JP2017106775A - Constant force spring adjustment mechanism, constant force device, and mechanical timepiece - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a constant force spring adjustment mechanism which is capable of achieving the improvement of assemblability and miniaturization, while suppressing a manufacturing cost, with a simple structure and has high versatility and to provide a constant force device and a mechanical timepiece.SOLUTION: The constant force spring adjustment mechanism includes a support plate 120, an adjustment gear 111 and an operation gear 123 which are provided on the surface 120b of the support plate 120, and a constant force spring 68 whose both ends are attached to the adjustment gear 111 and an outer carriage respectively and which generates a spring force between the support plate 120 and the outer carriage. The adjustment gear 111 is provided to operate in the winding and unwinding directions of the constant force spring 68. The adjustment gear 111 is provided in the support plate 120 through spoke parts 113 and 114. The adjustment gear 111 is rotated when receiving force of a predetermined torque or more.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a constant force spring adjusting mechanism, a constant force device, and a mechanical timepiece.

  In a mechanical timepiece, when the rotational torque transmitted from the barrel to the escape wheel of the escapement speed control mechanism fluctuates according to the unwinding of the mainspring of the barrel, the balance angle of the balance changes and the rate of the watch changes. . Therefore, a constant force device has been proposed in which a constant force spring is disposed between the barrel and the escapement speed control mechanism in order to suppress fluctuations in rotational torque transmitted to the escape wheel.

  The constant force spring imparts a rotational force to the escape wheel and thereby can suppress the influence of the rotational torque that varies in accordance with the unwinding of the mainspring. However, if the winding amount of the constant force spring changes for each timepiece, the rate of such a timepiece cannot be stabilized. For this reason, in order to always keep the winding amount of the constant force spring assembled to the timepiece, various techniques capable of adjusting the winding amount have been proposed.

  For example, a technique is disclosed in which a constant force spring is provided on an adjustment member having a tooth portion, and a toothed pinion that is meshed with a tooth portion of the adjustment member is provided. The toothed kana is provided on the base plate or the train wheel bridge so as to be able to contact and separate from the tooth portion of the adjustment member. And when adjusting the winding amount of a constant force spring, a toothed pinion is meshed | engaged with the tooth | gear part of an adjustment member, and an adjustment member is rotated through a toothed pinion (for example, refer patent document 1).

  In addition, a technique is disclosed in which one end of a constant force spring is attached to one end of a shaft and the other end of the constant force spring is attached to an adjustment lever. The adjustment lever is rotatably supported on the shaft. And when adjusting the winding amount of a constant force spring, an adjustment lever is rotated centering on an axis | shaft (for example, refer patent document 2).

Special table 2012-503187 gazette China Utility Model Publication No. 201575783 Specification

  However, in Patent Document 1, since the toothed pinion is provided on the main plate or the train wheel bridge so as to be able to contact and separate from the tooth portion of the adjustment member, the structure becomes complicated. For this reason, there is a problem that the manufacturing cost of the constant force device increases and the constant force device becomes large. In addition, when the constant force device is provided, it is necessary to change the design of the main plate and the train wheel bridge. For this reason, there exists a subject that versatility is low and the assembly | attachment property of a constant force apparatus is also bad.

  Moreover, in patent document 2, the adjustment range of the winding amount of a constant force spring and the movable range of an adjustment lever are proportional. That is, for example, if the constant force spring is to be wound up by one turn, the adjustment lever must also be turned one turn. For this reason, the space for ensuring the movable range of an adjustment lever is needed, and there exists a subject that a constant force apparatus will enlarge.

  Accordingly, the present invention has been made in view of the above-described circumstances, and is capable of improving assemblability and downsizing while suppressing the manufacturing cost with a simple structure and is a highly versatile constant force spring. An adjustment mechanism, a constant force device, and a mechanical timepiece are provided.

  In order to solve the above-described problem, a constant force spring adjusting mechanism according to the present invention includes a support portion, a plurality of operation portions provided on one surface of the support portion, and linked to each other, and the plurality of operation portions. One of the first operating parts, a constant force spring that is attached to both ends of the rotating body and the first operating part, and generates a spring force between the support part and the rotating body, The first operating portion is provided so as to be operable in a winding direction and an unwinding direction of the constant force spring, and at least one of the plurality of operating portions includes a torque transmitting portion on the support portion. The torque transmission unit is actuated when receiving a force exceeding a predetermined torque.

Thus, since all the components are arranged on the support portion, the constant force spring adjustment mechanism can be unitized. For this reason, while being able to improve the assembly | attachment property of a constant force spring adjustment mechanism, versatility can be improved.
In addition, since it is not necessary to provide other operation units detachably from the first operation unit as in the prior art, the structure can be simplified and the size can be reduced.

  In the constant force spring adjusting mechanism according to the present invention, the operation unit is a gear.

  With this configuration, it is only necessary to secure an arrangement space for the operation unit, so that a space for securing a movable range of the operation unit is not required as in the related art. For this reason, the constant force spring adjusting mechanism can be further reduced in size.

  The constant force spring adjusting mechanism according to the present invention is characterized in that the number of teeth of the operation unit other than the first operation unit is set smaller than the number of teeth of the first operation unit.

  By comprising in this way, the rotation ratio of a 1st operation part can be made smaller than the rotation ratio of operation parts other than this 1st operation part. That is, when it is going to rotate 1st operation part 1 time, operation parts other than this 1st operation part will be rotated 1 rotation or more. For this reason, it is possible to facilitate fine adjustment of the rotation amount of the first operation unit.

  In the constant force spring adjusting mechanism according to the present invention, the torque transmitting portion is composed of two spring members that sandwich a support shaft erected on one surface of the support portion with a predetermined pressing force from outside in the radial direction, Both ends of the two spring members are fixed to the portion.

  By comprising in this way, a torque transmission part can be made into a simple structure, and manufacturing cost can also be held down.

  In the constant force spring adjusting mechanism according to the present invention, a step portion for positioning the two spring members is formed at a position corresponding to the spring member of the support shaft, and is adjacent to the step portion. A tapered portion is formed, and the tapered portion is formed so as to gradually increase in diameter in a direction away from the stepped portion in the axial direction, and from the stepped portion of the two spring members in the axial direction. It is characterized by suppressing movement in a direction away from each other.

