JP2008096192A - Bearing mechanism for timepiece gear train, timepiece gear train structure, and timepiece equipped therewith - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing mechanism for a timepiece gear train capable of adjusting easily each inter-shaft distance between wheels constituting the timepiece gear train in response to a desire, and a timepiece equipped therewith. <P>SOLUTION: The bearing mechanism 1 for the timepiece gear train typically has the first bearing support lever A40 for supporting the third wheel A30 engaged with the first and second wheels between the first and second wheels A10, A20 among a series of three wheels constituting the timepiece gear train, and having the first tip side arm part with the first bearing supporting long hole on the tip side, and mounted turnably on a timepiece gear train support A6 on a middle part; the second bearing support lever A50 having the second tip side arm part equipped with the second bearing supporting long hole crossed and overlapped with the first bearing supporting long hole, and mounted rotatably on the timepiece gear train support A6 on the middle part; and a bearing part A31 fitted with the first and second bearing supporting long holes and supported at a crossing part J of the first and second bearing supporting long holes A45, A55. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a timepiece bearing mechanism, and more particularly to a timepiece wheel train bearing mechanism, a timepiece wheel train structure, and a timepiece having the same.

  A timepiece has a train wheel formed by a large number of wheels (gears, etc.) meshed with each other or sequentially. It is desirable that the distance between the cars constituting the train wheel be precisely defined so that the cars constituting the watch train wheel are small and can move with minimal power. However, due to tolerances when the timepiece parts are mass-produced, it may be difficult to manufacture the timepiece wheel train with an appropriate distance between the wheels. Further, even with a watch train wheel initially set to an appropriate state, rotation may become difficult to be transmitted smoothly due to wear of the tenon portion of the car due to long-term use of the watch.

  There has been proposed a timepiece in which the position of the bearing portion of one vehicle can be adjusted so that the distance between the two meshing vehicles can be adjusted (Patent Document 1).

  In the watch disclosed in Patent Document 1, the tenon of one of the two intermeshing wheels is supported by a bearing made of a hole stone (receiving stone) and a tenon frame in the form of an eccentric pin, and the eccentric pin is rotated. Thus, the position of the central axis of the stone is adjusted so that the distance between the vehicle supported by the bearing and one specific vehicle meshing with the vehicle can be adjusted.

  In the watch of this Patent Document 1, although the distance between the axles of the pair of cars can be adjusted, the rotation center of the car adjusted by the eccentric pin is displaced along a circle whose radius is the eccentric amount of the eccentric pin. The adjustment of the inter-axis distance is limited. That is, if the changeable amount of the center axis position of the vehicle is increased, it is difficult to avoid that the center axis position of the vehicle inevitably shifts laterally along the circle.

In the timepiece disclosed in Patent Document 1, the center of rotation of the vehicle adjusted by the eccentric pin is displaced along a circle whose radius is the amount of eccentricity of the eccentric pin, and thus is rotated around mutually different central axes. In the series of three cars, the position adjustment of the rotation center axis of the third car located between the first and second cars and meshing with the first and second cars cannot be practically performed. That is, by adjusting the position of the central axis of the third vehicle and adjusting the inter-axis distance between one of the first and second vehicles and the third vehicle according to the structure of Patent Document 1, According to the adjustment, the inter-axis distance between the other of the first and second cars and the third car also changes unambiguously. Accordingly, it is difficult to effectively transmit rotation between the first vehicle and the second vehicle via the third vehicle.
JP 2003-279670 A

  The present invention has been made in view of the above-described points, and a first object thereof is to provide a watch wheel train bearing mechanism and a timepiece that can easily adjust a distance between axles of a wheel constituting the watch train wheel as desired. An object is to provide a train wheel structure and a timepiece having the same.

  A second object of the present invention is a timepiece capable of effectively transmitting rotation between a series of three wheels rotated around mutually different rotation center axes in a time train including a plurality of vehicles. An object is to provide a wheel train bearing mechanism, a timepiece wheel train structure, and a timepiece including the same.

  In order to achieve the first object, the timepiece wheel train bearing mechanism of the present invention constitutes a timepiece wheel train, and is one of a series of two vehicles rotated around different rotation center axes. A bearing mechanism for a watch wheel train for rotatably supporting a car, having a first tip arm having a first bearing support slot on the tip side and attached to the watch train wheel support. A second tip having a first bearing support lever and a second bearing support slot extending in a direction intersecting the first bearing support slot and overlapping the first bearing support slot A second bearing support lever having a side arm portion on the distal end side and rotatably attached to the watch wheel train support body at an intermediate portion between the distal end and the proximal end; and the first and second bearings And a bearing portion for the one of the vehicles fitted and supported in the first and second bearing support slots at the intersection of the support slots.

  In the watch wheel train bearing mechanism according to the present invention, “the second tip arm having the second bearing support elongated hole is provided on the tip side, and the watch wheel train is provided at an intermediate portion between the tip and the base end. Since the second bearing support lever pivotally attached to the support body is provided and "the bearing portion for one vehicle is fitted and supported in the second bearing support slot", the first When the second bearing support lever is rotated with respect to the timepiece wheel train support body, the second tip side arm part of the second tip side arm part is rotated along with the turning of the second tip side arm part of the second bearing support lever. The one vehicle bearing portion fitted in the second bearing support elongated hole is displaced together with the second tip side arm portion. In the watch wheel train bearing mechanism of the present invention, “the first tip arm having a first bearing support elongated hole on the tip end side and attached to the watch train wheel support body” A bearing support lever "is provided, and one of the vehicle bearing portions is fitted and supported in the first and second bearing support slots at the intersection of the first and second bearing support slots. Therefore, when the bearing portion for one of the vehicles is displaced, the bearing portion extends in the extending direction of the first bearing support slot in the first tip side arm portion of the first bearing support lever. Will be displaced along. That is, in the timepiece wheel train bearing mechanism of the present invention, the first bearing support length of the first tip side arm portion of the first bearing support lever is obtained by rotating the second bearing support lever. It can be displaced along the extending direction of the hole. Therefore, by disposing the first bearing support lever so that the first bearing support slot faces the desired specific direction, the bearing can be displaced in the direction defined by the slot. As a result, the bearing, that is, the one bearing can be surely displaced by a desired distance in the intended direction. In other words, in the watch wheel train bearing mechanism of the present invention, the distance between the axes of a series of two cars constituting the watch train wheel is easily changed by a desired amount, and the engagement of the two cars is brought into an optimum state. The torque can be adjusted and the rotational force can be transmitted efficiently.

  In the above, the one bearing is used for supporting the first and second bearings so as to be slidable in the longitudinal direction with respect to each of the first and second bearing supporting slots. It is fitted in the long hole. The first bearing support slot typically extends linearly, but may be somewhat curved or serpentine if desired. The same applies to the second bearing support slot.

In the watch wheel train bearing mechanism of the present invention,
(1) Even if the one of the cars is located at the end of the clock train,
(2) The one vehicle is located between a first vehicle and a second vehicle among a series of three vehicles constituting a watch train wheel and rotating around mutually different rotation center axes. And the third vehicle meshing with the second vehicle, and the other vehicle of the series of two vehicles may be the first or second vehicle.

  In the former case (1), the first bearing support lever is typically fixed to the watch train wheel support. However, it may be movable.

