CH713705A2 - Mechanism with constant force, movement of timepiece and timepiece. - Google Patents

Abstract

The invention relates to a constant force mechanism (20) comprising: a first power wheel (25) rotates about a first axis of rotation O1; a second power wheel (26) which is disposed coaxially with the first power wheel and is rotatable relative to the first power wheel about the first axis of rotation; a power spring (27) which is disposed between the first power wheel and the second power wheel and transmits stored energy to the first power wheel and the second power wheel; and a cycle control mechanism (22) that intermittently rotates the second power wheel relative to the first power wheel and provides energy to the power spring. The cycle control mechanism comprises a first control wheel (55) which rotates about a second axis of rotation O2 as a function of the rotation of the first power wheel; a second control wheel (26) which is arranged coaxially with the first control wheel and which is able to rotate relative to the first control wheel about the second axis of rotation and which meshes with the second power wheel; and a planetary mechanism (57) which is disposed between the first drive wheel and the second drive wheel and causes, intermittently, depending on the rotation of the first drive wheel, that an engagement pawl equipping the first control wheel engages with and releases itself with a stopwheel equipping the second control wheel. The first power wheel or the first control wheel transmits power from the power spring to an exhaust. Power from a power source is transmitted to the second power wheel or the second drive wheel.

Description

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a torque generating mechanism, a constant force mechanism, a timepiece movement and a timepiece. 2. DESCRIPTION OF THE RELATED ART [0002] In general, in a mechanical timepiece, if the torque (power) transmitted from the barrel bridge to the escapement varies with the fact that the spring of barrel disarms, the angle of oscillation of the sprung balance varies according to the variation of the torque so as to cause that the daytime running (the degree of delay or advance of the timepiece) of the piece d watchmaking is changing. Therefore, in order to suppress the torque transmitted to the exhaust varies, it is known to provide a constant force mechanism within the power transmission from the barrel bridge to the exhaust.

As a constant force mechanism of this type, constant force mechanisms of various types have been proposed. For example, when focusing on cycle control, constant force mechanisms are generally classified into three types, which are the cam type, the wheel type, and the planetary gear type.

The constant-force mechanism of the cam type comprises, for example, a cam follower or a fork which cooperates with a cam connected to an exhaust side wheel and which switches according to the rotation of the cam. The constant force mechanism cyclically engages an engagement and release pawl on the cam follower or fork to engage or disengage with an exhaust wheel coupled to a source side wheel. of power to control a cycle of engagement and release. Therefore, it is possible to arm a constant torque spring between the power source side wheel and the exhaust side wheel.

[0005] In the constant-force mechanism of the wheel type, a power source side wheel and an exhaust side wheel are connected by a differential mechanism. The constant force mechanism is capable of cyclically controlling a phase difference by causing an engagement and release pawl, which engages and releases with a stopping wheel, to enter and exit the housing. a trajectory of the stop wheel. For example, as described in Patent Document 1 (Swiss Patent Application Publication No. 707,938), the planetary gear type constant force mechanism comprises a planetary mechanism which uses a stopwheel as a planetary gear. planetary. The constant force mechanism is able to cyclically control, with the planet mechanism, a phase difference between the power source side wheel and the exhaust side wheel. The planetary gear rotates while rotating to follow an engagement and release pawl on a sun wheel associated with the escape wheel.

However, in a cam-type constant force mechanism, for example, when the engagement rhythms of the escape wheel and the engagement and release pawl with each other and of release of this escape wheel and this pawl of engagement and release from each other shifts for any reason, it is likely that a phenomenon of over-release (commonly so called) occurs in which the constant force spring suddenly disarms excessively.

In this respect, in the constant force mechanism of the wheel type, the over-release occurs less easily due to a structure in which the power source side wheel and the side wheel side wheel exhaust are connected by a differential mechanism. However, since the structure requires a large meshing, the number of components constituting the constant force mechanism is increased. Therefore, a large plan space is needed.

In a constant-force mechanism of the planetary gear type, the over-release occurs less easily than in the constant-force mechanism of the cog wheel type. However, other major functional components must be arranged in the direction of the thickness in order not to prevent rotational and revolution movements of the stop wheel, which is the planetary gear. As a result, the thickness of the complete constant force mechanism is increased.

SUMMARY OF THE INVENTION

The present invention has been designed in view of such circumstances and an object of the present invention is to provide a constant force mechanism, a timepiece movement and a timepiece that can lead to a compact character and to gain space.

[0010] (1) A constant force mechanism according to the present invention comprises: a first power wheel which rotates about a first axis of rotation; a second power wheel which is disposed coaxially with the first power wheel and is rotatable relative to the first power wheel about the first axis of rotation; a power spring which is disposed between the first power wheel and the second power wheel and transmits stored energy to the first power wheel and the second power wheel; and a cycle control mechanism that intermittently rotates the second power wheel relative to the first power wheel and provides power to the power spring. The cycle control mechanism includes a first control wheel which rotates about a second axis of rotation as a function of the rotation of the first power wheel; a second control wheel which is disposed coaxially with the first control wheel and is rotatable relative to the first control wheel, the engagement pawl has an engagement surface with which the control portion with stop gear is engaged and from which the locking gear portion is released, and such that, between the moment when the locking gear portion engages the engaging surface until the in that the staggered portion engaged with the engagement surface is released (ceases to be engaged), the support lever carries the engagement pawl such that a fictitious line extending according to the force resulting from a thrust force, with which the locking gear portion pushes against the engaging surface, and a frictional force generated by the sliding of the locking gear portion on the engagement surface crosses the second axis of rotation.

In this case, when the time since engagement between the stop wheel and the engagement pawle until release between the stop wheel and the engagement pawl is selected as forming a cycle, when one focuses on the rotational torque generated in the support lever that carries the engagement pawl, it is possible to keep constant an average torque on a cycle.

When the stop wheel engages with the engaging surface of the engagement pawl, the stop wheel engages deeply with the engagement pawl at an initial step. . Then, the staggered portion moves toward the end of the pawl end while sliding on the engagement surface in response to the release of the engaging pawl involved in rotation of the support lever. . As a result, the setting becomes progressively shallow (narrow). The stopwheel and the engaging pawl cease to be engaged at a time which occurs when the staggered portion passes over the end of the pawl of engagement.

In a succession of the cycle, since the angle that the engagement surface makes with the staggered portion changes, the direction of the resultant force changes as a result of the change affecting the angle. At this moment, at the moment when the direction of the resultant force crosses the second axis of rotation, the rotation torque normally generated by the support lever is not generated. On the other hand, when the direction of the resultant force decays from the second axis of rotation, the rotational torque is generated as a function of the magnitude of the shift. In particular, before and after the direction of the resultant force crosses the second axis of rotation, counterclockwise rotation torques are generated. In other words, the rotational torque to bring the support lever to the stop wheel is generated in the support lever and the rotational torque to move the support lever away from the stop wheel. is generated in the support lever. Therefore, although there are torque variations of the support lever when considering a cycle (on one cycle), it is possible to maintain constant average torque over one cycle (the average of the torque over one cycle). As a result, it is possible to obtain a constant torque property.

(4) The constant force mechanism may be such that the dummy line crosses the second axis of rotation in an intermediate position between a setting position, where the locking gear portion engages the setting surface. in engagement, and an end of setting position (release position), wherein the stopping portion ceases to engage the engagement surface.

In this case, it is possible to maintain a more stable constant average torque on a cycle. It is possible to obtain a more stable property of constant torque.

(5) The constant force mechanism may further include a power control mechanism that adjusts the power of the power spring through the first power wheel or the second power wheel.

In this case, since it is possible to adjust the power of the power spring, the exhaust can be operated more stably with the constant torque. For example, after the first power wheel, the second power wheel and the power spring have been combined, it is possible to supply power to the power spring. Therefore, it is possible to provide the power adjustment mechanism without worrying about the torque control mechanism. It is easy to adjust the power adjustment mechanism.

(6) The power control mechanism may comprise: an adjusting wheel capable of meshing with the first power wheel or with the second power wheel; and a movable member which moves the adjusting wheel between a meshing position, wherein the adjusting wheel meshes with the first power wheel or with the second power wheel, and a non-meshing position, where the meshing between the adjusting wheel and the first power wheel or with the second power wheel is absent.

In this case, it is possible to adjust the power of the power spring depending on the degree of rotation of the adjusting wheel. Therefore, it is possible to make the adjustment accurately and intuitively. It is easy to carry out the adjustment operation. In addition, by placing the adjusting wheel in the position of absence of meshing, it is possible to interrupt the meshing of the first power wheel or the second power wheel with the adjusting wheel. Therefore, when the power setting is not achieved, it is possible to prevent an unnecessary load (stress) from being rotated from being applied to the first power wheel or the second power wheel.

[0020] (7) The invention also relates to a timepiece movement comprising the constant-force mechanism.

[0021] (8) The invention also relates to a timepiece comprising the movement of a timepiece.

In this case, the timepiece movement and the timepiece include the constant force mechanism that provides compactness and space saving. Therefore, it is possible to obtain a timepiece movement and a timepiece whose size and thickness can be more easily reduced.

According to the present invention, it is possible to obtain a constant force mechanism, a timepiece movement and a timepiece that can reach the goal of being compact and the purpose of allowing a gain of square.

BRIEF DESCRIPTION OF THE DRAWINGS

[0024]

Fig. 1 is an exterior view of a timepiece showing an embodiment of the present invention.

Fig. 2 is a block diagram of a motion shown in FIG. 1.

Fig. 3 is a perspective view of a constant force mechanism shown in FIG. 2.

Fig. 4 is a top view of the constant force mechanism shown in FIG. 3.

Fig. 5 is a sectional view along the line A-B shown in FIG. 4 and represents the constant-force mechanism.

Fig. 6 is a perspective view showing a portion of a second power wheel shown in FIG. 3.

Fig. 7 is a bottom view of the constant force mechanism shown in FIG. 3.

Fig. 8 is a perspective view showing part of a second control wheel and the second power wheel shown in FIG. 3.

Fig. 9 is a perspective view showing a portion of the second power wheel shown in FIG. 3.

Fig. 10 is a perspective view showing the second control wheel and a planetary gear mechanism shown in FIG. 3.

Fig. 11 is a plan view showing a state of engagement between an engagement pallet stone and a stop tooth shown in FIG. 10.

Fig. 12 is a sectional view of the control wheel and a stop wheel shown in FIG. 10.

Fig. 13 is a plan view showing a state of engagement between the engagement pallet stone and the stop tooth shown in FIG. 11.

Fig. 14 is a plan view showing a state in which the engagement pallet stone begins to release from the stop tooth from the state shown in FIG. 13.

Fig. 15 is a plan view showing a state in which the engagement pallet stone is released more from the stop tooth, from the state shown in FIG. 14.

Fig. 16 is a plan view showing a state in which the engagement pallet stone and the stop tooth are released from each other from the state shown in FIG. 4.

Fig. 17 is a plan view showing a state in which a support member of the stop wheel and a second lever member come into contact from the state shown in FIG. 4.

Fig. 18 is a sectional view along the line A-C shown in FIG. 4 and represents the constant-force mechanism.

Fig. 19 is a perspective view of the constant force mechanism and a diagram for explaining a power control mechanism.

Fig. 20 is a diagram showing the torque variations involved in engaging the engagement pallet stone with the stopping tooth and releasing them relative to one another.

Fig. 21 is a perspective view showing a state prior to the assembly of a mechanism for generating a torque shown in FIG. 3 and it is a diagram showing a state in which the first power wheel is placed above the second power wheel to which is assembled a constant force spring.

Fig. 22 is a diagram showing a state in which the first power wheel and the second power wheel are placed one above the other so that a definition segment is in an opening of a hole to sliding, from the state shown in FIG. 11.

Fig. 23 is a diagram showing a state in which the first power wheel and the second power wheel are rotated relative to each other in opposite directions and the definition segment is engaged with the inner side of the borehole. sliding, from the state shown in FIG. 22.

Fig. 24 is a variant diagram according to the present invention and is a plan view showing a state of engagement between the engagement pallet stone and the stop tooth in a fixed gear portion of a external gear type.