  By comprising in this way, while supporting a spindle reliably by two spring members, the position of the two spring members with respect to a spindle can be maintained. For this reason, two spring members can function reliably as a torque transmission part.

  In the constant force spring adjusting mechanism according to the present invention, the torque transmission part is an elastic jumper provided in the support part, and the jumper is arranged to be detachable from the teeth of the operation part. It is characterized by.

  By comprising in this way, a torque transmission part can be made into a simple structure, and manufacturing cost can also be held down.

  In the constant force spring adjusting mechanism according to the present invention, a part of the operation portion arranged on the outermost side in the surface direction of the one surface of the support portion protrudes outward in the surface direction of the one surface from the support portion. It is characterized by.

  By comprising in this way, since the operation part arrange | positioned on the outermost side can be easily operated, without a support part becoming obstructive, the adjustment operation | work by a constant force spring adjustment mechanism can be facilitated.

  A constant force device according to the present invention is provided in the constant force spring adjusting mechanism described above, an outer carriage that is the rotating body, an inner carriage that is rotatably supported by the outer carriage, and the inner carriage. And a stopper provided on the outer carriage and engageable with the stop wheel, and the support portion is provided on the inner carriage.

  With such a configuration, it is possible to improve the assembly property and reduce the size while reducing the manufacturing cost with a simple structure, and it is possible to provide a highly versatile constant force device.

  A mechanical timepiece according to the present invention includes the constant force device described above, wherein the outer carriage is rotatably supported with respect to a base plate, and the escapement speed control mechanism is provided on the inner carriage. And the driving force of the train wheel is transmitted to the outer carriage.

With such a configuration, it is possible to improve the assembling property and reduce the size while suppressing the manufacturing cost with a simple structure, and it is possible to provide a highly versatile mechanical timepiece.
Further, the outer carriage to which the driving force of the train wheel is transmitted can be rotated or stopped (tact drive) with respect to the inner carriage by the stop wheel and the stopper, so that the constant force spring is periodically provided. Can be rolled up. For this reason, the influence on the escapement speed control mechanism by unwinding the mainspring can be reduced.

  According to the present invention, since all the parts are arranged on the support portion, the constant force spring adjustment mechanism can be unitized, and the assembly of the constant force spring adjustment mechanism can be improved and the versatility can be enhanced. In addition, the structure of the constant force spring adjustment mechanism can be simplified and the size can be reduced.

It is a top view of the front side of the movement of the mechanical timepiece in the embodiment of the present invention. It is the perspective view which abbreviate | omitted illustration of the escape control mechanism of the tourbillon with a constant force apparatus in 1st Embodiment of this invention. It is the side view which abbreviate | omitted illustration of the escape control mechanism of the tourbillon with a constant force apparatus in 1st Embodiment of this invention. It is the perspective view which looked at the outer carriage in 1st Embodiment of this invention from the carriage receiving side. It is the perspective view which looked at the inner carriage in 1st Embodiment of this invention from the main plate side. It is the perspective view which looked at the constant force spring adjustment mechanism in 1st Embodiment of this invention from the main plate side. It is sectional drawing which follows the AA line of FIG. It is a perspective view of the adjustment gear in a 1st embodiment of the present invention. It is the perspective view which looked at the constant force spring adjustment mechanism in 1st Embodiment of this invention from the carriage receiving side. It is the perspective view which looked at the constant force spring adjustment mechanism in 2nd Embodiment of this invention from the main plate side.

  Next, embodiments of the present invention will be described with reference to the drawings.

(Mechanical watch)
FIG. 1 is a plan view of the front side of the movement of the mechanical timepiece 1.
As shown in FIG. 1, the mechanical timepiece 1 includes a movement 10 and a casing (not shown) that houses the movement 10.

The movement 10 has a ground plane 11 constituting a substrate. A dial (not shown) is disposed on the back side of the base plate 11. A train wheel incorporated on the front side of the movement 10 is referred to as a front train wheel, and a train wheel incorporated on the back side of the movement 10 is referred to as a back train wheel.
A winding stem guide hole 11a is formed in the base plate 11, and a winding stem 12 is rotatably incorporated therein. The winding stem 12 is positioned in the axial direction by a switching device having a setting lever 13, a yoke 14, a yoke spring 15 and a back presser 16. In addition, a chichi wheel 17 is rotatably provided on the guide shaft portion of the winding stem 12.

  Under such a configuration, the winding stem 12 is rotated in a state where the winding stem 12 is in the first winding stem position (0th stage) closest to the inside of the movement 10 along the rotation axis direction. Then, the wheel 17 is rotated through the rotation of a not-shown pinion wheel. And when this chi-wheel 17 rotates, the round hole wheel 20 which meshes with this rotates. And when this round hole wheel 20 rotates, the square wheel 21 which meshes with this rotates. Further, when the square wheel 21 is rotated, the main spring (not shown) accommodated in the barrel complete 22 is wound up.

The front train wheel of the movement 10 includes a second wheel 25, a third wheel 26, a fourth wheel 27, and a fifth wheel 28 in addition to the barrel wheel 22 described above. It performs the function of transmitting. A tourbillon 30 with a constant force device is arranged on the front side of the movement 10.
The center wheel 25 is a gear that meshes with the barrel complete 22. The third wheel 26 is a gear that meshes with the second wheel 25. The fourth wheel 27 is a gear that meshes with the third wheel 26. The fifth wheel 28 is a gear that meshes with the fourth wheel 27. The fifth wheel 28 is engaged with a tourbillon 30 with a constant force device.

(Tourbillon with constant force device)
FIG. 2 is a perspective view in which the escapement speed regulating mechanism 100 of the tourbillon 30 with a constant force device is omitted. FIG. 3 is a side view in which the escapement speed regulating mechanism 100 of the tourbillon 30 with a constant force device is not shown.
As shown in FIGS. 1 to 3, a tourbillon 30 with a constant force device includes an escapement speed control mechanism 100 (see FIG. 1) for controlling the rotation of the front train wheel, and the escapement speed control mechanism 100. A constant force device 3 for suppressing fluctuations in the transmitted rotational torque is provided. The constant force device tourbillon 30 includes a base plate 11, an outer carriage 33 rotatably supported by a carriage receiver (not shown) disposed opposite to the base plate 11, and the outer carriage 33. An inner carriage 34 that is rotatably supported with respect to the outer carriage 33 is provided inside 33.