  On the other hand, in the latter case (2), the first bearing support lever is typically configured to be movable with respect to the watch train wheel support. However, in the case where the extension direction of the first bearing support slot of the first bearing support lever is set in a predetermined direction in consideration of the tolerance that normally occurs for a series of three cars. The first bearing support lever may be fixed to the timepiece train wheel support.

  Below, the case of said (2) is mainly demonstrated.

  That is, in order to achieve the second object, the timepiece wheel train bearing mechanism of the present invention is “a series in which the one wheel is rotated around different rotation center axes constituting the timepiece wheel train. Among the three cars, a third car that is located between the first and second cars and meshes with the first and second cars, and the other of the series of two cars is the first car. The first bearing support lever is rotatably attached to the timepiece wheel train support body at an intermediate portion between the front end and the base end.

  In this case, as described above, by rotating the second bearing support lever, the bearing of the one vehicle, that is, the bearing of the third vehicle is moved to the first bearing support slot of the first bearing support lever. In addition to being able to be displaced along the extending direction of the first bearing support lever, by rotating the first bearing support lever, the third bearing of the second bearing support slot of the second bearing support lever It can be displaced along the extending direction. Accordingly, the bearing of the third car is placed at a desired position in the two-dimensional plane, that is, the bearing of the third car has an arbitrary rotation center axis relative to the rotation center axes of the first and second cars. It can be displaced away by a desired distance (where the inter-axis distance between the third car and each of the first and second cars is any desired magnitude). As a result, the relative position of the series of three cars can be adjusted to an inter-axis distance such that rotation transmission by the series of three cars can be efficiently performed. Therefore, the rotation transmission efficiency of the train wheel is lowered due to the variation of the parts when the parts are assembled in the movement, or the rotation transmission efficiency of the train wheel is lowered due to wear of the tenon part due to long-term use. Even in this case, it is possible to increase the rotation transmission efficiency to a desired level by adjusting the third car located in the middle of the three cars constituting the train wheel to an arbitrary position. In the above, the amount of rotation of the first and second bearing support levers is typically a minute amount.

  In the bearing mechanism for a watch wheel train of the present invention, for example, when the first and second cars are arranged at a right angle position or a relative position not greatly deviated from the right angle with respect to the third car, Specifically, the rotation center axis of the first bearing support lever is coaxial with the rotation center axis of the first vehicle.

  Similarly, in the watch wheel train bearing mechanism of the present invention, for example, the first and second cars are arranged at a right angle or a relative position not greatly deviated from the right angle with respect to the third car. In this case, typically, the rotation center axis of the second bearing support lever is coaxial with the rotation center axis of the second vehicle.

  In these cases, when the lever is rotated, the relative positional relationship between the center of the third vehicle and the first and second centers can always be visually recognized, so that the position adjustment can be easily performed.

  In the watch wheel train bearing mechanism of the present invention, for example, when the first and second cars are arranged at a relative position greatly deviated from a right angle with respect to the third car, The bearing support lever is rotated around the watch train wheel support so that the extending direction of the second bearing support slot is perpendicular to the direction connecting the rotation centers of the first and third vehicles. Mounted movably. The bearing support levers arranged to intersect in this way may be the first bearing support lever instead of the second bearing support lever. In any case, since the first and second bearing support levers can be arranged at right angles to each other in practice, it is easy to efficiently adjust the rotation center axis of the third vehicle in the two-dimensional plane. . That is, in this case, the rotation of the first or second bearing support lever is the adjustment of the inter-axis distance between the third vehicle and the second or first vehicle, respectively.

  In the bearing mechanism for a watch wheel train of the present invention, typically, the first bearing support lever has a rotation center axis of the first bearing support portion of the first bearing support lever on the base end side thereof. Is provided with a first rotation position adjustment mechanism for adjusting the rotation position around the.

  In this case, the amount of rotation of the first bearing support lever can be adjusted by operating the first rotation adjustment mechanism.

  In the watch wheel train bearing mechanism of the present invention, typically, the second bearing support lever has a rotation center axis of the second bearing support portion of the second bearing support lever on the base end side thereof. Is provided with a second rotation position adjustment mechanism for adjusting the rotation position around the.

  In this case, the amount of rotation of the first bearing support lever can be adjusted by operating the second rotation adjustment mechanism.

  In the timepiece wheel train bearing mechanism of the present invention, typically, the rotational position adjusting mechanism includes an eccentric pin.

  In this case, only by rotating the eccentric pin, the corresponding bearing support lever can be rotated, and the bearing can be translated along the longitudinal direction of the other bearing support lever.

  In the watch wheel train bearing mechanism of the present invention, typically, at least one of the first and second bearing support slots is opened at the tip of the corresponding bearing support lever. . In this case, assembly and disassembly of the bearing support lever and the bearing can be easily performed. In this case, typically, at least one of the first and second bearing support levers is a leaf spring that elastically sandwiches the bearing fitted in the bearing support slot. Thereby, the bearing can be supported with a minimum thickness.

  The timepiece wheel train structure according to the present invention preferably includes the bearing mechanism for the timepiece wheel train at both ends of the third vehicle. In this case, the shaft of the third wheel can be kept parallel to the shafts of the first and second wheels, and the transmission efficiency of rotation can be kept high. However, the timepiece wheel train bearing mechanism may be provided only at one end of the third wheel. In that case, in consideration of meshing between the third vehicle and another vehicle, it may be selected which end of the third vehicle is provided.

  In the watch train wheel structure of the present invention, the watch train wheel includes a series of four or more cars, and an intermediate car of at least two sets of three cars of the series of cars is the above-described car. Such a watch wheel train bearing mechanism may be provided.

  In that case, the inter-shaft distance between a plurality of sets of vehicles can be optimized, and the rotation transmission efficiency of the timepiece wheel train structure can be maximized.

  Therefore, the timepiece of the present invention includes the above-described watch wheel train bearing mechanism or the above-described watch train train structure.

  A preferred embodiment of the present invention will be described based on a preferred example shown in the accompanying drawings.

  First, a watch wheel train bearing mechanism 1 according to a preferred embodiment of the present invention will be described with reference to FIG.

  FIG. 1 is a plan view showing a part of a timepiece wheel train structure 2 including a bearing mechanism 1. The timepiece wheel train structure 2 is attached to a main body of a timepiece wheel train support body such as a main plate or a train wheel bridge. There is provided a lever support A6 that is fixed to the lever support A6. The lever support A6 forms a part of the timepiece wheel train support body by being fixed to the main plate or the train wheel bridge. The lever support A6 may be a part of a main plate or a train wheel bridge. The watch train wheel structure 2 includes a series of three wheels A10, A20, A30 supported by a watch train wheel support A7 including a lever support A6. Among these three cars A10, A20, A30, a third car A30 is arranged between the first and second cars A10, A20. Therefore, the third wheel A30 is meshed with the gear portion (not shown) of the first wheel A10 at its gear portion (not shown), and the second wheel 20 at its gear portion (not shown). Is engaged with a gear portion (not shown). Here, it is meshed with a gear part (not shown) of the third car A30 and a gear part (not shown) of the second car A20 meshed with a gear part (not shown) of the first car A10. The gear portion (not shown) of the third vehicle A30 may be the same gear portion or another concentric gear portion. When it is another gear part, typically two gear parts are comprised integrally. However, as long as the two gear portions are concentric, they may be slip-engaged with each other.

