directly transmitted to the sprung balance by an impulse when the spring balance is turned. escape wheel is in contact with the second impulse vane, and the sprung balance can be replenished with energy. Therefore, the semi-direct-semi-indirect impulse type escapement is considered to be an escapement having better torque transmission efficiency (exhaust efficiency) than the Swiss lever escapement.

In the related prior art escapements, the torque transmitted from the escapement to the sprung balance is uniform due to a difference in the pulses. For this reason, when the mainspring of the energy source is disarmed and the torque transmitted to the exhaust mobile decreases, the final instant of one of the pulses takes place earlier than the final instant of the another impulse, and the torque applied to the sprung balance from the escapement is smaller than the torque of the hairspring acting on the sprung balance. When the torque applied to the sprung balance from the escapement at the final moment of the impulse is smaller than the hairspring torque acting on the sprung balance, the operation of the escapement stops without the end of the momentum is reached. Therefore, in the related prior art exhausts, there is room for improvements to prevent an early shutdown of the exhaust operation due to a decrease in power to the power source. and increase the running time of the exhaust.

Summary of the invention

One aspect of the present application is to provide an escapement and adjustment device, a timepiece movement and a timepiece having excellent running time.

The exhaust and adjustment device according to demand comprises a hairspring, a sprung balance which rotates alternately in a first direction of rotation and in a second direction of rotation about a first axis as the hairspring expands and contracts, the first direction of rotation and the second direction of rotation being opposite to each other, an escapement comprising an anchor which pivots about a second axis and an escapement mobile which is able to be separate from the anchor, and a torque transmission member which transmits torque from the escapement to the sprung balance, in which the escapement applies torque to the sprung balance by means of at least two pulses during a cycle of the sprung balance, and when a balance spring balance is defined as the difference obtained by subtracting the balance spring torque from the torque received by the sprung balance from the escapement, the torque transmission member is provided as such manner that the balance of the balance spring balance at the final instant of each pulse of the escapement is identical, in other words (always) the same (the torque transmission member is designed in such a way that the balance of the balance -spiral at the final moment of the exhaust impulse is identical, in other words the same, whatever the impulse).

According to the request, even if the torque received by the sprung balance from the escapement decreases because the torque received by the exhaust mobile from the energy source decreases, the situation in which the torque at the instant final pulse in any one of the exhaust pulses becomes insufficient sooner than that in another pulse can be avoided. Therefore, the situation where any pulse of the escapement fails to reach the end of the pulse before another pulse can be avoided. Therefore, the running time of the exhaust and tuning unit can be improved.

One possibility is that, in the exhaust and adjustment device described above, the torque transmission member pivots integrally with the sprung balance.

[0021] According to the request, the torque can be efficiently transmitted from the escapement to the sprung balance, by comparison with the configuration in which the teeth mesh (the) one (s) with (the) the other (s) in a torque transmission chain from the torque transmission member to the sprung balance.

One possibility is that, in the exhaust and adjustment device described above, the exhaust mobile cooperates with the torque transmission member and transmits a torque to the sprung balance when the sprung balance pivots in the first direction of rotation, and the escapement mobile cooperates with the anchor and transmits a torque to the sprung balance when the sprung balance pivots in the second direction of rotation.

According to the request, as the exhaust can be configured as an exhaust of the type commonly called semi-indirect-semi direct pulses, the exhaust and adjustment device can have an excellent torque transmission efficiency, compared with the case where the escapement is configured as an escapement of the type commonly called indirect impulse.

[0024] One possibility is that, in the escapement and adjustment device described above, the escapement mobile cooperates with the anchor and transmits a torque to the sprung balance when the sprung balance pivots in the first direction of rotation and when the sprung balance rotates in the second direction of rotation.

According to the request, the running time can be improved in an exhaust and adjustment device comprising an exhaust of the type commonly called indirect impulse such as a Swiss lever escapement which transmits the torque from the mobile of ' escapement to the sprung balance only via the anchor.

In the exhaust and adjustment device described above, the torque transmission member may include a plate pin which is able to separate from the anchor, and, when looking at the axial direction of the first axis, a center of the platform peg may be positioned in a position offset about the first axis, with respect to a virtual straight line passing through the first axis and through the second axis, in a stationary state in which no hairspring torque does not act on the sprung balance.

When looking in the axial direction of the first axis, in the stationary state, in the configuration in which the center of the impulse pin is placed on the virtual straight line passing through the first axis and through the second axis, the balance of the sprung balance at the final moment of the impulse differs (is not the same) according to the direction of rotation of the sprung balance (different impulses). Depending on demand, the torque transmission member can be positioned in such a way that the balance of the sprung balance at the final moment of the pulse (at the final moment of the pulses) of the escapement is the same (identical), whatever the impulse. Therefore, the operation effects described above can be obtained.

In the exhaust and adjustment device described above, when looking in the axial direction, the center of the plate peg can be positioned in a position offset by an angle greater than 0 ° and less than or equal to 15 °, around the first axis, relative to the virtual straight line, in the stationary state.

Here, the stationary position is defined as being the position of the torque transmission member when the sprung balance is in a stationary state. According to this request, the exhaust and adjustment device may be such that the torque transmission member passes the stationary position during the pulse after the exhaust mobile has been released (and therefore has ceased to be stopped. ). Therefore, when the torque transmitted to the exhaust mobile from the power source is lower, the exhaust mobile stops in the occupied position during the pulse, and the ability to restart can be ensured when the transmitted torque. to the mobile exhaust is increased.

The exhaust and adjustment device described above may further include an adjustment unit for adjusting the position of the torque transmission member about the first axis.

According to the request, since the torque transmission member can be positioned in such a way that the balance of the balance spring balance at the final moment of the impulse is the same regardless of the impulse , the operating effects described above can be obtained.

In the exhaust and adjustment device described above, the torque transmission member can be fixed to the sprung balance, and the adjustment unit can include a support which retains the sprung balance rotatably , a stud which is attached to an outer peripheral portion of the hairspring, and a stud holder which carries the stud, the stud holder being attached to a peripheral surface of the support which surrounds the first axis.

According to the request, when the eyebolt holder is assembled to the support, the positions of the sprung balance and of the torque transmission member relative to the support, around the first axis, can be adjusted by adjusting the position of the eyebolt relative to the support, around the first axis.

In the exhaust and adjustment device described above, the torque transmission member can be fixed to the sprung balance, and the adjustment unit can include a sprung balance shaft, and a ferrule which is mounted on the shaft and fixed to an inner end of the hairspring.

According to the request, when the ferrule is assembled to the sprung balance shaft, the positions of the sprung balance and of the torque transmission member relative to the support, around the first axis, can be adjusted by adjusting the position of the ferrule with respect to the shaft, around the first axis.

In the exhaust and adjustment device described above, the sprung balance may include a shaft, the torque transmission member may include a mounting portion mounted on the shaft of the sprung balance, and the The adjustment unit may include the sprung balance shaft and the mounting portion.

According to the request, when assembling the mounting portion of the torque transmission member to the shaft of the sprung balance, the position of the torque transmission member relative to the sprung balance, around of the first axis, i.e. the position of the torque transmission member relative to the support, about the first axis, can be adjusted by adjusting the position of the mounting portion of the torque transmission member. torque relative to the shaft, around the first axis.

A timepiece movement according to the request comprises the exhaust and adjustment device described above.

A timepiece according to demand comprises the timepiece movement described above.

[0040] According to demand, a timepiece movement and a timepiece having a long running time can be provided since there is an exhaust and adjusting device having an excellent running time.

[0041] According to demand, an escapement and adjustment device, a timepiece movement and a timepiece which have an excellent running time are proposed.