(Outer carriage)
FIG. 4 is a perspective view of the outer carriage 33 as seen from the carriage receiving side.
As shown in FIGS. 3 and 4, the outer carriage 33 includes a substantially disc-shaped first outer carriage bearing portion 35 disposed on the main plate 11 side and a substantially disc-shaped second disposed on the carriage receiving side. And an outer carriage bearing portion 36.

In the first outer carriage bearing portion 35, the outer surface 35a on the base plate 11 side is rotatably supported by the base plate 11, while the inner surface 35b on the opposite side to the base plate 11 rotatably supports the inner carriage 34. In the second outer carriage bearing portion 36, an outer surface 36a on the carriage receiving side is rotatably supported by the carriage receiver, and an inner surface 36b on the opposite side of the carriage receiver rotatably supports the inner carriage 34.
In the following description, the rotational axis direction of the outer carriage 33 is simply referred to as an axial direction, the rotational direction of the outer carriage 33 is referred to as a circumferential direction, and a direction perpendicular to the axial direction and the circumferential direction is referred to as a radial direction.

A ring-shaped external gear portion 41 is provided on the radially outer side of the first outer carriage bearing portion 35. The external gear 41 is meshed with the fifth wheel & pinion 28. Further, the external gear portion 41 and the first outer carriage bearing portion 35 are connected to each other by three first arm portions 42. The three first arm portions 42 extend along the radial direction and are arranged at equal intervals in the circumferential direction.
On the other hand, three second arm portions 43 extending outward in the radial direction are integrally formed on the outer peripheral portion of the second outer carriage bearing portion 36. These second arm parts 43 are arranged at equal intervals in the circumferential direction so as to correspond to the first arm part 42 on the first outer carriage bearing part 35 side.

  At the connection portion between the first arm portion 42 and the external gear portion 41 and the tip of the second arm portion 43, substantially disk-shaped shaft mounting seats 44 and 45 are integrally formed, respectively. A shaft 46 extending along the axial direction is provided between the shaft mounting seats 44 and 45. Both ends of the shaft 46 are fastened and fixed to the shaft mounting seats 44 and 45 by screws 47 screwed from above the shaft mounting seats 44 and 45.

  In addition, a support bar 48 formed in a ring shape so as to surround the first outer carriage bearing portion 35 is provided between the first outer carriage bearing portion 35 and the external gear portion 41. The support bar 48 is integrally formed so as to be connected to the first arm portion 42. The support bar 48 is provided with a stop wheel bearing unit 50 and a stop wheel 70 that is rotatably supported by the stop wheel bearing unit 50. Here, the stop wheel bearing unit 50 and the stop wheel 70 constitute the constant force device 3. Details of the constant force device 3 will be described later.

(Inner carriage)
FIG. 5 is a perspective view of the inner carriage 34 as seen from the main plate 11 side.
As shown in FIGS. 3 and 5, the inner carriage 34 includes a substantially disk-shaped first inner carriage bearing portion 81 disposed on the main plate 11 side and a substantially disk-shaped second disposed on the carriage receiving side. And an inner carriage bearing portion 82. The first inner carriage bearing portion 81 and the second inner carriage bearing portion 82 are arranged coaxially with the first outer carriage bearing portion 35 and the second outer carriage bearing portion 36 of the outer carriage 33.

The first inner carriage bearing portion 81 is rotatably supported on the inner surface 35 b side of the first outer carriage bearing portion 35 via a part of the constant force device 3. Further, the second inner carriage bearing portion 82 is rotatably supported on the inner surface 36 b side of the second outer carriage bearing portion 36.
The escapement speed control mechanism 100 is provided between the first inner carriage bearing portion 81 and the second inner carriage bearing portion 82 that are rotatably supported in this manner.

  As shown in FIG. 1, the escapement speed control mechanism 100 includes a escape wheel 101 that rotates by receiving the rotational force of the inner carriage 34 and a balance 102 that freely vibrates by receiving the rotational force of the escape wheel 101. I have. The escape wheel & pinion 101 always moves backward at a constant period under the influence of the free vibration of the balance with hairspring 102.

  Returning to FIGS. 3 and 5, three first arm portions 88 extending outward in the radial direction are integrally formed on the outer peripheral portion of the first inner carriage bearing portion 81. In addition, three second arm portions 89 extending outward in the radial direction are integrally formed on the outer peripheral portion of the second inner carriage bearing portion 82. The first arm portion 88 and the second arm portion 89 are arranged at equal intervals in the circumferential direction, and are further arranged to face each other in the axial direction.

  A substantially disk-shaped shaft mounting seat 91, 92 is integrally formed at the tip of each arm portion 88, 89, respectively. A shaft 93 extending in the axial direction is provided between the shaft mounting seats 91 and 92. Both ends of the shaft 93 are fastened and fixed to the shaft mounting seats 91 and 92 by screws 94 screwed from above the shaft mounting seats 91 and 92. In addition, the length of each arm part 88 and 89 is set to the length which the shaft 93 does not interfere with the balance with hairspring 102.

Further, on the radially outer side of the first inner carriage bearing portion 81, a support bar 95 formed in a ring shape so as to surround the first inner carriage bearing portion 81 is provided. The support bar 95 is integrally formed so as to be connected to the first arm portion 88. The support bar 95 is provided with a stopper 96 constituting the constant force device 3.
The stopper 96 is engaged with and released from a later-described collar portion 76 of the stop wheel 70. The stopper 96 includes a support portion 99 fixed to the support bar 95 and a claw portion 98 that is held by the support portion 99 and provided so as to protrude from the support portion 99 along the circumferential direction.

(Constant force device)
As shown in FIGS. 3 to 5, the constant force device 3 includes the outer carriage 33 in addition to the stop wheel bearing unit 50 and the stop wheel 70 provided on the outer carriage 33 and the stopper 96 provided on the inner carriage 34. The constant force spring adjusting mechanism 110 is provided between the first outer carriage bearing portion 35 and the first inner carriage bearing portion 81 of the inner carriage 34.

