CH713702B1 - Torque compensation mechanism, constant force mechanism, timepiece movement and timepiece. - Google Patents

Abstract

The invention relates to a torque generating mechanism (21) comprising a first power transmission wheel (25) which rotates around a first axis of rotation, a second power transmission wheel (26) which is disposed coaxial with the first power transmission wheel, and a spiral drive spring (27) which is disposed between the first power transmission wheel and the second power transmission wheel and which transmits stored energy , to the first power transmission wheel and to the second power transmission wheel. A first engagement part (46) is provided on the first power transmission wheel (25). At one end (27b) of the drive spring are provided a second engagement portion (47) capable of reversibly engaging the first engagement portion (46) so as to define the position of the aforementioned end in the radial direction, as well as a rotation limiter (48) adapted to abut against a part of the first power transmission wheel to limit the rotation of the aforementioned end around the first axis of rotation with the deformation of the drive spring.

Description

BACKGROUND OF THE INVENTION

1. Field of the invention

The present invention relates to a torque generating mechanism, a constant force mechanism, a timepiece movement and a timepiece.

2. Description of Related Prior 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 barrel spring unwinds, the angle of oscillation of the balance-spring varies according to the variation of the torque so as to cause the diurnal rate (the degree of delay or advance of the timepiece) of the timepiece to change. Consequently, in order to prevent the torque transmitted to the escapement from varying, it is known to provide a constant-force mechanism within the power transmission from the barrel bridge to the escapement.

[0003] In a constant force mechanism of this type, in order to suppress the torque variations affecting the output torque, it is desired to use a drive spring (a constant force spring) which can ensure a large deflection angle. As an example of such a drive spring, a coil spring and a coil spring are known. Among the springs, the spiral spring is widely used from the viewpoint of its superiority in cross section, i.e., superiority for thickness reduction. For example, patent document 1 (European patent application having publication number 2034374) discloses a constant force mechanism comprising a coil spring as the drive spring.

[0004] However, in the conventional constant-force mechanism, as a general method for fixing a hairspring within a hairspring balance, an outer end of the hairspring is fixed to a peak by, for example, gluing or caulking. Therefore, a power source-side wheel and an exhaust-side wheel, which are coupled to each other by the drive spring, are integrally combined by means of the drive spring to constitute an assembled component. Therefore, in particular, during an overhaul, the outer end of the spiral spring and the eyebolt cannot be separated unless the gluing, caulking or the like of the outer end of the spiral spring and the eyebolt is rendered ineffective. Therefore, the maintainability is low. When assembling the constant force mechanism, since one must assemble the constituent parts while maintaining a coil spring winding amount after the coil spring winding of a given amount, the feasibility of the assembly is weak. Further, since the outer end of the coil spring and the eyebolt are integrally coupled, the feasibility of, for example, lubrication for maintenance is also low.

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 torque generating mechanism, a constant force mechanism, a timepiece movement and a timepiece which are more practical, for example to revise. (1) A torque generating mechanism according to the present invention is defined by claim 1.

[0006] With the torque generating mechanism according to the present invention, the second engaging part provided at one of the ends of the driving spring (i.e. a circumferential end of the driving spring drive) is reversibly engaged with the first engagement portion provided on the first power transmission wheel. Therefore, the driving spring and the first power transmitting wheel can be easily dissociated by a simple operation of breaking the engagement of the second engaging part with respect to the first engaging part. in take.

[0007] Therefore, it is possible to improve the maintainability and it is possible to easily perform overhaul or the like. Since the drive spring and the first power transmission wheel can be easily separated, maintenance work such as lubrication can also be easily performed.

[0008] Further, when the assembly is carried out simply by engaging the second engaging part with the first engaging part, it is possible to integrally combine the driving spring, the first transmission wheel power transmission wheel and the second power transmission wheel and it is possible to define and position the position in the radial direction of the aforementioned end of the drive spring. Therefore, it is possible to cock the drive spring and produce and store power (torque) in the drive spring, by rotating the first power transmission wheel and the second power transmission wheel relative to each other, in opposite directions, around the first axis of rotation, while maintaining the aforementioned end of the drive spring in position. Therefore, it is possible to increase the assembling feasibility.

Furthermore, during the winding of the drive spring, the rotation limiter provided at the aforementioned end of the drive spring can be brought into contact with the rotation limiting part. Consequently, it is possible to limit the rotation of the aforementioned end around the first axis of rotation with, for example, the rotation torque related to the elastic deformation of the drive spring. Therefore, it is possible to cock the drive spring while preventing the spring segments within the drive spring from coming into contact with each other. Therefore, it is possible to prevent a torque difference (hysteresis) from occurring between the moment of charging the driving spring and the moment of releasing power by the driving spring. In addition, during the winding of the drive spring, since the rotation limiter comes into contact with the rotation limiting part more strongly gradually depending on the winding, it is easy to determine a winding amount , that is to say to preload the drive spring. (2) The torque generating mechanism may be according to claim 2.

[0010] In this case, when the assembly is performed, since the second engaging part can be engaged by sliding, it is possible to further improve the assembly feasibility. When the energy stored in the drive spring decreases for one reason or another, i.e. when the preload decreases, the second engagement part ceases to be in engagement with the first part of engagement. Therefore, it is possible to move the second engagement part away from the inside of the slider, which forms the first engagement part. Accordingly, a change in the relative positional relationship between the first engagement portion and the second engagement portion can be readily visually apprehended. One can easily and certainly apprehend that the power stored in the drive spring decreases, for example that the amount of winding has decreased to zero. (3) A constant force mechanism according to the present invention is defined by claim 3.

With the constant force mechanism according to the present invention, as this constant force mechanism comprises a control mechanism, it is possible to supply power to the drive spring. Therefore, it is possible to keep the power of the drive spring constant. For example, it is possible to actuate the escapement in a stable manner, with a constant torque.

[0012] In particular, the upkeep, the feasibility of maintenance and the feasibility of assembly are improved. Since the constant-force mechanism includes the torque-generating mechanism which is excellent in handleability, it is possible to achieve a useful constant-force mechanism which is also excellent in handleability. (4) The drive mechanism may include: a first drive wheel which is rotatable about a second axis of rotation depending on the rotation of the first power transmission wheel; a second control wheel which is arranged coaxially with the first control wheel and which is rotatable relative to the first control wheel, around the second axis of rotation, and which is meshed with the second power transmission wheel; and a planetary mechanism which is arranged between the first control wheel and the second control wheel and which is such that, intermittently, depending on the rotation of the first control wheel, a pawl fitted to the first control wheel is able to engage with and release from with a stop wheel fitted to the second control wheel. It is possible that the first power transmission wheel and the first drive wheel transmit power from the drive spring to the escapement. It is possible that power from a power source is transmitted to the second power transmission wheel or the second control wheel.

[0013] In this case, when the first power transmission wheel rotates, it is possible to rotate the first control wheel. It is possible to transmit power from the drive spring to the escapement, via the first power transmission wheel or the first drive wheel. Therefore, it is possible to operate the escapement. The planetary mechanism which intermittently causes the pawl to engage and disengage from the stopper wheel depending on the rotation of the first drive wheel is provided between the first drive wheel and the second drive wheel. control. Therefore, it is possible to intermittently rotate the second power transmission wheel relative to the first power transmission wheel and perform cycle control by means of engagement and disengagement. in engagement with the planetary mechanism.

[0014] The power resulting from the difference between the power coming from the power source and the power coming from the driving spring acts on the second power transmission wheel and on the second control wheel. However, when the pawl and the stopper wheel are engaged, rotation of the second power transmission wheel and the second drive wheel is prevented by the engagement (being engaged). When the first control wheel rotates according to the rotation of the first power transmission wheel from this state, since the pawl and the stopper wheel are not engaged, the second power transmission wheel and the second drive wheel both rotate with the power resulting from the difference between the power from the power source and the power from the drive spring. Therefore, it is possible to intermittently rotate the second power transmission wheel with respect to the first power transmission wheel. It is possible to supply power to the drive spring. Therefore, it is possible to keep the power of the drive spring constant. It is possible to actuate the escapement with a constant torque.

[0015] It will be noted that, simultaneously with the supply of power to the drive spring, the pawl and the stop wheel again engage according to the rotation of the second control wheel. Therefore, it is possible to repeat the engagement and release between the pawl and the stopper wheel. It is possible to intermittently rotate the second power transmission wheel with respect to the first power transmission wheel. (5) A timepiece movement according to the present invention includes the torque generating mechanism. (6) A timepiece movement according to the present invention includes the constant force mechanism. (7) A timepiece according to the present invention includes the timepiece movement.

[0016] In this case, it is possible to achieve a useful timepiece movement and a useful timepiece which are excellent in handleability.

According to the present invention, it is possible to obtain a torque generating mechanism, a constant force mechanism, a timepiece movement and a timepiece whose ability to be manipulated is improved.

BRIEF DESCRIPTION OF DRAWINGS

Figure 1 is an exterior view of a timepiece representing an embodiment of the present invention. Figure 2 is a block diagram of a movement shown in Figure 1. Figure 3 is a perspective view of a constant force mechanism shown in Figure 2. Figure 4 is a top view of the force mechanism constant force shown in Figure 3. Figure 5 is a sectional view along the line A-B shown in Figure 4 and shows the constant force mechanism. Figure 6 is a perspective view showing part of a second power transmission wheel shown in Figure 3. Figure 7 is a bottom view of the constant force mechanism shown in Figure 3. Figure 8 is a perspective view showing part of a second control wheel and the second power transmission wheel shown in Figure 3. Figure 9 is a perspective view showing part of the second power transmission wheel shown in Fig. 3. Fig. 10 is a perspective view showing the second drive wheel and a planetary gear mechanism shown in Fig. 3. Fig. 11 is a plan view showing an engagement state between a paddle and a tooth stopper shown in Fig. 10. Fig. 12 is a cross-sectional view of the control wheel and a stopper wheel shown in Fig. 10. Fig. 13 is a plan view showing an on state. e engaged between the pallet and the stopper tooth shown in Fig. 11. Fig. 14 is a plan view showing a state in which the pallet begins to release from the stopper tooth from the state shown in Fig. 13. Fig. 15 is a plan view showing a state in which the pallet no longer releases the stopper tooth, from the state shown in Fig. 14. Fig. 16 is a plan view showing a state in which the pallet and the stopper tooth are released from each other, from the state shown in Fig. 4. Fig. 17 is a plan view showing a state in which an element support of the stop wheel and a second lever portion come into contact, from the state shown in Figure 4. Figure 18 is a sectional view along the line A-C shown in Figure 4 and shows the constant force mechanism. Fig. 19 is a perspective view of the constant force mechanism and a diagram for explaining a power adjusting mechanism. Figure 20 is a diagram showing the torque variations involved in engaging the paddle with the stopper tooth and releasing them from each other. Fig. 21 is a perspective view showing a state prior to assembly of a torque generating mechanism shown in Fig. 3, and it is a diagram showing a state in which the first power transmission wheel is placed above the second power transmission wheel to which is assembled a constant force spring. Fig. 22 is a diagram showing a state in which the first power transmission wheel and the second power transmission wheel are put on top of each other so that a definition segment is in a opening a slide, from the state shown in Fig. 11. Fig. 23 is a diagram showing a state in which the first power transmission wheel and the second power transmission wheel are rotated one by one. relative to each other in opposite directions and the defining segment engages the inner side of the slider, from the state shown in Figure 22. Figure 24 is a diagram showing a variation according to the present invention and it is a plan view showing a state of engagement between the pallet and the stopper tooth in a fixed-tooth part of an external gear type. Fig. 25 is a plan view showing a state in which the pallet begins to release from the stopper tooth, from the state shown in Fig. 24. Fig. 26 is a plan view showing a state in wherein the pallet is further released from the stopper tooth, from the state shown in Fig. 25. Fig. 27 is a perspective view showing a variation of the torque generating mechanism according to the present invention. Fig. 28 is a perspective view showing another variation of the torque generating mechanism according to the present invention.