Brief description of the drawings

Figure 1 is a plan view showing a timepiece according to one embodiment. Fig. 2 is a plan view of a movement according to said embodiment, as seen from the front side. Fig. 3 is a perspective view of an exhaust and adjustment device according to said embodiment, as seen from the front side. Fig. 4 is a plan view of the regulating device according to said embodiment, as seen from the front side. Figure 5 is a cross-sectional view along the line VV of Figure 4. Figure 6 is a perspective view of a sprung balance and a plate according to said embodiment, as seen from the front side. . Fig. 7 is a perspective view of the exhaust and adjustment device according to said embodiment, as seen from the rear side. Fig. 8 is a plan view of the exhaust and the plate according to said embodiment, as seen from the front side. Fig. 9 is a plan view showing an operation of the exhaust and adjustment device according to said embodiment. Fig. 10 is a plan view showing the operation of the exhaust and adjustment device according to said embodiment. Fig. 11 is a plan view showing the operation of the exhaust and adjustment device according to said embodiment. Fig. 12 is a plan view showing the operation of the exhaust and adjustment device according to said embodiment. Fig. 13 is a plan view showing the operation of the exhaust and adjustment device according to said embodiment. Fig. 14 is a plan view showing the operation of the exhaust and adjustment device according to said embodiment. Fig. 15 is a plan view showing the operation of the exhaust and adjustment device according to said embodiment. Fig. 16 is a plan view showing the operation of the exhaust and adjustment device according to said embodiment. Fig. 17 is a plan view showing the operation of the exhaust and adjustment device according to said embodiment. Fig. 18 is a plan view showing the operation of the exhaust and adjustment device according to said embodiment. Fig. 19 is a plan view showing the operation of the exhaust and adjustment device according to said embodiment. Fig. 20 is a plan view showing the operation of the exhaust and adjustment device according to said embodiment. Fig. 21 is a graph showing the balance of sprung balance torque at the final instant of each escapement pulse. Fig. 22 is a graph showing the torque acting on the sprung balance during a direct impulse in the escapement and adjustment device according to said embodiment. Fig. 23 is a graph showing the torque acting on the sprung balance during an indirect impulse in the escapement and adjustment device according to said embodiment. Fig. 24 is a graph showing the torque acting on a sprung balance during a direct impulse in an escapement and tuning device according to a comparison embodiment. Fig. 25 is a graph showing the torque acting on the sprung balance during an indirect pulse in the escapement and adjustment device according to said comparison embodiment. Fig. 26 is a graph showing the torque acting on a sprung balance during a direct impulse in an escapement and adjustment device according to a variant of said embodiment. Fig. 27 is a graph showing the torque acting on the sprung balance during an indirect impulse in the escapement and adjustment device according to the variant of said embodiment.

Description of embodiments

In what follows, an embodiment of the invention will be described with reference to the drawings. In the present embodiment, a mechanical timepiece will be described as an example of the timepiece.

In general, a mechanical body comprising a drive part of the timepiece is called a "movement". When a dial and hands have been attached to the movement and everything has been placed in a timepiece box, the finished product is called a complete timepiece. Of the two sides of the plate which constitutes a plate of the timepiece, the side where the crystal of the watchpiece case is provided (that is to say the side where the dial is provided) is called the “back side” of the movement. Furthermore, of the two sides of the plate, the side where the bottom of the timepiece case is provided (ie the side opposite the dial) is called the “front side” of the movement. In the present embodiment, the direction from the dial to the caseback is defined as the upper side and the opposite side is defined as the lower side.

Figure 1 is a plan view showing a timepiece according to said embodiment.

As shown in Figure 1, a complete timepiece 1, according to the present embodiment, comprises a movement 10 (corresponding to what is called a "timepiece movement" in the appended claims), a dial 3 having graduations for indicating at least one piece of information relating to time, as well as indicating elements including a 5 hour hand, 6 minute hand and 7 seconds hand in a coin box clockwork comprising a caseback (not visible) and a crystal 2.

Figure 2 is a plan view of the movement according to said embodiment, as seen from the front side. In FIG. 2, some components of the movement 10 are omitted in order to make the drawing easier to view.

As shown in Figure 2, the movement 10 comprises a plate 11, which constitutes a plate. The movement 10 comprises a finishing gear 12 and an escape and adjustment device 13 on the front side of the plate 11.

The finishing gear 12 mainly comprises a barrel 20, an intermediate pinion 21, a center mobile 22, an average mobile 23, a second mobile 24 and an intermediate exhaust mobile 25. The barrel 20 is mounted pivoting between the plate 11 and a barrel bridge (not shown), and a mainspring (power source) (not shown) is housed therein. The mainspring is armed by rotating a winding rod 27 coupled to a crown 26 shown in FIG. 1.

The intermediate gear 21, the center mobile 22, the average mobile 23, the second mobile 24 and the intermediate exhaust mobile 25 are pivotally supported between the plate 11 and a gear bridge (not shown ). When the barrel 20 rotates due to the elastic return force produced by the armed mainspring, the intermediate gear 21, the center wheel 22, the average wheel 23, the seconds wheel 24 and the intermediate escape wheel 25 rotate on the basis of rotation.

In other words, the intermediate pinion 21 meshes with the barrel 20 and rotates by the rotation of this barrel 20. The center mobile 22 meshes with the intermediate pinion 21 and rotates by the rotation of this intermediate pinion 21. The mobile of average 23 meshes with the mobile of center 22 and rotates by the rotation of this mobile of center 22. The mobile of seconds 24 meshes with the mobile of average 23 and rotates by the rotation of this mobile of average 23. The seconds hand 7, visible in FIG. 1, is attached to the seconds mobile 24 and this seconds hand 7 indicates the seconds as a function of the rotation of the seconds mobile 24. The seconds hand 7 performs a revolution in one minute, at a speed set by the exhaust and regulating device 13.

When the second mobile 24 rotates, a center mobile (not shown) rotates by rotation. The minute hand 6, shown in FIG. 1, is attached to this central mobile and indicates the minutes as a function of the rotation of this central mobile. The minute hand 6 performs one revolution in one hour, at a speed of rotation set by the escapement and adjustment device 13.

When the center mobile, not shown, rotates, a minute wheel (not shown) rotates by rotation and, in addition, an hour wheel (not shown) rotates according to the rotation of the minute wheel. The hour hand 5, shown in FIG. 1, is attached to the hour wheel and indicates the hours by the rotation of the hour wheel. The hour wheel makes one revolution in 12 hours, at a speed of rotation set by the exhaust and adjustment device 13.

The intermediate exhaust mobile 25 meshes with the second mobile 24 and rotates according to the rotation of this second mobile 24. The intermediate exhaust mobile 25 meshes with an exhaust pinion 61 (see figure 3) an exhaust mobile 60 which will be described later.

Figure 3 is a perspective view of an exhaust and adjustment device according to said embodiment as seen from the front side. In Figure 3, a balance 42, which will be described later, is shown by means of a virtual line (two-dot dashed line) and part of this balance 42 is omitted in order to make the drawing easier to view.

As shown in Figures 2 and 3, the exhaust and adjustment device 13 comprises an exhaust 14 which controls the rotation of the finishing gear 12, a regulating device 15 which controls the exhaust 14, as well as a plate 45 (corresponding to what is called a "torque transmission member" in the appended claims) which transmits a torque from the escapement 14 to a sprung balance 40 of the regulating device 15.

Figure 4 is a plan view of the adjusting device according to the embodiment, as seen from the front side. Figure 5 is a cross-sectional view taken along the line V-V of Figure 4.

As shown in Figures 4 and 5, the regulating device 15 comprises a hairspring 30, a pin support device 33 which holds an outer end of the hairspring 30, the sprung balance 40 which pivots back and forth around a first axis 01 when the hairspring 30 expands and retracts, a cock 16 (corresponding to what is called a "support" in the appended claims) which is fixed to the plate 11 (see figure 2) and which rotatably supports the spring balance 40. The spring 30 is spiral wound, while a ferrule 31 is fixed to an inner end of the hairspring and a stud 34 is fixed to the outer end 30a. The eyebolt 34 can be fixed to an outer peripheral portion of the hairspring 30.

The piton support device 33 comprises the piton 34 and a piton holder 35, which carries the piton 34. The piton holder 35 is fixed to the plate 11. In particular, the piton holder 35 is carried by the rooster 16. The stud holder 35 is attached to an outer peripheral surface 16a of a shaft portion, extending around the first axis O1, of the rooster 16, by means of a stud holder support 36 circular. The eyebolt 35 may be mounted on the outer peripheral surface or an inner peripheral surface, extending around the first axis O1, of the rooster 16 without the eyebolt holder 36. The eyebolt 35 includes a eyebolt arm. 37 which holds the eyebolt 34. The eyebolt arm 37 is shaped with a slot 37a which vertically penetrates the eyebolt arm 37. A cylindrical eyebolt holder plate 38 is fitted in the slot 37a.