  As shown in detail in FIGS. 3 and 4, the stop wheel bearing unit 50 includes a first stop wheel bearing portion 52 attached to the base plate 11 side of the support bar 48 in the outer carriage 33, and a carriage receiver of the support bar 48. And a second stop wheel bearing portion 53 attached to the side. The first stop wheel bearing 52 is fastened and fixed to the support bar 48 by screws (not shown). Further, the second stop wheel bearing portion 53 is fastened and fixed to the support bar 48 by screws 64. A gap S <b> 1 is formed between the support bar 48 and the second stop wheel bearing portion 53.

  The stop axle body 71 is rotatably supported by the first stop wheel bearing portion 52 and the second stop wheel bearing portion 53. A stop pinion 71a is integrally formed in most of the axial center of the stop axle 71. The stop pinion 71a is meshed with a fixed wheel (not shown) provided on the main plate 11. A stop wheel 70 is provided on the carriage receiving side of the stop axle 71 so as to be interposed in the gap S1 between the support bar 48 and the second stop wheel bearing portion 53.

  The stop wheel 70 is a member made of, for example, a metal material or a material having a crystal orientation such as single crystal silicon, and is a LIGA (Lithographie Galvanforming) incorporating an optical technique such as electroforming or photolithography. It is formed by an Abforming process, DRIE (Deep Reactive Ion Etching), MIM (Metal Injection Molding), and the like.

  The stop wheel 70 is formed in a ring shape so as to surround the periphery of the hub portion 73, which is disposed on the outer side in the radial direction of the hub portion and a central hub portion (not shown) that is fitted and fixed to the stop axle 71. A rim portion 74 and a spoke portion 75 that connects the hub portion 73 and the rim portion 74 are integrally formed. A plurality (five in this embodiment) of flanges 76 are formed on the outer periphery of the rim 74 so as to protrude outward in the radial direction. The claw portion 98 of the stopper 96 provided on the inner carriage 34 is engaged with and released from the flange portion 76.

  Further, the support bar 48 is provided with a whisk holder 66. A beard 67 is inserted into the beard holder 66. The whiskers 67 are fastened and fixed to the whiskers 66 by screws 105. An outer end portion 68 a of a constant force spring 68 constituting the constant force spring adjusting mechanism 110 is fixed to the whisker 67.

(First embodiment)
(Constant force spring adjustment mechanism)
FIG. 6 is a perspective view of the constant force spring adjusting mechanism 110 as viewed from the main plate 11 side. FIG. 7 is a cross-sectional view taken along the line AA of FIG.
As shown in FIGS. 4 to 7, the constant force spring 68 is for generating a spring force between the outer carriage 33 and the inner carriage 34. In other words, the constant force spring 68 applies a rotational force to the inner carriage 34 with respect to the outer carriage 33. The constant force spring 68 is formed in a spiral shape, and the inner end portion 68 b is fixed to the adjustment gear 111.

FIG. 8 is a perspective view of the adjustment gear 111.
As shown in the figure, the adjustment gear 111 is for adjusting the winding amount of the constant force spring 68 by rotating the adjustment gear 111. The adjustment gear 111 has a gear body 112 formed in an annular shape. A tooth portion 112 a is formed on the outer peripheral portion of the gear body 112. A pair of spoke portions 113 and 114 extending in parallel in one direction are integrally formed on the inner peripheral portion of the gear body 112. Each of the spoke portions 113 and 114 has elasticity, and is configured to be slightly elastically deformable in a direction away from each other.

  In addition, support shaft holding portions 113a and 114a are formed at the center in the longitudinal direction of the spoke portions 113 and 114 so as to bend in directions away from each other. These spindle holding parts 113a and 114a are in a state of being arranged along one arbitrary circle. Of the two support shaft holding portions 113a and 114a, one support shaft holding portion 114a is formed with a welding base 115 extending toward the side opposite to the support shaft holding portion 113a.

  A through hole 115 a is formed in the welding base 115. A substantially cylindrical constant force spring inner end welded portion 116 is inserted into the through hole 115a. The constant force spring inner end welded portion 116 protrudes toward the main plate 11 side, and a notch 116a is formed at the tip. The inner end 68b of the constant force spring 68 is fixed to the notch 116a. In addition, as a fixing method of this inner end part 68b, methods, such as laser welding, are mentioned, for example.

Returning to FIGS. 6 and 7, each of the support shaft holding portions 113 a and 114 a holds the support shaft 117. The support shaft 117 is formed in a stepped cylindrical shape so that the diameter of the support shaft 117 is reduced through a step portion as the outer peripheral surface moves toward the tip. That is, the support shaft 117 is formed with a first reduced diameter portion 117b via a first stepped portion 117a in order from the base end side, and the second reduced diameter portion 117b is connected to a second stepped portion 117c through a second stepped portion 117c. A reduced diameter portion 117d is formed.
Under such a configuration, the shaft portion 108 is inserted into the support shaft 117 (see FIGS. 4 and 7). The shaft portion 108 is for causing the first inner carriage bearing portion 35 of the outer carriage 33 to rotatably support the first inner carriage bearing portion 81 of the inner carriage 34.

Further, the support shaft holding portions 113a and 114a of the adjustment gear 111 are arranged on the second reduced diameter portion 117d of the support shaft 117 so as to hold the second reduced diameter portion 117d.
More specifically, the support pinching portions 113a and 114a sandwich the second reduced diameter portion 117d while being elastically deformed so as to be slightly expanded by the second reduced diameter portion 117d. For this reason, a predetermined frictional force is generated between the second reduced diameter portion 117d and the support shaft holding portions 113a and 114a. For this reason, the adjustment gear 111 does not rotate with respect to the support shaft 117 unless a torque greater than a predetermined rotational torque acts on the adjustment gear 111.