  The timepiece train wheel structure 2 includes tenon receivers A11, A21, and A31 as three bearings. The tenon receivers A11 and A21 rotatably support the thin shaft portions at the ends of the first and second vehicles A10 and A20, that is, the tenon portions A12 and A22. On the other hand, of the three tenon receivers A11, A21, A31, the third tenon receiver A31 is loosely fitted in the opening (not shown) of the watch wheel train support A6 and is the end of the third wheel 30. The thin shaft portion or tenon portion A32 of the shaft is rotatably supported.

  A cylindrical center pin A15 is fitted into the hole A14 of the lever support A6 concentrically with the first tenon receiver A11, and a cylindrical center pin A25 concentric with the second tenon receiver A21 is inserted into the hole A24. Is inserted. The center pins A15 and A25 protrude toward the front from the surface of FIG. Among them, the first center pin A15 is attached to the lever support A6 at the position AP1, and the second A25 is attached to the timepiece train wheel support A6 at the position AP2. Here, the positions of the tenon receivers A11 and A21 and the center pins A15 and A25 indicate the positions of the center axes AC1 and AC2.

  The tenon receiver A31 takes the form of a tenon receiving structure composed of a stone receiver A34 and a tenon frame A35, and the tenon frame A35 has a cylindrical portion A36 and a flange-shaped portion A37. The jewel A34 is fitted in the cylindrical portion A36 of the tenon frame A35.

  The timepiece train wheel structure 2 also includes fine rotation levers A40 and A50 as a pair of bearing support levers. Of the pair of levers A40 and A50, the first fine rotation lever A40 is elastically attached to the outer periphery of the cylindrical portion of the center pin A15 at the spring portion A42 of the attachment portion A41 so as to be rotatable around the center axis AC1. It has been. The first lever A40 has a distal arm portion A43 on the distal end side of the attachment portion A41, and a proximal arm portion A44 on the proximal end side of the attachment portion A41. In this example, the distal end side arm portion A43 and the proximal end side arm portion A44 form an angle α1 so that an eccentric pin A48 described later can be easily disposed. If there is an attachment area for the eccentric pin A48, the lever 40 may be linear.

  The front end side arm portion A43 is a fork-like arm portion having a slit or groove portion A45 as a long hole extending from the front end edge A43A to the circular outer peripheral portion A41A of the mounting portion A41 and a pair of elastic arm portions A46, A46 on both sides thereof. It is a form. In the groove portion A45 of the fork-shaped arm portion A43, a third tenon receiver A31 is fitted in the body portion A36 of the tenon frame A35 so as to be movable in the longitudinal direction B of the groove portion A45.

  Accordingly, when the fork-shaped arm portion A43 is rotated in the directions D1 and D2 around the rotation center axis AC1 of the first lever A40, the third tenon receiver A31 is in accordance with the fork-shaped arm portion A43 according to D1, D2. It is rotated in the D2 direction and is movable in the B1 and B2 directions along the longitudinal direction B of the groove portion A45 of the fork-shaped arm portion A43.

  The base end side arm portion A44 includes a concave portion A47 having a constant width and a depth similar to the width at the base end edge A44A. An eccentric head A49 of an eccentric pin A48 that is rotatably attached to the lever support A6 is fitted in the recess A47. Here, the eccentric pin A48 is formed with a cylindrical shaft portion (not shown) rotatably fitted in the cylindrical hole of the lever support A6, and formed in an eccentric state with respect to the cylindrical shaft portion. It consists of a large-diameter disk-shaped head, that is, an eccentric head A49. On the top surface of the eccentric head A49, a minus groove A49A in which the tip of a tool such as a minus driver can be engaged is formed. As long as the outer peripheral surface of the head A49 can function as a cam surface, the head A49 may have an elliptical shape or other noncircular shape instead of the eccentric circular shape.

  When the eccentric head A49 of the eccentric pin A48 is rotated in the directions E1 and E2 around the central axis E of the shaft portion (not shown) of the eccentric pin A48, the eccentric direction and the magnitude of the eccentricity of the eccentric head A49 Accordingly, the proximal arm A44 engaged with the eccentric head A49 in the proximal recess A47 is rotated in the D1 and D2 directions, and the distal arm A43 is also rotated in the D1 and D2 directions. Then, the third tenon receptacle A31 is moved.

  Of the pair of levers A40, A50, the second fine rotation lever A50 is a cylindrical body portion of the center pin A25 at the spring portion A52 of the attachment portion A51 so that it can rotate in the H1, H2 direction around the center axis AC2. Basically, it is configured in the same manner as the first lever A40 except that it is elastically attached to the outer periphery of the first lever A40.

  That is, the second lever A50 has a distal end side arm portion A53 on the distal end side of the attachment portion A51, and a proximal end side arm portion A54 on the proximal end side of the attachment portion A51. In this example, the distal arm portion A53 and the proximal arm portion A54 have an angle α2 opposite to that of the first lever A40 so that an eccentric pin A48 described later can be easily disposed. Eggplant. As long as there is a mounting area for the eccentric pin A58, the lever 50 may also be linear.

  The distal end side arm portion A53 is in the form of a fork-like arm portion having a groove portion A55 as a long hole and a pair of elastic arm portions A56, A56 on both sides thereof. In the groove portion A55 of the fork-shaped arm portion A53, a body portion A36 of a tenon frame A35 of the third tenon receptacle A31 is fitted so as to be movable in the F1 and F2 directions along the longitudinal direction F of the groove portion A55. Yes.

  That is, the body part A36 of the third tenon receiver A31 includes a front end side arm part A43 extending in the B direction of the first lever A40 and a front end side arm part A53 extending in the F direction of the second lever A50. Is positioned and supported at the intersection J of both arms A43 and A53.

  The base end side arm portion A54 includes a concave portion A57 having a constant width and a depth substantially equal to the width at the base end edge A54A. An eccentric head A59 of an eccentric pin A58 that is rotatably attached to the watch train wheel support A6 is fitted in the recess A57. The eccentric pin A58 has the same form as the eccentric pin A48, and a minus groove A59A is formed on the top surface of the eccentric head A59.

  Accordingly, when the eccentric head A59 of the eccentric pin A58 is rotated in the G1 and G2 directions around the central axis G of the eccentric pin A58, the proximal end is determined according to the eccentric direction and the magnitude of the eccentricity of the eccentric head A59. The proximal arm A54 engaged with the eccentric head A59 by the side recess A57 is rotated in the H1 and H2 directions around the rotation center axis AC2 of the second lever A50, and accordingly, the distal arm A43 is rotated. The third tenon receiver A31 engaged with the groove A55 of the first lever 40 is also rotated in the H1 and H2 directions around the rotation center axis AC2, and B1, B2 along the longitudinal direction B of the groove A45 of the first lever 40. It can move in the direction.

  In the watch wheel train bearing mechanism 1 configured as described above, for example, when the eccentric pin A48 for the first lever A40 is rotated in the E1 or E2 direction, the first lever A40 is rotated in the D1 or D2 direction. Moved. Accordingly, the third tenon receiver A31 is swung in the D1 or D2 direction in the same manner as the fork-shaped arm portion A43 of the first lever A40, and when swung in the D1 or D2 direction, On the other hand, it is displaced in the F1 or F2 direction along the extending direction F of the groove portion A55 of the second lever A50 which is actually kept stationary.