The eyebolt 34 is inserted inside the eyebolt retaining plate 38 and it is stably held by the eyebolt retaining plate 38 in a state where a eyebolt 39 prevents it from coming out. The eyebolt 34 holds the outer end of the hairspring 30 by, for example, gluing or crimping. Consequently, the outer end of the hairspring 30 is fixed to the cock 16 and to the plate 11.

The sprung balance 40 comprises a balance shaft 41 (corresponding to what is called a "shaft" in the appended claims) and a balance 42. The sprung balance 40 uses the hairspring 30 as a source of energy. to rotate alternately (back and forth) around the first axis 01 with a stable amplitude (pivot angle) corresponding to an output torque of the barrel 20.

In particular, as shown in Figure 4, the sprung balance 40 rotates alternately around the first axis 01 in a first direction of rotation M1 and a second direction of rotation M2, which are opposite to each other . In the present embodiment, in a plan view obtained when looking from the front side of the movement 10, the direction of rotation of the sprung balance 40 when this sprung balance 40 rotates clockwise. around the first axis 01 is called the first direction of rotation M1, while the direction of rotation of the sprung balance 40 when this sprung balance 40 rotates counterclockwise around the first axis O1 is called the second direction of rotation M2.

As shown in Figure 5, the balance shaft 41 is retained, so as to be able to pivot, by the plate 11 and the cock 16, at its two ends in the axial direction. The ferrule 31 is mounted on the balance shaft 41. Consequently, the inner end of the balance spring 30 is fixed to the sprung balance 40. The ferrule 31 is attached to an outer peripheral surface 41a of the balance shaft 41, this outer peripheral surface 41a surrounding the first axis O1. The balance 42 is fixed to the balance shaft 41. The balance 42 is fitted to the balance shaft 41, below the ferrule 31. The shape of the balance 42 is not limited to that of the example. shown and can be freely modified.

As shown in Figure 3, a small rod 43 is provided below a portion of the mounting shaft 41, this portion being a portion for an external adjusted mounting of the balance 42. The small rod 43 has a column shape whose rotational path has a smaller diameter than the plate 45. A crescent-shaped portion 43a, which is recessed by being hollowed out with a curved surface shape on an inner side in the axial direction, is provided in a part of the small rod 43 which is opposite, in the axial direction, a plate pin 50, which will be described later (see also FIG. 6). The crescent-shaped portion 43a has the function of a relief which prevents an anti-tip dart 82 (which will be described later) from coming into contact with the small rod 43 when a fork entry 81 (which will be described later) (see Figure 8) and the chainring pin 50 are engaged. The anti-rollover dart 82 can be brought into sliding contact with the outer peripheral surface of the small rod except at the crescent-shaped portion 43a.

FIG. 6 is a perspective view of the sprung balance and of the plate according to said embodiment, as seen from the front side. In FIG. 6, the balance 42 is shown in virtual lines (phantom with two points) so that the drawing is easier to look at.

As shown in Figure 6, the plate 45 is coaxial with the sprung balance 40 and integral with this sprung balance 40. The plate 45 comprises a plate body 46 (corresponding to what is called a „portion of assembly “in the appended claim) fixed to the balance shaft 41, the platform pin 50 fixed to the platform body 46, as well as a contact vane 55 (impulse vane).

The plate body 46 is mounted on the balance shaft 41. The plate body 46 is adjacent to the lower side of the small rod 43 of the balance shaft 41. The plate body 43 is disposed at a height corresponding to the exhaust mobile 60. The tray body 46 is made of a material having a crystalline orientation such as a metallic material or a monocrystalline silicon. A process for making the tray body 46 can be, for example, electroforming, the LIGA process including an optical process such as the photolithography technique, the DRIE process, metal powder injection molding (referred to as its acronym MIM stands for “Metal injection molding”), or the like. However, the invention is not limited to this and the tray body 46 can be made by other methods.

The tray body 46 is formed with a through hole 47 which penetrates the tray body 46 vertically and with a slot 48 extending in a U-shaped radial direction and open outwardly in a radial direction. As seen in the axial direction of the first axis O1, the through hole 47 has a flat surface on the outer side in a radial direction and has a semicircular shape bulging in an arc on the inner side in the radial direction.

The platform pin 50 is driven into the through hole 47. The platform pin has a semicircular shape in a plan view and has a flat surface 51 on the outer side in a radial direction and an arcuate surface 52 on the inner side in the radial direction, which corresponds to the shape of the through-hole 47. The plate peg 50 is made of an artificial stone such as ruby. The platen pin extends upwardly more than the platen body 46. Therefore, the platen peg 50 can be brought into contact with the anchor 70 (which will be described later), which is disposed above. of the exhaust mobile 60 (see FIG. 3). The chainring pin 50 rotates alternately around the first axis 01 in synchronization with the sprung balance 40 and separably engages with the fork entry 81 (which will be described later) (see Figure 8) at middle of the stone's rotation 50.

The contact pallet 55 is inserted into the slot 48 of the tray body 46 and it is fixed by, for example, an adhesive agent. The contact paddle 55 is made of an artificial stone such as ruby, such as the platen pin 50. The contact paddle 55 has a rectangular plate shape extending in a radial direction with respect to the first axis O1. One end at the end of the contact vane 55 protrudes outward in a radial direction, more than the outer peripheral edge of the platen body 46. The contact vane 55 can be brought into contact with exhaust teeth. 63 (which will be described later) (see FIG. 3) of the escape wheel set (60) and it is a pallet which transmits to the sprung balance 40, the torque transmitted to the escape wheel set 60.

As shown in Figures 3 and 6, a side surface from the tip to the end of the contact pallet 55 is oriented towards the second direction of rotation M2, is flat in a radial direction and forms a contact surface 56 , which can be brought into contact (collision) with an action surface 63a of the exhaust teeth 63. An inclined surface 57 facing the first direction of rotation M1 is provided on the tip at the end of the contact vane 55. The contact vane 55 is fixed in the slot 48 of the tray body 46 so as not to protrude upwardly from the tray body 46. Therefore, it is possible to prevent the contact vane 55 from protruding upwardly from the tray body 46. and anchor 70 (which will be described later) contact each other.

Repeatedly, the contact paddle 55 enters and withdraws from the rotational path R (see Figure 8) of the escape wheel 64 (which will be described later), by the pivoting of the balance -spiral 40. Therefore, the action surface 63a of the escape teeth 63 of the escape wheel 64 can be brought into contact (collision) with the contact surface 56 of the contact vane 55. When the surface action 63a of the exhaust teeth 63 comes into contact with the contact surface 56 of the contact paddle 55, the torque is transmitted from the exhaust mobile 60 to the contact paddle 55.

Figure 7 is a perspective view of the exhaust and adjustment device according to the embodiment, as seen from the rear side.

As shown in Figures 3 and 7, the exhaust 14 comprises the exhaust mobile 60 which rotates due to a torque transmitted from the mainspring of the barrel 20, via the finishing gear 12, as well as an anchor 70 which pivots as a function of the pivoting of the sprung balance and which allows the escapement mobile 60 to rotate and stops. In what follows, the axis of rotation of the anchor 70 is called the second axis of rotation 02 and the axis of rotation of the exhaust mobile 60 is called the third axis of rotation 03.

The exhaust mobile 60 comprises a part with shaft for escape wheel 62 comprising the exhaust pinion 61 which meshes with the intermediate exhaust mobile 25 (see Figure 2), as well as the wheel. exhaust 64 which is integrally attached to the escapement wheel shaft part 62 by, for example, driving or the like and which has a plurality of exhaust teeth 63. In said embodiment, the number of exhaust teeth 63 is eight and the number of teeth of the exhaust pinion 61 is ten, by way of example. However, the invention is not limited to this, the number of exhaust teeth 63 and the number of teeth of the exhaust pinion 61 can be changed as needed.