Further, the support pinching portions 113a and 114a are positioned with respect to the support shaft 117 by contacting the second stepped portion 117c.
Further, a reverse tapered portion 118 is formed in the second reduced diameter portion 117d between the second stepped portion 117c and the second stepped portion 117c slightly from the substantially axial center. That is, the reverse taper portion 118 is formed at a location corresponding to the support pinch portions 113a and 114a of the second reduced diameter portion 117d and adjacent to the second stepped portion 117c. The reverse taper portion 118 is formed so as to be gradually reduced in diameter toward the second stepped portion 117c. By forming the reverse taper portion 118, the support shaft holding portions 113a and 114a are not easily removed from the support shaft 117.
On the other hand, a substantially disc-shaped support plate 120 is externally fitted and fixed to the first reduced diameter portion 117b of the support shaft 117.

FIG. 9 is a perspective view of the constant force spring adjusting mechanism 110 as seen from the carriage receiving side.
As shown in FIGS. 5 to 7, 9, the support plate 120 is fastened and fixed to the base plate 11 side of the first inner carriage bearing portion 81 constituting the inner carriage 34 by screws 106. The diameter of the support plate 120 is set to be substantially the same as the diameter of the first inner carriage bearing portion 81.

  A through hole 120 a is formed at the substantially radial center of the support plate 120. The first reduced diameter portion 117b of the support shaft 117 is externally fitted and fixed to the through hole 120a by, for example, press fitting. Further, the support plate 120 is in contact with the first stepped portion 117a of the support shaft 117, whereby the relative position between the support plate 120 and the support shaft 117 is determined. The support shaft 117 is in a state in which the second reduced diameter portion 117d protrudes from the surface (surface on the base plate 11 side) 120b of the support plate 120 in a state where the support shaft 120 is externally fitted and fixed.

  An operation gear 123 that meshes with the adjustment gear 111 is disposed on the surface 120 b of the support plate 120. The operation gear 123 has a role of rotating the adjustment gear 111 by rotating the operation gear 123. The operation gear 123 is rotatably supported by a sub-support shaft 124 protruding from the surface 120 b of the support plate 120. A tooth portion 123 a is formed on the outer peripheral portion of the operation gear 123. The tooth portion 123 a is meshed with the tooth portion 112 a of the adjustment gear 111.

  Here, the reference circle diameter of the operation gear 123 is set smaller than the reference circle diameter of the adjustment gear 111. For this reason, the number of teeth of the tooth portion 123 a of the operation gear 123 is set to be smaller than the number of teeth of the tooth portion 112 a of the adjustment gear 111. Further, the operation gear 123 is arranged such that a part of the tooth portion 123 a protrudes radially outward from the outer peripheral portion of the support plate 120.

Further, on the back surface (carriage receiving surface) 120c side that is the surface opposite to the front surface 120b of the support plate 120, a stepped surface 121 that is thinned through a step over the entire circumference of the outer peripheral portion is formed. Has been. Further, the support plate 120 is formed with a through hole 122 into which the screw 106 is inserted, slightly inward in the radial direction from the step surface 121. A counterbore 122a is formed on the surface 120b side of the through hole 122. This prevents the head of the screw 106 inserted into the through hole 122 from protruding from the support plate 120.
Further, on the back surface 120 c of the support plate 120, positioning pins 125 project from both sides of the support shaft 177 at positions avoiding the through holes 122.

On the other hand, the first inner carriage bearing portion 81 of the inner carriage 34 has an annular ridge corresponding to the stepped surface 121 of the support plate 120 on the surface on the ground plate 11 side, and a female screw corresponding to the through hole 122 of the support plate 120. , And positioning recesses (both not shown) corresponding to the positioning pins 125 of the support plate 120 are formed.
Under such a configuration, the back surface 120c of the support plate 120 is superimposed on the surface of the first inner carriage bearing portion 81 on the ground plate 11 side. The support plate 120 is fastened and fixed to the first inner carriage bearing portion 81 by screws 106.

  Here, when the support plate 120 is fastened and fixed to the first inner carriage bearing portion 81, the first inner carriage bearing portion 81 is formed by the protrusions of the first inner carriage bearing portion 81 and the step surface 121 of the support plate 120. And the support plate 120 are positioned at the center in the radial direction. Further, the positioning of the first inner carriage bearing portion 81 and the support plate 120 in the radial center is also performed by the positioning concave portion of the first inner carriage bearing portion 81 and the positioning pin 125 of the support plate 120. Further, the positioning in the circumferential direction of the first inner carriage bearing 81 and the support plate 120 is performed by the positioning recess of the first inner carriage bearing 81 and the positioning pin 125 of the support plate 120. Then, a screw 106 is inserted into the through hole 122 from the surface 120 b side of the support plate 120, and this screw 106 is screwed into the female screw portion of the first inner carriage bearing portion 81.

(Operation of tourbillon with constant force device)
Next, the operation of the tourbillon 30 with a constant force device will be described.
In the outer carriage 33, since the external gear 41 is meshed with the fifth wheel & pinion 28 (see FIG. 1), the rotational force of the barrel wheel 22 is transmitted to the outer carriage 33 via the front wheel train. Further, the stop wheel 70 is meshed with a fixed wheel (not shown) in which a stop pinion portion 71 c is provided on the main plate 11. Therefore, when the outer carriage 33 rotates, the stop wheel 70 revolves around the rotation axis of the outer carriage 33 while rotating around the axis of the stop pinion 71c.

On the other hand, the inner carriage 34 is rotatably supported with respect to the outer carriage 33 and is connected to the outer carriage 33 via a constant force spring adjustment mechanism 110 (constant force spring 68). For this reason, the inner carriage 34 rotates with respect to the outer carriage 33 under the urging force of the constant force spring 68.
Further, the escapement speed control mechanism 100 is driven by the rotational force of the inner carriage 34. Specifically, the escape wheel 101 that rotates by receiving the rotational force of the inner carriage 34 rotates, and the balance with hairspring 102 receives the rotational force of the escape wheel 101 to freely vibrate. The escape wheel & pinion 101 always moves backward at a constant period under the influence of the free vibration of the balance with hairspring 102. For example, the inner carriage 34 is configured to rotate once per minute.

Further, as the inner carriage 34 rotates, the collar portion 76 of the stop wheel 70 and the pawl portion 98 of the stopper 96 are repeatedly engaged and released.
Specifically, in a state where the collar portion 76 of the stop wheel 70 and the claw portion 98 of the stopper 96 are engaged, the outer carriage 33 does not rotate and only the inner carriage 34 continues to rotate. At this time, since the stopper 96 rotates integrally with the inner carriage 34, the stopper 96 moves in a direction in which the pawl 98 is released.