  In this example, since the fork-like arm portions A43 and A53 extend in a substantially perpendicular direction, the D1 and D2 directions (tangent directions thereof) actually coincide with the F1 and F2 directions. When the A40 rotates in the direction D1 or D2, the third mortise receiver A51 is maintained at a constant distance from the rotation center axis AC1 of the first car A10, and the rotation center of the second car A20 is maintained. It is separated from or close to the axis AC2.

  The same applies to the case where the second lever A50 is rotated by the eccentric pin A58. Thus, when the second lever A50 is rotated in the H1 or H2 direction, the third tenon receiver A51 and the second vehicle The distance from the rotation center axis AC2 of A20 is kept away from or close to the rotation center axis AC1 of the first vehicle 10 while being kept constant in practice.

  When the extending directions of the two levers A40, A50 are deviated from 90 degrees, the third tenon receiver A31 is not connected to the other lever A50, A40 regardless of which lever A40, A50 is rotated. Along the longitudinal directions F and B of the grooves A55 and A45, the rotation center axes AC2 and AC1 of the second or first wheels 20 and 10 are respectively close to or separated from each other. Therefore, broadly speaking, adjacent parallelograms are moved in order to move in a diagonal direction of a parallelogram (however, strictly speaking, each side consists of a circular arc, and the lengths of facing sides are slightly different). The two levers A40 and A50 are sequentially rotated by a desired angle so as to move the third tenon receptacle A51 in order along the two sides. Such an example will be described later in detail with reference to FIGS. Here, the distance to be adjusted is typically on the order of 0.01 mm. However, it may be larger or smaller.

  In the above description, an example in which the rotation center axes of the first and second levers A40 and A50 coincide with the rotation center axes AC1 and AC2 of the first and second wheels 10 and 20 has been described. One or both of the rotation center axes of the second levers A40 and A50 may be different from the rotation center axes AC1 and AC2 of the first and second wheels 10 and 20.

  That is, when the directions B and F (the imaginary lines extending in the direction) are substantially different from each other, the rotation center axis of at least one of the first and second levers is displaced from the rotation center axes of the first and second vehicles. You may arrange in the place.

  Next, the timepiece 3 according to a preferred embodiment of the present invention will be described in more detail with reference to FIGS.

  The timepiece 3 has a timepiece body 4 as shown in the plan view of FIG. 2 and the cross-sectional view of FIG. In the watch body 4, the first wheel or barrel complete 10, the second wheel or minute wheel 20, the third wheel 30, the fourth wheel or second wheel 40, the escape wheel 51 and the balance 52 are connected by an ankle 53. And a speed control escapement mechanism 50 and an hour wheel 58 (FIG. 3). The barrel wheel 12 of the barrel wheel 10 equipped with the mainspring 11 meshes with the second pinion 21 of the second wheel 20, the second gear 22 of the second wheel 20 meshes with the third pinion 31 of the third wheel 30, and three The third gear 32 of the number wheel 30 is engaged with the fourth pinion 41 of the fourth wheel 40, and the fourth gear 42 of the fourth wheel 40 is engaged with the escape pinion 54 of the escape wheel 51 of the speed control escapement mechanism 50. A watch wheel train structure 5 is formed. The hour wheel 58 is meshed with the center wheel & pinion 20 via a minute wheel (not shown).

  The cars constituting the watch train wheel structure 5 are rotatably or rotatably supported by a wheel train receiver such as a main plate 61 as a watch train wheel support body, a first receiver 62 and a second receiver 65, respectively. Yes. As can be seen from FIG. 2, the barrel wheel 10, the second wheel 20 and the hour wheel 58, the third wheel 30, the fourth wheel 40, the escape wheel 51 and the balance 52 have the center axes C1, C2, C3, C4 and C5, respectively. And rotatable around C6.

  A second kana true 24 is rotatably fitted in the shaft portion of the center wheel & pinion 20, that is, in the cylindrical second or second cylinder 23. The second pinion true 24 includes a second pinion 25 meshed with the third gear 32.

  More specifically, the center wheel & pinion 20 is fitted to the first receiver 62 at the tenon portion 26 on the front side (back cover side (hereinafter the same)) of the second kana true 24 coaxial with the second barrel 23. A central axis line is provided by a tenon support (stone receiving) 27 and a bearing or tenon support (receiving stone) 28 fitted to the base plate 61 in the second cylinder 23 extending to the back side (the dial side (hereinafter the same)). It is rotatably supported around C2. The fourth wheel 40 receives the tenon of the base plate 61 by a tenon receiver (stone) 45 of the first receiver 62 at the tenon portion 44 of the front end of the fourth stem 43 and at the tenon portion 46 of the rear end. A (stone) 47 is rotatably supported around the central axis C4. Similarly, the escape wheel 51 also has a ground plate at the tenon portion 55C on the back side by the tenon receiving (stone) 55B of the first receiving portion 62A in the tenon portion 55A on the front side of the escape gear 55 in which the hook 51 is formed. 61 is supported by a tenon receiver (stone) 55D so as to be rotatable around the central axis C5.

  The third wheel 30 has a central axis C3 by a tenon receiving structure 35 serving as a bearing at a tenon portion 34 at the front end of the third wheel 33 and a tenon receiving structure 37 serving as a bearing at a tenon portion 36 at the rear end. Is supported so that it can rotate freely.

  The tenon receiving structure 35 includes a tenon frame 35A and a receiving stone 35B. The tenon frame 35A has a cylindrical body portion 35C and a flange-like protrusion portion 35D at the end of the body portion 35C. 35E is a retaining ring. The receiving stone 35B is fitted into the hole of the cylindrical body portion 35C of the tenon frame 35A, and the tenon portion 34 of the third truer 33 is rotatably supported by the tenon hole. The tenon receiving structure 37 includes a tenon frame 37A and a receiving stone 37B, similarly to the tenon receiving structure 35. The tenon frame 37A has a cylindrical trunk portion 37C and a flange-like protrusion 37D at the end of the trunk portion 37C. 37E is a retaining ring. The receiving stone 37B is fitted into the hole of the cylindrical body portion 37C of the tenon frame 37A, and the tenon portion 36 of the third truer 33 is rotatably supported by the tenon hole.

  Openings 63 and 64 are formed in the first receptacle 62 and the base plate 61, and the cylindrical body portions 35C and 37C of the tenon frames 35A and 37A of the tenon receiving structures 35 and 37 respectively correspond to the corresponding openings 63 and 64 and freely displaceable within the openings 63 and 64 along the extending surfaces of the first support 62 and the base plate 61.

  Next, the bearing mechanism of the timepiece wheel train structure 5, that is, the bearing mechanism 6 for the timepiece wheel train will be described in detail based on the specific arrangement (FIG. 2) of the cars constituting the wheel train. The structure of the lever of the watch wheel train bearing mechanism 6 and the support structure thereof are the same as those shown in FIG. Therefore, in the following, except for the fact that the crossing angle of the two levers is different, the planar shape and structure of the lever and its supporting part can be understood from FIG. 1 and the above description based on this. Based on the premise, an example of the structure will be described mainly based on the sectional view of FIG.

  In the following, the lever supports 70A and 70B correspond to the lever support A6 in FIG. 1, the levers 80, 80A and 80B correspond to the lever A40 or A50 in FIG. 1, and the levers 90, 90A and 90B in FIG. Corresponds to lever A50 or A40. Further, the tenon receiving structures 35 and 37 correspond to the tenon receiver A31 of FIG.