In addition, the present embodiment is described as an example of the case where the exhaust mobile 60 rotates counterclockwise, when looking from the front side, around the third axis of rotation 03, due to the torque transmitted from the intermediate exhaust mobile 25, via the exhaust pinion 61. The counterclockwise direction for a rotation around the third axis of rotation 03 is called the reverse direction clockwise M3 and the direction opposite to it is called the clockwise direction M4. In addition, the rotational path R traveled by the end of the escape teeth 63 with the rotation of the escape wheel set 60 is simply called the rotational path R of the escape wheel 64 (see FIG. 8).

The exhaust mobile 60 is retained, so as to be able to pivot, by the plate 11 (see FIG. 2) and by a gear bridge (not shown), at both ends in the axial direction of the part with shaft for escape wheel 62.

The escape wheel 64 is made of a material having a crystalline orientation such as a metallic material, monocrystalline silicon or the like, such as the platter body, for example. An example of a method for manufacturing the escape wheel 64 comprises electroforming, the LIGA method comprising an optical method such as the photolithography technique, the DRIE method, metal powder injection molding (designated in English by its acronym MIM for "Metal injection molding"), or the like. However, the invention is not limited to them and the escape wheel 64 can be produced by other manufacturing methods.

The escape wheel 64 comprises a circular hub 65 in a central portion of which an insertion hole 65a is made, and the part with the shaft for an escape wheel 62 is combined with the circular hub 65 by, for example , driving in the insertion hole 65a. The escape wheel 64 comprises eight spokes 66, which extend outwardly, radially, from the circular hub 65 and which are arranged at regular intervals in the circumferential direction. The hub 65 and the spokes 66 are made in one piece.

Each spoke 66 becomes thinner going outwards, radially, and its end to end is slightly curved counterclockwise M3. The end of each spoke 66 forms an escape tooth 63 (and has the function thereof). Therefore, the exhaust mobile 60 in said embodiment has eight exhaust teeth 63. A side surface of each exhaust tooth 63 faces counterclockwise M3 and forms the surface d. The action 63a which contacts the contact vane 55 and which engages an entry vane 72 and an exit vane 73, which will be described later.

The escapement wheel set 60 arranged as described above has the role of directly transmitting the torque received from the intermediate escape wheel set 25, to the sprung balance 40, when the sprung balance 40 pivots in the first direction of rotation M1, and indirectly transmitting the torque received from the second mobile 24, to the sprung balance 40, via the anchor 70, when the sprung balance pivots in the second direction of rotation M2.

The anchor 70 controls the rotation of the exhaust mobile 60, that is to say controls the starts and stops of the rotation of the exhaust mobile 60. The anchor 40 includes the input pallet 72 and the outlet vane 73 which are able to separate from the exhaust teeth 63. The anchor 70 comprises an anchor rod 75, which is a rotation shaft, as well as an anchor body 78 having two anchor rods 76A and 76B, as well as a positioning arm 77.

The anchor rod 75 is coaxial with the second axis 02. The anchor rod 75 is retained, so as to be pivoting, by the plate 11 and the gear bridge (not shown), at both ends according to the axial direction.

The anchor body 78 is fixed to the anchor rod 75 by, for example, driving. The anchor body 78 is made with a flat shape by, for example, electroforming or MEMS technology, and it is disposed above the exhaust mobile 60 and the tray body 46. An insertion hole for attachment. of the anchor rod 75 is formed in a connecting portion 79 connecting the two anchor rods 76A and 76B within the anchor body 78. The anchor body 78 is fixed to and integral with the rod of the anchor. anchor 75, by inserting this anchor rod 75 into the insertion hole, by driving or the like.

Figure 8 is a plan view of the exhaust and the plate according to said embodiment, as seen from the front side. In Figure 8, the anti-rollover dart 82 is shown in virtual line (two-dot dashed line) so that the design is easier to view.

As shown in Figure 8, the anchor rod 76A extends from the connecting portion 79, to which the anchor rod 75 is attached, towards the plate side 45, that is to say in the direction corresponding to the direction of clockwise M4 opposite to the direction of rotation of the exhaust mobile 60. The anchor rod 76B extends from the connection portion 79, to which the anchor rod 75 is fixed, in the direction corresponding to the counterclockwise direction M3 identical to the direction of rotation of the exhaust mobile 60. The arm 77 extends from the connection portion 79, to which the anchor rod 75 is fixed, towards the side remote from the exhaust mobile 60.

A pair of inlet and outlet horns 80 arranged side by side in the circumferential direction around the second axis of rotation 02 is provided at one end at the end of the anchor rod 76A. The interior between the inlet and outlet horns 80 form the fork inlet 81, which opens towards the small rod side 43 of the balance shaft 41 and in which the chainring pin is detachably received. 50, which moves with the reciprocating pivoting of the sprung balance 40.

In addition, the anti-overturning dart 82 is attached to the end at the end of the anchor rod 76A. The anti-tip dart 82 is secured to the anchor stick 76A by being fitted snugly in the tip at the end of the anchor stick 76A, from the top side, by, for example, driving. However, the invention is not limited to this and the anti-overturning dart 82 may be attached at the end to the end of the anchor rod 76A by means of an adhesive agent, crimping or the like.

The anti-rollover dart 82 is placed between the inlet and outlet horns 80 (i.e. on the inside of the fork inlet 81) in a plan view, and it s' extends by projecting slightly more than the input and output horns 80, towards the small rod side 43 of the balance shaft 41. The anti-overturn dart 82 is disposed above the chainring pin 50 and it is fixed so as to be positioned at the same height as the small rod 43 of the balance shaft 41. The end at the end of the anti-overturn dart 82 is directed towards the radial direction, with a slight projection beyond 'a portion of the outer peripheral surface of the small rod 43, except for the crescent-shaped portion 43a, when the plate peg 50 is out of the fork entry 81, and it is received in the portion crescent-shaped 43a when the plate peg 50 is engaged with the fork entry 81.

When the plate peg 50 is outside the fork inlet 81, since the end at the end of the anti-overturning dart 82 is opposite the outer peripheral surface of the small rod 43 in the radial direction , with a small protrusion, for example, the tip at the end of the anti-tip dart 82 can be brought into contact with the outer peripheral surface of the small rod 43 first, even if a disturbance is applied during free oscillation of the sprung balance 40 and the stop of the anchor 70 must be released due to the effect of the disturbance. Therefore, movement of the anchor 70 due to disturbance can be prevented and the anchor 70 can be prevented from being released.

[0091] In addition, the anchor rod 76A is shaped with a pallet mounting hole 83 provided for the attachment of the entry pallet 72 at a portion located on one side of the shank. anchor 75, namely the side of the anti-tip dart 82. The paddle mounting hole 83 vertically penetrates the anchor rod 76A. The entry pallet 72 is a pallet which can be engaged with and separated from the action surface 63a of the escape teeth 63 of the escape wheel 64 and which can stop and release the escape mobile 60.

[0092] The entry pallet 72 is made of an artificial stone such as a ruby, such as the platen peg 50, and it is secured in the pallet mounting hole 83 by, for example, punching, or is fixed by gluing by means of an adhesive agent or the like. The inlet pallet 72 has the shape of a square column extending downward more than the anchor rod 76A and is fixed at a height equivalent to that of the exhaust mobile 60. A side surface of the pallet d 'inlet 72 is oriented in the direction corresponding to the direction of clockwise M4 opposite to the direction of rotation of the exhaust mobile 60 and forms an engaging surface 72a (rest surface) with which the action surface 63a of the escape teeth 63 of the escape wheel 64 is engaged.

A slot 85 for fixing the outlet pallet 73 is provided at the end forming the end of the anchor rod 76B. The slot 85 penetrates the anchor rod 76B up and down and is open at the exhaust movable side 60. The outlet vane 73 is a vane which is able to separate from the surface of the slit. action 63a of the escape teeth 63 of the escape wheel 64, which is designed to stop and release the escape wheel set 60 and which is designed to transmit, to the sprung balance 60, via the anchor 70 , the torque received from the exhaust mobile 60.