DESCRIPTION OF EMBODIMENTS

An embodiment according to the present invention will be explained below, with reference to the drawings. Note that in this embodiment, a mechanical timepiece is explained as an example of a timepiece. On the drawings, the proportions (scales) of the components are changed where appropriate by the need to show the components at visually recognizable sizes.

Basic constitution of the timepiece

[0020] Generally, a machine body comprising a driving part of a timepiece is called the “movement”. The condition of the finished product obtained by attaching a dial and hand to the movement and mounting the movement in a timepiece box is called an “as-built” timepiece.

[0021] Among the two sides of the plate forming a frame of the timepiece, the side where the glass of the timepiece case is located (that is to say the side where the dial is ) is called the „back side“ of the movement. Of the two sides of the plate, the side where the caseback of the timepiece case is located (i.e. the side opposite the dial) is called the "front side" of the movement.

[0022] It should be noted that in the following explanations in this embodiment, the dial direction towards the bottom of the case is defined as the upward direction and that the opposite direction is defined as the downward direction. A clockwise direction of rotation as seen from above, around axes of rotation, is called clockwise, while a counterclockwise direction of rotation clockwise as seen from above, around axes of rotation, is called counter-clockwise.

As shown in Figure 1, a timepiece in the complete state 1 in this embodiment comprises, inside a timepiece case comprising a case bottom not shown and a crystal 2, a movement 10 (the timepiece movement in accordance with the present invention), a dial 3 comprising a scale indicating information relating at least to the time, as well as hands 4 including an hour hand 5 , a 6 minute hand and a 7 second hand.

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

It should be noted that the cog wheel on the power source side 12 in this embodiment designates a cog wheel located more towards the side of the barrel 11, which is the power source, than does the is the constant force mechanism 20 when viewed from the constant force mechanism 20. Similarly, the escapement side cog wheel 15 in this embodiment refers to the cog wheel located more on the escapement side 14 than 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 an average mobile generally forming a front cog wheel. A function of the average mobile is fulfilled by the set of wheels which are a first power transmission wheel 25, a second power transmission wheel 26, a first control wheel 55 and a second control wheel 56 explained below. .

It should be noted that, as shown in Figure 3, the first power transmission wheel 25 and the second power transmission wheel 26 rotate around a first axis of rotation O1. The first control wheel 55 and the second control wheel 56 rotate around a second axis of rotation 02 disposed at a position offset in a direction in the plane of a plate not shown, relative to the first axis of rotation O1.

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

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

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

As shown in Figures 3 and 4, the center wheel set 18 is axially supported between the plate and a gear bridge, not shown, and it rotates around a third axis of rotation 03, due to the rotation of the barrel 11 The third axis of rotation 03 is arranged at a position offset in a direction of the plane of the plate, with respect to the second axis of rotation 02.

[0032] It should be noted that, when the center mobile 18 rotates, this leads to a roadway not shown rotating. The minute hand 6 shown in Figure 6 is secured to the floor. The minute hand indicates the „minutes“ according to the rotation of the road. The minute hand 6 rotates at a rotational speed set by the escapement 14 and the speed regulator 13 at the rate of one revolution per hour.

[0033] When the center mobile 18 rotates, this causes a minute wheel, not shown, to rotate. In addition, an hour wheel, not shown, 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 gear wheel 12. The hour hand 5 shown in FIG. 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 rotational speed set by the escapement 14 and the speed regulator 13, for example at the rate of one revolution every 12 hours.

As shown in Figure 2, the escapement side gear wheel 15 mainly comprises a seconds mobile 19.

As shown in Figures 3 and 4, the seconds wheel 19 is supported axially between the plate and the gear bridge and rotates around a fourth axis of rotation 04, depending on the rotation of the first wheel. power transmission 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, with respect to the first axis of rotation O1. The seconds hand 7 represented in FIG. 1 is attached to the seconds wheel 19. The seconds hand 7 indicates the “seconds”, according to the rotation of the seconds wheel 19. The seconds hand 7 rotates at a speed regulated by the exhaust 14 and the speed regulator 13, for example at the rate of one revolution per minute.

[0036] The escapement 14 mainly comprises an escapement wheel set, not shown, and an anchor, not shown.

[0037] The escape wheel set is supported axially between the plate and the gear-train bridge and meshes with the seconds wheel set 19. Consequently, the power coming from a constant-force spring 27 described below, within the constant-force mechanism 20, is transmitted to the escapement wheel through the seconds wheel 19. Consequently, the escape wheel rotates with the power coming from the constant-force spring 27.

[0038] 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 a pallet, not shown. The two stones forming a pallet are alternately in engagement with and released from an escapement toothing within the escapement wheel set, according to a cycle predetermined by the speed regulator 13. Consequently, the escapement wheel set is able to be released according to the predetermined cycle.

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

[0040] The balance-spring comprises a balance shaft, a balance wheel, as well as a hairspring, and it is supported axially between the plate and a balance bridge, not shown. The balance-spring performs an alternating rotational movement (it rotates regularly with reversal of direction) having a fixed angle of oscillation, using the balance-spring as a power source.

Constitution of the constant force mechanism

As shown in Figures 2 to 4, the constant force mechanism 20 is a mechanism provided to suppress variations (torque variations) affecting the power transmitted to the escapement 14. The constant force mechanism 20 mainly comprises a torque generating mechanism 21 and a control mechanism 22.

Constitution of the torque generation mechanism

[0042] The torque generating mechanism 21 comprises the first power transmission wheel 25 which rotates around the first axis of rotation O1, the second power transmission wheel 26 which is arranged coaxially with the first power transmission wheel 25 and which is able to rotate relatively with respect to the first power transmission wheel 25, around the first axis of rotation O1, as well as the constant force spring 27 (the drive spring according to the present invention), which is disposed between the first power transmission wheel 25 and the second power transmission wheel 26 and transmits the stored power to the first power transmission wheel 25 and the second power transmission wheel 26.

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

As shown in Figures 3 to 6, the second power transmission wheel 26 is supported axially between the plate and the gear bridge. The second power transmission wheel 26 comprises a shaft 30 extending along the first direction of rotation O1, a part with coupling teeth 31 formed integrally with the shaft 30, a first part with adjustment teeth of torque 33 assembled in a single piece with the part with coupling teeth 31, as well as a second part with power teeth 35 which comprises a torque adjustment jumper 34, which is releasably engaged (reversibly) with a coupling tooth 32 within the coupling toothed part 31 and is connected to the coupling toothed part 31 via the torque adjustment jumper 34.

[0045] It will be noted that the second power transmission wheel 26 rotates with the power transmitted from the constant force spring 27.

As shown in Figure 5, shaft 30 extends upward beyond first power transmission wheel 25.

The coupling gear portion 31 is provided between the middle portion in the top-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 toothed part 31, at intervals from each other along the circumferential direction of this coupling toothed part 31.

[0048] Each of the mating teeth 32 includes a first engaging surface 32a facing the counterclockwise side around the first axis of rotation 01 and a second engaging surface 32b facing to the side in a clockwise direction around this first axis of rotation O1.

The first engagement surface 32a is formed along the radial direction orthogonal to the first axis of rotation O1. On the other hand, the second engaging surface 32b tilts so as to gradually extend to the counterclockwise side to the outer side in the radial direction, from the outer circumferential surface of the coupling tooth part 31.

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

As shown in Figures 5 and 7, first torque adjusting teeth 33a, with which second torque adjusting teeth 111a of a second torque adjusting tooth portion 111 described below mesh, are formed. over the entire outer circumference of the first part with torque adjustment teeth 33.

As shown in Figures 5 and 6, the second power tooth part 35 has an annular shape surrounding the coupling teeth 32, from the outer side in the radial direction, and it is placed on the first part with torque adjustment teeth 33 so as to be able to rotate around the first axis of rotation 01. In the example shown in the figures, the second part with power teeth 35 is formed so as to have a larger diameter than the first part with torque adjustment teeth 33.

[0053] Second power teeth 35a, with which second control teeth 62a mesh within a second control toothing part 62 described below, are formed over the entire outer circumference of the second power toothing part. 35.

In the second part with power teeth 35, is formed an opening 36 (opening portion) which crosses vertically right through the second part with power teeth 35 and which uncovers (gives access) the coupling teeth 32 on a fixed range. The torque adjustment jumper 34 is integral with the second part with power teeth 35 so as to be in the opening 36.

[0055] Specifically, a proximal end 34a of the torque setting jumper 34 is integral with the second power toothed portion 35 and, formed as a free end, a distal end 34b of the torque setting jumper couple 34 is elastically deformable around the proximal end 34a so as to move in the radial direction.

[0056] A portion of the distal end 34b of the torque adjustment jumper 34 projects towards the part with coupling teeth 31 and it is arranged so as to penetrate between the coupling teeth 32 adjacent to each other. in the circumferential direction. At this time, the distal end 34b of the torque adjusting jumper 34 is urged by a predetermined spring force (elastic restoring force) so as to penetrate between the coupling teeth 32 adjacent to each other along the circumferential direction. .