Fig. 25 is a plan view showing a state in which the engagement pallet stone begins to release from the stop tooth from the state shown in FIG. 24.

Fig. 26 is a plan view showing a state in which the engagement pallet stone is further released from the stop tooth from the state shown in FIG. 25.

Fig. 27 is a perspective view showing a variant of the torque generating mechanism according to the present invention.

Fig. 28 is a perspective view showing another variant of the torque generating mechanism according to the present invention.

DESCRIPTION OF THE EMBODIMENTS

We will explain below an embodiment according to the present invention, with reference to the drawings. It should be noted that, in this embodiment, a mechanical timepiece is explained as an example of a timepiece. In the drawings, the proportions (scales) of the components are modified where appropriate by the need to show the components at visually recognizable sizes.

Basic constitution of the timepiece [0026] In general, a machine body comprising a driving part of a timepiece is called the "movement". The state of the finished product obtained by attaching a dial and a needle to movement and mounting the movement in a timepiece case is called a "complete" timepiece.

Among the two sides of the plate forming a frame of the timepiece, the side where is the ice of the timepiece box (that is to say the side where the dial is located ) is called the "back side" of the movement. On both sides of the platen, the side where the box bottom of the timepiece box (i.e. the opposite side of the dial) is located is called the "front side" of the movement.

It should be noted that in the following explanations in this embodiment, the dial direction to the box bottom is defined as the upward direction and that the opposite direction is defined as the downward direction. A direction of rotation in the clockwise direction as seen from above, around axes of rotation, is called clockwise, while a direction of rotation in the opposite direction of clockwise as viewed from the top, around axes of rotation, is called the counterclockwise direction.

As shown in FIG. 1, a timepiece in the complete state 1 in this embodiment comprises, within a timepiece box comprising a not shown bottom and a mirror 2, a movement 10 (the timepiece movement according to the present invention), a dial 3 comprising a scale indicating information relating to at least the hour, as well as needles 4 among which an hour hand 5, a minute hand 6 and a seconds hand 7.

As shown in FIG. 2, the movement 10 comprises a movement cylinder 11, which is a power source, a power source side wheel 12 associated with the movement barrel 11, an exhaust 14 regulated by a speed regulator 13, a wheel of a gear exhaust side 15 associated with the exhaust 14, and a constant-force mechanism 20 disposed between the power source side wheel 12 and the exhaust side wheel 15.

It should be noted that the power source side wheel 12 in this embodiment designates a gear wheel located more towards the side of the movement barrel 11, which is the source of power, that does not is the constant-force mechanism 20 when viewed from the constant-force mechanism 20. Similarly, the exhaust-side gear wheel 15 in this embodiment refers to the wheel gear located further on the side of the engine. 14 that is the constant force mechanism 20, when viewed from this constant force mechanism 20.

In this embodiment, the constant force mechanism 20 is provided at a location equivalent to a mobile average generally forming a wheel of the front wheel. A function of the average wheel is fulfilled by the set of wheels that are a first power wheel 25, a second power wheel 26, a first control wheel 55 and a second control wheel 56 explained below.

[0033] It should be noted that, as shown in FIG. 3, the first power wheel 25 and the second power wheel 26 rotate about a first axis of rotation 01. The first control wheel 55 and the second control wheel 56 rotate about a second axis of rotation 02 disposed at a position shifted in a direction in the plane of a not shown plate, relative to the first axis of rotation 01.

As shown in FIG. 2, the movement barrel 11 is supported axially between the plate and a barrel bridge not shown. A barrel spring 16 is housed inside the movement barrel 11. The barrel spring 16 is armed by means of a rotation of a not shown winding stem coupled to a ring 17 shown in FIG. 1. The movement barrel 11 rotates thanks to the power (the torque) brought into play by the disarming of the mainspring 16 and transmits the power to the constant force mechanism 20, via the gear wheel source side power 12.

It should be noted that, in this embodiment, the example explained is that in which the power from the movement barrel 11 is transmitted to a constant force mechanism 20 via a However, the transmission of power from the movement barrel 11 is not limited to this case. For example, the power from the movement barrel 11 can be transmitted directly to the constant force mechanism 20, without passing through the power source side wheel 12.

The power source side wheel 12 mainly comprises a center wheel 18.

As shown in FIGS. 3 and 4, the center wheel 18 is axially supported between the plate and a not shown wheel wheel axle and it rotates about a third axis of rotation 03, due to the rotation of the movement barrel 11. The third axis of rotation 03 is disposed at a position offset in a direction of the plane of the plate relative to the second axis of rotation O2.

It should be noted that when the center wheel 18 rotates, this leads to a roadway not shown rotates. The minute hand 6 shown in FIG. 6 is subject to the roadway. The minute hand indicates the "minutes" depending on the rotation of the roadway. The minute hand 6 rotates at a rotation speed set by the exhaust 14 and the speed regulator 13 at a rate of one revolution per hour.

When the center wheel 18 rotates, this means that a minute wheel not shown rotates. In addition, a not shown hour wheel rotates by the rotation of the minute wheel. It should be noted that the minute wheel and the hour wheel are timepiece components constituting the power source side wheel 12. The hour hand 5 shown in FIG. 1 is subject to the hour wheel. The hour hand 5 indicates the "hours" according to the rotation of the hour wheel. The hour hand 5 rotates at a rotation speed set by the exhaust 14 and the speed regulator 13, for example at a rate of one turn every 12 hours.

As shown in FIG. 2, the escape wheel of the wheel 15 comprises mainly a mobile seconds 19.

As shown in Figs. 3 and 4, the seconds wheel 19 is supported axially between the plate and the gear wheel bridge and rotates about a fourth axis of rotation 04, depending on the rotation of the first power wheel 25 described below, constituting the constant force mechanism 20. The fourth axis of rotation 04 is disposed at a position offset in a direction of the plane of the plate relative to the first axis of rotation 01. The second hand 7 shown in FIG. fig. 1 is subject to the seconds mobile 19. The seconds hand 7 indicates the "seconds", according to the rotation of the seconds mobile 19. The seconds hand 7 rotates at a speed set by the exhaust 14 and the cruise control 13, for example at a rate of one revolution per minute.

The escapement 14 mainly comprises an unrepresented escapement and an anchor not shown.

The escapement mobile is axially supported between the plate and the gear wheel bridge and meshes with the seconds mobile 19. Therefore, the power from a spring constant force 27 described below, at the within the constant-force mechanism 20, is transmitted to the escapement mobile via the seconds mobile 19. Therefore, the escapement mobile rotates with the power from the constant-force spring 27.

The anchor is supported between the plate and an anchor bridge not shown so as to be pivotable (tilting) and it comprises two stones forming pallet not shown. The two pallet stones are alternately engaged with and released from with an escape toothing within the escape wheel, according to a cycle predetermined by the cruise control 13. Therefore, the escape wheel is able to to be released according to the predetermined cycle.

The speed regulator 13 mainly comprises a balance spring not shown.

The sprung balance comprises a balance shaft, a balance wheel, and a hairspring, and is supported axially between the plate and a pendulum bridge not shown. The sprung balance performs an alternating rotation movement (it rotates regularly with reversal of direction) having a fixed oscillation angle, by means of the hairspring as power source.

Constitution of the Constant Force Mechanism [0047] As shown in FIGS. 2 to 4, the constant force mechanism 20 is a mechanism for suppressing the variations (torque variations) affecting the power transmitted to the exhaust 14. The constant force mechanism 20 mainly comprises a torque generating mechanism 21 and a cycle control mechanism 22.

Constitution of the Torque Generating Mechanism The torque generating mechanism 21 comprises the first power wheel 25 which rotates about the first axis of rotation 01, the second power wheel 26 which is arranged coaxially with the first power wheel 25 and which is able to rotate relatively relative to the first power wheel 25, about the first axis of rotation 01, and the constant force spring 27 (the power spring according to the present invention), which is disposed between the first power wheel 25 and the second power wheel 26 and which transmits the stored power to the first power wheel 25 and the second power wheel 26.

It should be noted that the first power wheel 25 is placed above the second power wheel 26.

As shown in Figs. 3 to 6, the second power wheel 26 is supported axially between the plate and the wheel axle wheel. The second power wheel 26 comprises a shaft 30 extending in the first direction of rotation 01, a coupling gear portion 31 formed integrally with the shaft 30, a first torque setting portion. 33 integrally assembled with the coupling gear portion 31, as well as a second power gear portion 35 which includes a torque adjusting jumper 34, releasably (reversibly) engaged with a coupling tooth 32 in the coupling gear portion 31 and is connected to the coupling gear portion 31 via the torque adjusting jumper 34.

It will be noted that the second power wheel 26 rotates with the power transmitted from the constant-force spring 27.

As shown in FIG. 5, the shaft 30 extends upwardly beyond the first power wheel 25.

The coupling gear portion 31 is provided between the middle portion in the up-down direction and the lower end of the shaft 30 and has a predetermined thickness. As shown in fig. 6, a plurality of coupling teeth 32 are formed on the outer circumferential surface of the coupling gear portion 31, at intervals from each other in the circumferential direction of said coupling gear portion 31.

Each of the coupling teeth 32 comprises a first engaging surface 32a turned towards the counterclockwise side about the first axis of rotation 01 and a second engaging surface 32b rotated. towards the side in a clockwise direction about this first axis of rotation 01.

The first engagement surface 32a is formed in the radial direction orthogonal to the first axis of rotation 01. On the other hand, the second engagement surface 32b tilts so as to gradually extend towards the counter-clockwise side towards the outer side in the radial direction from the outer circumferential surface of the coupling gear portion 31.

As shown in FIG. 5, the first torque adjusting gear portion 33 has an annular shape surrounding the coupling gear portion 31 from the outer side in the radial direction. The first torque adjusting gear portion 33 is fitted to a portion lying lower than the coupling teeth 32 within the coupling gear portion 31. Therefore, the first torque setting gear portion 33 and the coupling gear portion 31 are combined as if they were integral with each other, as explained above.

As shown in FIGS. 5 and 7, first torque adjusting teeth 33a, with which second torque adjusting teeth 111a of a second torque adjusting gear portion 111 described below are formed, are formed along the entire length of the surface. outer circumferential portion of the first portion having a torque adjustment toothing.

As shown in FIGS. 5 and 6, the second power tooth portion 35 has an annular shape surrounding the coupling teeth 32, from the outer side in the radial direction, and is placed on the first torque adjusting gear portion 33 of FIGS. so as to be able to rotate about the first axis of rotation 01. In the example shown in the figures, the second power-tooth portion 35 is formed to have a diameter greater than the first portion with setting teeth of torque 33.

Second power teeth 35a, with which meshes second control teeth 62a within a second control gear portion 62 described below, are formed along the entire length of the outer circumferential surface of the second part. with power teeth 35.

In the second portion with power teeth 35 is formed an opening 36 (opening portion) which passes vertically through the second portion with power teeth 35 and which discovers (gives access) the coupling teeth 32 on a fixed beach. The torque adjusting jumper 34 is integral with the second power tooth portion 35 so as to be in the opening 36.

Specifically, a proximal end 34a of the torque adjusting jumper 34 is integral with the second power tooth portion 35 and, formed as a free end, a distal end 34b of the regulating jumper 34. torque 34 is resiliently deformable about the proximal end 34a to move in the radial direction.

A portion of the distal end 34b of the torque adjusting jumper 34 protrudes towards the coupling gear portion 31 and is arranged to penetrate between the coupling teeth 32 adjacent to each other in the circumferential direction. At this moment, the distal end 34b of the torque adjusting jumper 34 is pushed by a predetermined spring force (elastic return force) so as to penetrate between the coupling teeth 32 adjacent to each other in the circumferential direction .

Therefore, the distal end 34b of the torque adjusting jumper 34 is engaged with the first engagement surface 32a of that of the coupling teeth 32 adjacent to each other in the circumferential direction. thereafter, clockwise, the distal end 34b and engages with the second engagement surface 32b of the other coupling tooth 32 after, in the opposite direction of the clockwise, the distal end 34b of the torque adjustment jumper 34.