The output pallet 73 is made of an artificial stone such as a ruby, such as the plate peg 50, and is fixed in the slot 85 by, for example, driving or is fixed by gluing by means of an adhesive agent or the like. The outlet vane 73 has a rectangular plate shape extending along the slot 85, and is fixed so as to protrude more from the exhaust movable side 60 than the anchor rod 76B. The outlet pallet 73 is formed so as to extend downwards more than the anchor rod 76B, and is fixed at a height equivalent to that of the exhaust mobile 60.

An engaging surface 73a (resting surface) and a sliding surface 73b (impulse surface) are provided on the tip at the end of the output pallet 73 so as to be oriented in the direction corresponding to the direction of clockwise M4 counterclockwise to the direction of rotation of the exhaust mobile 60. The engagement surface 73a is flat according to the slot 85 and can be engaged with the action surface 63a of the tooth. exhaust 63 of the escape wheel 64. The sliding surface 73b is an inclined surface which is positioned on the exhaust movable side 60 with respect to the engaging surface 73a, which extends from the slot side. 85 towards the mobile exhaust side 60 by going counterclockwise M3, which is the direction of rotation of the exhaust mobile 60, the exhaust teeth 63 thus being able to slide.

In particular, the exhaust teeth 63 on the exhaust mobile 60 are configured to slide on the sliding surface 73b after having been released from the engagement surface 73a. When the action surface 63a of the exhaust teeth 63 slides on the sliding surface 73b, a torque is transmitted from the exhaust mobile 60 to the output pallet 73.

The anchor 70 configured in this way pivots about the second pivot axis 02 as a function of the pivoting of the sprung balance 40 as described above. In particular, the anchor 70 pivots around the second axis 02 in the opposite direction to the direction of rotation of the sprung balance 40, by means of the plate pin 50 which moves with the alternating rotation of the sprung balance 40. At this time, the inlet vane 72 and the outlet vane 73 enter and withdraw from the rotational path R of the escape wheel 64, repeatedly, by the pivoting of the anchor 70. For example, therefore, the action surface 63a of the escape teeth 63 of the escape wheel 64 may be engaged with the engaging surface 72a of the input vane 73 or with the engaging surface 73a of the entry vane. the exit pallet 73. In particular, as the entry pallet 72 and the exit pallet 73 are arranged with the second axis 02 sandwiched between them, when an exhaust tooth 63 and the entry pallet 72 are in engagement, the output vane 73 is separated from an exhaust tooth 63, while when a tooth exhaust 63 and the outlet vane 72 are engaged, the inlet vane 72 is separated from an exhaust tooth 63.

More specifically, when the sprung balance 40 pivots in the first direction of rotation M1, the engagement between one of the exhaust teeth 63 and the input vane 72 ceases, one of the exhaust teeth 63 and the vane contact 55 come into contact, then an exhaust tooth 63 and the outlet vane 73 engage with each other. When the sprung balance 40 pivots in the second direction of rotation M2, the engagement between an exhaust tooth 63 and the output vane 73 ceases and, after this exhaust tooth 63 has moved relatively by sliding on the sliding surface 73b of the output vane 73, an exhaust tooth 63 engages the input vane 72. This point will be described in detail later.

The exhaust 14 comprises a limiting pin 90, which positions the anchor 70 when the inlet pallet 72 and the outlet pallet 73 are engaged with the escape wheel 64 of the escape wheel 60. The limiting pin 90 is positioned on the side opposite to the exhaust mobile 60, the anchor rod 76A being disposed between it and this exhaust mobile 60. The limiting pin 90 is arranged between the anchor rod 76A and arm 77 in a plan view, away from anchor rod 76A and shaft 77. The limiting pin is secured so that it points upward, from the platen, for example, and it is positioned at the same height as the anchor body 78.

[0100] Since the limit pin 90 is arranged in this way, the anchor rod 76A and the arm 77 can be brought into contact with the limit pin 90. Therefore, positioning can be achieved by regulating the pivoting of the pin. anchor 70.

[0101] In the exhaust and adjustment device 13 configured as described above, when looking in the axial direction of the first axis O1, a center C of the plate pin 50 is arranged in a position offset by a predetermined angle θ around the first axis O1, with respect to a virtual straight line L passing through the first axis O1 and through the second axis 02, in a stationary state in which the hairspring 30 does not produce any torque on the sprung balance 40 In particular, when looking in the axial direction of the first axis O1, the center C of the platform pin 50 is in a position offset by the predetermined angle θ, in the second direction of rotation M2, with respect to the virtual straight line L. The predetermined angle θ is greater than 0 ° and it is less than or equal to 15 °. Consequently, the plate 45 is provided in such a way that the balance of torque of the sprung balance at the final instant of each pulse of the escapement 14 is constant. This point will be described in detail later. When looking in the axial direction of the first axis O1, the center C of the platform pin 50 is the center between the two ends of the platform pin, in the circumferential direction around the first axis O1.

Let us return to FIG. 5. The exhaust and adjustment device 13 comprises several adjustment units 101, 102 and 103 for adjusting the position of the plate 45 around the first axis O1. The first adjustment unit 101 comprises the cock 16, the eyebolt 34 and the eyebolt holder 35. When the eyebolt 35 is mounted on the rooster 16, the first adjustment unit 101 makes it possible to adjust the positions of the hairspring 30, of the sprung balance 40 and the plate 45 relative to the cock 16, by adjusting the position around the first axis O1, relative to the cock 16. The second adjustment unit 102 comprises the balance shaft 41 and the ferrule 31. When the ferrule 31 is mounted on the balance shaft 41, the second adjustment unit 102 makes it possible to adjust the positions of the sprung balance 40 and of the plate 45 with respect to the cock 16, by adjusting the position around the first axis O1, with respect to to the balance shaft 41. The third adjustment unit 103 includes the balance shaft 41 and the chainring body 46. When the chainring body 46 is mounted on the balance shaft 41, the third adjustment unit 103 makes it possible to adjust the positions of the plate 45 in relation to the sprung balance 40, by adjusting the position around the first axis O1 relative to the balance shaft 41. When looking in the axial direction of the first axis O1, the position of the center C of the plate pin 50 is adjusted by means of one at least adjustment units 101, 102 and 103.

Referring to Figures 9 to 20, we will now describe the operation of the exhaust and regulation device 13 arranged as described above. Figs. 9 to 20 are plan views showing the operation of the exhaust and adjustment device according to said embodiment.

[0104] In a state of start of operation in the following description, as shown in Fig. 9, the action surface 63a of an escape tooth 63 is engaged with the engagement surface 72a of. the inlet pallet 72, and the arm 77 of the anchor 70 is in contact with the limiting pin 90 to position the anchor 70. Consequently, the escape mobile 60 is stopped. The plate pin 50 moves in the first direction of rotation M1 due to the free oscillation of the sprung balance 40, and enters the entry of the pallet 81. The contact pallet 55 is out of the rotational path R escape wheel 64.

From this starting state of operation, the operation of the escapement and adjustment device 13 accompanying the alternating rotation of the sprung balance 40 will be described step by step.

[0106] From the state shown in FIG. 9, when the sprung balance 40 has pivoted more in the first direction of rotation M1 by the elastic energy stored in the hairspring 30, the chainring pin 50 comes into play. contacts and engages the inner surface of the input and output horns 80 which lie in the path of the chainring pin 50 relative to the chainring pin 50 on the inner surface of the fork entry 81 , and pushes the fork input 81 in the first direction of rotation M1. Therefore, the torque from the hairspring 30 is transmitted to the anchor 70, through the chainring pin 50. When the fork inlet 81 and the chainring pin are engaged (interacting) with each other. the other, the small rod 43 and the tray peg do not touch each other since the crescent shaped portion 43a is provided. Therefore, the torque from the hairspring 30 can be efficiently transmitted to the anchor 70.

[0107] Therefore, as shown in Figure 10, the anchor 70 rotates counterclockwise around the second axis 02 when viewed from the front side, and the arm 77 separates from it. limiting pin 90. As anchor 70 pivots, input pallet 72 moves in a direction toward a separation from escape wheel 64 (direction toward withdrawal out of the rotational path R of the wheel. exhaust 64). Then, the input pallet 72 reaches a position slightly offset from the rotational path R of the escape wheel 64, whereby the input pallet 72 can be separated from the escape tooth 63 with which it can be stopped. to be engaged. Consequently, the escape mobile 60 can be released.