[0057] Consequently, the distal end 34b of the torque adjustment jumper 34 is in engagement with the first engagement surface 32a of that of the coupling teeth 32 adjacent to each other in the circumferential direction. clockwise after the distal end 34b and engages the second engaging surface 32b of the other mating tooth 32 counterclockwise after it. clockwise, the distal end 34b of the torque setting 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 setting jumper 34 with the first engaging surface 32a of the mating tooth 32 being farther clockwise than the distal end 34b of the torque setting jumper 34. It is possible to cause the second power-toothed portion 35 co-rotates counter-clockwise, through the torque setting jumper 34, as long as the distal end 34b and the first engagement surface 32a are not not uncoupled.

[0059] It will be noted that when the counter-clockwise torque, wherein the distal end 34b of the torque setting jumper 34 and the first engaging surface 32a of the coupling tooth 32 are not in engagement (unmated), is applied to the coupling tooth portion 31, the distal end 34b of the torque adjusting jumper 34 and the first engaging surface 32a are not in engagement ( are not coupled). Therefore, the coupling tooth 32 moves counterclockwise while crossing the distal end 34b of the torque adjusting jumper 34 in the circumferential direction. Therefore, it is possible to rotate the coupling toothed part 31 relatively, counterclockwise, with respect to the second power toothed part 35.

On the other side, when the coupling gear portion 31 rotates clockwise, the distal end 34b of the torque setting jumper 34 is pushed outward in the direction radially, while sliding on the second engagement surface 32b with the inclination of this second engagement surface 32b of the coupling tooth 32 located after, in the counterclockwise direction, the distal end 34b of the torque adjustment jumper 34.

[0061] Consequently, the distal end 34b of the torque adjustment jumper 34 and the second engagement surface 32b are not engaged (are not mated, are released). The coupling tooth 32 moves clockwise while crossing the distal end 34b of the torque setting jumper 34 in the circumferential direction. Therefore, it is possible to relatively rotate the coupling gear part 31 clockwise, with respect to the second power gear part 35.

[0062] In other words, the torque setting jumper 34 and the coupling teeth 32 function as a ratchet mechanism (ratcheting mechanism) which, when the coupling tooth part 31 rotates in the opposite direction clockwise, causes the second power toothed part 35 to rotate together and which, when the coupling toothed part 31 rotates clockwise, allows relative rotation of the coupling toothing 31 with respect to the second power toothing part 35.

[0063] It will be noted that a spring force (an elastic return) of the torque adjustment jumper 34 is adjusted so that, when the coupling toothed part 31 is turned counterclockwise with a torque Tj, the distal end 34b of the torque setting jumper 34 and the first engaging surface 32a of the coupling tooth 32 are not engaged (are uncoupled). In the following explanation, the torque Tj is referred to as the jumper torque Tj of the torque setting jumper 34.

[0064] Further, the spring force (elastic return) produced by the torque adjustment jumper 34 is adjusted so that when the coupling toothed portion 31 is rotated clockwise with a torque Tk, the distal end 34b of the torque setting jumper 34 and the second engaging surface 32b of the mating teeth 32 are not engaged (are uncoupled). In the following explanations, the torque Tk is called the jumper torque Tk of the torque setting jumper 34.

As shown in Figure 5, a limiting ring 37 which prevents the distal end 34b of the torque adjustment jumper 34 from moving upwards is arranged above the second part with power teeth 35.

[0066] The limiting ring 37 has an annular shape surrounding the part with coupling teeth 31 from the outer side in the radial direction. In a state where there is no contact with the second power toothed part 35, the limiting ring 37 is fitted in a portion lying above the coupling tooth 32 within the part to coupling teeth 31.

[0067] Therefore, it is possible to prevent the distal end 34b of the torque adjusting jumper 34 from jumping or floating upward. It is possible to stabilize (ensure) the engagement of the distal end 34b of the torque adjustment jumper 34 and the coupling tooth 32 with each other.

As shown in Figures 3 to 5, the first power transmission wheel 25 comprises a rotating cylindrical body 40 disposed coaxially (centered on) the first axis of rotation 01, as well as a first part with power teeth 41 secured to the rotating cylindrical body 40 as if they were integral.

[0069] It will be noted that the first power transmission wheel 25 rotates clockwise with the power transmitted from the constant force spring 27. It will be noted that the first power transmission wheel 25 and the second power transmission wheel 26 are able to rotate in opposite directions with respect to each other, around the first axis of rotation O1, with the power transmitted from the constant force spring 27.

[0070] The shaft 30 of the second power transmission 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 like rings, from precious stones such as ruby are driven into the upper and lower ends of the rotating cylindrical body 40. The shaft 30 of the second power transmission wheel 26 is inserted into the stones 42. Therefore, the first power transmission wheel 25 and the second power transmission wheel 26 are assembled so as to be rotatable relative to each other. to the other around the first axis of rotation 01, with little clearance.

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

The first part with power teeth 41 comprises several arms 41a arranged at intervals from each other in the circumferential direction around the first axis of rotation O1, as well as a rim 41b formed like a ring and coupled to the outer ends of the arm 41a.

In the example shown in the figures, four arms 41a are formed at regular intervals, which is 90 degrees, around the first axis of rotation O1. However, the number, arrangement and shape of the arms 41a are not limited to this case and can be changed freely.

First power teeth 41c, with which the first control teeth 71c mesh within a first part with control teeth 71 described later, are formed over the entire outer circumference of the rim 41b. The first power teeth 41c also mesh with a second pinion 19a constituting the seconds mobile 19. Consequently, the first power transmission wheel 25 is able to transmit power from the constant-force spring 27 to the mobile seconds 19, that is to say the gear wheel on the escapement side 15 associated with the escapement 14, as indicated by the arrow R1 shown in Figure 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 escapement 14 via the cog wheel 15 on the escapement side. 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 escapement 14, without the cog wheel 15 on the escapement side being provided.

Further, the first power toothed part 41 is formed with a diameter equal to the diameter of the second power toothed part 35. However, the diameters are not limited to this case. The first part with power toothing 41 and the second part with power toothing 35 can have different diameters.

The constant force spring 27 is a thin plate spring made of a metal such as steel or nickel or even an alloy, and it has the shape of a spiral. Specifically, the constant force spring 27 has the shape of a spiral extending along an Archimedean curve in a polar coordinate system having as its origin the first axis of rotation O1. Consequently, the constant-force spring 27 winds over several turns or coils adjacent to each other, at substantially regular intervals in the radial direction when viewed from the first axis of rotation 01.

As shown in Figures 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 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 transmission wheel 26. Therefore, the constant force spring 27 is capable of transmitting the stored energy, respectively to the first power transmission wheel 25 and to the second power transmission wheel 26.

[0079] It will be noted that a part of the outermost circumferential portion in the constant-force spring 27 has the form of an arcuate segment moved outwardly, in the radial direction, by means of a shape-changing segment 27c and having a greater radius of curvature 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.

[0080] The constant force spring 27 is cocked with a predetermined amount of winding in a counter-clockwise direction toward the outer end 27b, with the inner end 27a chosen as the winding start position. . The constant force spring 27 is elastically deformed to decrease in diameter by winding (by winding) and is applied with a preload. Therefore, torque power Tc 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 transmission wheel 25 and to the second power transmission wheel 26, because the constant force spring 27 deforms to elastically return to its initial shape. Therefore, the first power transmission wheel 25 is able to rotate clockwise and the second power transmission wheel 26 is able to rotate counterclockwise. In the following explanations, the torque Tc is referred to as the rotating torque Tc 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 transmission wheel 25 and to the second power transmission wheel 26.

As shown in Figure 5, Figure 8 and Figure 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 transmission wheel 26.

The fixed ring 45 is, for example, fitted to a portion located between the limiting ring 37 and the rotating cylindrical body 40 within the first power transmission wheel 25 in the shaft 30. The inner end 27a of constant force spring 27 is secured to stationary ring 45 by, for example, caulking 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 portion according to the present invention) which is reversibly engaged in a slider 46 (the first engaging part according to the present invention) provided on the side of the first power transmission wheel 25 and defines a position, according to the radial direction , of the outer end 27b, and a limiting lever 48 (the rotation limiting segment according to the present invention) which comes into contact with the rotating cylindrical body 40 (the rotation limiting segment according to the present invention) within the first power transmission wheel 25 and prevents the outer end 27b from rotating around the first axis of rotation O1 due to elastic return of the constant force spring 27 to its initial shape are provided.

The slide 46 is formed in the arm 41a of the first part with power teeth 41. The slide 46 has a shape that extends in the circumferential direction around the first axis of rotation O1 and it emerges from the side in the counterclockwise.

As shown in Figure 8 and Figure 9, the defining segment 47 includes a shaft 50 which has a vertically extending columnar shape and engages the inner side (the inner edge) of the slider 46, a head 51 provided at the upper end of the shaft 50, as well as a leg 52 having a forked shape formed at the lower end of the shaft 50. In the shaft 50, a segment of larger diameter 53 having a larger diameter than the head 51 is formed in a portion between the head 51 and the leg 52.

[0088] The outer end 27b of the constant force spring 27 is fixed to the leg 52 by, for example, gluing or caulking, in a state in which the outer end 27b is inserted inside 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 formed in this way is inserted into the slide 46 in a sliding motion. Accordingly, shaft 50 engages the inner edge of slider 46. In particular, the outer end 27b of constant force spring 27 is pulled clockwise by the setting torque. rotation (winding torque) involved in the elastic return of the constant force spring 27 to its initial shape. As a result, defining segment 47 is pulled toward the circumferential end wall side of slider 46. Shaft 50 is pushed against and engages the circumferential wall. In this way, the defining segment 47 engages the inner edge of the slider 46 and defines a position, in the radial direction, of the outer end 27b of the constant force spring 27.

[0090] It will be noted that the arm 41a, in which the slide 46 is formed, is arranged so as to be held between the head 51 and the segment of larger diameter 53. Consequently, the defining segment 47 in engagement with the inside edge of slide 46 is prevented from sliding out, up and down.

As shown in Figure 9, the limiting lever 48 is combined with the defining segment 47 so as to be as if in one piece therewith. In the example shown in the figure, the proximal end of the limiting lever 48 is combined with a portion lying between the larger 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 rotating cylindrical body 40 of the first power transmission wheel 25, from the outer side in the radial direction.

[0092] Consequently, 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 O1 due to the rotational torque implied by the springback. of the constant force spring 27 to its initial shape.

Structure of the operating mechanism

[0093] As shown in Figures 2 to 5, the control mechanism 22 is a mechanism provided to intermittently rotate the second power transmission wheel 26 relative to the first power transmission wheel 25 in order to provide power to the constant force spring 27, as indicated by the arrow R2 in Fig. 2. The operating mechanism 22 is placed at a position offset in plan, from the constant force mechanism 20.