  Then, when the engagement state between the collar portion 76 and the pawl portion 98 is released, the outer carriage 33 rotates, and the stop wheel 70 rotates along with the axis of the stop pinion portion 71c. Revolves around 33 rotation axes. Then, the collar portion 76 and the pawl portion 98 are engaged again, and the outer carriage 33 stops. At this time, the constant force spring 68 is wound up by the amount of rotation of the outer carriage 33, and the inner carriage 34 continues to rotate by the biasing force of the constant force spring 68. By repeating this, the inner carriage 34 continues to rotate at a constant speed, and the escapement governing mechanism 100 continues to perform escapement at a constant period.

(Adjustment method of constant force spring adjustment mechanism)
Next, an adjustment method of the constant force spring adjustment mechanism 110 will be described based on FIG.
Here, as described above, the winding amount of the constant force spring 68 of the constant force spring adjusting mechanism 110 affects the operations of the inner carriage 34 and the escapement speed adjusting mechanism 100. Specifically, the swing angle (amplitude) of the balance with hairspring 102 changes. That is, the winding amount of the constant force spring 68 is determined in accordance with a desired swing angle. As a desired swing angle, a high swing angle (280 to 300 °) that is not easily affected by disturbance or the movement of the center of gravity of a hairspring (not shown), or a single weight of a balance wheel (not shown) (the center of gravity is shifted from the axis). 220 ° or the like where the influence of the case) is eliminated. For this reason, it is desirable that the initial winding amount of the constant force spring 68 is adjusted based on a desired swing angle (amplitude) of the balance with hairspring 102.

  As shown in FIG. 6, in order to adjust the amount of winding of the constant force spring 68, the operation gear 123 is rotated. The operation gear 123 is arranged such that a part of the tooth portion 123 a protrudes radially outward from the outer peripheral portion of the support plate 120. For this reason, the operation gear 123 can be easily rotated by rotating this protruding part using a finger or a tool. When the operation gear 123 is rotated, the rotational force is transmitted to the adjustment gear 111 meshed with the operation gear 123.

  Here, the adjustment gear 111 is attached to a support shaft 117 protruding from the support plate 120 via support shaft clamping portions 113a and 114a. For this reason, when a torque greater than a predetermined rotational torque acts on the adjustment gear 111, the adjustment gear 111 rotates with respect to the support shaft 117. That is, the spoke portions 113 and 114 (support shaft clamping portions 113a and 114a) function as torque transmission units that rotate the adjustment gear 111 with respect to the support shaft 117 when a torque greater than a predetermined value is applied to the adjustment gear 111. .

Since the adjustment gear 111 is connected to the inner end portion 68b of the constant force spring 68, the amount of winding of the constant force spring 68 is adjusted by the rotation of the adjustment gear 111. Then, when the amount of winding of the constant force spring 68 reaches a predetermined amount, the adjustment of the constant force spring adjustment mechanism 110 is completed.
The friction force generated between the support shaft 117 (second reduced diameter portion 117d) and the support shaft clamping portions 113a and 114a is such that the adjusting gear 111 rotates with respect to the support shaft 117 when the constant force spring 68 is applied. It is set to a force that does not occur.

As described above, in the constant force spring adjustment mechanism 110 in the first embodiment described above, the adjustment gear 111, the operation gear 123, and the constant force spring 68 are all provided on the surface 120 b of the support plate 120. For this reason, the constant force spring adjustment mechanism 110 can be unitized. Then, by simply attaching the support plate 120 of the unitized constant force spring adjusting mechanism 110 to the first inner carriage bearing portion 81 of the inner carriage 34, the attaching operation of the constant force spring adjusting mechanism 110 can be almost completed. it can. Therefore, the assembling property of the constant force spring adjusting mechanism 110 can be improved and versatility can be enhanced.
Further, unlike the prior art, it is not necessary to provide the operation gear 123 so as to be able to contact and separate from the adjustment gear 111. Therefore, the structure of the constant force spring adjustment mechanism 110 can be simplified and the size can be reduced.

  Furthermore, in order to adjust the winding amount of the constant force spring 68, only the two gears 111 and 123 (the adjustment gear 111 and the operation gear 123) are rotated. Since the gears 111 and 123 rotate around the support shaft 117 and the sub support shaft 124, respectively, they do not move on the support plate 120. For this reason, unlike the prior art, there is no need for a space for securing a movable range of the operation portion for adjusting the amount of winding of the constant force spring 68. Therefore, the constant force spring adjustment mechanism 110 can be further reduced in size.

  Further, the number of teeth of the tooth portion 123 a of the operation gear 123 is set to be smaller than the number of teeth of the tooth portion 112 a of the adjustment gear 111. For this reason, the rotation ratio of the adjustment gear 111 can be made smaller than the rotation ratio of the operation gear 123. That is, when the adjustment gear 111 is to be rotated once, the operation gear 123 is rotated one or more times. For this reason, the amount of rotation of the adjustment gear 111 can be easily finely adjusted.

  Further, the adjustment gear 111 is attached to a support shaft 117 protruding from the support plate 120 via support shaft clamping portions 113a and 114a. The spoke portions 113 and 114 that constitute the support shaft holding portions 113a and 114a have elasticity. And the frictional force is generated in the support shaft clamping portions 113a and 114a with respect to the support shaft 117 by using the elastic force of each of the spoke portions 113 and 114. For this reason, a torque transmission portion that prevents the adjustment gear 111 from rotating with respect to the support shaft 117 can be realized with a simple structure unless a torque greater than a predetermined rotational torque acts on the adjustment gear 111. Therefore, the manufacturing cost of the constant force spring adjustment mechanism 110 can be reduced.

  Further, the operation gear 123 is arranged such that a part of the tooth portion 123 a protrudes radially outward from the outer peripheral portion of the support plate 120. For this reason, the operation gear 123 can be easily rotated by rotating this protruding part using a finger or a tool.