When the exhaust tooth 63 and the input vane 72 cease to be engaged, since the input vane 72 has a draw angle, the exhaust mobile 60 momentarily moves back in the direction. clockwise M4 counterclockwise M3, which is its original direction of rotation. After having momentarily retreated, the exhaust mobile 60 resumes its rotation in the anti-clockwise direction M3, by the torque transmitted via the finishing gear 12. In this way, by the momentary recoil of the mobile d In the exhaust 60, the engagement (locking) of the finishing gear 12 can be made more reliable and this finishing gear 12 can operate with stability and with high reliability.

[0109] Then, as shown in Figure 11, while the exhaust mobile 60 resumes its rotation in the anti-clockwise direction M3, the action surface 63a of an exhaust tooth 63 meets (collision) the contact surface 56 of the contact paddle 55 which entered the rotational path R of the escape wheel 64 by rotating with the sprung balance 40 in the first direction of rotation M1. Due to the pulse when the contact paddle 55 is in contact with the escape wheel 64, the torque transmitted to the escape wheel 60 can be transmitted directly to the sprung balance 40 via the plate 45, and the anchor 70 can be continuously rotated to follow the plate pin 50. In this way, by virtue of the fact that the torque transmitted to the escape wheel 60 is transmitted directly to the sprung balance 40, the torque can replenish the sprung balance with energy. 40. When the action surface 63a of the exhaust tooth 63 comes into contact with the contact surface 56 of the contact vane 55, the plate 45 is positioned with an offset in the second direction of rotation M2, relative to to the stationary position (neutral) occupied when the sprung balance is in a stationary state (see figure 8).

[0110] When an exhaust tooth 63 comes into contact with the contact paddle 55 as described above, this exhaust tooth 63 rotates counterclockwise M3 while sliding on the surface of contact 56, and the contact paddle 55 gradually moves in a direction towards a separation of the escape wheel 64 (direction towards a withdrawal from the rotational path R of the escape wheel 64) with the rotation of the balance. hairspring 40. As shown in Fig. 12, when the contact vane 55 moves in the direction toward a separation of the escape wheel 64 due to the pivoting of the sprung balance 40, the exit vane 73 begins to move in. the rotational path R of the escape wheel 64 with the counterclockwise rotation of the anchor 70.

[0111] Then, when the contact vane 55 moves to a position away from the rotational path R of the escape wheel 64, as shown in Figure 13, the contact vane 55 is separated from the escape tooth 63, and the action surface 63a of an escape tooth 63 contacts the engaging surface 73a of the exit vane 73 which has entered the rotational path R of the escape wheel 64. Therefore, escape wheel 64 is in a state where its rotation is stopped (first stop). When the contact paddle 55 is separated from the exhaust tooth 63, the plate 45 is positioned with an offset in the first direction of rotation M1, with respect to the stationary position (neutral).

[0112] At an initial stage of contact, although the anchor rod 76A of the anchor 70 moves towards the limiting pin 90 as the anchor 70 rotates counterclockwise, the rod anchor 76A is not in contact with limiting pin 90. Therefore, anchor 70 rotates slightly while an escape tooth 63 and exit vane 73 are in contact with each other. other. Then, when the anchor rod 76A contacts the limiting pin 90, the anchor 70 is positioned without being able to pivot further. Therefore, the exhaust tooth 63 and the output vane 73 are engaged. Also, the anchor is stopped, and the escape mobile 60 is in a state in which its rotation is stopped (second stop). At this point, operation with direct torque transmission to the chainring pin 50 is finished.

[0113] After that, as shown in Figure 14, the chainring pin 50 moves away from the inside of the fork entry 81 and separates from the anchor 70 as the sprung balance 40 pivots in the first. direction of rotation M1. Then, the sprung balance 40 continues to pivot in the first direction of rotation M1 due to inertia, and the resulting rotational energy is stored in the hairspring in the form of elastic energy. Then, when all the rotational energy (kinetic energy) is stored in the hairspring 30, the sprung balance 40 stops rotating in the first direction of rotation M1, remains stationary for a moment, then begins to pivot in the second direction of rotation M2 reverses the first direction of rotation M1, due to the elastic energy stored in the hairspring 30.

[0114] Consequently, the plate pin 50 begins to move to move closer to the anchor 70 again, as the sprung balance 40 pivots in the second direction of rotation M2.

[0115] Then, as shown in Figure 15, when the plate peg enters the fork entry 81 of the anchor 70, the plate peg 50 contacts and cooperates with the internal surface of the entry horns. and output 80 lying in the path of the chainring pin 50 relative to the chainring pin 50 within the inner surface of the fork entry 81, and pushes the fork entry 81 into the second direction of rotation M2. Therefore, the torque from the hairspring 30 is transmitted to the anchor 70 via the chainring pin 50.

[0116] Therefore, as shown in Figure 16, the anchor 70 rotates around the second axis 02, clockwise when viewed from the front side, and the anchor rod 76A has separated from the limit pin 90. As the anchor 70 rotates, the outlet vane 73 moves in a direction toward a separation from the escape wheel 64 (direction toward a withdrawal out of the rotating path. R of the escape wheel 64). Then, as shown in Fig. 17, the engaging surface 73a of the outlet vane 73 moves to a position slightly away from the rotational path R of the escape wheel 64, whereby the Engaging surface 73a ceases to engage with exhaust tooth 63. Therefore, exhaust mobile 60 ceases to be stopped.

Since the output pallet 73 has a draw angle like the input pallet 72, the exhaust mobile starts again in rotation in the anti-clockwise direction M3 by the torque transmitted via the gear train. finishing 12, after a momentary backward movement clockwise M4. Then, when the exhaust mobile 60 starts rotating again in the anti-clockwise direction M3, as shown in FIG. 18, the exhaust mobile 60 has a relative movement while the exhaust tooth 63 slides. on the sliding surface 73b of the output pallet 73, and rotates counterclockwise M3. Due to the impulse produced during sliding between the output vane 73 and the exhaust tooth 63, the torque transmitted to the exhaust mobile 60 can be transmitted to the anchor 70 via the vane. outlet 73, and a portion of the inner surface of the fork inlet 81, namely the inner surface of the inlet and outlet horn side 80 which is positioned on the side opposite to the direction of advance of the chainring pin 50 by relative to the chainring pin 50, contacts and cooperates with the chainring pin 50. When the engaging surface 73a of the outlet vane 73 contacts the exhaust tooth 63, the chainring 45 is positioned. with an offset in the first direction of rotation M1, with respect to the stationary position (neutral). When the output pallet 73 has separated from the exhaust tooth 63, the plate 45 is positioned with an offset in the second direction of rotation M2, with respect to the stationary position (neutral).

[0118] Consequently, the torque transmitted to the exhaust mobile 60 can be transmitted indirectly to the sprung balance 41 via the anchor 70, and the anchor 70 can be driven in continuous pivoting to follow the plate pin 50. In this way, by virtue of the fact that the torque transmitted to the escape wheel set 60 is transmitted indirectly to the sprung balance 40, this torque can replenish the sprung balance 40 with energy.

[0119] Then, when the output pallet 73 moves to a position outside the rotational path R of the escape wheel 64 due to the pivoting of the anchor 70, as shown in Figure 19, the surface action 63a of an escape tooth 63 contacts the engaging surface 72a of the input vane 72 which has entered the rotational path R of the escape wheel 64. Therefore, the escape wheel 64 is in a state in which its rotation is stopped (first stop).

[0120] At an initial stage of contact, although the arm 77 of the anchor 70 moves towards the limiting pin 90 as the anchor 70 rotates clockwise, the arm 77 is not not in contact with the limiting pin 90. Therefore, the anchor 70 rotates slightly while the exhaust tooth 63 and the input vane contact each other. Then, as shown in Fig. 20, when the arm 77 of the anchor 70 contacts the limiting pin 90, the anchor 70 is positioned without being able to pivot further. Therefore, the exhaust tooth 63 and the input vane 72 are engaged. Consequently, the anchor 70 is stopped and the escape mobile 60 is in a state in which its rotation is stopped (second stop). At this point, the operation with indirect torque transmission to the chainring pin 50 is finished.