[0094] The control mechanism 22 comprises the first control wheel 55 which rotates around the second axis of rotation 02 by the rotation of the first power transmission wheel 25, the second control wheel 56 disposed coaxially with the first control wheel 55 and capable of rotating relatively with respect to the first control wheel 55, around the second axis of rotation 02, as well as a planetary mechanism 57 disposed between the first control wheel 55 and the second wheel command 56.

[0095] It will be noted that the first control wheel 55 is arranged above the second control wheel 56.

As shown in Figure 3 and Figure 5, the second control wheel 56 is supported axially between the plate and the gear bridge. The second control wheel 56 comprises a shaft 60 extending along the second axis of rotation 02, a second control pinion 61 which is in one piece with the shaft 60 and which meshes with the center mobile 18, as well as a second drive tooth portion 62 comprising second drive teeth 62a which mesh with the second power teeth 35a within the second power transmission wheel 26.

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

The second control pinion 61 is provided between the central portion, in the top-down direction, of the shaft 60 and the lower end of this shaft 60. Since the second control pinion 61 meshes with the center 18, the second control pinion 61 rotates according to the rotation of the center wheel set 18. Consequently, the power coming from the barrel 11 is transmitted to the second control wheel 56 via the center wheel set 18, that is to say of the cog wheel on the power source side 12.

[0099] It will be noted that the second control wheel 56 rotates in the counter-clockwise direction around the second axis of rotation 02. The power of the torque Tb is transmitted to the second control wheel 56, from the barrel 11. In the following explanation, torque Tb is referred to as the rotational torque produced by barrel 11. It will be noted that when barrel spring 16 in barrel 11 is armed with a predetermined amount of winding , the rotating torque Tb is selected to be higher than the rotating torque Tc produced by the constant force spring 27.

[0100] As shown in Figure 5, Figure 7 and Figure 8, the second part with control teeth 62 comprises several arms 62b arranged at intervals (with an interval between them) in the circumferential direction around the second axis of rotation 02, a rim 62c having a ring shape and coupled to the outer ends of the arms 62b, as well as a support plate 62d integral with the arms 62b.

The second control teeth 62a are formed over the entire outer circumference of the serge 62c. Therefore, the rotational torque Tc provided to rotate the second control wheel 56 clockwise is transmitted to the second control wheel 56, from the second power transmission wheel 26 which rotates counter-clockwise.

[0102] At this time, the rotation torque Tb greater than the rotation torque Tc as explained above and acting in the opposite direction to the rotation torque Tc is transmitted to the second control wheel 56 , through the power source side cog wheel 12. Consequently, the second drive wheel 56 is prevented from rotating clockwise.

[0103] However, when the rotation torque Tb produced by the barrel 11 is smaller than the rotation torque Tc produced by the constant-force spring 27, for example because the barrel spring 16 in the barrel 11 is disarmed or when the second torque adjustment toothed part 111 is forcedly rotated counterclockwise by a power adjustment mechanism 110 described below, the second control wheel 56 is able to to turn clockwise.

As shown in Figure 3 and Figure 5, the first control wheel 55 comprises a rotating cylindrical body 70 disposed coaxially with the second axis of rotation 02, as well as a first part with control teeth 71 coupled to the rotating cylindrical body 70 so as to be as if integral with the latter.

[0105] The shaft 60 of the second drive wheel 56 is inserted into (passes through) the rotating cylindrical body 70, from below. The shaft 60 protrudes so as to protrude above the rotating cylindrical body 70. Stones 72, which are the same as the stones 42, are driven into the upper and lower ends of the rotating cylindrical body 70. The shaft 60 of the second driving wheel 56 passes through the interior space of the stones 72. Accordingly, the first driving wheel 55 and the second driving wheel 56 are combined so as to be able to rotate relatively about the second axis of rotation 02 with less play.

The first part with control teeth 71 comprises several arms 71a arranged at intervals (offset from each other) in the circumferential direction around the second axis of rotation 02, as well as a rim 71b having a shape like 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 around the second rotation axis θ2. 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.

[0108] However, the number, arrangement and shape of the arms 71a are not limited to this case and can be freely modified.

[0109] First control teeth 71c, which mesh with the first power teeth 41c within the first power transmission wheel 25, are formed over the entire outer circumference of the rim 71b. Therefore, the control wheel 55 rotates counterclockwise around the second axis of rotation 02, depending on the rotation of the first power transmission wheel 25.

[0110] It will be noted that the first part with drive teeth 71 is formed with a diameter equal to the diameter of the second part with drive teeth 62. However, the diameters are not limited to this case. The first part with drive teeth 71 and the second part with drive teeth 62 can be made so as to have different diameters.

[0111] The planetary mechanism 57 comprises a pallet 80 (the pawl according to the present invention) which is provided on the side of the first control wheel 55 and which rotates around the second axis of rotation 02 according to the rotation of the first wheel drive wheel 55, a stop wheel 81, which is a toothed planetary part which is provided on the second drive wheel 56 side and which performs revolutions around the second axis of rotation 02 while rotating according to the rotation of the second control wheel 56, as well as a part with fixed teeth 82 provided for making rotations and revolutions of the stop wheel 81. The planetary mechanism 57 intermittently causes the pallet 80 to engage and disengages from (uncouples from) the stopper wheel 81 depending on the rotation of the first drive wheel 55.

The pallet 80 is made of an artificial precious stone such as ruby and it is attached to a support lever 85 which rotates around the second axis of rotation 02 depending on the rotation of the first control wheel 55.

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

The pallet 80 can be integral with the support lever 85, instead of being made as a separate element from the support lever 85.

As shown in Figure 5, Figure 8, Figure 10 and Figure 11, the support lever 85 is coupled to a portion as if it were integral with this portion, which is in - below the first part with control teeth 71, within the rotary cylindrical body 70 within the first control wheel 55.

[0116] The support lever 85 comprises a first lever portion 86 and a second lever portion 87 extending in the radial direction of the first control wheel 55, from the side of the rotary cylindrical body 70, towards the rim 71b. The first lever portion 86 and the second lever portion 87 are disposed with a fixed interval therebetween along the circumferential direction and are disposed so as to fit into the interior of the opening 73 in a plan view.

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

[0118] The stop wheel 81 is arranged between the first portion of lever 86 and the second portion of lever 87. It will be noted that the first portion of lever 86 is arranged further away, in the counter-clockwise direction. , than the stopper wheel 81, while the second lever portion 87 is disposed further, clockwise, than the stopper wheel 81.

As shown in Figure 11, a stone support portion forming a pallet 88 opens towards the stop wheel 81 being provided on the side of the outer end of the first lever portion 86. The support portion of paddle stone 88 carries paddle 80 through this opening. The paddle 80 is maintained in a state where this paddle 80 protrudes toward the stopper wheel 81, more than the paddle stone support portion 88. On a protruding portion of the paddle 80, a side surface facing inside in the radial direction forms an engagement surface 80a, with which a working surface 95a described below within the stop wheel 81 is capable of being engaged and from which this working surface can be uncoupled 95a. In the example shown in the figure, the engagement surface 80a is formed as a flat surface which is flat over the entire surface.

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

[0121] The support element 90 comprises a lower plate 91 fixed to the support plate 62d, as well as an upper plate 92 raised upwards, from the lower plate 91, and projecting above the wheel. stop 81. In the example shown in the figure, the lower plate 91 is fixed by fixing means such as fixing rods, fixing screws or the like. However, the fixing of the bottom plate 91 is not limited to this case.

[0122] Stones 93 made of an 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 each other. It will be noted that the stones 93 can be made, for example, of other fragile materials or of metals such as steel-based alloys.

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 rotate around of a fifth axis of rotation 05.

The stopper wheel 81 includes a stopper tooth portion 96 comprising a plurality of stopper teeth 95 capable of engaging and disengaging from the engaging surface 80a of the pallet. 80, as well as a stop pinion 97 which is provided below the stop toothed part 96 and which meshes with the fixed toothed part 82.

As shown in Figure 5 and Figure 10, the part with fixed teeth 82 comprises a ring gear 100 formed as a ring and disposed between the first drive wheel 55 and the second drive wheel 56 and coaxially with the second axis of rotation 02, as well as a fixed arm 101 formed integrally with the ring gear 100 and fixed to a fixed component, not shown. In the example shown in the figures, the ring gear 100 is formed so as to have a diameter slightly smaller than the first part with drive teeth 71 and than the second part with drive teeth 62. Fixed teeth 100a, with which engages the stop pinion 97, are formed on the entire inner circumference of the ring gear 100. Therefore, the fixed-tooth portion 82 in this embodiment is of the internal-tooth type.

[0126] Since the fixed-toothed part 82 is of the internal-toothed type, as shown in FIG. 11, the stopper wheel 81 performs counterclockwise revolutions around the second axis of rotation 02 while rotating clockwise about the fifth axis of rotation 05 depending on the counterclockwise rotation of the second control wheel 56. As shown in Figure 10, the stop wheel 96 is disposed above the fixed toothed part 82 and it is able to rotate without coming into contact with the fixed toothed part 82 and the support element 90.

As shown in Figure 11, the stop teeth 95 are twelve in number. However, the number of teeth is not limited thereto and can be suitably changed. On the stopper tooth 95, a clockwise facing side surface forms a working surface 95a which engages and disengages from the engagement surface 80a belonging to the pallet 80. A trajectory M followed by the tips of the stopper teeth 95 depending on the rotation of the stopper wheel 81 is called the trajectory of the stopper tooth part 96.

The paddle 80 and stopper wheel 81 constituted as explained above are in a relationship in which the paddle 80 and stopper wheel 81 intermittently engage each other and intermittently uncouple from each other depending on the rotation of the first control wheel 55. This point will be explained in detail.

[0129] The working surface 95a of the stopper tooth 95 engages the engagement surface 80a of the pallet 80 depending on the rotation and the revolution of the stopper wheel 81. After the engaged, the support lever 85 and the paddle 80 rotate counter-clockwise, around the second axis of rotation 02, in accordance with the counter-clockwise rotation of the first control wheel 55. Consequently, the support lever 85 and the pallet 80 are progressively uncoupled from the part with stopping teeth 96 (that is to say, they gradually come out of the trajectory M).

[0130] Therefore, as shown in Fig. 13, at an initial stage of engagement, the working surface 95a of the detent tooth 95 engages deeply (substantially) with the pallet 80. Then , as shown in Figure 14, the working surface 95a of the detent tooth 95 moves toward the tip of the paddle 80, while sliding on the engaging surface 80a as the paddle 80 uncouples. Thereafter, the catch of the detent 95 and paddle 80 becomes progressively shallow (less significant). As shown in Figure 15, detent 95 and pallet 80 are uncoupled at a time that occurs when the working surface 95a of detent 95 passes over the tip of pallet 80.