As explained above, the first engagement surface 32a is formed in a radial direction, while the second engagement surface 32b is inclined. Therefore, when the coupling gear portion 31 rotates counterclockwise, it is possible to engage, in the circumferential direction, the distal end 34b of the torque adjusting jumper 34 with the first engagement surface 32a of the coupling tooth 32 located farther in the direction of clockwise than the distal end 34b of the torque adjusting jumper 34. It is possible to cause that the second the power-toothed portion 35 rotates counter-clockwise together via the torque adjusting jumper 34, since the distal end 34b and the first engagement surface 32a are not engaged.

Note that when the torque in the opposite direction of clockwise, wherein the distal end 34b of the torque adjusting jumper 34 and the first engagement surface 32a of the coupling tooth 32 are not engaged (not coupled), are applied to the coupling gear portion 31, the distal end 34b of the torque control jumper 34 and the first engagement surface 32a are not engaged ( are not mated). As a result, the coupling tooth 32 moves counterclockwise while passing the distal end 34b of the torque adjusting jumper 34 in the circumferential direction. Therefore, it is possible to turn the coupling gear 31 relatively counterclockwise with respect to the second power gear portion 35.

On the other side, when the coupling gear portion 31 rotates clockwise, the distal end 34b of the torque adjusting jumper 34 is pushed outwardly in the direction of rotation. radial, while sliding on the second engaging surface 32b with the inclination of this second engaging surface 32b of the coupling tooth 32 located later, in the counterclockwise direction, distal end 34b of the torque adjustment jumper 34.

Therefore, the distal end 34b of the torque adjusting jumper 34 and the second engagement surface 32b are not engaged (are not coupled, are released). The coupling tooth 32 moves clockwise while passing the distal end 34b of the torque adjusting jumper 34 in the circumferential direction. Therefore, it is possible to relatively rotate the coupling gear portion 31 clockwise with respect to the second power gear portion 35.

In other words, the torque adjusting jumper 34 and the coupling teeth 32 function as a ratchet mechanism (snap mechanism) which, when the coupling gear portion 34 rotates in the opposite direction clockwise, causes the second power tooth portion 35 to rotate together and which, when the mating gear portion rotates clockwise, allows relative rotation of the geared portion. coupling member 31 with respect to the second power gear portion 35.

Note that a spring force (an elastic return) of the torque control jumper 34 is adjusted so that when the coupling gear portion 31 is rotated counterclockwise with a torque Tj, the distal end 34b of the torque adjusting jumper 34 and the first engagement surface 32a of the coupling tooth 32 are not engaged (are uncoupled). In the following explanation, the torque Tj is called the jumper pair Tj of the torque control jumper 34.

In addition, the spring force (the elastic return) produced by the torque adjusting jumper 34 is adjusted so that when the coupling gear portion 31 is rotated clockwise. with a torque Tk, the distal end 34b of the torque adjusting jumper 34 and the second engagement surface 32b of the coupling teeth 32 are not engaged (are uncoupled). In the explanations that follow, the torque Tk is called the jumper pair Tk of the torque control jumper 34.

As shown in FIG. 5, a limiting ring 37 which prevents the distal end 34b of the torque adjusting jumper 34 from moving upwards is disposed above the second power tooth portion 35.

The limiting ring 37 has an annular shape surrounding the coupling gear portion 31 from the outer side in the radial direction. In a state where there is no contact with the second power-toothed portion 35, the limiting ring 37 is fitted into a portion above the coupling tooth 32 within the coupling gear 31.

Therefore, it is possible to prevent the distal end 34b of the torque adjusting jumper 34 jumps or floats upwards. It is possible to stabilize (ensure) the engagement of the distal end 34b of the torque adjusting jumper 34 and the coupling tooth 32 with each other.

As shown in FIGS. 3 to 5, the first power wheel 25 comprises a rotatable cylindrical body 40 arranged coaxially (centered on) the first axis of rotation 01, and a first power tooth portion 41 secured to the rotary cylindrical body 40 as if they were in one piece.

Note that the first power wheel 25 rotates in the direction of clockwise with the power transmitted from the constant-force spring 27. It will be noted that the first power wheel 25 and the second power wheel 26 are able to rotate in opposite directions relative to each other, around the first axis of rotation 01, with the power transmitted from the constant-force spring 27.

The shaft 30 of the second power wheel 26 is inserted into (passes through) the rotating cylindrical body 40, from below. The shaft 30 protrudes above the rotating cylindrical body 40. Stones 42 formed as rings, from jewels (precious stones) such as ruby are driven into the interiors of the upper and lower ends of the rotating cylindrical body 40. The shaft 30 of the second power wheel 26 is inserted into the interior of the stones 42. As a result, the first power wheel 25 and the second power wheel 26 are assembled so as to be able to turn one of them. relative to the other around the first axis of rotation 01, with a small clearance.

Note that the stones 42 are not limited to those made of artificial stones and can be made, for example, other fragile materials and metals such as alloys based on steel.

The first power tooth portion 41 comprises a plurality of arms 41a disposed at intervals from each other in the circumferential direction about the first axis of rotation 01, and a main body of toothed portion 41b formed as a ring and coupled to the outer ends of the arms 41a.

In the example shown in the figures, four arms 41a are formed at regular intervals, which is 90 degrees, about the first axis of rotation 01. However, the number, the disposition and the shape of the arms 41a n ' is not limited to this case and can be changed freely.

First power teeth 41c, with which meshes first control teeth 71d within a first control gear portion 71 described below are formed along the entire length of the outer circumferential surface of the main body of the main body. toothed portion 41b. The first power teeth 41c also mesh with a second pinion 19a constituting the second mobile 19. Therefore, the first power wheel 25 is able to transmit power from the constant force spring 27 to the second mobile 19, that is to say the wheel on the exhaust side 15 associated with the exhaust 14, as indicated by the arrow R1 shown in FIG. 2.

It will be noted that, in this embodiment, the example explained is that in which the power from the constant-force spring is transmitted to the exhaust 14 via the escape-side gear wheel 15. However, the transmission of power from the constant-force spring 27 is not limited to this case. For example, the power from the constant-force spring 27 can be transmitted directly to the exhaust 14, without the exhaust-side gear wheel 15 being provided.

In addition, the first power tooth portion 41 is formed with a diameter equal to the diameter of the second power gear portion 35. However, the diameters are not limited to this case. The first power gear portion 41 and the second power gear portion 35 may have different diameters.

The constant force spring 27 is a thin plate spring made of a metal such as steel or nickel or an alloy, and it has the shape of a spiral. Specifically, the constant force spring 27 has the shape of a spiral extending in an Archimedean curve in a polar coordinate system having as its origin the first axis of rotation 01. Therefore, the constant force spring 27 is wound on several turns or turns adjacent to each other, at substantially regular intervals in the radial direction when viewed from the first axis of rotation 01.

As shown in FIGS. 8 and 9, among the ends of the constant-force spring 27, the outer end 27b (one end according to the present invention), which is a circumferential end, is coupled to the side of the first power wheel 25 and the inner end. 27a (the other end), which is the other circumferential end, is coupled to the side of the second power wheel 26. Therefore, the constant force spring 27 is able to transmit the stored energy, respectively to the first power wheel 25 and the second power wheel 26.

It will be noted that a part of the outermost circumferential portion in the constant-force spring 27 is in the form of an arched segment that is outwardly outwardly in the radial direction by means of a shape-changing segment 27c and having a radius of curvature greater than the radius of curvature of the other portions. The end of the arcuate segment is formed as the outer end 27b of the constant force spring 27.

The constant force spring 27 is armed with a predetermined amount of arming in the counterclockwise direction towards the outer end 27b, with the inner end 27a chosen as the starting position of the winding . The constant force spring 27 is elastically deformed to decrease in diameter by arming (by winding) and is applied with prestressing. As a result, the power of a torque Te is generated in the constant-force spring 27 and energy is stored in the constant-force spring 27.

The stored energy is transmitted to the first power wheel 25 and the second power wheel 26, because the constant force spring 27 is deformed to return elastically to its original shape. Therefore, the first power wheel 25 is able to turn clockwise and the second power wheel 26 is able to turn counterclockwise. In the following explanations, the torque Te is called the rotation torque Te produced by the constant-force spring 27.

We will now describe in detail the constitution for fixing the constant force spring 27 to the first power wheel 25 and the second power wheel 26.

As shown in FIG. 5, fig. 8 and FIG. 9, the inner end 27a of the constant force spring 27 is fixed to a fixed ring 45 secured to the shaft 30 of the second power wheel 26.

The fixed ring 45 is, for example, fitted on a portion located between the limiting ring 37 and the rotary cylindrical body 40 within the first power wheel 25 in the shaft 30. The end Inner 27a of the constant force spring 27 is fixed to the fixed ring 45 by, for example, matting or welding.

As shown in FIG. 3, fig. 4, fig. 8 and FIG. 9, at the outer end 27b of the constant force spring 27, a defining segment 47 (the second engaging segment of the present invention) reversibly engaged in a sliding hole 46 (the first engagement segment according to the present invention) provided on the side of the first power wheel 25 and defines a position, in the radial direction, of the outer end 27b, and a limiting lever 48 (the limiting element according to the present invention) which comes into contact with the rotating cylindrical body 40 (the rotational limitation segment according to the present invention) within the first power wheel 25 and prevents the outer end 27b from rotating about the first axis of rotation. rotation 01 due to an elastic return of the spring constant force 27 to its original shape are provided.

The sliding hole 46 is formed in the arm 41a of the first power tooth portion 41. The sliding hole 46 has a shape extending in the circumferential direction around the first axis of rotation 01 and it is opening on the side in the opposite direction of clockwise.

As shown in FIG. 8 and FIG. 9, the defining segment 47 comprises a shaft 50 which has a vertically extending columnar shape and is engaged with the inner side (the inner edge) of the sliding hole 46, a head 51 provided at the upper end. of the shaft 50, as well as a leg 52 having a fork shape formed at the lower end of the shaft 50. In the shaft 50, an increased diameter segment 53 having a larger diameter than the head 51 is formed in a portion between the head 51 and the leg 52.

The outer end 27b of the constant force spring 27 is fixed to the leg 52 by, for example, gluing or matting, in a state in which the outer end 27b is inserted into the inside of the leg 52. Therefore, the outer end 27b of the constant force spring 27 and the defining segment 47 are combined as if they were one piece.

The definition segment 47 constituted in this manner is inserted into the sliding hole 46 in a sliding motion. Therefore, the shaft 50 is engaged with the inner side (the inner wall) of the sliding hole 46. In particular, the outer end 27b of the constant force spring 27 is pulled in a clockwise direction. by the rotation torque (armature torque) involved in the spring return of the constant force spring 27 to its initial shape. As a result, the defining segment 47 is pulled toward the circumferential end wall side of the slip hole 46. The shaft 50 is pushed against and engaged with the circumferential wall. In this way, the definition segment 47 is engaged with the inner side (the inner wall) of the sliding hole 46 and defines a position, in the radial direction, of the outer end 27b of the constant force spring 27.

It will be noted that the arm 41a, in which the sliding hole 46 is formed, is arranged to be held between the head 51 and the increased diameter segment 53. Therefore, the definition segment 47 engaged with the inner side (the inner wall or the inner edge) of the sliding hole 46 is prevented from sliding out, upwards and downwards.

As shown in FIG. 9, the limiting lever 48 is combined with the defining segment 47 so as to be integral with it. In the example shown in the figure, the proximal end of the limiting lever 48 is combined with a portion located between the increased diameter segment 53 and the leg 52 within the shaft 30 within the defining segment 47 A distal end 48a of the limiting lever 48 is in contact with the rotatable cylindrical body 40 within the first power wheel 25 from the outer side in the radial direction.

Therefore, the limiting lever 48 is used to limit the rotation of the outer end 27b of the constant force spring 27 around the first axis of rotation 01 due to the rotational torque that involves the springback. spring constant force 27 to its original form.

Constitution of the Cycle Control Mechanism [0099] As shown in FIGS. 2 to 5, the cycle control mechanism 22 is a mechanism for intermittently rotating the second power wheel 26 relative to the first power wheel 25 to provide power to the constant force spring 27, such as indicates the arrow R2 in FIG. 2. The cycle control mechanism 22 is placed at a plane offset position from the constant force mechanism 20.