[0121] Then, the plate pin 50 comes out of the inside of the fork entry 81 and separates from the anchor 70, as the sprung balance 40 pivots in the second direction of rotation M2. Then, the sprung balance 40 continues its pivoting in the second direction of rotation M2 due to the inertia, and the resulting rotational energy (kinetic energy) is stored in the hairspring 30 in the form of elastic energy. Then, when all the rotational energy (kinetic energy) is stored in the hairspring 30, the sprung balance 40 stops rotating in the second direction of rotation M2, is stationary for a moment, then begins to pivot in the first direction of rotation M1 opposite to the second direction of rotation M2, due to the elastic energy stored in the hairspring 30.

[0122] Then, the escapement and adjustment device 13 repeats the operation described above with the reciprocating rotation of the sprung balance 40. Consequently, the escapement 14 communicates a torque to the sprung balance 40 by means of two pulses during a cycle of the sprung balance 40, these two pulses being a direct pulse, when the escape wheel 64 is in contact with the contact paddle 55 of the plate 45, and an indirect pulse, when the escape wheel 64 is in contact with the outlet pallet 73 of the anchor 70. In other words, while the sprung balance 40 performs a round trip, the escapement and adjustment device 13 consecutively performs (alternates) the transmission. direct torque via the plate 45 which pivots coaxially with the sprung balance 40, and the indirect torque transmission via the anchor 70, which pivots around an axis different from that of the sprung balance 40 , and the balance- hairspring 40 can be replenished with energy. At the same time, the rotation of the escapement mobile 60 can be controlled by the constant oscillation of the sprung balance 40. In other words, the operation of the escapement 14 of the semi-indirect-semi-direct pulse type, which uses both a direct pulse and an indirect pulse, can be obtained and the efficiency of torque transmission can be increased as compared with a Swiss lever escapement of the indirect pulse type of the prior art.

Here, the balance of the spring balance torque is defined as being the difference obtained by subtracting the torque received by the sprung balance 40 from the spring 30 from the torque received by this sprung balance 40 from the escapement 14.

[0124] FIG. 21 is a graph showing the balance of torque of the sprung balance at the final instant of each pulse of the escapement. In FIG. 21, the stationary position of the plate 45 when the predetermined position in the circumferential direction around the first axis O1 is chosen as a reference and that the first direction of rotation M1 with respect to the predetermined position is chosen as positive, is shown in abscissa (horizontal axis). In FIG. 21, the balance of the spring balance at the final moment of the impulse is plotted on the ordinate (vertical axis). In figure 21, a solid line represents the balance of spring balance torque at the final instant of the direct impulse, and a broken line (in dashed line) represents the balance of spring balance torque at the instant end of an indirect impulse. The balance of the sprung balance shown in FIG. 21 is obtained when the torque of the barrel 20 is constant.

[0125] As shown in FIG. 21, the balance of torque of the sprung balance at the final instant of the direct impulse increases when the stationary position of the plate pin 50 is further in the first direction of rotation M1. In other words, when the stationary position of the chainring pin 50 is moved in the second direction of rotation M2, the balance of the sprung balance tends to 0 or less when the torque of the barrel 20 is smaller. Therefore, the forward pulse does not reach the end of the pulse and the operation of the exhaust and regulating device 13 tends to stop. On the other hand, the balance of the balance spring balance at the final instant of the indirect impulse decreases when the stationary position of the plate pin 50 is further in the first direction of rotation M1. In other words, when the stationary position of the chainring pin 50 is moved in the first direction of rotation M1, the balance of the spring balance tends to be 0 or less when the barrel torque is smaller. Consequently, the indirect pulse does not reach the end of the pulse and the operation of the exhaust and regulating device 13 tends to stop. For example, when looking in the axial direction of the first axis O1, in a configuration in which the center C of the platform peg 50 is positioned on the virtual straight line L in the stationary state, the indirect pulse does not can not reach the end of the pulse earlier than the direct pulse.

In the present embodiment, when looking in the axial direction of the first axis O1, the stationary position of the plate 45 is chosen such that the center C of the plate pin 50 of the plate 45 in the stationary position is placed in a position offset by a predetermined angle θ around the first axis O1, relative to the virtual straight line L described above. Therefore, the plate 45 is provided (positioned) so that the balance of spring balance at the final moment of the pulse of the escapement 14 is the same (does not change), regardless of the impulse.

[0127] Fig. 22 is a graph showing the torque acting on the sprung balance during the direct impulse in the escapement and adjustment device according to said embodiment. Fig. 23 is a graph showing the torque acting on the sprung balance during the indirect impulse in the escapement and adjustment device according to said embodiment. In each figure, the pivot angle of the sprung balance 40 when a state in which the torque of the spring 30 does not act on the sprung balance 40 is chosen as corresponding to 0 and the direction of rotation of the balance hairspring 40 is chosen as being positive and is shown on the abscissa (horizontal axis). In each figure, the torque applied to the sprung balance 40 is plotted on the ordinate (vertical axis). In each figure, a continuous line represents the torque received by the sprung balance 40 from the escapement 14 in a first state in which the mainspring housed in the barrel 20 is sufficiently armed, a broken line (in broken line) represents the torque received by the sprung balance 40 from the escapement 14 in a state in which the mainspring housed in the barrel 20 is disarmed starting from the first state, and the phantom line represents the torque received by the sprung balance 40 from the hairspring 30.

As shown in Figures 22 and 23, the balance of torque of the sprung balance at the end of each pulse of the escapement 14 is the same in the first state in which the mainspring of the barrel 20 is sufficiently charged. Therefore, even if the mainspring of the barrel 20 disarms and the torque received by the sprung balance from the escapement is small, the situation in which, at the final moment of the pulse, the torque in the one of the direct and indirect pulses becomes insufficient sooner than that in the other pulse can be avoided.

[0129] Now, a comparison embodiment will be described, corresponding to a case in which, when looking in the axial direction of the first axis O1, the stationary position of the plate 45 is adjusted in such a way that the center C of the platform pin 50 of the platform 45 in the stationary position is positioned on the virtual straight line L described above. Fig. 24 is a graph obtained with the comparison embodiment and corresponds to Fig. 22. Fig. 25 is a graph obtained with the comparison embodiment and corresponds to Fig. 23.

[0130] As shown in FIGS. 24 and 25, the balance of the balance spring balance at the final instant of the indirect impulse from the escapement 14 is smaller than the balance of the balance spring balance at the end. final instant of the direct pulse in the first state in which the mainspring of the barrel 20 is sufficiently armed. Therefore, when the torque received by the sprung balance from the escapement 14 becomes small, the balance of sprung balance at the final moment of the impulse, in the indirect impulse, becomes zero earlier than that. in the direct impulse, and the indirect impulse is in a state of not being able to reach the end of the impulse earlier than the direct impulse.

[0131] Therefore, according to the present embodiment, it is possible to prevent one of the direct and indirect pulses from failing to reach the end of the pulse earlier than the other. Therefore, the running time can be improved with the exhaust and tuning device 13.

[0132] The plate 45 pivots integrally with the sprung balance 40. Consequently, the torque transmitted from the escapement 14 to the sprung balance 40 can be transmitted efficiently by comparison with the configuration in which the teeth mesh (the). one (s) with (the) the other (s) on a torque transmission chain from the plate to the sprung balance.

[0133] The escape wheel set 60 comes into contact with the plate 45 and transmits a torque to the sprung balance 40 when the sprung balance 40 pivots in the first direction of rotation M1. The escape wheel set 60 comes into contact with the anchor 70 and transmits a torque to the sprung balance 40 when the sprung balance 40 pivots in the second direction of rotation M2. According to this configuration, since the escapement 14 can be of the type commonly called semi-indirect-semi-direct impulse, the escapement 14 can have an excellent torque transmission efficiency, compared to the case where the escapement is configured as an escapement. of the type commonly called indirect impulse such as the Swiss lever escapement.