  A plate-like front lever support 70A is fixed to the first receiver 62 with a set screw 71A and the like, and a plate-like back lever support 70B is similarly fixed to the base plate 61.

  The front lever support 70A includes an opening 72A having the same size at the same position as the opening 63 of the first receiver 62, and also includes circular holes 73A1 and 73A2 around the central axis C2 and in the vicinity of the central axis C4. Furthermore, holes 74A1 and 74A2 for pin presser bushings are provided.

  Similarly to the front lever support 70A, the back lever support 70B has an opening 72B of the same size at the same position as the opening 64 of the main plate 61, and also around the center axis C2 and in the vicinity of the center axis C4. Circular holes 73B1 and 73B2 are provided, and further, pin holding bush holes 74B1 and 74B2.

  The timepiece 3 has first and second bearing support levers 80A and 90A similar to the first and second bearing support levers A40 and A50 of FIG. 1 on the front side, and the first side of FIG. The first and second bearing support levers 80B and 90B are the same as the second bearing support levers A40 and A50. When the first and second bearing support levers 80A and 90A on the front side and the first and second bearing support levers 80B and 90B on the back side are mirror-symmetrical, and when the front side and the back side are not distinguished, or collectively The subscripts A and B are omitted, and expressed by 80 and 90. The same applies to each element of the levers 80 and 90.

  In the circular holes 73A1 and 73A2 of the front lever support 70A, there are center pins 75A1 and 75A2 that serve as rotation center shaft portions for rotatably supporting the first and second bearing support levers 80A and 90A on the front side, respectively. It is fitted with a large diameter body. The center pins 75A1 and 75A2 are in close contact with the back surface of the front lever support 70A at the flange-like portion in the fitted state. Similarly, in the circular holes 73B1 and 73B2 of the back side lever support body 70B, the center pins 75B1 serving as the rotation center shaft portions for rotatably supporting the first and second bearing support levers 80B and 90B on the back side, respectively. 75B2 is fitted in the large-diameter trunk. The center pins 75B1 and 75B2 are in close contact with the back surface (front side surface) of the back lever support 70B at the flange-like portion in the fitted state.

  Pin presser bushings 76A1 and 76A2 are fitted into the holes 74A1 and 74A2 of the front side lever support 70A, and pin presser bushings 76B1 and 76B2 are fitted into the holes 74B1 and 74B2 of the back side lever support 70B.

  The first bearing support lever 80A on the front side includes a bearing hole 81A serving as a fulcrum in the middle, and is fitted to the small diameter shaft portion of the center pin 75A1 in the bearing hole 81A. Therefore, the first bearing support lever 80A on the front side can be rotated around the central axis C2. The bearing support lever 80A includes arm portions 82A and 83A on both sides of the bearing hole 81A. The distal arm portion 82A has a fork shape, and is a slit or groove 84A as a long hole extending in the longitudinal direction from the distal edge, and a pair of elastic arm portions 85A and 85A (one not shown) on both sides thereof. Have The width of the slit or groove portion 84A matches or is slightly larger than the outer diameter of the body portion 35C of the tenon frame 35A, and is loosely fitted to the body portion 35C of the tenon frame 35A by the groove portion 84A. Accordingly, the tenon frame 35A is slidable along the longitudinal direction of the groove 84A of the first bearing support lever 80A on the front side.

  On the other hand, the base end side arm portion 83A includes a substantially square-shaped recess 86A at the base end edge. A front-side first lever rotation adjusting eccentric pin 87A for adjusting the rotation position of the front-side first bearing support lever 80A is attached to the bearing 76A1. The eccentric pin 87A has a cylindrical shaft portion 87A1 that is fitted to the pin presser bushing 76A1 so as to be slidable and rotatable, and a large-diameter disk-shaped head portion 87A2 that is eccentric with respect to the shaft portion 87A1. The outer diameter of the head 87A2 of the eccentric pin 87A is equal to or slightly smaller than the width of the proximal recess 86A of the proximal arm portion 83A of the first bearing support lever 80A on the front side, and the head of the eccentric pin 87A. The base end side arm portion 83A of the first bearing support lever 80A on the front side is loosely fitted to the portion 87A2 by a base end recess 86A.

  The second bearing support lever 90A on the front side is also configured in the same manner as the first bearing support lever 80A. That is, the second bearing support lever 90A on the front side is fitted to the small diameter shaft portion of the center pin 75A2 serving as the rotation center shaft portion in the bearing hole 91A located in the middle and serving as the fulcrum, and rotates around the center axis C4. It is possible to move. In detail, as illustrated in FIG. 3, the center axis of the center pin 75 </ b> A <b> 2 may be shifted from the rotation center axis C <b> 4 of the fourth wheel & pinion 40. In the following, for the sake of simplicity of explanation, it is assumed that the center axis of the center pin 75A2 coincides with the rotation center axis C4 of the fourth wheel & pinion 40. The bearing support lever 90A is provided with arm portions 92A and 93A on both sides of the bearing hole 91A on the front end side and the base end side. Or it has the groove part 94A and a pair of elastic arm parts 95A and 95A (one is not shown) of the both sides. The width of the groove portion 94A is the same as the width of the groove portion 84A of the first bearing support lever 80A, and the second bearing support lever 90A has its distal arm portion 92A at the distal arm portion of the first bearing support lever 80A. The groove portion 94A is loosely fitted to the body portion 35C of the tenon frame 35A of the tenon receiving structure 35 so as to overlap with 82A in an intersecting state. The tenon frame 35A of the tenon receiving structure 35 is slidable along the longitudinal direction of the groove 94A of the second bearing support lever 90A on the front side. Here, the distal end side arm portions 82A and 92A of the levers 80A and 90A are slidably overlapped with each other between the flange portion 35D and the retaining ring 35E of the tenon frame 35A.

  The proximal arm 93A includes a substantially square recess 96A at the proximal edge. A front-side second lever rotation adjusting eccentric pin 97A for adjusting the rotation position of the front-side second bearing support lever 90A is attached to the pin presser bushing 76A2. The eccentric pin 97A has a cylindrical shaft portion 97A1 that is fitted to the pin presser bushing 76A2 so as to be slidable and rotatable, and a large-diameter disk-shaped head portion 97A2 that is eccentric with respect to the shaft portion 97A1. The outer diameter of the head portion 97A2 of the eccentric pin 97A is equal to or slightly smaller than the width of the proximal recess portion 96A of the proximal end arm portion 93A of the second bearing support lever 90A on the front side, and the head of the eccentric pin 97A. The base end side arm portion 93A of the second bearing support lever 90A on the front side is loosely fitted to the portion 97A2 by a base end recess 96A.

  The back side first bearing support lever 80B is attached to the back side lever support body 70B in a mirror-symmetrical state with the front side first bearing support lever 80A.

  That is, the first bearing support lever 80B on the back side is fitted to the small diameter shaft portion of the center pin 75B1 serving as the rotation center shaft portion in the bearing hole 81B serving as the fulcrum located in the middle, and rotates around the center axis C2. It is possible to move. The bearing support lever 80B includes arm portions 82B and 83B on both sides of the bearing hole 81B. The distal end side arm portion 82B has a fork shape, and has a slit or groove portion 84B as a long hole extending in the longitudinal direction from the distal end edge, and a pair of elastic arm portions 85B and 85B (one is not shown). The width of the groove portion 84B is equal to or slightly larger than the outer diameter of the body portion 37C of the tenon frame 37A of the tenon receiving structure 37, and the groove portion 84B is free to play in the body portion 37C of the tenon frame 37A of the tenon receiving structure 37. It is fitted. Therefore, the tenon frame 37A of the tenon receiving structure 37 can slide along the longitudinal direction of the groove 84B of the first bearing support lever 80B on the back side.