  Further, a reverse tapered portion 118 is formed in the second reduced diameter portion 117d of the support shaft 117 at a location corresponding to the support shaft holding portions 113a and 114a of the adjustment gear 111. By forming the reverse taper portion 118, it is possible to prevent the support shaft clamping portions 113a and 114a from coming off from the support shaft 117. Therefore, the support shaft 117 can be securely held by the support shaft holding portions 113a and 114a, and the positions of the support shaft holding portions 113a and 114a with respect to the support shaft 117 can be maintained. Therefore, the spoke parts 113 and 114 (support shaft clamping parts 113a and 114a) can be functioned reliably as a torque transmission part.

  Note that the adjustment gear 111 may be lightly press-fitted into the support shaft 117, and the adjustment gear 111 may rotate with respect to the support shaft 117 when a torque of a predetermined level or more is applied to the adjustment gear 111. This configuration functions as a torque transmission portion that replaces the spoke portions 113 and 114 (support shaft clamping portions 113a and 114a).

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG.

(Constant force spring adjustment mechanism)
FIG. 10 is a perspective view of the constant force spring adjusting mechanism 210 in the second embodiment as viewed from the side of the base plate 11 and corresponds to the above-described FIG. In addition, the same code | symbol is attached | subjected to the aspect same as 1st Embodiment, and description is abbreviate | omitted.
As shown in the figure, the difference between the first embodiment and the second embodiment is that, in the first embodiment, the adjustment gear 111 is supported on the support shaft 117 via the support shaft clamping portions 113a and 114a. On the other hand, in the second embodiment, the support shaft 117 is inserted into the adjustment gear 211.

  The adjustment gear 211 is formed in a substantially disk shape, and a tooth portion 212a is formed on the outer peripheral portion. A through hole (not shown) is formed in the center of the adjustment gear 211 in the radial direction, and a support shaft 117 is inserted into the through hole. For this reason, the adjustment gear 211 is configured to rotate without any extra frictional force acting on the support shaft 117.

  Here, a jumper 230 is provided on the surface 120 b of the support plate 120. The jumper 230 includes a base portion 231 that extends in an arc shape along the outer peripheral portion of the support plate 120, a circumferential direction of the base portion 231, along the surface direction of the surface 120 b, and an adjustment gear. The arm portion 232 extending along the outer periphery of 211 is integrally formed.

The base portion 231 has a through hole 231a formed at the center in the circumferential direction, and positioning holes 231b formed on both sides of the through hole 231a.
On the other hand, a female screw portion (not shown) is engraved in the support plate 120 at a position corresponding to the through hole 231a. The support plate 120 is provided with a positioning pin 241 inserted into the positioning hole 231b at a position corresponding to the positioning hole 231b.
The jumper 230 is positioned with respect to the support plate 120 by the positioning holes 231b and the positioning pins 241. Further, the screw 240 is inserted into the through-hole 231a, and the screw 240 is screwed into the female screw portion of the support plate 120, whereby the jumper 230 is fastened and fixed to the support plate 120.

  The arm portion 232 is configured such that the tip thereof can be elastically deformed in a direction away from the adjustment gear 211. In addition, a flange portion 233 that can be engaged with and released from the tooth portion 212 a of the adjustment gear 211 is integrally formed at the tip of the arm portion 232. Specifically, the flange portion 233 extends radially inward from the tip of the arm portion 232. And the collar part 233 is formed so that it may taper off gradually toward the radial inside.

Under such a configuration, when the operation gear 123 is rotated, the rotational force is transmitted to the adjustment gear 211 meshed with the operation gear 123. The tooth portion 212a of the adjustment gear 211 is engaged with the flange portion 233 of the jumper 230. When a rotational force is applied to the adjustment gear 211, a pressing force directed radially outward acts on the flange portion 233. .
For this reason, when a torque greater than a predetermined rotational torque acts on the adjustment gear 211, the arm portion 232 of the jumper 230 is pushed and the engagement between the tooth portion 212a of the adjustment gear 211 and the flange portion 233 of the jumper 230 is released. The That is, the adjustment gear 211 and the jumper 230 have a so-called rotation latch structure. In other words, the jumper 230 functions as a torque transmission unit that rotates the adjustment gear 211 with respect to the support shaft 117 when a predetermined torque or more is applied to the adjustment gear 211.

Then, when the arm portion 232 of the jumper 230 is expanded, the engagement between the tooth portion 212a of the adjustment gear 211 and the flange portion 233 of the jumper 230 is released. As a result, the adjustment gear 211 rotates with respect to the support shaft 117.
Since the adjustment gear 211 is connected to the inner end 68b of the constant force spring 68, the amount of winding of the constant force spring 68 is adjusted by the rotation of the adjustment gear 211. When the amount of winding of the constant force spring 68 reaches a predetermined amount, the adjustment of the constant force spring adjustment mechanism 210 is completed.
Therefore, according to the second embodiment described above, the same effects as those of the first embodiment described above can be achieved.

The present invention is not limited to the above-described embodiment, and includes various modifications made to the above-described embodiment without departing from the spirit of the present invention.
For example, in the above-described embodiment, the case where the constant force spring adjusting mechanisms 110 and 210 are provided in the tourbillon 30 with the constant force device has been described. However, the present invention is not limited to this, and the constant force spring adjusting mechanisms 110 and 210 can be provided in various constant force devices (devices having constant force springs) incorporated in the train wheel.

  Further, in the above-described embodiment, the constant force spring adjusting mechanisms 110 and 210 include two gears of the adjustment gears 111 and 211 and the operation gear 123, respectively, and the two gears are rotated to wind up the constant force spring 68. The case of adjusting the amount has been described. However, the present invention is not limited to this, and the constant force spring adjustment mechanisms 110 and 210 may be configured by meshing a plurality of gears.

In this case, two or more operation gears 123 may be engaged with the adjustment gear 111 to which the inner end portion 68b of the constant force spring 68 is connected. By varying the number of teeth of the tooth portion 123a of each operation gear 123, for example, one operation gear 123 can be used for coarse adjustment, and the other operation gear 123 can be used for fine adjustment. That is, each operation gear 123 can be used properly according to the application.
In addition, a plurality of gears may be linked to the adjustment gear 111 in a line. By comprising in this way, the position of a gear can be changed flexibly according to the arrangement space of a constant force spring adjustment mechanism. For this reason, the design freedom of a constant force spring adjustment mechanism can be raised.