The cycle control mechanism 22 comprises the first control wheel 55 which rotates about the second axis of rotation 02 due to the rotation of the first power wheel 25, the second control wheel 56 arranged coaxially with the first control wheel 55 and able to turn relatively relative to the first control wheel 55, around the second axis of rotation 02, and a planetary mechanism 57 disposed between the first control wheel 55 and the second wheel order 56.

It will be noted that the first control wheel 55 is disposed above the second control wheel 56.

[0102] As shown in FIG. 3 and FIG. 5, the second control wheel 56 is axially supported between the plate and the gear wheel bridge. The second control wheel 56 comprises a shaft 60 extending along the second axis of rotation O2, a second control gear 61 which is integral with the shaft 60 and which meshes with the center wheel 18, and a second control gear portion 62 comprising second control teeth 62a which meshing with the second power teeth 35a within the second power wheel 26.

[0103] The shaft 60 extends beyond the first control wheel 55 upwards.

The second control gear 61 is provided between the central portion, in the up-down direction, of the shaft 60 and the lower end of this shaft 60. Since the second control gear 61 meshes with the movable center 18, the second control gear 61 rotates as a function of the rotation of the center wheel 18. Consequently, the power from the movement barrel 11 is transmitted to the second control wheel 56 via the center wheel 18, that is, the power source side wheel 12.

It will be noted that the second control wheel 56 rotates counterclockwise about the second axis of rotation 02. The power of the torque Tb is transmitted to the second control wheel 56, from the barrel In the following explanation, the torque Tb is called the rotational torque produced by the movement cylinder 11. Note that when the barrel spring 16 in the movement barrel 11 is armed with a predetermined arming amount, the spinning torque Tb is selected to be higher than the spinning torque Te produced by the constant-force spring 27.

As shown in FIG. 5, fig. 7 and FIG. 8, the second control gear portion 62 comprises a plurality of arms 62b spaced apart (with a gap therebetween) in the circumferential direction about the second axis of rotation 02, a toothed main body having a ring-like shape and coupled at the outer ends of the arms 62b, and a support plate 62d integral with the arms 62b.

The second control teeth 62a are formed along the entire length of the outer circumferential surface of the main body of the toothed portion 62c. Therefore, the rotating torque Te provided for rotating the second control wheel 56 in a clockwise direction is transmitted to the second control wheel 56 from the second power wheel 26 which rotates. in the opposite direction of clockwise.

At this time, the rotation torque Tb greater than the rotation torque Te as explained above and acting in the opposite direction to the rotation torque Te is transmitted to the second control wheel 56. via the power source side wheel 12. This prevents the second control wheel 56 from turning clockwise.

However, when the rotation torque Tb produced by the movement barrel 11 is smaller than the rotation torque Te produced by the constant-force spring 27, for example because the cylinder spring 16 in the movement barrel 11 is disarmed or when the second torque adjusting gear portion 111 forcibly rotates counterclockwise by a power adjusting mechanism 110 described below, the second control wheel 56 is able to turn in a clockwise direction.

As shown in FIG. 3 and FIG. 5, the first control wheel 55 comprises a rotatable cylindrical body 70 coaxially disposed with the second axis of rotation O2, and a first control gear portion 71 coupled to the rotatable cylindrical body 70 so as to be like one piece with this one.

The shaft 60 of the second control wheel 56 is inserted into (passes through) the rotating cylindrical body 70 from below. The shaft 60 protrudes above the rotating cylindrical body 70. Stones 72, which are the same as the stones 42, are driven into the interior of the upper and lower ends of the rotating cylindrical body 70. The shaft 60 of the second control wheel 56 passes through the interior space of the stones 72. Therefore, the first control wheel 55 and the second control wheel 56 are combined so as to be able to rotate relatively second axis of rotation 02 with less play.

The first control gear portion 71 comprises a plurality of arms 71a arranged at intervals (offset from each other) in the circumferential direction about the second axis of rotation O2, and a main body of the toothed portion having a shape such as a ring and coupled to the outer ends of the arms 71a.

In the example shown in the figures, three arms 71a are provided. Two of the three arms 71a are provided with an interval of 180 degrees between them about the second axis of rotation 02. Therefore, an opening 73 (opening space) extending much in the circumferential direction is obtained between the offset arms 71a. with an interval of 180 degrees between them around the second axis of rotation 02.

However, the number, the disposition and the shape of the arms 71a is not limited to this case and can be freely modified.

First control teeth 71c, which meshes with the first power teeth 41c within the first power wheel 25, are formed over the entire length of the outer circumferential surface of the main body of the toothed portion 71b. Therefore, the control wheel 55 rotates counterclockwise about the second axis of rotation 02, depending on the rotation of the first power wheel 25.

It will be noted that the first control gear portion 71 is formed with a diameter equal to the diameter of the second control gear portion 62. However, the diameters are not limited to this case. The first control gear portion 71 and the second control gear portion 62 may be made to have different diameters.

The planetary mechanism 57 comprises an engagement pallet stone 80 (the engagement pawl according to the present invention) which is provided on the side of the first control wheel 55 and which rotates about the second axis of rotation. 02 as a function of the rotation of the first control wheel 55, a stop wheel 81, which is a planetary geared portion which is provided on the second control wheel 56 and which revolves about the second axis of rotation 02 all rotating as a function of the rotation of the second control wheel 56, and a fixed-toothed portion 82 provided for rotations and revolutions to the stopwheel 81. The planetary mechanism 57 causes intermittently that the engaging pallet stone 80 engages and disengages with (disconnects from) the stop wheel 81 as a function of the rotation of the first control wheel 55.

[0118] The engagement pallet stone 80 is made of an artificial jewel (a precious stone) such as ruby and is secured to a support lever 85 which rotates about the second axis of rotation 02 as a function of the rotation of the first control wheel 55.

It will be noted that, like the stones 42 and 72, the stone forming an engagement pallet 80 is not limited to that made of an artificial jewel and may be made, for example, of other fragile materials and metals such as steel-based alloys.

The engagement pallet stone 80 may be integral with the support lever 85, instead of being formed as a separate member of the support lever 85.

As shown in FIG. 5, fig. 8, FIG. 10 and FIG. 11, the support lever 85 is coupled to a portion as if it were integral with that portion, which is below the first control gear portion 71, within the rotatable cylindrical body 70 at the within the first control wheel 55.

The support lever 85 comprises a first lever part 86 and a second lever part 87 extending in the radial direction of the first control wheel 55, from the side of the rotary cylindrical body 70, towards the body main gear 71b. The first lever part 86 and the second lever part 87 are arranged with a fixed gap between them in the circumferential direction and are arranged to fit into the interior of the opening 73 in a plan view.

In the example shown in the figures, the first lever piece 86 and the second lever piece 87 are made to have the same shape and size. However, the shapes and sizes of the first lever piece 86 and the second lever piece 87 are not limited to this case. The first lever piece 86 and the second lever piece 87 may be made to have different shapes and sizes.

The stop wheel 81 is disposed between the first lever piece 86 and the second lever piece 87. Note that the first lever piece 86 is disposed further away from the counterclockwise side of the needle. shows that the stop wheel 81, while the second lever piece 87 is disposed farther from the clockwise side than the stop wheel 81.

[0125] As shown in FIG. 11, a pallet stone support portion 88 opens toward the stop wheel 81 being provided on the outer end of the first lever portion 86. The pallet stone support portion 88 carries the stone forming engagement pallet 80 by means of this aperture. The engagement pad stone 80 is maintained in a state where this engagement pad stone 80 protrudes toward the stop wheel 81, rather than the paddle stone support portion 88. On a protruding portion of the engagement pallet stone 80, a radially inwardly facing lateral surface forms an engaging surface 80a with which a work surface 95a described below is engageable. within the stop wheel 81 and from which this working surface 95a can be disconnected. In the example shown in the figure, the engaging surface 80a is formed as a flat surface which is flat over the entire surface.

As shown in FIG. 8, FIG. 10 and FIG. 12, between the first lever member 86 and the second lever member 87, the stop wheel 81 is axially supported between the support plate 62d within the second control wheel 56 and a support member 90 attached to the support plate 62d.

The support member 90 comprises a lower plate 91 fixed to the support plate 62d, and an upper plate 92 raised upwards, from the lower plate 91 and protruding above the wheel. In the example shown in the figure, the bottom plate 91 is fixed by fixing means such as fixing rods, fixing screws or the like. However, the fixing of the lower plate 91 is not limited to this case.

93 stones made of an artificial jewel (artificial gemstone) such as ruby are provided respectively in the support plate 62d and in the upper plate 92, so as to be vertically opposed to one another. It should be noted that the stones 93 can be made, for example, of other fragile materials or of metals such as alloys based on steel.

The stop wheel 81 is disposed between the support plate 62d and the upper plate 92, supported axially by the stones 93 formed in the support plate 62d and the upper plate 92, and it is able to turn around. a fifth axis of rotation 05.

The stop wheel 81 comprises a locking gear portion 96 comprising a plurality of stop teeth 95 able to engage with and disengage from the engagement surface 80a of the stone. forming an engagement pallet 80, as well as a stop gear 97 which is provided below the locking gear portion 96 and which meshes with the fixed gear portion 82.

As shown in FIG. 5 and FIG. 10, the fixed-toothed portion 82 comprises a toothed portion main body 100 formed as a ring and disposed between the first control wheel 55 and the second control wheel 56 and coaxially with the second rotation axis 02, as well as a fixed arm 101 formed integrally with the main body of toothed portion 100 and fixed to a fixed component not shown. In the example shown in the figures, the toothed portion main body 100 is formed to have a diameter slightly smaller than the first control gear portion 71 and the second gear tooth portion 62. Fixed teeth 100a, with which the pinion gear 97 meshes, are formed along the entire length of the inner circumferential surface of the toothed portion main body 100. Therefore, the fixed gear portion 82 in this embodiment is of the geared type. internal.

Since the fixed gear portion 82 is of the internal gear type, as shown in FIG. 11, the stop wheel 81 rotates counterclockwise about the second axis of rotation O2 while turning clockwise about the fifth axis of rotation 05 as a function of the counter-clockwise rotation of the second control wheel 56. As shown in FIG. 10, the stop wheel 96 is disposed above the fixed toothing portion 82 and is rotatable (rotate and revolve) without contacting the fixed gear portion 82 and support member 90.

As shown in FIG. 11, the stop teeth 95 are twelve in number. However, the number of teeth is not limited to this and can be suitably modified. On the stop tooth 95, a clockwise side surface forms a work surface 95a which engages and disengages from the engaging surface 80a belonging to the stone. 80. A rotational path M followed by the tips of the stop teeth 95 as a function of the rotation of the stop wheel 81 is called the rotational trajectory of the locking gear portion 96. .

[0134] The engagement pad 80 and the stop wheel 81 formed as explained above are in a relationship in which the engagement pad 80 and the stop wheel 81 engage with each other. intermittently with each other and disconnect intermittently from one another depending on the rotation of the first control wheel 55. This point will be explained in detail.

The working surface 95a of the stop tooth 95 engages with the engagement surface 80a of the engagement pallet stone 80 in accordance with the rotation and revolution of the drive wheel. After engagement, the support lever 85 and the engaging pallet stone 80 turn counterclockwise about the second rotational axis 02, depending on the rotation. counterclockwise of the first control wheel 55. Therefore, the support lever 85 and the engaging pallet stone 80 gradually decouple from the locking gear portion 96 (c i.e. progressively leaves the rotation path M).

Therefore, as shown in FIG. 13, at an initial stage of engagement, the work surface 95a of the stop tooth 95 is deeply (significantly) engaged with the engagement pallet stone 80. Then, as shown in FIG. fig. 14, the working surface 95a of the stop tooth 95 moves toward the end of the engagement pallet stone 80, while sliding on the engagement surface 80a as a function of the disconnection of the pallet stone 80. Then, the setting of the stop tooth 95 and the engaging pallet stone 80 becomes progressively shallower (less important). As shown in fig. 15, the stop tooth 95 and the engagement pad stone 80 are uncoupled at a time which occurs when the working surface 95a of the stop tooth 95 passes over the tip of the paddle stone of engagement 80.