  On the other hand, the base end side arm part 83B includes a substantially square-shaped recess 86B at the base end edge. A back-side first lever rotation adjustment eccentric pin 87B for adjusting the rotation position of the back-side first bearing support lever 80B is mounted on the pin presser bushing 76B1. The eccentric pin 87B has a cylindrical shaft portion 87B1 fitted to the pin presser bushing 76B1 so as to be slidable and rotatable, and a large-diameter disk-shaped head portion 87B2 which is eccentric with respect to the shaft portion 87B1. The outer diameter of the head 87B2 of the eccentric pin 87B is equal to or slightly smaller than the width of the proximal recess 86B of the proximal arm portion 83B of the first bearing support lever 80B on the back side, and the head of the eccentric pin 87B. The base end side arm portion 83B of the first bearing support lever 80B on the back side is loosely fitted to the portion 87B2 at the base end concave portion 86B.

  The second bearing support lever 90B on the back side is also configured in the same manner as the first bearing support lever 80B. That is, the second bearing support lever 90B on the back side is fitted to the small diameter shaft portion of the center pin 75B2 that is the rotation center shaft portion in the bearing hole 91B that is located in the middle and serves as a fulcrum, and rotates around the center axis C4. It is possible to move. In detail, as illustrated in FIG. 3, the center axis of the center pin 75B2 may be shifted from the rotation center axis C4 of the fourth wheel & pinion 40, but here, as described above, the explanation is simplified. Therefore, description will be made assuming that the center axis of the center pin 75B2 coincides with the rotation center axis C4 of the fourth wheel & pinion 40. The bearing support lever 90B includes distal and proximal arm portions 92B and 93B on both sides of the bearing hole 91B. The fork-shaped distal arm portion 92B is a slit as a long hole extending in the longitudinal direction from the distal edge. Or it has a groove part 94B and a pair of elastic arm parts 95B and 95B (one is not shown). The width of the groove portion 94B is the same as the width of the groove portion 84B of the first bearing support lever 80B. The second bearing support lever 90B has a distal arm portion 92B having a distal arm portion of the first bearing support lever 80B. The groove portion 94B is loosely fitted to the trunk portion 37C of the tenon frame 37A of the tenon receiving structure 37 so as to overlap with 82B in an intersecting state. The tenon frame 37A of the tenon receiving structure 37 is slidable along the longitudinal direction of the groove 94B of the second bearing support lever 90B on the back side. Here, the distal side arm portions 82B and 92B of the levers 80B and 90B overlap with each other between the flange portion 37D of the tenon frame 37A and the retaining ring 37E so as to be slidable with each other.

  The proximal end arm portion 93B includes a substantially square recess 96B at the proximal end edge. A back-side second lever rotation adjusting eccentric pin 97B for adjusting the rotation position of the back-side second bearing support lever 90B is attached to the pin presser bushing 76B2 as a bearing. The eccentric pin 97B has a cylindrical shaft portion 97B1 fitted to the pin presser bushing 76B2 so as to be slidable and rotatable, and a large-diameter disk-shaped head portion 97B2 which is eccentric with respect to the shaft portion 97B1. The outer diameter of the head portion 97B2 of the eccentric pin 97B is equal to or slightly smaller than the width of the proximal recess portion 96B of the proximal arm portion 93B of the second bearing support lever 90B on the back side, and the head of the eccentric pin 97B. The base end side arm portion 93B of the second bearing support lever 90B on the back side is loosely fitted to the portion 97B2 at the base end concave portion 96B.

  In the timepiece wheel train bearing mechanism 6 of the train wheel structure 5 of the main body 4 of the timepiece 3 configured as described above, the first bearing support lever 80 is moved along the rotation center axis C2 by rotating the eccentric pin 87. By rotating around, the bearing structures 35 and 37 can be moved along the groove 94 in the longitudinal direction of the second bearing support lever 90, and by rotating the eccentric pin 97, the second bearing support lever The bearing structure 35, 37 can be moved along the groove 84 in the longitudinal direction of the first bearing support lever 80 by rotating 90 around the rotation center axis C4. Therefore, by turning the eccentric pins 87 and 97, the levers 80 and 90 can be rotated, and the bearing structures 35 and 37 of the third wheel & pinion 30 can be adjusted to arbitrary positions in the two-dimensional plane.

  Accordingly, in the watch train wheel bearing mechanism 6 of the train wheel structure 5 of the main body 4 of the watch 3, there is an error that cannot be ignored or the wear of the tenon portion or the like proceeds due to use, and the second wheel 20 to the third wheel 30. Even if it is difficult to effectively transmit rotation or rotational force in the reverse direction or to the fourth wheel 40 via the center wheel C3, the center axis C3 and the center of the second wheel 20 and the fourth wheel 40 are connected to the third wheel 30. The distance between the axes C2 and C4 can be adjusted so that both are appropriately sized, and the rotation or rotation from the second wheel 20 to the fourth wheel 40 through the third wheel 30 or in the opposite direction. It can be adjusted to a state where force transmission can be performed effectively.

  In the watch train wheel bearing mechanism 6 of the train wheel structure 5 of the main body 4 of the watch 3 shown in FIG. 3, the levers 80 and 90 include front levers 80A and 90A and back levers 80B and 90B, respectively. Typically, the position adjustment of the front bearing structure 35 that supports the tenon 34 on the front side of the third wheel 30 and the position adjustment of the rear bearing structure 37 that supports the tenon 36 on the back side of the third wheel 30 are alternately performed. Preferably it is done. However, if desired, for example, after one position adjustment is performed a plurality of times, the other position adjustment may be performed a plurality of times.

  Of course, if desired, instead of providing the levers 80 and 90 on both the front side and the back side, the lever may be provided only on one side.

  The first bearing support levers 80A and 80B on the front side and the back side have two centers so that the distance L2 between the rotation center axis C2 of the second wheel 20 and the rotation center axis C3 of the third wheel 30 can be adjusted. It extends in the direction connecting the axes C2 and C3. Therefore, this bearing support lever 80 is schematically represented by a straight line 80 in FIG. On the other hand, the second bearing support levers 90A and 90B on the front side and the back side are arranged so that the distance L4 between the rotation center axis C4 of the fourth wheel 40 and the rotation center axis C3 of the third wheel 30 can be adjusted. It extends in a direction connecting the two central axes C4 and C3. Therefore, this bearing support lever 90 is schematically represented by a straight line 90 in FIG. In FIG. 4B, for ease of viewing, the distal arm portions 82 and 92 of the first and second levers 80 and 90 are indicated by solid lines, and the proximal arm portions 83 and 93 are shown. Is shown with imaginary lines.