Here, when looking in the axial direction of the first axis O1, in the stationary state in which no torque from the hairspring 30 acts on the sprung balance 40, in the configuration in which the center C of the plate pin 50 of the plate 45 is positioned on the virtual straight line L passing through the first axis O1 and through the second axis 02, the balance of torque of the sprung balance at the final moment of the impulse differs depending on the direction of rotation of the sprung balance 40 (different impulses). In the present embodiment, when looking in the axial direction of the first axis O1, the center C of the platform peg 50 is placed in a position offset around the first axis 01, with respect to the virtual straight line L , in the steady state. According to this configuration, the plate 45 can be arranged in such a way that the balance of torque of the sprung balance at the final instant of any impulse is the same. Therefore, the operation effects described above can be obtained.

[0135] In addition, when looking in the axial direction of the first axis O1, the center C of the platform pin 50 is placed in a position offset around the first axis O1, by an angle greater than 0 ° and less than or equal to 15 °, on the side of the third axis 03, with respect to the virtual straight line L, in the stationary state. According to this configuration, the exhaust and adjustment device 13 can be made in such a way that the plate passes through the stationary position during the impulse after the exhaust mobile 60 has been released (ceased to be stopped). Therefore, when the mainspring of the barrel 20 is disarmed and the torque transmitted to the exhaust mobile 60 is reduced, this exhaust mobile 60 stops in a position during the pulse, and the ability to restart can be. ensured when the mainspring is reset and when the torque transmitted to the exhaust mobile 60 is increased.

The exhaust and adjustment device 13 comprises the adjustment units 101, 102 and 103 for adjusting the position of the plate around the first axis O1. According to this configuration, since the plate 45 is arranged in such a way that the balance of torque of the sprung balance at the final moment of the impulse is the same whatever the impulse, the operating effects described above can be obtained.

In the embodiment described above, the balance of torque of the sprung balance at the final moment of the impulse is the same whatever the impulse, in the first state in which the mainspring is sufficiently armed. However, the balance of sprung balance torque at the final moment of the escapement impulse 14 may be the same regardless of the impulse, in any state in which the mainspring is charged, other than a state in which the balance of torque is zero in at least one of the direct and indirect pulses (a state in which the escapement 14 is stopped).

[0138] Figure 26 is a graph obtained with a variant of said embodiment and corresponds to Figure 22. Figure 27 is a graph obtained with said variant of the embodiment and corresponds to Figure 23.

As shown in Figures 26 and 27, in said variant, the balance of torque of the sprung balance at the final moment of the pulse of the escapement 14 is the same regardless of the pulse, in a state released from the first state in which the mainspring of the barrel 20 is sufficiently charged. Therefore, when the mainspring of the barrel 20 has disarmed, the balance of spring balance torque is zero in both the direct impulse and the indirect impulse. Therefore, the situation where the torque at the final moment of the pulse in one of the direct and indirect pulses becomes insufficient earlier than that in the other pulse can be effectively avoided.

[0140] The invention is not limited to the embodiment which has been described with reference to the drawings, and various modifications can be considered within the technical scope of the invention.

[0141] For example, in said previous embodiment, although the case where the escapement 14 is configured as an escapement of the type commonly called semi-indirect-semi-direct pulses has been described, the configuration of the unit d The exhaust and tuning is not limited to this case. In other words, the escapement can be an escapement commonly referred to as a Swiss lever escapement, in which the torque is transmitted to the sprung balance by indirect pulses when the escapement wheel comes into contact with the paddles of the anchor. when the sprung balance pivots in the first direction of rotation and when it pivots in the second direction of rotation. Even in this case, by positioning the platter pin of the platter in a similar manner to what is done in said previous embodiment, the above-mentioned operating effects can be obtained.

[0142] Although the exhaust mobile 60 has a single-stage (single-layer) structure in said previous embodiment, the exhaust mobile may have a two-stage (two-layer) structure.

[0143] Although the escapement 14 comprises a single anchor in said previous embodiment, the escapement may comprise a pin device comprising several anchors. Also, the escapement can be configured to apply torque to the sprung balance by means of three or more pulses during one cycle of the sprung balance.

[0144] Although the exhaust and adjustment device 13 comprises several adjustment units for adjusting the position of the plate 45 around the first axis O1 in said previous embodiment, at least one of the adjustment units 101, 102 and 103, any, can be provided. The adjustment units for adjusting the position of the plate 45 around the first axis 01 may include the hairspring 30 and a peg which allows a fixed position of the hairspring 30 to be adjusted. In other words, the positions of the hairspring 30, of the balance- hairspring 40 and the plate 45 can be adjusted relative to the cock 16 by adjusting the fixed position of the eyebolt fixed to the cock 16 and to the plate 11 and the fixed position of the outer peripheral portion of the hairspring 30.

[0145] In addition, the constituents of said embodiment described above can be suitably replaced by known constituents without departing from the spirit of the invention.

Claims (12)

1. Exhaust and regulating device, comprising: a hairspring; a sprung balance (40) which rotates alternately in a first direction of rotation (M1) and in a second direction of rotation (M2) around a first axis (O1) as the hairspring expands and contracts, the first direction of rotation and the second direction of rotation being opposite to each other; an escapement (14) comprising an anchor (70) which pivots about a second axis (02), as well as an escapement mobile (60) which is able to separate from the anchor (70); and a torque transmission member (45) which transmits torque from the escapement to the sprung balance; in which the escapement (14) applies a torque to the sprung balance (40) by means of at least two pulses during a cycle of the sprung balance (40), and when a balance of the balance spring balance (40) is defined as being the difference obtained by subtracting the torque of the balance spring (30) from the torque received by the balance spring (40) from the escapement (14), the torque transmission member (45) is provided such that the balance of the balance spring balance at the final instant of each pulse of the escapement (14) is identical. 2. Exhaust and adjustment device according to claim 1, wherein the torque transmission member pivots integrally with the sprung balance. 3. Exhaust and adjustment device according to claim 1 or 2, wherein the escapement mobile cooperates with the torque transmission member and transmits a torque to the sprung balance when the sprung balance pivots in the first direction of rotation, and the escape mobile cooperates with the anchor and transmits a torque to the sprung balance when the sprung balance swivels in the second direction of rotation. 4. Exhaust and adjustment device according to claim 1 or 2, wherein the escapement mobile cooperates with the anchor and transmits a torque to the sprung balance when the sprung balance pivots in the first direction of rotation and when the spring balance pivots in the second direction of rotation. 5. Exhaust and adjustment device according to one of claims 1 to 4, wherein the torque transmission member comprises a chainring pin which is able to separate from the anchor, and when looking in the axial direction of the first axis, a center (C) of the platform peg is positioned in a position offset about the first axis, with respect to a virtual straight line (L) passing through the first axis and by the second axis, in a stationary state in which no hairspring torque acts on the sprung balance. 6. Exhaust and adjustment device according to claim 5, wherein when looking in the axial direction, the center (C) of the platform pin is positioned at a position offset by an angle greater than 0 ° and less than or equal to 15 °, around the first axis, with respect to to the virtual straight line (L), in the stationary state. 7. Exhaust and adjustment device according to claim 5 or 6, further comprising: an adjustment unit for adjusting the position of the torque transmission member about the first axis. 8. Exhaust and adjustment device according to claim 7, wherein the torque transmission member is attached to the sprung balance, and the adjustment unit includes: a support (16) which rotatably retains the sprung balance; a stud which is fixed to an outer peripheral portion of the hairspring; and a eyebolt which carries the eyebolt, the eyebolt being attached to a peripheral surface of the support which surrounds the first axis. 9. Exhaust and adjustment device according to claim 7 or 8, wherein the torque transmission member is attached to the sprung balance, and the adjustment unit includes: a shaft (41) of the sprung balance; and a ferrule (31) which is mounted on the shaft (41) and fixed to an inner end of the hairspring. 10. Exhaust and adjustment device according to one of claims 7 to 9, wherein the sprung balance comprises a shaft (41), the torque transmission member comprises a mounting portion (46) mounted on the shaft (41) of the sprung balance, and the adjustment unit includes: the shaft (41) of the sprung balance; and the mounting portion (46). 11. Timepiece movement, comprising: an exhaust and adjustment device according to one of claims 1 to 10. 12. Timepiece, comprising: a timepiece movement according to claim 11.