It will be noted that in FIGS. 13 to 15, the support lever 85 is shown schematically, while the second lever member 87 is not shown.

When the stop tooth 95 and the engaging pallet stone 80 are uncoupled, as shown in FIG. 16, the connection between the first control wheel 55 and the second control wheel 56 through the engaging pallet stone 80 and the stop wheel 81 ceases. Therefore, it is possible to rotate the second control wheel 56 counterclockwise about the second axis of rotation 02. Therefore, the stop wheel 81 rotates counterclockwise. a watch about the second axis of rotation 02 so as to follow the engagement pallet stone 80 while rotating clockwise about the fifth axis of rotation 05 as a function of the rotation of the second control wheel 56. Then, it is possible to cause the working surface 95a of the next stop wheel 95 to engage the engagement surface 80a belonging to the engaging pallet stone 80.

By means of a repetition of the operation explained above, it is possible to bring the stone forming the engagement pallet 80 to engage with and to disconnect from with intermittently the wheel 81. It will be noted that the stop teeth 95 engage one by one with the engaging pallet stone 80.

From the moment when the working surface 95a of the stop tooth 95 engages the engagement surface 80a of the engagement pallet stone 80 as shown in FIG. 13 until the working surface 95a and the engagement surface 80a are uncoupled as shown in FIG. 14 and FIG. 15, the support lever 85 carries the engagement pallet stone 80 so that a dummy line L extends according to a force F3 resulting from a thrust force F1, with which the stop tooth 95 pushes on the engagement surface 80a, and a friction force F2 generated by the sliding of the stop tooth 95 on the engaging surface 80a crosses the second axis of rotation O2.

In this embodiment, the dummy line L crosses the second axis of rotation O2 in an intermediate position P3 shown in FIG. 14 and being in the middle between a setting position P1 shown in FIG. 13, where the stop tooth 95 is engaged with the engaging surface 80a, and an end setting position (release position) P2 shown in FIG. 15, where the stop tooth 95 ceases to engage the engagement surface 80a.

It will be noted that, as explained above, when the rotation torque Tb produced by the movement cylinder 11 is smaller than the rotation torque Te produced by the constant-force spring 27, for example because the barrel spring 16 in the movement barrel 11 is disarmed or when the second torque adjusting gear portion 111 is forcibly forcibly turned counterclockwise by the power adjusting mechanism 110 described lower down, the second control wheel 56 rotates clockwise.

In this case, the upper plate 92 of the support element 90 moves towards the second lever part 87 of the support lever 85 as a function of the rotation of the second control wheel 56. Therefore, then, the upper plate 92 comes into contact with the second lever piece 87 as shown in FIG. 17. Next, it is possible to limit, by means of the second lever part 87, a rotation of the second control wheel 56 to go further in the direction of clockwise.

Constitution of the Power Adjustment Mechanism [0144] As shown in FIG. 3, fig. 4, fig. 18 and FIG. 19, the constant force mechanism 20 in this embodiment further comprises the power control mechanism 110 provided for adjusting the power of the constant force spring 27, via the first power wheel 25 or the second power wheel 26.

It will be noted that in this embodiment, the example explained is that in which the power of the constant-force spring 27 is regulated by means of the second power wheel 26. However, the adjustment of the power constant force spring 27 is not limited to this case. The power of the constant force spring 27 can be adjusted via the first power wheel 25 as explained above.

The power adjusting mechanism 110 comprises the second torque adjusting gear portion 111 (the adjusting wheel according to the present invention) capable of meshing with the first torque adjusting gear portion 33 within the the second power wheel 26 and a rocking lever 113 (the movable member according to the present invention) which moves the second torque adjusting gear portion 111 between a meshing position P4 (see Fig. 19), wherein the second torque adjusting gear portion 111 and the first torque adjusting gear portion 33 meshing with each other, and a non-engaging position P5 (see Fig. 19), wherein the second torque adjusting gear portion 111 and the first torque adjusting gear portion 33 no longer mesh with each other.

The rocking lever 113 is disposed between a plate 115 and a torque adjusting bridge 116 and is able to tilt around a tilting rod 117 fixed to the plate 115. A fork portion 118 divided with a fork form is provided at one end of the rocking lever 113.

An eccentric pin 119 carried by the plate 115 to be rotatable is disposed on the inner side of the forked portion 118. The inner circumferential surface of the fork portion 118 and the outer circumferential surface of the pin to eccentric 119 are in sliding contact with each other.

The eccentric rod 119 is exposed on the outside of the torque adjusting bridge 116. For example, a negative groove 119a is formed at the upper end of the eccentric rod 119. Then, it is possible to optionally rotating the eccentric pin 119 by means of, for example, a driving tool employing the negative groove 119a. However, the means for the rotation maneuver are not limited to the negative groove 119a. Means for optionally operating the eccentric pin 119 should only be formed at the upper end of the eccentric pin 119.

By turning the eccentric rod 119 described above, as shown in FIG. 19, the tilting lever 113 can be tilted about the tilt rod 117. The other end of the tilting lever 113 can be brought into contact with the first torque adjusting gear portion 33 or the other end. of the rocking lever 113 separates from the first torque-adjusting gear portion 33.

As shown in FIG. 7, FIG. 18 and FIG. 19, the second torque adjusting gear portion 111 is carried by the guide rod 112 to be rotatable, the lower end of this guide rod 112 being attached to the other end of the rocking lever 113. Torque adjusting teeth 111a engageable with the first torque adjusting teeth 33a are formed along the entire length of the outer circumferential surface of the second torque adjusting gear portion 111.

The second torque adjusting gear portion 111 is disposed at the other end of the rocking lever 113 by means of the guide rod 111. Therefore, the second gear tooth portion can be moved. torque 111 by tilting the rocking lever 113. Note that the position where the other end of the rocking lever 113 is closest to the first torque adjusting gear portion 33 is set as the meshing position P4. It is possible to make the first torque adjusting teeth 33a and the second torque adjusting teeth 111a meshing with each other.

On the other hand, a position in which the other end of the rocking lever 113 is further away from the first torque adjusting gear portion 33 is selected as the release position P5. It is possible to make the first torque adjusting teeth 33a and the second torque adjusting teeth 111a cease to mesh with each other.

[0154] The upper end of the guide rod 112 is inserted so as to be movable in a swinging groove 120, which is formed in the torque adjusting bridge 116 as shown in FIG. 4, along the tilting groove 120. The tilting groove 120 is formed to extend in a tilting direction from the other end of the tilting lever 113. Next, the second tine gear portion 111 is worn. stably via the guide rod 112 with less play and moves between the meshing position P4 and the non-meshing position P5 as a function of the tilting lever 113 tilting.

As shown in FIG. 7, FIG. 18 and FIG. 19, an operating wheel 121 which rotates the second torque adjusting gear portion 111 is disposed between this second torque adjusting gear portion 111 and the tilt rod 117.

The actuating wheel 121 comprises a portion with operating gear 122 whose actuating teeth 122a meshing with the second torque adjusting teeth 111a. The operating teeth 122a are formed along the entire length of the outer circumferential surface of the operating gear portion 122. The operating wheel 121 is supported axially between the plate 115 and the torque control bridge 116.

Note that the operating wheel 121 is arranged to pass vertically through a through hole 123 formed in the rocking lever 113. The through hole 123 is formed to extend in a direction of tilting of the lever tipping 112.

Therefore, the operating wheel 121 is axially supported between the plate 115 and the torque adjusting bridge 116 without being affected by the tilting of the rocking lever 113. It will be noted that the operating teeth 122a of the operating wheel 121 always meshes with the second torque adjusting teeth 111a, regardless of the position of the second torque adjusting gear portion 111.

The upper end of the operating wheel 121 is located on the side of the upper surface of the torque adjusting bridge 116 as shown in FIG. 4. A maneuver of rotation of the operating wheel 121 can be performed from the outside. In the example shown in the figures, a negative groove 121a is formed at the upper end of the operating wheel 121. It is optionally possible to rotate the operating wheel 121 by means of, for example , of a training tool employing the negative groove 121a. However, means for performing the maneuver of rotation of the operating wheel 121 are not limited to the negative groove 121a. Maneuvers to optionally perform the maneuver of rotation of the operating wheel 121 must only be formed at the upper end of the operating wheel 121.

Since the power adjustment mechanism 110 is constituted as explained above, as shown in FIG. 19, it is possible to turn the first torque adjusting gear portion 33 through the second torque adjusting gear portion 111, by rotating the operating wheel 121 after moving the second torque adjusting gear portion 111 to the meshing position P4. It is possible to arm or disarm the constant-force spring 27 and optionally to adjust the power of the constant-force spring 27.

This setting will be explained in detail below.

Action of the constant force mechanism The operation of the constant force mechanism 20 constituted as explained above will be explained.

Note that, in an initial state, it is assumed that the barrel spring 16 in the movement barrel 11 is armed with a predetermined amount of arming and that the power of the rotating torque Tb is transmitted to from the movement barrel 11 to the second control wheel 56, via the power source-side gear wheel 12. It is assumed that the constant-force spring 27 is armed with a predetermined amount of arming and that the power of the rotating torque Te smaller than the rotating torque Tb is transmitted from the constant-force spring 27 to the first power wheel 25 and the second power wheel 26. In addition, it is assumed that the second portion with torque adjusting gear 111 is placed in the non-meshing position P5 and that the first torque adjusting gear portion 33 and the second torque adjusting gear portion 111 within the second of power wheel 26 do not mesh with each other.

With the constant force mechanism 20 of this embodiment, since the constant force mechanism 20 comprises the constant force spring 27 as shown in FIGS. 2 to 4, the energy stored in the constant force spring 27 can be transmitted to the first power wheel 25 and the first power wheel 25 can rotate clockwise about the first axis of rotation 01 Then, the power of the constant force spring 27 can be transmitted from the first power wheel 25 to the second wheel 19. The second wheel 19 can rotate about the fourth axis of rotation 04 depending on the rotation of the first power wheel. 25.

In other words, as indicated by the arrow R1 in FIG. 2, the power can be transmitted from the constant force spring 27 to the escape wheel 15, via the first power wheel 25. The exhaust 14 can be actuated.

Since the power from the constant force spring is also transmitted to the second power wheel 26, the second power wheel 26 is rotated counterclockwise about the first axis of rotation. 01 with the torque Te.

Specifically, the power from the constant-force spring 27 is transmitted to the shaft 30 and to the coupling gear 31 through the fixed ring 45. In addition, the power transmitted to the coupling gear portion 31 is transmitted to the second power gear portion 35 via the torque adjusting jumper 34, and then transmitted to the second gear tooth portion 62 of the second control wheel 56. Next, the power to turn the second control wheel 56 clockwise about the second axis of rotation 02 with the rotating torque Te is transmitted to the second control wheel 56 from constant force spring 27.

However, the rotation torque Tb (torque greater than the rotation torque Te) provided for rotating the second control wheel counterclockwise about the second axis of rotation 02 is transmitted to the second control wheel 56 from the power source side wheel 12. Therefore, the second control wheel 56 is prevented from turning clockwise.

It will be noted that a power resulting from a difference (the rotation torque Tb - the rotation torque Te) between the rotation torque Tb transmitted from the power source side wheel 12. and the rotation torque Te transmitted from the constant force spring 27 acts on the second control wheel 56. However, since the stop wheel 81 and the engagement pallet stone 80 are engaged, the second control wheel 56 and the first control wheel 55 can be linked through this engagement (through this coupling). The second control wheel 56 is prevented from rotating counterclockwise about the second axis of rotation 02.

Therefore, at a stage when the stop wheel 81 and the engaging pallet stone 80 are in engagement, the second control wheel 56 is prevented from rotating about the second axis of rotation 02. Therefore the second power wheel 26 is prevented from rotating about the first axis of rotation 01.

It will be noted that, since the power resulting from the difference acts on the second control wheel 56, the working surface 95a of the stopping tooth 95 of the stopping wheel 81 is engaged with the staking surface. engaged 80a of the engagement pallet stone 80 in a state of high thrust.