Note that in Figures 13 to 15, the support lever 85 is shown in a simplified manner, while the second portion of lever 87 is not shown.

[0132] When the stop tooth 95 and the pallet 80 are uncoupled, as shown in Figure 16, the link between the first control wheel 55 and the second control wheel 56 via the pallet 80 and the stop wheel 81 ceases. Therefore, it is possible to rotate the second control wheel 56 counterclockwise around the second axis of rotation 02. Therefore, the stop wheel 81 rotates counterclockwise. a clock around the second axis of rotation 02 so as to follow the pallet 80 while rotating clockwise around the fifth axis of rotation 05 depending on the rotation of the second control wheel 56. Then , it is possible to cause the working surface 95a of the following stop wheel 95 to engage with the engaging surface 80a belonging to the pallet 80.

[0133] By means of a repetition of the operation explained above, it is possible to cause the pallet 80 to engage with and to disconnect from, intermittently, the stop wheel 81. Note that the stopper teeth 95 engage the pallet 80 one at a time.

[0134] From the time the working surface 95a of the detent tooth 95 engages the engaging surface 80a of the paddle 80 as shown in Figure 13 until the time the work surface 95a and the engagement surface 80a are uncoupled as shown in Figure 14 and Figure 15, the support lever 85 carries the pallet 80 so that a dummy line L extending according to a force F3 resulting from a pushing force F1, with which the stopper tooth 95 pushes on the engagement surface 80a, and a frictional force F2 generated by the sliding of the stopper tooth 95 on the engagement surface 80a crosses the second axis of rotation 02.

In this embodiment, the fictitious line L crosses the second axis of rotation O2 in an intermediate position P3 shown in Figure 14 and located in the middle between a grip position P1 shown in Figure 13, where the tooth detent 95 is in engagement with engagement surface 80a, and an end-of-engagement position (release position) P2 shown in Fig. 15, where detent tooth 95 ceases to engage with the engagement surface 80a.

It will be noted that, as explained above, when the rotation torque Tb produced by the barrel 11 is smaller than the rotation torque Tc produced by the constant-force spring 27, for example because the spring cylinder 16 in the cylinder 11 is decocked or when the second part with torque adjustment teeth 111 is forcedly turned counterclockwise by the power adjustment mechanism 110 described below, the second control wheel 56 rotates clockwise.

[0137] In this case, the upper plate 92 of the support member 90 moves towards the second lever portion 87 of the support lever 85 depending on the rotation of the second control wheel 56. Therefore, next, the upper plate 92 comes into contact with the second lever portion 87 as shown in Figure 17. Then, it is possible to limit, by means of the second lever portion 87, that a rotation of the second control wheel 56 goes further clockwise.

Constitution of the power adjustment mechanism

As shown in Fig. 3, Fig. 4, Fig. 18, and Fig. 19, the constant force mechanism 20 in this embodiment further includes the power adjustment mechanism 110 for adjusting the power of the spring. constant force 27, through the first power transmission wheel 25 or the second power transmission 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 adjusted via the second power transmission wheel 26. However, the adjustment of the power of the 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 transmission wheel 25 as explained above.

[0140] The power adjustment mechanism 110 comprises the second part with torque adjustment teeth 111 able to mesh with the first part with torque adjustment teeth 33 within the second power transmission wheel 26 and a rocker lever 113 which moves the second torque-adjusting toothed part 111 between a meshing position P4 (see Fig. 19), in which the second torque-adjusted toothed part 111 and the first torque-adjusted toothed part torque 33 mesh with each other, and a non-mesh position P5 (see Fig. 19), in which the second torque-adjusting gear portion 111 and the first torque-adjusting gear portion 33 no longer mesh with each other.

[0141] The tilting lever 113 is arranged between a plate 115 and a torque adjustment bridge 116 and it is able to tilt around a tilting rod 117 fixed to the plate 115. A fork 118 is provided at one end rocker lever 113.

An eccentric rod 119 carried by the plate 115 so as to be rotatable is arranged on the inner side of the fork 118. The inner circumferential surface of the fork 118 and the outer circumferential surface of the eccentric rod 119 are made of sliding contact with each other.

[0143] The eccentric rod 119 is uncovered on the outer side of the torque adjustment bridge 116. For example, a groove 119a is formed at the upper end of the eccentric rod 119. Then, it is possible to make optionally a rotational maneuver of the eccentric rod 119 by means, for example of a driving tool employing the groove 119a. However, the means for the rotational operation of the eccentric rod 119 are not limited to the groove 119a. Means for optionally operating the eccentric rod 119 need only be formed at the upper end of the eccentric rod 119.

[0144] By turning the eccentric rod 119 described above, as shown in Figure 19, the tilting lever 113 can be tilted around the tilting rod 117. The other end of the tilting lever 113 can be brought close to the first portion with torque adjustment teeth 33 or cause this other end of the rocker lever 113 to separate from the first portion with torque adjustment teeth 33.

As shown in Figure 7, Figure 18 and Figure 19, the second part with torque adjustment teeth 111 is carried by a rod forming a guide 112 so as to be rotatable, the lower end of this rod forming guide 112 being fixed to the other end of the rocker lever 113. Second torque adjusting teeth 111a capable of meshing with the first torque adjusting teeth 33a are formed on the entire outer circumference of the second toothed portion of torque adjustment 111.

The second portion with torque adjustment teeth 111 is arranged at the level of the other end of the rocker lever 113, by means of the rod forming a guide 112. Consequently, the second part with torque adjustment teeth can be moved torque 111 by rocking the rocker lever 113. Note that the position where the other end of the rocker 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 mesh with each other.

[0147] On the other hand, a position in which the other end of the rocker lever 113 is further away from the first torque adjusting gear part 33 is chosen as the release position P5. It is possible to make the first torque adjusting teeth 33a and the second torque adjusting teeth 111a stop meshing with each other.

[0148] The upper end of the guide rod 112 is movably inserted into a groove 120, which is formed in the torque adjustment bridge 116 as shown in Figure 4, along the groove 120. The groove 120 is formed so as to extend in a tilting direction of the other end of the rocker lever 113. Then, the second torque-adjusting tooth part 111 is stably carried via the rod forming a guide 112 with less clearance and moves between the meshing position P4 and the non-mesh position P5 depending on the tilting of the rocker lever 113.

As shown in FIG. 7, FIG. 18 and FIG. 19, an operating wheel 121 which rotates the second part with torque adjustment teeth 111 is arranged between this second part with torque adjustment teeth 111 and tilt rod 117.

The operating wheel 121 comprises a part with operating teeth 122 whose operating teeth 122a mesh with the second torque adjustment teeth 111a. Operating teeth 122a are formed over the entire outer circumference of operating toothed part 122. Operating wheel 121 is supported axially between plate 115 and torque adjustment bridge 116.

[0151] It will be noted that the operating wheel 121 is arranged so as to pass vertically through a through hole 123 formed in the tilting lever 113. The through hole 123 is formed so as to extend in a direction of tilting of the lever failover 112.

[0152] Consequently, the operating wheel 121 is axially supported between the plate 115 and the torque adjustment 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 mesh with the second torque adjusting teeth 111a, regardless of the position of the second torque adjusting tooth part 111.

The upper end of the operating wheel 121 is uncovered on the side of the upper surface of the torque adjustment bridge 116 as shown in FIG. 4. A rotational maneuver of the operating wheel 121 can be carried out from the 'outside. In the example shown in the figures, a groove 121a is formed at the level of the upper end of the maneuvering wheel 121. It is possible optionally to carry out a rotation maneuver of the maneuvering wheel 121 by means, for example, of a driving tool employing the groove 121a. However, means making it possible to carry out the maneuver of rotation of the operating wheel 121 are not limited to the groove 121a. Actuators for optionally performing the rotational operation of the maneuver wheel 121 need only be formed at the upper end of the maneuver wheel 121.

[0154] Since the power adjustment mechanism 110 is constituted as explained above, as shown in Figure 19, it is possible to rotate the first torque adjustment toothed part 33 via the second toothed part. torque adjustment 111, by performing a rotation maneuver of the maneuvering wheel 121 after having moved the second part with torque adjustment teeth 111 towards the meshing position P4. It is possible to wind or unwind the constant-force spring 27 and optionally 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.

It will be noted that, in an initial state, it is assumed that the barrel spring 16 in the barrel 11 is armed with a predetermined amount of winding and that the power of the rotation torque Tb is transmitted from the barrel 11 to the second control wheel 56, via the power source side cog wheel 12. It is assumed that the constant force spring 27 is armed with a predetermined amount of winding and that a torque of rotation Tc smaller than the rotation torque Tb is transmitted from the constant force spring 27 to the first power transmission wheel 25 and the second power transmission wheel 26. Further, it is assumed that the second torque-adjusting toothed part 111 is placed in the non-mesh position P5 and that the first torque-adjusting toothed part 33 and the second torque-adjusting toothed part 111 within the second power transmission 26 gears not with each other.

[0158] With the constant force mechanism 20 of this embodiment, since the constant force mechanism 20 includes the constant force spring 27 as shown in Figures 2-4, the energy stored in the constant force spring 27 can be transmitted to the first power transmission wheel 25, and the first power transmission wheel 25 can rotate clockwise around the first rotation axis 01. Then the power of the constant force spring 27 can be transmitted from the first power transmission wheel 25 to the seconds mobile 19. The seconds mobile 19 can rotate around the fourth axis of rotation 04 depending on the rotation of the first power transmission wheel 25.

[0159] In other words, as the arrow R1 in FIG. power transmission 25. Exhaust 14 can be operated.

[0160] Since the power from the constant force spring is also transmitted to the second power transmission wheel 26, this second power transmission wheel 26 takes place to rotate counterclockwise around the first axis of rotation O1 with the torque Te.

[0161] Specifically, the power from the constant force spring 27 is transmitted to the shaft 30 and to the coupling gear part 31, via the stationary ring 45. In addition, the power transmitted to the coupling toothed part 31 is transmitted to the second power toothed part 35, via the torque adjustment jumper 34, and then transmitted to the second control toothed part 62 of the second drive wheel 56. Then, the power to rotate the second drive wheel 56 clockwise around the second rotation axis 02 with the rotating torque Tc is transmitted to the second drive wheel 56 from the constant force spring 27.

[0162] However, the rotation torque Tb (torque greater than the rotation torque Tc) provided for rotating the second control wheel in the counterclockwise direction around the second axis of rotation 02 is transmitted to the second drive wheel 56 from the power source side cog wheel 12. Therefore, the second drive wheel 56 is prevented from rotating clockwise.