  In FIG. 4B, three circles Q21, Q22, and Q23 centered on the center axis C2 of the center wheel & pinion 20 have tolerances and the like when the center of the center wheel & pinion 20 is at the position of the center axis C2. In consideration, the circle with the radius of the minimum inter-axis distance R21, the circle with the radius R22 being the reference inter-axis distance, and the maximum axis between the third wheel 30 and the second wheel 20 may be properly engaged. A circle whose radius is the distance R23 is shown. Similarly, the three circles Q41, Q42, and Q43 centered on the central axis C4 of the fourth wheel 40 are three in consideration of tolerances when the center of the fourth wheel 40 is at the position of the central axis C4. A circle whose radius is a minimum inter-axis distance R41, a circle whose radius is a reference inter-axis distance R42, and a maximum inter-axis distance R43 which is likely to be in an appropriate meshing state with the fourth wheel 40. Indicates the circle to be. In consideration of various tolerances, strictly speaking, certain circles Q21, Q23, Q41, Q43, etc. are not generally determined for the same type of timepiece, but a specific train wheel structure composed of specific parts. It only applies to the specific clock in 5.

  FIG. 4A shows an enlarged view of the intersection region of the circles Q21, Q22, Q23 and the circles Q41, Q42, Q43. The rotation center axis C3 of the third wheel & pinion 30 is surrounded by the arcs P21 and P23 of the circles Q21 and Q23 and the arcs P41 and P43 of the circles Q41 and Q43 defined by the intersections of the circles Q21 and Q23 and the circles Q41 and Q43. Position adjustment should be performed within the area S (the area hatched in FIG. 4A).

  For example, when the center axis C3 of the third wheel & pinion 30 is at a position T1 (initial position or current position) in the region S in FIG. 4A, the bearing support lever 80 is rotated around the center axis C2. Then, the bearing structures 35, 37 of the third wheel & pinion 30 are rotated by the tip side arm portion 82 of the lever 80, and the extending direction of the lever 90, that is, the extending direction of the elongated hole (groove) 94 of the lever 90. Displaced along U90. On the other hand, when the center axis C3 of the third wheel & pinion 30 is at the position T1, when the bearing support lever 90 is rotated around the center axis C4, the bearing structures 35 and 37 of the third wheel & pinion 30 are moved to the lever 90. It is displaced along the extending direction of the lever 80, that is, along the extending direction U 80 of the elongated hole (groove) 84 of the lever 80 while being rotated by the distal end side arm portion 92.

  Therefore, for example, when moving the center C3 of the third wheel & pinion 30, that is, the center C3 of the bearing structures 35 and 37, from the initial position T1 in the region S to the target position T2, the above operation is performed a plurality of times. Repeatedly, typically, the bearing structures 35 and 37 of the third wheel & pinion 30 are moved in the region S along the zigzag path. In this watch wheel train bearing mechanism 6, the central axis C3 of the third wheel & pinion 30 can be moved in two directions intersected by the levers 80 and 90. Therefore, the third wheel & pinion 30 can be moved to any desired region in the region S. The position of the third wheel & pinion 30 can be adjusted such that the center axis C <b> 3 is moved and the meshing relationship between the second wheel 20, the third wheel 30 and the fourth wheel 40 configuring the wheel train 5 is optimized.

  Here, for example, when the watch 3 is a watch that has been used for a long time, the stability or variation of the rate obtained by observing the daily rate of the watch body 4 at the current position T1, and the related tenon of the car The target position T2 is determined according to the degree of wear or the like confirmed by the observation. It should be noted that a change in the stability of the rate when the center axis C3 is moved from the position T1 to another desired position on a trial basis is observed as a kind of sensitivity analysis, and is used as a reference to determine the moving direction, distance, or target. The position may be determined.

  4A, for example, in the timepiece 3 that has been used for a long time, the tenon portion of each of the cars 20, 30, 40 is worn, and the tenon portion of the fourth wheel 40 is more than the tenon portion of the second wheel 20. In the situation where the vehicle is more worn away, the vehicle is closer to both the cars 20 and 40 and closer to the fourth wheel 40 than to the second wheel 20. In this example, the train wheel bearing mechanism 6 is adjusted so that the center of the wheel 30 is moved from the position T1 to the target position T2.

  Depending on the situation of tolerance, there may be a meshing state that hinders the movement of the central axis C3 of the third wheel 30 in the region S. If the load for position adjustment is excessively high, the route should be Change it. Of course, trying to displace the central axis C3 of the third wheel & pinion 30 in a direction that makes position adjustment difficult is naturally likely to be in a direction opposite to the direction that should be adjusted. The target position itself to be adjusted may be changed with reference to this information.

  The rotation center axis of the bearing support levers 80, 90 is a vehicle (second wheel and fourth wheel in this example) meshing with a vehicle (third wheel in this example) 30 whose position is to be adjusted. ) It may be in a position different from the rotation center axes C2 and C4 of 20,40. For example, in the example shown in FIGS. 2 to 4, the second wheel 20, the third wheel 30, and the fourth wheel 40 are in a relative position close to a straight line, and the center C <b> 2 of the second wheel 20 and the third wheel 30 are Since the angle formed by the line connecting the center C3 and the line connecting the center C3 of the third wheel 30 and the center C4 of the fourth wheel 40 is a relatively large obtuse angle, as shown in FIG. Compared with the case where the levers A40 and A50 extend in a substantially right angle, the position adjustment by the bearing support levers 80 and 90 takes time.

  Therefore, for example, as shown in FIG. 5A, the lever 90W disposed at the position indicated by the imaginary line 90W as two levers supporting the bearing structures 35 and 37 (FIG. 3) of the third wheel 30. Is used in place of the lever 90 and combined with the lever 80 between the central axes C2 and C3 to form the watch wheel train bearing mechanism 6W, the lever 80Y disposed at the position indicated by the imaginary line 90Y is the lever 80 Alternatively, the watch wheel train bearing mechanism 6Y may be formed in combination with the lever 90 between the central axes C3 and C4. Here, the lever 90 </ b> W can be rotated around the fulcrum WC <b> 4 and is rotated in the vicinity of a state that is actually orthogonal to the lever 80. Note that the shape and structure of the lever 90W, the structure of the supporting portion thereof, and the like may all be the same as those of the lever 90 described above. Similarly, the lever 80 </ b> Y is rotatable around the fulcrum YC <b> 2 and is rotated in the vicinity of a state that is substantially orthogonal to the lever 90. It should be noted that the shape and structure of the lever 80Y and the structure of the supporting portion thereof may all be the same as those for the lever 80 described above.

  Further, when it is desired to take the same state for the two cars 20 and 40, the levers 180 and 190 disposed at the positions shown in FIG. The watch wheel train bearing mechanism 106 may be used. Here, the structures of the levers 180 and 190 are, for example, the same as the structures of the levers 80 and 90, respectively, and the respective rotation center axes corresponding to the rotation center axes C2 and C4 of the levers 80 and 90 are denoted by reference numerals. It is in a position indicated by 1C2 and 1C4. In this case, since the levers 180 and 190 are oriented substantially perpendicular to each other, the bearing structure of the third wheel 30 is displaced in the longitudinal direction of the other levers 190 and 180 by the rotation of the levers 180 and 190. Easy to do. In addition, since each lever 180, 190 has an angle sufficiently shifted from 0 degree or 180 degrees with respect to the direction connecting each car 20, 40 and the third wheel 30, the central axis C3 of the third wheel 30 is The amount of movement in the direction to be adjusted can be increased.