When the first power wheel 25 rotates with the power from the constant-force spring 27, the first control wheel 55 rotates counterclockwise about the second axis of rotation O 2, according to the rotation of the first power wheel 25. When the first control wheel 55 rotates, the support lever 85 rotates counterclockwise about the second axis of rotation 02, depending on the rotation of the first control wheel 55. Therefore, the engagement pallet stone 80 can progressively release itself from the stop gear portion 96 to remove the engagement pallet stone 80 from the rotation path M of the locking gear portion 96.

Therefore, as shown in FIG. 14, the work surface 95a of the stop tooth 95 moves toward the end of the engagement pallet stone 80 while sliding on the engagement surface 80a as a function of the uncoupling of the pallet stone. engaging 80 from the state shown in FIG. 13. As shown in fig. 15, at a time which is when the working surface 95a of the stop tooth 95 passes over the end of the engagement pallet stone 80, the stop tooth 95 and the setting pallet stone engaged 80 cease to be engaged. Then, the connection between the first control wheel and the second control wheel 55 through the engagement pallet stone 80 and the stop wheel 81 ends.

Therefore, the second control wheel 56 rotates counterclockwise about the second axis of rotation O2, as shown in FIG. 16, because of the power (the rotation torque Tb - the rotation torque Te) resulting from the difference between the rotation torque Tb transmitted from the power source side wheel 12 and the torque of rotation Te transmitted from the spring constant force 27.

When the second control wheel 56 rotates, the second power gear portion 35 can turn clockwise about the first axis of rotation 01. As shown in FIG. 6, the second power gear portion 35 is bonded to the coupling gear portion 31 because the torque control jumper and the coupling tooth 32 are engaged. Therefore, when the second power tooth portion 35 rotates clockwise, the first engaging surface 32a on the coupling tooth 32 moves relative to the distal end 34b of the jumper 34 and it is about to cross the distal end 34b.

However, since the power acting on the second power gear portion 35 is the power (the spinning torque Tb - the spinning torque Te) resulting from the difference between the spinning torque Tb transmitted from the power source side gear wheel 12 and the rotation torque Te transmitted from the constant-force spring 27 as explained above, the power is smaller than the jumper torque Tg produced by the power supply jumper As a result, it is possible to maintain a state in which the distal end 34b of the torque adjusting jumper 34 and the first engaging surface 32a of the coupling tooth 32 are engaged.

As a result, the power, which is transmitted to the second power gear portion 35, can be transmitted to the coupling gear portion 31 via the torque adjusting jumper 34. coupling gear portion 31 and shaft 30 are rotatable clockwise about the first axis of rotation 01.

Therefore, the constant force spring 27 can be armed via the fixed ring 45 attached to the shaft 30. Power can be supplied to the constant force spring 27. In other words, a loss of power due to the transmission of power to the first power wheel 25 can be compensated by means of the power transmitted from the side of the motion cylinder 11, which is the power source. Then, the power of the constant force spring 27 can be kept constant. The exhaust 14 can be actuated by means of a constant torque.

Note that, even when the power is supplied to the constant-force spring 27, the first power wheel 25 rotates with power from the constant-force spring 27 and transmits power from the constant-force spring 27. at the escape wheel 15.

When the power is supplied to the constant-force spring 27 as explained above, as shown in FIG. 16, the stop wheel 81 rotates counterclockwise about the second axis of rotation O2 while turning clockwise about the fifth axis of rotation 05 and follows the engaging shoe stone 80 as a function of the rotation of the second drive wheel 56. The stop wheel 81 catches with the engaging pallet stone 80 by turning a tooth of the drive wheel. 95. The working surface 95a of the stop tooth 95 is again engaged with the engagement surface 80a of the engagement pallet stone 80.

Therefore, as the first control wheel 55 and the second control wheel 56 are linked again, the rotation of the second control wheel 56 and the second power wheel 26 is prevented. The power ceases to be supplied to the constant force spring 27.

By means of a repetition of the operation described above, the stop wheel 81 and the engaging pallet stone 80 may intermittently be engaged and cease to engage. In other words, the planet mechanism 57 can intermittently engage and interlock the stopwheel 81 and the engagement pallet stone 80 and intermittently the second power wheel 26 relative to the first power wheel 25 as a function of the rotation of the first power wheel 25 and the first control wheel 55. Then, a power can be supplied intermittently to the spring with constant force 27.

As explained above, with the constant force mechanism 20 of this embodiment, the exhaust 14 can be operated by means of energy stored in the constant force spring 27 and the power can be supplied. intermittently, from the barrel side of movement 11 to the constant force spring 27. Therefore, the power of the constant force spring 27 can be kept constant, constant torque properties can be maintained and the exhaust 14 can be maintained. be operated in an operation where the torque variations are suppressed.

[0184] The constant force mechanism 20 of this embodiment performs cycle control by means of the planetary mechanism 57. Therefore, unlike a conventional cam type constant force mechanism, it is unlikely that a phenomenon will occur. over-release occurs in the constant-force spring 27.

[0185] As shown in FIG. 3 and FIG. 4, the torque generating mechanism 21 and the cycle control mechanism 22 are arranged to be offset in plan (parallel to a plane). As a result, the thickness of the entire constant force mechanism 20 can be reduced compared to a conventional planetary gear type. In addition, the constant force spring 27 is disposed between the first power wheel 25 and the second power wheel 26. The planetary mechanism 57 is disposed between the first control wheel 55 and the second control wheel 56. Therefore, a scatter in the plane can be reduced. The constant force mechanism 20 may be disposed in a planar space which is small compared to the conventional planetary gear type.

Therefore, it is possible to obtain the constant-force mechanism 20 which achieves compactness and space-saving both in the plane of the timepiece 1 and in the direction of the thickness of the workpiece. 1. The movement 10 and the timepiece 1 can be obtained whose sizes and thicknesses can be easily reduced.

In addition, in the constant force mechanism 20 according to this embodiment, from the moment when the working surface 95a of the stop tooth 95 is engaged with the engagement surface 80a of the engagement pallet stone 80 as shown in FIG. 13 until the working surface 95a and the engagement surface 80 cease to engage as shown in FIG. 15, the support lever 95 holds the engagement pallet stone 80 so that the dummy line L extends according to the force F3 resulting from the combination of the thrust force F1, with which the stopping tooth 95 pushes on the engagement surface 80a, and the friction force F2 resulting from the stop tooth 95 sliding on the engagement surface 80a, crosses the second axis of rotation O2.

Therefore, when the time between engagement and the end of the engagement between the stop tooth 95 and the engagement pallet stone 81 is selected as a cycle, as shown in FIG. fig. 20, an average torque on one cycle can be kept constant when focusing on the rotational torque generated in the support lever 85.

As explained above, in the initial state of engagement illustrated in FIG. 13, the working surface 95a of the stop tooth 95 is engaged deeply with the engagement pallet stone 80. Then, as shown in FIG. 14, depending on the release of the engagement pallet stone 80, the working surface 95a of the stop tooth 95 moves toward the end of the engagement pallet stone 80 while sliding on the engaging surface 80a. As shown in fig. 15, the work surface 95a of the stop tooth 95 and the engagement pad stone 80 cease to be engaged at a time which occurs when the work surface 95a passes the end of the paddle stone 80. In this succession of a cycle, since the angle made by the engagement surface 80a with the stopping tooth 95 changes little, the direction of the resultant force F3 changes according to the change of angle.

At this moment, at the moment when the direction of the resultant force F3 crosses the second axis of rotation O2 in FIG. 14, the rotational torque generated in the support lever 85 is not generated. On the other hand, when the direction of the resulting force F3 is shifted from the second axis of rotation 02 as shown in FIG. 13 and FIG. 15, the rotational torque is generated as a function of the amount of offset.

In particular, before and after the direction of the resultant force F3 crosses the second axis of rotation O2, counter-directional rotation torques are generated. In other words, a rotational torque T tending to bring the support lever 85 toward the stop wheel 81 is generated in the support lever 85 as shown in FIG. 13 and a rotation torque T tending to move the support lever 85 away from the stop wheel 81 is generated in the support lever 85 as shown in FIG. 15.

Therefore, as shown in FIG. 20, although there is a torque variation of the support lever 85 during one cycle, an average torque per cycle can be kept constant. As a result, it is possible to obtain a constant torque as property.

In addition, in this embodiment, the imaginary line L crosses the second axis of rotation O2 in the intermediate position P3 shown in FIG. 14 being in the middle between the setting position P1 shown in FIG. 13, where the stop tooth 95 is engaged with the engagement surface 80a, and a take-off position P2 shown in FIG. 15, where the stop tooth 95 ceases to engage the engagement surface 80a. Then, the average torque on one cycle can be even more stably constant. The result of a constant torque can be obtained even more stably.

In addition, as shown in FIG. 19, the constant force mechanism 20 of this embodiment includes the power control mechanism 110. Therefore, the power of the constant force spring 27 can be adjusted as needed.

For example, we will explain a case in which the constant force spring is armed to increase the power.

In this case, firstly, the eccentric pin 119 is rotated to swing the rocking lever 113 about the tilt rod 117. The second torque adjusting gear portion 111 is moved from the position of absence of meshing P5 to the meshing position P4. Then, the first torque adjusting tooth 33a of the first torque adjusting gear portion 33 can be brought into engagement with the second torque adjusting tooth 111a of the second torque adjusting gear portion 111.

Then, the operating wheel 121 is rotated clockwise. At this moment, the operating wheel 121 is rotated with a higher input torque than the torque obtained by adding the rotation torque Te produced by the constant-force spring 27 and the jumper torque Tk produced by the jumper The second torque-setting portion may be rotated counterclockwise. The power provided for turning the first torque adjusting gear portion 33 clockwise about the first axis of rotation 01 can be transmitted to the first torque adjusting gear portion 33 through the second portion with a torque adjustment tooth 111.

The first torque adjusting gear portion 33 is combined with the coupling gear portion 31 so as to be integral with it. As a result, the power to turn the coupling gear portion 31 clockwise about the first axis of rotation 01 is transmitted to the coupling gear portion 31. At this time, since the power transmitted to the coupling gear portion 31 constitutes the input torque, the coupling gear portion 31 shown in FIG. 6 rotates relative clockwise with respect to the second power tooth portion 35. In other words, the distal end 34b of the torque adjusting jumper 34 and the second engaging surface 34 in engagement 32b of the coupling tooth 32 may cease to be engaged. The coupling gear portion 31 can be rotated clockwise while terminating the rotation limitation by the torque adjusting jumper 34.

Note that the coupling teeth 32 move while passing over the distal end 34b of the torque control jumper 34 one after the other in the circumferential direction, by the rotation of the portion to coupling gear 31.

[0200] Since the coupling gear portion 31 can be rotated in this manner, the fixed ring 45, secured to the shaft 30, can be turned clockwise and the inner end 27a constant force spring 27 can be rotated clockwise. Therefore, a winding of the constant force spring 27 can be realized. It is possible to increase the prestressing of the constant force spring 27 and to adjust the rotation torque Te to increase.

Note that although the second power gear portion 35 does not rotate during the adjustment explained above, the power to turn this second power tooth portion 35 clockwise is transmitted to the second power gear portion 35. The power at this time is set for a torque equal to or greater than the jumper torque Tk. This power is transmitted to the second control wheel 56 and acts to turn this second control wheel 56 counterclockwise about the second axis of rotation 02. At this time, as explained above, the power to turn the second control wheel 56 counterclockwise about the second axis of rotation 02 with the rotating torque Tb is transmitted to the second control wheel 56, from the power source side wheel 12.

Therefore, the power obtained by adding the power from the second power gear portion 35 and the power from the power source side wheel 12 acts on the second drive wheel 56. The working surface 95a of the stopping tooth 95 of the stopping wheel 81 engages the engaging surface 80a of the engagement staple stone 80 in a high thrust state. Therefore, it is possible to appropriately prevent the second power wheel 35 from rotating. The armature of the spring constant force 27 can be achieved quickly, with a good reaction.

We will now expose a case in which the constant force spring 27 is disarmed to reduce the power.