It will be noted that a power resulting from a difference (the rotation torque Tb - the rotation torque Tc) between the rotation torque Tb transmitted from the cog wheel on the power source side 12 and the rotating torque Tc transmitted from the constant force spring 27 acts on the second control wheel 56. However, since the stopper wheel 81 and the paddle 80 are in mesh, the second control wheel 56 and the first control wheel 55 can be linked thanks to this engagement (thanks to this coupling). The second control wheel 56 is prevented from rotating counterclockwise around the second axis of rotation 02.

[0164] Therefore, at a stage where the stopper wheel 81 and the pallet 80 are engaged, the second control wheel 56 is prevented from rotating around the second axis of rotation 02. Therefore, the second transmission wheel power 26 is prevented from rotating around the first axis of rotation 01.

[0165] 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 stopper tooth 95 of the stopper wheel 81 is in mesh with the putting surface. in engagement 80a of the pallet 80 in a state of strong thrust.

[0166] When the first power transmission wheel 25 rotates with the power coming from the constant force spring 27, the first control wheel 55 rotates counterclockwise, around the second axis of rotation 02 , depending on the rotation of the first power transmission wheel 25. When the first control wheel 55 rotates, the support lever 85 rotates counterclockwise around the second axis of rotation 02, in function of the rotation of the first control wheel 55. Consequently, the pallet 80 can progressively free itself from the stop toothed part 96 to withdraw the pallet 80 from the path M of the stop toothed part 96.

[0167] Therefore, as shown in Fig. 14, the working surface 95a of the detent tooth 95 moves toward the tip of the pallet 80 while sliding on the engagement surface 80a depending on the uncoupling of the paddle 80 from the state shown in Figure 13. As shown in Figure 15, at a time which is when the working surface 95a of the stop tooth 95 passes over the tip of the paddle 80 , the stop tooth 95 and the pallet 80 cease to be engaged. Then, the link between the first control wheel 55 and the second control wheel 56 via the paddle 80 and the stopper wheel 81 is terminated.

[0168] Consequently, the second control wheel 56 rotates counterclockwise around the second axis of rotation 02, as shown in Figure 16, due to the power (the rotation torque Tb - the spinning torque Te) resulting from the difference between the spinning torque Tb transmitted from the power source side cog wheel 12 and the spinning torque Tc transmitted from the constant force spring 27.

When the second control wheel 56 rotates, the second part with power teeth 35 can rotate clockwise around the first axis of rotation O1. As shown in FIG. 6, the second power toothed part 35 is linked to the coupling toothed part 31 because the torque adjusting jumper 34 and the coupling tooth 32 are in mesh. Accordingly, as the second power tooth portion 35 rotates clockwise, the first engaging surface 32a on the mating tooth 32 moves relatively toward the distal end 34b of the torque setting jumper 34 and it is about to cross the distal end 34b.

[0170] However, since the power acting on the second power toothed part 35 is the power (the spinning torque Tb - the spinning torque Tc) resulting from the difference between the spinning torque Tb transmitted from the power source side cog wheel 12 and the rotational torque Tc transmitted from the constant force spring 27 as explained above, the power is smaller than the jumper torque Tg produced by the spring adjustment jumper. torque 34. Therefore, 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.

[0171] It follows that the power, which is transmitted to the second power toothed part 35, can be transmitted to the coupling toothed part 31 via the torque adjustment jumper 34. Then, the coupling toothed part 31 and the shaft 30 can rotate clockwise around the first axis of rotation O1.

[0172] Therefore, the constant force spring 27 can be cocked through the stationary 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 transmission wheel 25 can be compensated by means of the power transmitted from the side of the barrel 11, which is the power source. Then, the power of the constant force spring 27 can be kept constant. The escapement 14 can be actuated by means of a constant torque.

[0173] It will be noted that, even when power is supplied to the constant-force spring 27, the first power-transmitting wheel 25 rotates with the power from the constant-force spring 27 and transmits the power from the constant-force spring 27. constant 27, to the cog wheel on the escapement side 15.

[0174] When power is supplied to the constant force spring 27 as explained above, as shown in Figure 16, the stopper wheel 81 rotates counter-clockwise around the second axis of rotation 02 while rotating clockwise around the fifth axis of rotation 05 and follows the pallet 80 depending on the rotation of the second control wheel 56. The stop wheel 81 catches with the pallet 80 by rotating one tooth of stopper wheel 95. Working surface 95a of stopper tooth 95 again engages engagement surface 80a of paddle 80.

[0175] Therefore, since 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 transmission wheel 26 is prevented. Power ceases to be supplied to the constant force spring 27.

[0176] By repeating the operation described above, stopper wheel 81 and paddle 80 may intermittently engage and disengage. In other words, the planetary mechanism 57 can intermittently engage and uncouple the stopper wheel 81 and the paddle 80, and it intermittently rotates the second stopper wheel. power transmission 26 with respect to the first power transmission wheel 25 according to the rotation of the first power transmission wheel 25 and the first drive wheel 55. Then, power may be intermittently supplied to the spring at constant force 27.

As explained above, with the constant force mechanism 20 of this embodiment, the escapement 14 can be actuated by means of energy stored in the constant force spring 27 and power can be supplied. intermittently, from the barrel side 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 escapement 14 can be actuated in operation where torque variations are suppressed.

[0178] The constant-force mechanism 20 of this embodiment achieves cycle control by means of the planetary mechanism 57. Therefore, unlike a conventional cam-type constant-force mechanism, a phenomenon is unlikely to occur. over-release occurs in the constant force spring 27.

As shown in Figure 3 and Figure 4, the torque generating mechanism 21 and the control mechanism 22 are arranged so as to be offset in plan (parallel to a plane). Therefore, the thickness of the entire constant force mechanism 20 can be reduced compared to a conventional planetary gear type. Further, the constant force spring 27 is disposed between the first power transmission wheel 25 and the second power transmission wheel 26. The planet gear 57 is disposed between the first drive wheel 55 and the second drive wheel 56 Therefore, a scatter in the plane can be reduced. The constant force mechanism 20 can be disposed in a plane space which is small compared to the conventional planetary gear type.

[0180] Consequently, the constant force mechanism 20 can be obtained which achieves compactness and space saving both in the plane of the timepiece 1 and in the direction of the thickness of the timepiece. timepiece 1. It is possible to obtain the movement 10 and the timepiece 1 whose sizes and thicknesses can be easily reduced.

[0181] Further, in the constant force mechanism 20 according to this embodiment, from the moment the working surface 95a of the stop tooth 95 is in engagement with the engaging surface 80a of the paddle 80 as shown in Figure 13 until the work surface 95a and the engagement surface 80 cease to be engaged as shown in Figure 15, the support lever 95 holds the paddle 80 manner that the fictitious line L extending according to the force F3 resulting from the combination of the pushing force F1, with which the stop tooth 95 pushes on the engagement surface 80a, and the frictional force F2 resulting that the stop tooth 95 slides on the engagement surface 80a, crosses the second axis of rotation 02.

[0182] Therefore, when the time between engagement and the end of engagement between the stop tooth 95 and the pallet 81 is chosen as forming a cycle, as shown in Figure 20, an average torque over a cycle can be kept constant when focusing on the spinning torque generated in the support lever 85.

[0183] As explained above, in the initial engagement state illustrated in FIG. 13, the working surface 95a of the stopper tooth 95 is in deep engagement with the pallet Figure 14, depending on the release of the paddle 80, the working surface 95a of the stop tooth 95 moves toward the tip of the paddle 80 while sliding on the engagement surface 80a. As shown in Figure 15, the working surface 95a of the stop tooth 95 and the pallet 80 cease to be engaged at a time which occurs when the working surface 95a passes the tip of the pallet 80. In this succession of a cycle, since the angle that the engagement surface 80a makes with the stop tooth 95 changes little, the direction of the resultant force F3 changes according to the change of the angle.

[0184] At this time, when the direction of the resultant force F3 crosses the second axis of rotation 02 in Fig. 14, the rotation torque generated in the support lever 85 is not generated. On the other hand, when the direction of the resultant force F3 shifts from the second axis of rotation 02 as shown in Fig. 13 and Fig. 15, the rotational torque is generated according to the amount of shift .

In particular, before and after the direction of the resultant force F3 crosses the second axis of rotation O2, rotation torques in opposite directions are generated. In other words, a rotating torque T tending to bring the supporting lever 85 toward the stopper wheel 81 is generated in the supporting lever 85 as shown in Fig. 13 and a rotating 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 Figure 15.

[0186] Therefore, as shown in Fig. 20, although there is a variation in torque of the support lever 85 during a cycle, an average torque per cycle can be kept constant. As a result, it is possible to obtain a constant torque as a property.

In addition, in this embodiment, the fictitious line L crosses the second axis of rotation O2 in the intermediate position P3 shown in Figure 14 located in the middle between the grip position P1 shown in Figure 13, where detent tooth 95 is in engagement with engagement surface 80a, and an end-of-engagement position P2 shown in Figure 15, where detent tooth 95 ceases to engage with the engagement surface in 80a socket. Then the average torque over one cycle can be kept constant even more stably. The result of a constant torque can be obtained even more stably.

[0188] Further, as shown in Fig. 19, the constant force mechanism 20 of this embodiment includes the power adjusting mechanism 110. Therefore, the power of the constant force spring 27 can be adjusted as needed. .

[0189] For example, a case will be explained in which the constant force spring is armed to increase the power.

[0190] In this case, first, the eccentric rod 119 is rotated to rock the rocker lever 113 around the rocker rod 117. The second torque-adjusting toothed part 111 is moved from the meshing P5 up to the meshing position P4. Then, the first torque adjusting teeth 33a of the first torque adjusting gear part 33 can be brought into mesh with the second torque adjusting teeth 111a of the second torque adjusting tooth part 111.

[0191] Next, the maneuvering wheel 121 is turned clockwise. At this time, the operating wheel 121 is rotated with a higher input torque than the torque obtained by adding the rotating torque Tc produced by the constant-force spring 27 and the jumper torque Tk produced by the jumper torque adjuster 34. Then the second torque adjuster tooth portion can be turned counterclockwise. The power provided for rotating the first torque-adjusting toothed part 33 clockwise about the first axis of rotation O1 can be transmitted to the first torque-adjusting toothed part 33 via the second part with torque adjustment teeth 111.