Furthermore, in the above-described first embodiment, the case where the adjustment gear 111 is provided with the spoke portions 113 and 114 (support shaft clamping portions 113a and 114a) as torque transmission portions has been described. Further, in the above-described second embodiment, the case where the adjustment gear 211 is provided with the jumper 230 as a torque transmission unit so as to be engageable and disengageable has been described.
However, the invention is not limited to these, and the spoke portions 113 and 114 (support shaft clamping portions 113a and 114a) may be provided on the operation gear 123 side, or the jumper 230 may be provided so as to be engaged and disengaged. Even in the case of such a configuration, the winding amount of the constant force spring can be adjusted.

  Further, when the constant force spring adjusting mechanisms 110 and 210 are configured by meshing a plurality of gears, at least one of the plurality of gears is connected to the support plate 120 with the spoke portions 113 and 114 (support shaft clamping portions 113a). 114a) or a jumper 230. Alternatively, it is only necessary that at least one of the plurality of gears is lightly press-fitted to a support shaft protruding from the support plate 120 and this light press-fitting functions as a torque transmission unit.

Furthermore, a plurality of operation levers or the like may be arranged instead of the adjustment gears 111 and 211 and the operation gear 123. Even in this case, by providing a plurality of operation levers, the movable range of one operation lever can be saved. For this reason, a constant force spring adjustment mechanism can be reduced in size.
In addition to the operation lever, for example, the amount of winding of the constant force spring 68 may be adjusted using a push screw or the like.

  Furthermore, in the above-described embodiment, the case where the outer end portion 68a of the constant force spring 68 is attached to the outer carriage 33 and the inner end portion 68b is attached to the constant force spring adjusting mechanisms 110 and 210 has been described. However, the present invention is not limited to this, and the inner end portion 68b of the constant force spring 68 is attached to the inner carriage 34, and the outer end portion 68a of the constant force spring 68 is attached to the constant force spring adjustment mechanisms 110 and 210. May be. In this case, the support plate 120 of the constant force spring adjusting mechanisms 110 and 210 is attached to the outer carriage 33 side.

  In the above-described embodiment, the case where the operation gear 123 is rotated using a finger or a tool has been described. However, the present invention is not limited to this, and a configuration for rotating the operation gear 123 may be separately provided. For example, the operation gear 123 may be provided with a protrusion or the like that engages with the tool and rotated.

DESCRIPTION OF SYMBOLS 1 ... Mechanical timepiece 3 ... Constant force apparatus 11 ... Base plate 28 ... Fifth wheel (wheel train)
33 ... Outer carriage (rotating body)
34 ... Inner carriage (rotating body)
68 ... Constant force spring 70 ... Stop wheel 96 ... Stopper 100 ... Escape speed control mechanism 101 ... escape wheel (escape speed control mechanism)
102 ... balance (escape control mechanism)
110, 210 ... constant force spring adjustment mechanisms 111, 211 ... adjustment gear (first operation unit)
113, 114 ... Spoke part (spring member, torque transmission part)
113a, 114a ... support shaft clamping portion 117 ... support shaft 117c ... second step portion (step portion)
118 ... Reverse taper part (taper part)
120 ... support plate (support part)
120b ... surface (one side)
123 ... Operation gear (operation unit)
123a ... Teeth (teeth)
230 ... Jumper (torque transmission part)

Constant-force device according to the present invention, a constant force spring adjusting mechanism described above, the outer carriage which is the rotating body, and an inner carriage is rotatably supported by the outer carriage, provided on the outer carriage And a stopper provided on the inner carriage and engageable with the stop wheel, and the support portion is provided on the inner carriage.

Claims (9)

A support part;
A plurality of operation units provided on one surface of the support unit and linked to each other;
Both ends are attached to one of the plurality of operation units, the first operation unit, the rotating body, and the first operation unit, and generates a spring force between the support unit and the rotating body. A constant force spring;
With
The first operation portion is provided so as to be operable in a winding direction and an unwinding direction of the constant force spring.
At least one of the plurality of operation units is provided on the support unit via a torque transmission unit,
The constant force spring adjusting mechanism, wherein the torque transmitting portion is actuated when receiving a force greater than a predetermined torque.   The constant force spring adjustment mechanism according to claim 1, wherein the operation unit is a gear.   The constant force spring adjustment mechanism according to claim 2, wherein the number of teeth of the operation unit other than the first operation unit is set to be smaller than the number of teeth of the first operation unit. The torque transmission portion is composed of two spring members that sandwich a support shaft erected on one surface of the support portion with a predetermined pressing force from outside in the radial direction.
The constant force spring adjusting mechanism according to any one of claims 1 to 3, wherein both end portions of the two spring members are fixed to the operation portion. A step portion for positioning the two spring members is formed at a position corresponding to the spring member of the support shaft, and a tapered portion is formed adjacent to the step portion,
The tapered portion is formed so as to gradually expand in diameter in a direction away from the stepped portion in the axial direction, and the movement of the two spring members in a direction away from the stepped portion in the axial direction is performed. The constant force spring adjusting mechanism according to claim 4, wherein the constant force spring adjusting mechanism is suppressed. The torque transmission part is a jumper having elasticity provided in the support part,
4. The constant force spring adjustment mechanism according to claim 2, wherein the jumper is detachably disposed on a tooth of the operation unit.   The part of the operation part arranged at the outermost side in the surface direction of the one surface of the support part protrudes outward in the surface direction of the one surface from the support part. The constant force spring adjusting mechanism according to claim 6. The constant force spring adjustment mechanism according to any one of claims 1 to 7,
An outer carriage as the rotating body;
An inner carriage rotatably supported with respect to the outer carriage;
A stop wheel provided on the inner carriage;
A stopper provided on the outer carriage and engageable with the stop wheel;
With
A constant force device comprising the inner carriage provided with the support portion. A constant force device according to claim 8,
The outer carriage is supported rotatably with respect to the main plate,
The inner carriage is provided with a escapement speed control mechanism,
A mechanical timepiece wherein a driving force of a train wheel is transmitted to the outer carriage.

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