[0204] In this case, the operating wheel 121 shown in FIG. 19 is turned counterclockwise. At this time, the operating wheel 121 is rotated with an input torque smaller than the difference (Tj-Tc) between the jumper torque Tj of the torque adjusting jumper 34 and the rotation torque Te of the spring with constant force 27.

Therefore, it is possible to rotate the second torque adjusting gear portion 111 in a clockwise direction. The power to rotate the first torque adjusting gear portion 33 counterclockwise around the first axis of rotation 01 can be transmitted to the first torque adjusting gear portion 33 by via the second torque-adjusting gear portion 111.

Therefore, the power to turn the coupling gear portion 31 counterclockwise about the first axis of rotation 01 is transmitted to the coupling gear portion 31. At this time, since the power transmitted to the coupling gear portion 31 is the input torque, it is possible to cause the coupling gear portion 31 and the second power gear portion 35 to co-rotate. (Rotate together) counterclockwise, while holding the tap between the distal end 34b of the torque adjusting jumper 34 and the first engaging surface 32a of the coupling tooth 32.

Then, the second control wheel 56 rotates in the direction of clockwise, around the second axis of rotation 02, by the co-rotation (the simultaneous rotation). Therefore, after the upper plate 92 of the support member 90 has moved to the second lever member 87 of the support lever 85, by the rotation of the second control wheel 56, as shown in FIG. . 17, the upper plate 92 comes into contact with the second lever piece 87.

Therefore, it is possible to limit, by means of the second lever piece 87 that the second control wheel 56 rotates more clockwise.

Then, after the rotation of the second control wheel 56 in the direction of clockwise has been limited as explained above, the operating wheel 121 is turned more counterclockwise. shows, with an input torque greater than the difference (Tj-Tc) between the jumper torque Tj of the torque adjusting jumper 34 and the rotation torque Te produced by the constant-force spring 27. At this moment, since the rotation of the second control wheel 56 and the second power wheel 26 is prevented, the coupling gear portion 31 shown in FIG. 6 rotates relatively counterclockwise, relative to the second power wheel 35. In other words, the distal end 34b of the torque control jumper 34 may cease to be taken with the first engagement surface 32a of the coupling tooth 32. It is possible to rotate the coupling gear portion 31 counterclockwise, while releasing the rotation lock (rotation limitation) by the torque control jumper 34.

It will be noted that the coupling teeth 32 move over the distal end 34b, one after the other in the circumferential direction, due to the rotation of the coupling gear portion 31.

As the coupling gear portion 31 can be rotated as explained above, it is possible to rotate the fixed ring 45 fixed to the shaft 31 in the counterclockwise direction and it is possible to It is possible to rotate the inner end 27a of the constant force spring 27 counterclockwise. Therefore, it is possible to disarm the constant force spring 27. It is possible to reduce the prestressing of the constant force spring 27 and to adjust the rotation torque Te to decrease (in the direction of a decrease).

Note that this is not limited to the case of a power adjustment. Even when the rotation torque Tb produced by the movement barrel 11 is smaller than the rotation torque Te produced by the constant-force spring 27 because, for example, the barrel spring 16 in the barrel of movement 11 is disarmed, excessive rotation of the second control wheel in the direction of clockwise can be prevented as in the case explained above. Therefore, it is possible to prevent the constant torque spring 27 from being completely disarmed.

As explained above, since the constant force mechanism 20 includes the power control mechanism 110, it is possible to adjust the power of the constant force spring 27 as needed.

It is possible to operate more stably the exhaust 14, with a constant torque. It is possible to supply power to the constant force spring 27 after assembling the torque generating mechanism 21 explained below. Therefore, it is possible to improve the possibility of assembly. Further, since the second power wheel 26 is disposed in a planar offset position of the cycle control mechanism 22, it is possible to provide the power adjustment mechanism 110 without care (without having to worry). of the cycle control mechanism 22. It is easy to adjust (to mount) the power adjustment mechanism 110.

In addition, it is possible to adjust the power of the constant-force spring 27 by the rotation of the second torque-adjusting gear portion 111 rotated through the operating wheel 121. Therefore, it it is possible to carry out the adjustment in a fine and intuitive way. It is easy to carry out the adjustment work (the adjustment operation). Furthermore, by placing the second torque adjusting gear portion 111 in the non-meshing position P5, when the power setting is not achieved, it is possible to prevent an unintended load from being set. in rotation (unfortunate force of rotation) is applied to the second power wheel 26.

In addition, with the constant force mechanism 20 according to this embodiment, since the constant force mechanism 20 includes the torque generating mechanism 21, it is possible to further obtain the action and effects explained. lower.

In other words, as shown in FIG. 3 and FIG. 4, the definition segment 47 provided at the outer end 27b of the constant force spring 27 releasably (releasably) engages in the slip hole 46 provided in the first power wheel 25. Therefore, the constant force spring 27 and the first power wheel 25 can be easily dismantled by a simple operation to disengage the defining segment 47 from the inside of the slip hole 46.

Therefore, the maintainability of the torque generating mechanism 21 can be improved. The revision and the like can be easily realized. As the constant force spring 27 and the first power wheel 25 can be easily dismantled, maintenance work (maintenance) such as lubrication can also be easily performed.

When the assembly of the torque generating mechanism 21 is performed, simply by engaging the defining segment 47 in the sliding hole 46, it is possible to combine the first power wheel and the second power wheel. As if they were in one piece. It is possible to define a position in the radial direction of the outer end 27b of the constant force spring 27 and suitably position the outer end 27b of the constant force spring 27.

[0219] Specifically, as shown in FIG. 21, the first power wheel 25 is placed (set) above the second power wheel 26 with which the constant force spring 27 is combined. It will be noted that at this stage the constant force spring 27 is in a state in which this spring constant force 27 is not elastically deformed. Then, as shown in fig. 22, the first power wheel 25 and the second power wheel 26 are placed one on top of the other so that the defining segment 47 is in an open portion (an access portion) of the hole Sliding 46. Then, as shown in FIG. 23, the first power wheel 25 and the second power wheel 26 are rotated relatively to each other in opposite directions around the first axis of rotation 01, so that the definition segment 47 penetrates into the sliding hole 46. Therefore, it is possible to easily advance the definition segment 47 in the sliding hole 46, by the sliding movement. As shown in fig. 3 and FIG. 4, it is possible to engage the definition segment 47 with the inside of the sliding hole 46.

[0220] Therefore, it is possible to integrally assemble the first power wheel 25, the second power wheel 26 and the constant force spring 27. It is possible to define the position, in the radial direction, of the outer end 27b of the constant-force spring 27 and to position the outer end 27b of the constant-force spring 27.

Then, by rotating the first power wheel 25 and the second power wheel 26 relative to each other in opposite directions around the first axis of rotation 01 while maintaining positioned the outer end 27b spring constant force 27, it is possible to arm the spring constant force 27 and to give a preload (a preload) to this spring constant force 27. It is possible to store energy. In this case, for example, the arming of the constant force spring 27 by means of the power adjustment mechanism 110 explained above can be realized.

As a result, the torque generating mechanism 21 can be easily assembled. It is possible to improve the practicality (practicability) of the assembly.

In addition, during arming of the constant-force spring 27, the limiting lever 48 provided at the outer end 27b of the constant-force spring 27 can be brought into contact with the rotary cylindrical body 40 of the first power wheel 25. Therefore, it is possible to prevent (limit) that the outer end 27b rotates about the first axis of rotation 01 with the rotational torque implemented with the elastic deformation of the return spring constant force 27 to its initial state. Therefore, it is possible to arm the constant-force spring 27 while preventing segments of this constant-force spring 27 from coming into contact with each other.

Therefore, it is possible to prevent a difference in torque (hysteresis) occurring between a winding moment of the constant-force spring 27 and a moment of release of the energy of this constant-force spring. 27. In addition, at the time of arming the constant-force spring 27, the limiting lever 48 comes into contact with the rotating cylindrical body 40, in a strong manner, from the arming. Therefore, it is easy to maintain a quantity of arming, that is to say a prestressing or preloading of the constant force spring 27.

When the energy stored in the constant-force spring 27 decreases for any reason, that is to say when the prestressing decreases, it is possible to release the definition segment 47 from the inside of the hole. sliding 46 and to move the definition segment 47 away from the inside of the sliding hole 46. Therefore, a change affecting the relative positional relationship between the sliding hole 46 and the defining segment 47 can easily be identified by a visual recognition (it can be easily seen). It can be safely and easily apprehended that the energy stored in the constant-force spring 27 decreases, for example, that the arming amount decreases to 0.

[0226] As explained above, the maintainability, the practicability of maintenance and the feasibility of assembly are improved. Excellent handling ability of the torque generating mechanism 21 can be obtained. Therefore, similarly, it is possible to achieve that the useful constant force mechanism 20, the useful movement and the useful timepiece 1 are excellent in terms of maneuverability.

An embodiment of the present invention has been explained above. However, this embodiment has been presented by way of example and it does not intend to limit the scope of the invention. The embodiment may be implemented in a variety of other ways. Various deletions, replacements and modifications can be made within the scope of the invention (of the spirit of the invention). The embodiment and variants of this embodiment include, for example, embodiments and variants that one skilled in the art can readily assume, embodiments and variants substantially identical to the embodiments and variants thereof. question here, as well as the embodiments and variants in the scope of the equivalents.

For example, in the embodiments, the arrangement for transmitting the power of the mainspring spring 16 housed in the barrel movement 11 to the constant force mechanism 20 is explained by way of example. However, the transmission of power is not limited to this case. For example, the power can come from a mainspring 16 provided in a component other than the movement cylinder 11, up to the constant force mechanism 20.

In the embodiment described above, a movement 10 of the manual arming type for manually cocking the barrel spring 11 by means of the ring 17 is adopted. However, motion 10 is not limited to this case. The movement 10 may be, for example, a self-winding type movement comprising a rotor.

[0230] In the embodiment described above, the power from the movement barrel 11 is transmitted to the second control wheel 56 via the power source side wheel 12. The power from the spring constant force is transmitted from the first power wheel 25 to the exhaust 14, via the wheel on the exhaust side 15. However, the transmission of power is not limited to this case. For example, the power from the motion barrel 11 can be transmitted to the second power wheel 26 via the power source side wheel 12. The power from the constant force spring 27 can be transmitted to the power wheel 26. first control wheel 55 via the first power wheel 25 and transmitted from the first control wheel 55 to the exhaust 14 via the escape gear wheel 15.

In any case, the power from the movement barrel 11 must only be transmitted to the second control wheel 56 or to the second power wheel 26. The power from the constant force spring 27 must only be transmitted from the first power wheel 25 or the first control wheel 55 at the exhaust 14.

[0232] In the embodiment described above, the constant force mechanism 20 is provided at a position equivalent to the average gear. However, the position of the constant force mechanism 20 is not limited to this case. The constant force mechanism 20 may be provided, for example, at a position equivalent to the center pinion 18 or the seconds mobile 19. In all cases, the constant force mechanism 20 must only be provided between the barrel In this case, the constant force mechanism 20 may be arranged to form part of a successive gear train in which the movement barrel 11 and the escapement 14 are connected together. succession. The constant force mechanism 20 may be freely disposed in a power transmission (power transmission path) capable of transmitting power, even in a position out of the successive gear train (out of gear).

In the embodiment described above, the coupling gear portion 31 and the second power gearing portion 35 are connected by means of the torque adjusting jumper 34. However, the connection between the geared portion coupling 31 and the second power gear portion is not limited to this case. The coupling gear portion 31 and the second power gear portion 35 may be connected by means of, for example, a sliding and frictional structure.

In the embodiment described above, the stop wheel 81 is turned and inverted by means of a fixed-toothed portion 82 of the internal gear type. However, the fixed-tooth portion 82 is not limited to this case. The fixed-toothed portion 82 may be a fixed-toothed portion 82 of the external toothing type.

In this case, as shown in FIGS. 24 to 26, it is possible to invert the stop wheel 81 in a clockwise direction around the second axis of rotation 02 while turning the stop wheel 81 in the opposite direction of the needles of a shows around the fifth axis of rotation 05. Even in this case, the direction of rotation of the stop wheel 81 is only opposite to the direction of rotation of the embodiment described above. It is possible to obtain the same action and the same effects. It should be noted that in this case the engagement surface 80a of the engaging pallet stone 80 is turned outward only in the radial direction.