[0192] The first part with torque adjustment teeth 33 is combined with the part with coupling teeth 31 so as to be as if in one piece therewith. Therefore, the power for rotating the coupling gear part 31 clockwise around the first rotation axis O1 is transmitted to the coupling gear part 31. At this time, since the power transmitted to the coupling toothed part 31 constitutes the input torque, the coupling toothed part 31 shown in FIG. 6 rotates relatively clockwise with respect to the second part to power tooth 35. In other words, the distal end 34b of the torque setting jumper 34 and the second engaging surface 32b of the coupling tooth 32 can lose engagement. The coupling gear part 31 can be rotated clockwise while ending the rotation limitation by the torque setting jumper 34.

It will be noted that the coupling teeth 32 move while passing over the distal end 34b of the torque adjustment jumper 34 one after the other in the circumferential direction, due to the rotation of the part to coupling teeth 31.

[0194] Since the coupling gear part 31 can be rotated in this way, the fixed ring 45, fixed to the shaft 30, can be rotated clockwise and the inner end 27a of the constant force spring 27 can be turned clockwise. Therefore, winding of the constant force spring 27 can be achieved. It is possible to increase the preload of the constant force spring 27 and adjust the rotation torque Tc to increase.

[0195] It will be noted that, although the second power toothed part 35 does not rotate during the adjustment explained above, the power to rotate this second power toothed part 35 in the clockwise direction is transmitted to the second part with power teeth 35. The power at this instant 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 rotate this second control wheel 56 in the counter-clockwise direction, around the second axis of rotation 02. At this moment, as explained above, the power to rotate the second control wheel 56 in the counterclockwise direction, around the second axis of rotation 02, with the rotation torque Tb, is transmitted to this second control wheel 56, at from the cog wheel on the power source side 12.

[0196] Therefore, the power obtained by adding the power from the second power gear portion 35 and the power from the power source side cog wheel 12 acts on the second drive wheel 56. Therefore, the working surface 95a of the stopper tooth 95 of the stopper wheel 81 engages with the engagement surface 80a of the paddle 80, in a strong thrust state. Therefore, it is possible to appropriately prevent the second power transmission wheel 35 from rotating. The winding of the constant force spring 27 can be carried out quickly, with a good reaction.

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

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

[0199] Consequently, it is possible to rotate the second part with torque adjustment teeth 111 clockwise. The power to rotate the first torque setting gear part 33 counterclockwise around the first axis of rotation 01 can be transmitted to the first torque setting gear part 33, by through the second part with torque adjustment teeth 111.

[0200] Therefore, the power to rotate the coupling gear part 31 counterclockwise, around the first axis of rotation O1, is transmitted to the coupling gear part 31. At this time, since the power transmitted to the coupling gear portion 31 is the input torque, it is possible to bring the coupling gear portion 31 and the second power gear portion 35 into rotate (rotate together) counterclockwise, while maintaining engagement between the distal end 34b of the torque setting jumper 34 and the first engaging surface 32a of the coupling tooth 32 .

[0201] Then, the second control wheel 56 rotates 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 toward the second lever portion 87 of the support lever 85, by the rotation of the second control wheel 56, as shown in Fig. 17, top plate 92 comes into contact with second lever portion 87.

[0202] Consequently, it is possible to limit, by means of the second portion of lever 87, that the second control wheel 56 rotates more clockwise.

[0203] Then, after the rotation of the second control wheel 56 in the clockwise direction has been limited as explained above, the maneuvering wheel 121 is no longer turned in the counter-clockwise direction. shows, with an input torque greater than the difference (Tj - Tc) between the jumper torque Tj of the torque setting jumper 34 and the rotational torque Tc produced by the constant force spring 27. At this moment, since the rotation of the second control wheel 56 and the second power transmission wheel 26 is prevented, the coupling gear part 31 shown in Fig. 6 rotates relatively counterclockwise. a watch, with respect to the second power transmission wheel 35. In other words, the distal end 34b of the torque adjustment jumper 34 can disengage from the first engagement surface the coupling tooth 32. It is possible to fai re turn the coupling gear part 31 counterclockwise while releasing the rotation lock (rotation limitation) by the torque setting jumper 34.

[0204] It will be noted that the coupling teeth 32 move passing over the distal end 34b, one after the other in the circumferential direction, by the rotation of the part with coupling teeth 31.

[0205] As the part with coupling teeth 31 can be rotated as explained above, it is possible to rotate the fixed ring 45 fixed to the shaft 31 counterclockwise and 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 preload of the constant force spring 27 and set the rotation torque Tc to decrease (in the direction of decrease).

[0206] It will be noted that this is not limited to the case of power adjustment. Even when the rotation torque Tb produced by the barrel 11 is smaller than the rotation torque Tc produced by the constant-force spring 27 because, for example, the barrel spring 16 in the barrel 11 is disarmed , excessive rotation of the second control wheel in the clockwise direction can be prevented as in the case explained above. Therefore, it is possible to prevent the constant force spring 27 from being fully discharged.

As explained above, since the constant force mechanism 20 includes the power adjustment mechanism 110, it is possible to adjust the power of the constant force spring 27 according to what is needed. It is possible to actuate the escapement 14 in a more stable manner, 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 assemblability. Further, since the second power transmission wheel 26 is disposed at a position planarly offset from the control mechanism 22, it is possible to provide the power adjustment mechanism 110 without bothering (without having to worry) of the control mechanism 22. It is easy to adjust (mount) the power adjustment mechanism 110.

[0208] Furthermore, it is possible to adjust the power of the constant-force spring 27 by the rotation of the second portion with torque-adjusting teeth 111 rotated via the maneuvering wheel 121. Consequently, it is possible to carry out the adjustment in a fine and intuitive way. It is easy to perform the adjustment work (the adjustment operation). Further, by placing the second torque adjusting gear portion 111 in the non-mesh position P5, when the power adjustment is not performed, it is possible to prevent an unfortunate in rotation (unfortunate rotational force) is applied to the second power transmission wheel 26.

[0209] Further, 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 Figure 3 and Figure 4, the defining segment 47 provided at the outer end 27b of the constant force spring 27 is reversibly engaged (releasably ) in the slider 46 provided in the first power transmission wheel 25. Therefore, the constant force spring 27 and the first power transmission wheel 25 can be easily disassembled, by means of a simple operation to disengage the segment of definition 47 from the inside of the slide 46.

[0211] Therefore, the maintainability of the torque generating mechanism 21 can be improved. Overhaul and the like can be easily performed. Since the constant force spring 27 and the first power transmission wheel 25 can be easily disassembled, maintenance work (service) such as lubrication can also be easily performed.

[0212] When the assembly of the torque generating mechanism 21 is carried out, simply by engaging the defining segment 47 in the slider 46, it is possible to combine the first power transmission wheel and the second transmission wheel. power of 26 as if they were all 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 to appropriately position the outer end 27b of the constant force spring 27.

[0213] Specifically, as shown in Figure 21, the first power transmission wheel 25 is placed (adjusted) above the second power transmission 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 constant-force spring 27 is not elastically deformed. Then, as shown in Figure 22, the first power transmission wheel 25 and the second power transmission wheel 26 are laid on top of each other so that the defining segment 47 is in a open portion (an access portion) of the slider 46. Next, as shown in Fig. 23, the first power transmission wheel 25 and the second power transmission wheel 26 are rotated relative to each other. relative to the other, in opposite directions, around the first axis of rotation O1, so that the defining segment 47 enters the slide 46. Consequently, it is possible to easily advance the defining segment 47 in the slide 46, by the sliding movement. As shown in Figure 3 and Figure 4, it is possible to engage the defining segment 47 with the inside edge of the slider 46.

[0214] Consequently, it is possible to integrally assemble the first power transmission wheel 25, the second power transmission wheel 26 and the constant force spring 27. It is possible to define the position, according to 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.

[0215] Then, by rotating the first power transmission wheel 25 and the second power transmission wheel 26 more relative to each other in opposite directions around the first axis of rotation O1 while maintaining the outer end 27b of the constant force spring 27, it is possible to arm the constant force spring 27 and to give a preload (a preload) to this constant force spring 27. It is possible to store energy. In this case, for example, the winding of the constant force spring 27 by means of the power adjustment mechanism 110 explained above can be performed.

[0216] Therefore, the torque generating mechanism 21 can be easily assembled. It is possible to improve the practicality (practicability) of the assembly.

Further, during the winding 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 rotating cylindrical body 40 of the first power transmission wheel 25. Therefore, it is possible to prevent (limit) the outer end 27b from rotating around the first axis of rotation O1 with the rotational torque implemented with the elastic deformation of return of the constant force spring 27 to its initial state. Therefore, it is possible to cock the constant-force spring 27 while preventing segments of this constant-force spring 27 from coming into contact with each other.

[0218] Therefore, it is possible to prevent a torque difference (hysteresis) from occurring between a moment of winding the constant-force spring 27 and a moment of releasing the power of this constant-force spring 27. Further, at the time of winding the constant-force spring 27, the limiting lever 48 comes into contact, gradually strongly, with the rotary cylindrical body 40, through the winding. Therefore, it is easy to maintain an amount of windage, that is to say a preload or preload of the constant force spring 27.

[0219] When the energy stored in the constant force spring 27 decreases for any reason, that is to say when the preload decreases, it is possible to release the defining segment 47 from inside the slider. 46 and move defining segment 47 away from the interior of slider 46. Therefore, a change in the relative positional relationship between slider 46 and defining segment 47 can be readily identified, by visual recognition ( it can be easily seen). It can be apprehended easily and with certainty that the energy stored in the constant-force spring 27 decreases, for example that the amount of winding decreases until it reaches 0.

[0220] As explained above, the maintainability, maintenance practicability and assembly practicability are improved. Excellent maneuverability of the torque generating mechanism 21 can be achieved. Accordingly, similarly, it is possible to achieve that the useful constant force mechanism 20, the useful movement 10 and the useful timepiece 1 are excellent in workability.

An embodiment of the present invention has been explained above. However, this embodiment has been presented by way of example and it is not intended to limit the scope of the invention. The embodiment can be implemented in various other ways. Various deletions, substitutions and modifications may be made within the scope of the appended claims. The embodiment and variants of this embodiment include, for example, embodiments and variants that those skilled in the art can easily imagine, embodiments and variants substantially identical to the embodiments and variants in question here, as well as embodiments and variations within the scope of equivalents.

[0222] For example, in the embodiments, the arrangement for transmitting power from the barrel spring 16 housed in the barrel movement 11 to the constant-force mechanism 20 is explained by way of example. However, the power transmission is not limited to this case. For example, the power can come from a mainspring 16 provided in a component other than the barrel 11, to the constant force mechanism 20.