  In the above description, an example in which only the position of one vehicle 30 among a large number of vehicles constituting the train wheel is adjusted has been described. If desired, for example, in the train wheel shown in FIG. For example, in order to adjust not only the position of the central axis C3 of the 30th but also the position of the central axis C4 of the fourth wheel & pinion 40, another pair of levers similar to the levers 80 and 90 is provided. The inter-axis distance with respect to the number wheel 30 and the escape wheel 51 may be adjusted, and thereby the meshing state between the fourth wheel 40, the third wheel 30 and the escape wheel 51 may be adjusted.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an explanatory plan view showing a train wheel of a main body of a watch according to a preferred embodiment of the present invention to which a bearing mechanism for a watch train wheel according to a preferred embodiment of the present invention is applied. III-III sectional view explanatory drawing of the timepiece main body of FIG. FIG. 3 is an enlarged view of a part of the train wheel of FIG. 2, and (a) is an enlarged plan view showing an enlarged part of (b) in order to explain the adjustment of the center axis position of the third wheel & pinion. FIG. 4B is an explanatory plan view showing the second wheel, the third wheel and the fourth wheel in an enlarged manner. The arrangement of the bearing mechanism for the watch wheel train of the modified example is schematically shown. (A) is an explanatory plan view of an example in which two levers are actually orthogonal to each other. (B) Plane explanatory drawing of the example which took the angle which shifted | deviated sufficiently from 0 degree | times or 180 degree | times.

Explanation of symbols

1, 6, 6W, 6Y, 106 Clock train wheel bearing mechanism 2, 5 Clock train wheel structure 3 Clock 4 Clock body 10 First car (barrel car)
11 Mainspring 12 Incense box gear 20 Second wheel (minute wheel)
21 Kana 22 Second gear 23 Second 24 seconds Kana 25 seconds 26 Mortise 27, 28
30 Third wheel 31 Third wheel 32 Third gear 33 Third gear 34, 36 Tenon portion 35, 37 Tenon receiving structure 35A, 37A Tenon frame 35B, 37B Stone 35C, 37C Cylindrical body 35D, 37D Flange shape Protrusion 40 Fourth wheel (second wheel)
41 4th Kana 42 4th Gear 43 4th Truth 44, 46 Mortise 45, 47 Mortise (Stone)
50 speed control escapement mechanism 51 escape wheel 52 balance 53 ankle 54 escape gear 55 escape gear 55A, 55C mortise 55B, 55D mortise receiving (stone)
58 hour wheel
61 Ground plate 62 First ring (ring train holder)
63, 64 Opening 65 Second receiver (ring train receiver)
70A Front lever support body 70B Rear lever support bodies 72A, 72B Openings 73A1, 73A2, 73B1, 73B2 Circular holes 74A1, 74A2, 74B1, 74B2 Pin holding bush holes 75A1, 75A2, 75B1, 75B2 Center pins 76A1, 76A2, 76B1 76B2 Pin holding bushes 80, 80A, 80B First bearing support levers 81A, 81B, 91A, 91B Bearing holes 82, 82A, 82B, 92, 92A, 92B Tip side arm portions 83, 83A, 83B, 93, 93A, 93B Proximal arm part 84A, 84B, 94A, 94B Groove part (long hole)
85A, 85B, 95A, 95B Elastic arm portions 86A, 86B, 96A, 96B Recesses 87, 87A, 87B, 97A, 97B Lever rotation adjustment eccentric pins 87A1, 87B1, 97A1, 97B1 Cylindrical shaft portions 87A2, 87B2, 97A2, 97B2 Large-diameter disk-shaped head (eccentric head)
90, 90A, 90B Second bearing support lever A6 Lever support A7 Clock train wheel support A10 First car A11 First tenon receiver A12, A22, A32 Tenon part A15, A25 Center pin A20 Second car A21 Second tenon receiver A30 Third car A31 Third tenon receiver A34 Receiving stone A35 Tenon frame A36 Cylindrical shaft (body)
A37 Flange-shaped part A33 Third mortise trunk A40 First lever A41, A51 Mounting part A42, A52 Spring part A43, A53 Tip side arm part (fork-like arm part)
A43A Front edge A44, A54 Base end side arm A44A, A54A Base end edge A45, A55 Groove A46, A56 Elastic arm A47, A57 Recess A48, A58 Eccentric pin A49, A59 Eccentric pin eccentric head A50 Second lever AC1, AC2 lever rotation center axis AP1, AP2, AP3 Tenon receiving position B, F Longitudinal direction B1, B2, F1, F2 Movement direction C1, C2, C3, C4, C5, C6 Ship D1, D2, H1, H2 Lever rotation direction E1, E2, G1, G2 Eccentric pin rotation direction J Intersection of tip side arm of pair of levers S Position adjustable region T1 Initial position (current position)
T2 target position

Claims (12)

A watch wheel train bearing mechanism that constitutes a watch train wheel and rotatably supports one of a series of two vehicles that rotate around different rotation center axes,
A first bearing support lever having a first distal arm provided with a first bearing support slot on the distal end side and attached to the watch train wheel support;
A second distal arm having a second bearing support slot extending in a direction intersecting the first bearing support slot and overlapping the first bearing support slot is provided on the distal end side. A second bearing support lever pivotally attached to the watch train wheel support at an intermediate portion between the distal end and the proximal end;
For a watch wheel train having a bearing portion for one of the vehicles fitted and supported in the first and second bearing support slots at the intersection of the first and second bearing support slots. Bearing mechanism.   The one car is located between the first and second cars of a series of three cars that constitute a watch train wheel and rotate around mutually different rotation center axes. 2. The watch wheel train bearing mechanism according to claim 1, wherein the second wheel is the first wheel or the second wheel of the series of two wheels.   3. The timepiece wheel train bearing mechanism according to claim 2, wherein the first bearing support lever is rotatably attached to the timepiece wheel train support body at an intermediate portion between the front end and the base end.   4. The timepiece wheel train bearing mechanism according to claim 3, wherein a rotation center axis of the first bearing support lever is coaxial with a rotation center axis of the first vehicle.   The bearing mechanism for a watch wheel train according to claim 3 or 4, wherein a rotation center axis of the second bearing support lever is coaxial with a rotation center axis of the second vehicle.   The second bearing support lever is configured such that the extending direction of the second bearing support slot is perpendicular to the direction connecting the rotation centers of the first and third vehicles. The timepiece wheel train bearing mechanism according to claim 3 or 4, which is rotatably attached to the support body.   A first rotation position at which the first bearing support lever adjusts a rotation position of the first bearing support lever about the rotation center axis of the first bearing support portion on the base end side. The timepiece wheel train bearing mechanism according to any one of claims 3 to 6, further comprising an adjustment mechanism.   A second rotation position at which the second bearing support lever adjusts a rotation position of the second bearing support lever around the rotation center axis of the second bearing support portion on the base end side. The bearing mechanism for a watch wheel train according to any one of claims 2 to 7, further comprising an adjusting mechanism.   The timepiece wheel train bearing mechanism according to claim 7 or 8, wherein the rotation position adjusting mechanism includes an eccentric pin.   A timepiece wheel train structure comprising the watch wheel train bearing mechanism according to any one of claims 2 to 9 at one end or both ends of a third wheel.   10. The timepiece wheel train includes a series of four or more cars, and an intermediate car of at least two of the series of three cars of the series of cars according to any one of claims 2 to 9. A watch wheel train structure having a bearing mechanism for a watch train wheel.   A timepiece comprising the timepiece wheel train bearing mechanism according to any one of claims 1 to 9, or the timepiece wheel train structure according to claim 10 or 11.

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