In other words, as shown in FIG. 24, at an initial stage of engagement, the working surface 95a of the stopper tooth 95 engages deeply with the engagement pallet stone 80. Next, as shown in FIG. 25, the working surface 95a of the stopping tooth 95 moves toward the end of the engagement pallet stone 80 while sliding on the engagement surface 80a, by the stopping process. taking the stone forming an engagement pallet 80. As shown in FIG. 26, the working surface 95a of the stop tooth 95 and the engaging pallet stone 80 cease to be engaged at a time of the time which is when the working surface 95a of the stopping tooth 95 passes over the end forming pallet 80.

At this moment, the support lever 85 carries the engagement pallet stone 80 so that the imaginary line L extends according to the force F3 resulting from the thrust force F1, with which the tooth of stopping 95 pushes on the engaging surface 80a and the frictional force F2 generated by the fact that the stopping tooth 95 slides on the engagement surface 80a crosses the second axis of rotation 02. It should be noted that, in the case where the fixed-toothed portion 82 is of the type with external teeth, the direction of rotation of the stop tooth 81 is opposite to the direction of rotation occurring in the embodiment described above. Therefore, the resulting force F3 is rotated in the direction of the second axis of rotation O2.

[0238] Even in the case of a fixed-toothed part 82 of the type with external teeth, at the moment when the direction according to the resultant force F3 crosses the second axis of rotation 02 as represented in FIG. 25, the rotational torque generated in the support lever 85 is not generated. When the direction according to the resultant force F3 (the direction of this force) shifts from the second axis of rotation O2 as shown in Figs. 24 and 26, a rotational torque is generated depending on the amount of the offset.

In particular, before and after the direction of the resultant force F3 crosses the second axis of rotation 02, counter-rotating torques are generated. In other words, the rotation torque T for bringing the support lever 85 toward the stop wheel 81 is generated when the support lever 85 is as shown in FIG. 26, while the rotation torque T tending to move the support lever 85 away from the stop wheel 81 is generated when the support lever 85 is as shown in FIG. 24.

[0240] Therefore, even in the case of a fixed-toothed part 82 of the type with external teeth, when the period from the engagement to the cessation of engagement between the toothed portion 96 and the engagement pallet stone 80 is selected as a cycle, it is possible to maintain constant the average torque which is the average over one cycle of the rotational torque produced by the support lever 85.

In the embodiment described above, the distal end 48a of the limiting lever 48 is brought into contact with the rotatable cylindrical body 40 within the first power wheel 25. However, the contact of the end distal 48a of the limitation lever 48 is not limited to this case. For example, as shown in FIG. 27, an upwardly projecting pin 130 may be provided at the distal end 48a of the limiting lever 48. The limiting pin 130 may be brought into contact with an inner wall 131 (the limiting segment of rotation according to the present invention) of the opening in the power tooth portion 41. In this case, it is possible to obtain the same action and the same effects.

In addition, as shown in FIG. 28, the distal end 48a of the limiting lever 48 can be brought into contact with a limiting rod 135 (the rotation limiting segment according to the present invention) projecting downwardly from the arm 41a within the first power wheel 25. In this case, it is possible to obtain the same action and the same effects.

[0243] Note that in FIG. 28, a through hole 136 (the first engaging segment of the present invention) having an elongated hole shape extending in a direction orthogonal to the radial direction of the first axis of rotation O1 in a plan view is formed in the arm 41a. The head 51 of the definition segment 47 has a rectangular shape in a plan view according to the through hole 136 and is able to rotate about the central axis of the shaft 50. Therefore, by turning the head 51 after having inserted the head 51 into the through hole 136, it is possible to engage the defining segment 47 with the inside (inner side) of the through hole 136 and it is possible to prevent the defining segment 47 from slipping out of the through hole 136.

Therefore, in this case, it is possible to define the position, in the radial direction, of the outer end 27b of the constant force spring 27. It is possible to obtain the same action and the same effects.

In the embodiment described above, the inner end 27a of the constant force spring 27 is fixed to the second power wheel 26, via the fixed ring 45. The definition segment 47 which defines the position, in the radial direction, of the outer end 27b and the limiting lever 48 which limits the outer end 27b rotates about the first axis of rotation 01 by the spring return of the constant-force spring 27 towards its initial shape are provided at the outer end 27b of the constant force spring 27. However, the constitution of the constant force spring 27 is not limited to this case.

For example, the outer end 27b of the constant force spring 27 can be attached to the first power wheel 25 via, for example, a press stud. A definition segment which defines the position, in the radial direction, of the inner end 27a and a limiting lever which limits that the inner end 27a rotates about the first axis of rotation 01 due to the springback of the spring force constant 27 to its original position may be provided at the inner end 27a of the constant force spring 27.

With the constant force spring 27 configured in this way, it is possible to obtain the same action and the same effects.

In the explanation of the embodiment described above, the constant force spring 27 is armed (that is to say the number of revolutions is increased) by a winding operation carried out by the generating mechanism. However, the winding operation is not limited to this case. The constant force spring 27 can be unwound (its number of revolutions can be reduced) by the arming operation.

In this case, for example, the constant force spring 27 must only be attached (mounted) in the opposite direction to that of the embodiment described above (to be reversed). It is not necessary to modify the components such as the sliding hole 46, the defining segment 47 and the limiting lever 48. In addition, it is not necessary to change, for example the position of the spring force. constant with respect to the first power wheel 25 and the second power wheel 26.

In all cases, the torque generating mechanism 21 according to the present invention can be applied in any of the two cases in which winding and unwinding are performed by the winding operation. It is possible to store elastic energy in the constant-force spring 27. It should be noted that a reduction in the elastic energy of the constant-force spring 27 is called a disarming.

1. A constant force mechanism comprising: a first power wheel that rotates about a first axis of rotation; a second power wheel which is disposed coaxially with the first power wheel and is rotatable relative to the first power wheel about the first axis of rotation; a power spring which is disposed between the first power wheel and the second power wheel and transmits stored energy to the first power wheel and the second power wheel; and a cycle control mechanism that intermittently rotates the second power wheel relative to the first power wheel and provides energy to the power spring, the cycle control mechanism comprising: a first power wheel; control which rotates about a second axis of rotation according to the rotation of the first power wheel; a second control wheel which is arranged coaxially with the first control wheel and which is able to rotate relatively relative to the first control wheel, about the second axis of rotation, and which meshes with the second power wheel ; and a planetary mechanism which is disposed between the first control wheel and the second control wheel and which causes, intermittently, depending on the rotation of the first control wheel, that an engagement pawl equipping the first control wheel the control wheel engages and releases with a stop wheel fitted to the second control wheel, the first power wheel or the first control wheel transmitting power from the power spring to an exhaust, and the power from a power source is transmitted to the second power wheel or the second control wheel. The constant force mechanism of claim 1, wherein the engagement pawl rotates about the second axis of rotation as a function of the rotation of the first drive wheel, the stopwheel rotates about the second axis. rotating while rotating as a function of the rotation of the second control wheel and comprising a locking gear portion engageable with and disengaging from the engagement pawl, and

Claims (8)

In the embodiment described above, the inner end 27a of the constant force spring 27 is fixed to the second power wheel 26, via the fixed ring 45. The definition segment 47 which defines the position, in the radial direction, of the outer end 27b and the limiting lever 48 which limits the outer end 27b rotates about the first axis of rotation 01 by the spring return of the constant-force spring 27 towards its initial shape are provided at the outer end 27b of the constant force spring 27. However, the constitution of the constant force spring 27 is not limited to this case. For example, the outer end 27b of the constant force spring 27 can be attached to the first power wheel 25 via, for example, a press stud. A definition segment which defines the position, in the radial direction, of the inner end 27a and a limiting lever which limits that the inner end 27a rotates about the first axis of rotation 01 due to the springback of the spring force constant 27 to its original position may be provided at the inner end 27a of the constant force spring 27. [0247] With the constant force spring 27 configured in this way, it is possible to obtain the same action and the same effects. In the explanation of the embodiment described above, the constant force spring 27 is armed (that is to say the number of revolutions is increased) by a winding operation carried out by the generating mechanism. However, the winding operation is not limited to this case. The constant force spring 27 can be unwound (its number of revolutions can be reduced) by the arming operation. In this case, for example, the constant force spring 27 must only be attached (mounted) in the opposite direction to that of the embodiment described above (to be reversed). It is not necessary to modify the components such as the sliding hole 46, the defining segment 47 and the limiting lever 48. In addition, it is not necessary to change, for example the position of the spring force. constant in relation to the first power wheel 25 and the second power wheel 26. In any case, the torque generating mechanism 21 according to the present invention can be applied in either of the two cases. which winding and unwinding are performed by the winding operation. It is possible to store elastic energy in the constant-force spring 27. It should be noted that a reduction in the elastic energy of the constant-force spring 27 is called a disarming. claims A constant force mechanism comprising: a first power wheel which rotates about a first axis of rotation; a second power wheel which is disposed coaxially with the first power wheel and is rotatable relative to the first power wheel about the first axis of rotation; a power spring which is disposed between the first power wheel and the second power wheel and transmits stored energy to the first power wheel and the second power wheel; and a cycle control mechanism that intermittently rotates the second power wheel relative to the first power wheel and provides energy to the power spring, the cycle control mechanism comprising: a first power wheel; control which rotates about a second axis of rotation according to the rotation of the first power wheel; a second control wheel which is arranged coaxially with the first control wheel and which is able to rotate relatively relative to the first control wheel, about the second axis of rotation, and which meshes with the second power wheel ; and a planetary mechanism which is disposed between the first control wheel and the second control wheel and which causes, intermittently, depending on the rotation of the first control wheel, that an engagement pawl equipping the first control wheel the control wheel engages and releases with a stop wheel fitted to the second control wheel, the first power wheel or the first control wheel transmitting power from the power spring to an exhaust, and the power from a power source is transmitted to the second power wheel or the second control wheel. The constant force mechanism of claim 1, wherein the engagement pawl rotates about the second axis of rotation as a function of the rotation of the first drive wheel, the stopwheel rotates about the second axis. rotational while rotating as a function of the rotation of the second drive wheel and comprises a stopping gear portion engageable with and disengaging from the engagement pawl, and after the locking gear portion has engaged, the engaging pawl rotates about the second axis of rotation to release from the stopping gear portion, depending on the rotation of the first gear wheel. control and is released from the cut-away portion. The constant force mechanism of claim 2, further comprising a support lever which is rotatable about the second axis of rotation as a function of the rotation of the first control wheel and which carries the engagement pawl. a constant-force mechanism in which the engagement pawl has an engagement surface with which the locking gear portion is engaged and from which the locking gear portion is released, and between when the staggered portion engages the engaging surface until the staggered portion engaged with the engagement surface is released (ceases to be in engagement) , the support lever carries the engagement pawl such that a dummy line extends according to the force resulting from a pushing force, with which the stop gear portion pushes against the engagement surface , and a rubbing force ent generated by the sliding of the staggering portion on the engagement surface crosses the second axis of rotation. The constant force mechanism according to claim 3, wherein the dummy line crosses the second axis of rotation in an intermediate position between a setting position, wherein the locking gear portion engages the engagement surface. , and an end-of-setting position (release position), wherein the stopping-off portion ceases to engage the engagement surface. The constant force mechanism according to one of claims 1 to 4, further comprising a power control mechanism which adjusts the power of the power spring via the first power wheel or the second power wheel. . The constant force mechanism of claim 5, wherein the power control mechanism comprises: an adjusting wheel operable to mesh with the first power wheel or the second power wheel; and a movable member which moves the adjusting wheel between a meshing position, wherein the adjusting wheel meshes with the first power wheel or with the second power wheel, and a non-meshing position, where the meshing between the adjusting wheel and the first power wheel or with the second power wheel is absent. 7. Timepiece movement comprising a constant-force mechanism according to one of claims 1 to 6. 8. Timepiece comprising a timepiece movement according to claim 7.