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

In the embodiment described above, the power coming from the barrel 11 is transmitted to the second control wheel 56 via the cog wheel on the power source side 12. The power coming from the constant-force spring is transmitted from the first power transmission wheel 25 to the escapement 14, via the escapement side cog wheel 15. However, the power transmission is not limited to this case. For example, power from the barrel 11 can be transmitted to the second power transmission wheel 26 through the power source side cog wheel 12. Power from the constant force spring 27 can be transmitted to the first control wheel 55 via the first power transmission wheel 25 and transmitted from the first control wheel 55 to the escapement 14 via the exhaust-side cog wheel 15.

[0225] In any case, the power coming from the barrel 11 must only be transmitted to the second control wheel 56 or to the second power transmission wheel 26. The power coming from the constant force spring 27 must only be transmitted from the first power transmission wheel 25 or from the first control wheel 55 to the escapement 14.

In the embodiment described above, the constant force mechanism 20 is provided at a position equivalent to the average pinion. However, the position of the constant force mechanism 20 is not limited to this case. The constant-force mechanism 20 can be provided, for example, at a position equivalent to the center pinion 18 or to the seconds mobile 19. In any case, the constant-force mechanism 20 need only be provided between the barrel 11 and the escapement 14. In this case, the constant-force mechanism 20 can be arranged so as to form part of a train of successive gears in which the barrel 11 and the escapement 14 are connected in succession. The constant force mechanism 20 can 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 the cog).

In the embodiment described above, the coupling toothed part 31 and the second power toothed part 35 are connected by means of the torque adjustment jumper 34. However, the connection between the toothed part coupling 31 and the second part with power teeth is not limited to this case. The coupling toothed part 31 and the second power toothed part 35 can be connected by means, for example, of a sliding and friction structure.

[0228] In the embodiment described above, the stopper wheel 81 is turned and reversed by means of a fixed toothed part 82 of the internal toothed type. However, the fixed-tooth part 82 is not limited to this case. The fixed tooth part 82 may be a fixed tooth part 82 of the external tooth type.

[0229] In this case, as shown in Figures 24 to 26, it is possible to reverse the stop wheel 81 clockwise around the second axis of rotation 02, while turning the stopper wheel 81 counterclockwise around the fifth axis of rotation 05. Even in this case, the direction of rotation of the stopper wheel 81 is only opposite to the direction of rotation present in the mode implementation described above. It is possible to obtain the same action and the same effects. It will be noted that, in this case, the engagement surface 80a of the paddle 80 faces outwards in the radial direction.

[0230] In other words, as shown in Fig. 24, at an initial stage of engagement, the working surface 95a of the detent tooth 95 engages deeply with the paddle 80. Then, As shown in Fig. 25, the working surface 95a of the stopper tooth 95 moves toward the tip of the pallet 80, while sliding on the engagement surface 80a, by the process of terminating the engagement of the paddle 80. As shown in Figure 36, the working surface 95a of the stop tooth 95 and the paddle 80 ceases to be in engagement at an instant of time which is when the working surface 95a of the detent tooth 95 passes over the engagement paddle tip 80.

[0231] At this moment, the support lever 85 carries the pallet 80 so that the fictitious line L (direction of the vector F3) extending according to the force F3 resulting from the thrust force F1, with which the tooth of stopper 95 pushes on the engagement surface 80a, and the friction force F2, generated by the stopper tooth 95 sliding on the engagement surface 80a, crosses the second axis of rotation O2. It will be noted that, in the case where the part with fixed teeth 82 is of the type with external teeth, the direction of rotation of the stop tooth 81 is contrary to the direction of rotation taking place in the embodiment described above. Therefore, the resultant force F3 is rotated in the direction of the second axis of rotation 02.

[0232] Even in the case of a part with fixed teeth 82 of the type with external teeth, at the moment when the direction of the resultant force F3 crosses the second axis of rotation 02 as represented in FIG. rotation 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 shift.

In particular, before and after the direction of the resultant force F3 crosses the second axis of rotation O2, rotation torques in opposite directions are generated. In other words, the rotating torque T for driving the support lever 85 toward the stopper wheel 81 is generated when the support lever 85 is as shown in Fig. 26, while the rotation torque in rotation 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 Figure 24.

[0234] Therefore, even in the case of a fixed tooth part 82 of the external tooth type, when the period from engagement until the engagement ceases between the stop tooth part 96 and the pallet 80 is chosen as being a cycle, it is possible to maintain constant the average torque which is the average over a cycle of the rotation 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 rotating cylindrical body 40 within the first power transmission wheel 25. However, the contact of the The distal end 48a of the limiting lever 48 is not limited to this case. For example, as shown in Fig. 27, an upwardly projecting limit rod 130 may be provided at the distal end 48a of the limit lever 48. The limit rod 130 may be brought into contact with a wall internal 131 of the opening in the part with power teeth 41. In this case, it is possible to obtain the same action and the same effects.

[0236] Further, as shown in Figure 28, the distal end 48a of the limiter lever 48 can be brought into contact with a limiter rod 135 projecting downward from the arm 41a within the first wheel. power transmission 25. In this case, it is possible to obtain the same action and the same effects.

[0237] Note that, in Figure 28, a through hole 136 (the first engagement portion according to the present invention) having an elongated hole shape extending in a direction orthogonal to the radial direction of the first axis of O1 rotation in a plan view is formed in the arm 41a. The head 51 of the defining segment 47 has a rectangular shape in a plan view according to the through hole 136 and is able to rotate around the central axis of the shaft 50. Therefore, by rotating the head 51 after having inserted this 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 sliding out of the through hole 136.

Consequently, 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 transmission wheel 26, via the fixed ring 45. The segment of definition 47 which defines the position, in the radial direction, of the outer end 27b and the limiting lever 48, which limits that the outer end 27b rotates around the first axis of rotation O1 according to the elastic return of the constant force spring 27 to its original 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.

[0240] For example, the outer end 27b of the constant force spring 27 can be fixed to the first power transmission wheel 25 via, for example, a press stud. A defining segment which defines the position, according to the radial direction, of the inner end 27a and a limiting lever, which limits that the inner end 27a rotates around the first axis of rotation O1 according to the elastic return of the spring to constant force 27 to its original position, may be provided at the inner end 27a of the constant force spring 27.

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

[0242] In the explanation of the embodiment described above, the constant force spring 27 is wound (i.e. the number of turns is increased) by the winding operation performed by the torque generation 21. However, the winding operation is not limited to this case. The constant force spring 27 can be unwound (its number of turns can be reduced) by the winding operation.

[0243] In this case, for example, the constant force spring 27 only needs to be attached (mounted) in the opposite direction to that of the embodiment described above (being reversed). It is not necessary to modify components such as the slider 46, the defining segment 47 and the limiting lever 48. In addition, it is not necessary to change, for example, the position of the constant force spring with respect to the first power transmission wheel 25 and the second power transmission wheel 26.

[0244] In any case, the torque generating mechanism 21 according to the present invention can be applied in either of the two cases in which winding and unwinding are carried out by the winding operation. It is possible to store elastic energy in the constant force spring 27. Note that a reduction in the elastic energy of the constant force spring 27 is called a disarming.

[0245] Further, in the embodiment, the control mechanism 22 comprising the first control wheel 55, the second control wheel 56 and the planetary mechanism 57 is described as an example of what the mechanism may be. control. However, the control mechanism is not limited to this case.

[0246] For example, as the control mechanism, one can use that disclosed in Japanese Patent No. 6040063. Specifically, one can use a control mechanism which includes a follower or a fork which is engaged with a cam connected to a cog on the exhaust side which tilts according to the rotation of the cam. Cyclically, the operating mechanism engages an engagement and disengagement pawl provided on the follower or fork with and disengages from engagement with the engagement and disengagement pawl at from an escapement wheel connected to a power source side cog to drive the engagement and disengagement cycle and winds a constant force spring between the power source side cog and the exhaust side cog .

Claims (7)

1. Torque generation mechanism, comprising: a first power transmission wheel (25) which rotates around a first axis of rotation (01); a second power transmission wheel (26) which is disposed coaxially with the first power transmission wheel (25) and which is rotatable relative to the first power transmission wheel (25) , about the first axis of rotation (O1); and a spiral drive spring (27) which is arranged between the first power transmission wheel (25) and the second power transmission wheel (26) so as to be able to store energy with rotation of the second power transmission wheel (26) relative to the first power transmission wheel and transmitting this energy to the first power transmission wheel (25) and to the second power transmission wheel (26), wherein a first engagement portion (46; 136) is provided on the first power transmission wheel (25) and wherein , at one end (27b) of the drive spring (27), are provided a second engaging part (47) which is able to be reversibly engaged with the first engaging part (46; 136) so as to define the position of the aforementioned end (27b) according to the radial direction with respect to the first axis of rotation (01), and a rotation limiter (48) which is adapted to abut against a part (40:131; 135) of the first power transmission wheel (25) to limit the rotation of the aforementioned end (27b) around the first axis of rotation (O1) with the deformation of the drive spring (27). 2. Torque generating mechanism according to claim 1, wherein the first engagement part is a slider (46) rotatable about the first axis of rotation (O1) and having an open end, and the second engagement part (47) is able to be engaged with the first engagement part (46) by means of sliding. 3. Constant force mechanism, including: the torque generating mechanism (21) according to claim 1 or 2; and a control mechanism (22) which is adapted to rotate the second power transmission wheel (26) relative to the first power transmission wheel (25) and to control, depending on an intermittent rotation of the first power transmission wheel (25), when power can be transmitted to the drive spring (27) via the second power transmission wheel (26). 4. A constant force mechanism according to claim 3, wherein the control mechanism (22) comprises: a first control wheel (55) which is able to rotate around a second axis of rotation (02) depending on the rotation of the first power transmission wheel (25); a second control wheel (56) which is arranged coaxially with the first control wheel (55) and which is rotatable relative to the first control wheel (55), around the second axis of rotation (02), and which is meshed with the second power transmission wheel (26); and a planetary mechanism (57) which is disposed between the first control wheel (55) and the second control wheel (56) and which is such that, intermittently, depending on the rotation of the first control wheel (55 ), a pawl (80) fitted to the first control wheel (55) is able to engage with and be released from a stop wheel (81) fitted to the second control wheel (56), the first power transmission wheel (25) and the first drive wheel (55) being arranged to transmit power from the drive spring (27) to an escapement, and power from a power source being transmitted to the second power transmission wheel (26) or the second drive wheel (56). 5. Timepiece movement, comprising a torque generating mechanism (21) according to claim 1 or 2. 6. Timepiece movement, comprising a constant force mechanism (20) according to claim 3 or 4. 7. Timepiece, comprising a timepiece movement (10) according to claim 5 or 6.