JP5891019B2 - Watch bearing unit, movement and watch - Google Patents

Description

  The present invention relates to a timepiece bearing unit, a movement, and a timepiece.

  Conventionally, rotating mechanical parts such as gears used in timepieces are provided with bearings so as to include the end of the rotating shaft, and the rotating shaft is guided by the bearings to rotate and transmit torque, thereby transferring the time. It is configured to engrave.

Here, as a configuration of a conventional watch bearing, a configuration shown in FIG. 24 is known. In addition, FIG. 24 shows the cross section of the balance with a balance.
As shown in FIG. 24, the balance with hairspring 520 is rotatable around the central axis C at the small-diameter shaft portions 521 and 522 at both ends by a watch bearing 510 formed on the balance 505 and the main plate 504 along the central axis C. A supporting stem 523, an annular rim portion 524 forming a balance wheel body, and an arm portion 525 connected to both ends of the rim portion 524 and extending in the diameter direction of the rim portion 524 are provided, and an intermediate portion 526 of the arm portion 525 is provided. And a whistle ball 550 fixed to the central shaft portion 527 of the balance stem 523, and a swing seat 554 holding a swing stone 552.

  The watch bearing 510 is arranged in an outer bearing frame 512 held by the inner peripheral surface of the balance 505, an inner bearing frame 511 disposed in the outer bearing frame 512, and an inner diameter recess of the inner bearing frame 511. The hole 514 provided as a journal bearing for the small-diameter shaft portion 522 at the upper end of the balance stem 523 and the large-diameter recess portion of the inner bearing frame 511 and serving as a thrust bearing for the small-diameter shaft portion 522 of the balance stem 523 A stone 515 and a presser spring 516 that is locked in the groove of the outer bearing frame 512 and holds the receiving stone 515 in the large-diameter recess of the inner bearing frame 511.

  By the way, in the conventional watch bearing 510 described above, in order to allow the rotation of the shaft, there is a gap between the shaft body (small diameter shaft portion 522) and the bearing (receiving stone 515, hole stone 514). is necessary. Agaki is a gap provided in the thrust direction (between the small-diameter shaft portion 522 and the stone 515), and play is a gap provided in the radial direction (between the small-diameter shaft portion 522 and the hole stone 514). It is. Due to the presence of the post and backlash, the position of the shaft fluctuates when the position of the watch changes or when an impact is applied. Then, the torque transmitted from the barrel to the balance is changed, and the swing angle and the rate are changed. As a result, there is a problem that the timekeeping accuracy of the watch deteriorates.

  Then, the structure which employ | adopts a ball bearing as a timepiece bearing is examined. The ball bearing has a shaft and an outer ring having a rolling surface of a sphere, and a plurality of spheres arranged along the circumferential direction between the shaft and the outer ring (see, for example, Non-Patent Document 1). With the above-described configuration, the shaft body is rotatably supported.

Itomori, Hajimu, “Miniature Ball Bearing”, p. 7-13, (1961), Nikkan Kogyo Shimbun

  By the way, in the ball bearing mentioned above, it is necessary to hold | maintain between each sphere at the fixed pitch distance (distance between the spheres in the circumferential direction of an inner and outer ring). If the distance between the pitches of each sphere is different, when the shaft is in rotational contact with the bearing, the variation in bearing loss due to pitch deviation increases, and the variation in torque and rotation cycle of the shaft increases. Will get worse.

Therefore, in general ball bearings, a configuration is known in which a cage is provided between the inner and outer rings in order to hold each sphere in a state of being arranged at equal intervals.
In general ball bearings, a gap is provided between each sphere and the cage so that each sphere can roll. Since the aforementioned gap is sufficiently small with respect to the rolling diameter of each spherical body, the inclination of the central axis of the cage with respect to the longitudinal direction of the central axis of the shaft body or the outer ring is kept small, and the behavior of the cage is stabilized.
However, in a relatively small timepiece, the ball bearing incorporated in the timepiece is also very small, and the rolling diameter of the sphere is small. Further, when there is no inner ring and a spherical rolling surface is formed on the shaft instead of the inner ring, the spherical rolling surface may be further reduced. In other words, the amount of clearance between each sphere and the cage is approximately the same as the conventional one in terms of processing accuracy, but the rolling diameter of each sphere is very small. Therefore, the inclination of the longitudinal direction of the central axis of the cage with respect to the longitudinal direction of the central axis of the shaft body or the outer ring is increased, the attitude of the cage is changed, and the behavior during rotation becomes unstable. Therefore, the pitch-to-pitch distance of each sphere changes or the cage strongly collides with the shaft and outer ring. Therefore, the resistance in the ball bearing increases and varies, and the energy provided to the rotating shaft and the torque transmitted by the rotating shaft vary.
When the above-described ball bearing is used as a watch bearing, fluctuations in torque in the power, the train wheel and the escapement, and fluctuations in the rotation cycle in the governor increase. Therefore, there is a problem that the timekeeping accuracy of the watch deteriorates.

  Therefore, the present invention has been made in view of the above circumstances, and it is possible to improve the timing accuracy by reducing the longitudinal inclination of the central axis of the cage with respect to the longitudinal direction of the central axis of the shaft body or outer ring. The present invention provides a timepiece bearing unit, a movement, and a timepiece that can be realized.

The present invention provides the following means in order to solve the above-described problems.
A timepiece bearing unit according to the present invention is a timepiece bearing unit including a shaft body that rotates about a shaft center and a bearing that rotatably supports the shaft body, and the bearing contacts the outer peripheral surface of the shaft body. Along the outer peripheral surface of the shaft body between the shaft body and the outer ring, at least three or more sphere bodies arranged along the circumferential direction of the shaft body, the outer ring holding the sphere between the shaft bodies, And a cage that encloses the spheres at regular intervals, and the cage includes a guide portion between the shaft body and the outer ring.

  According to this configuration, in the timepiece bearing unit, the guide portion guided by the shaft body or the outer ring is formed on at least one of the inner peripheral surface and the outer peripheral surface of the cage, so that the spherical body is rotated when the shaft body is rotated. Can be positioned in the circumferential direction around the shaft body, the inclination of the longitudinal direction of the central axis of the cage with respect to the longitudinal direction of the central axis of the shaft body or the outer ring can be reduced, and the shaft body can be supported rotatably. As a result, the cage is guided to the shaft body or the outer ring by the guide surface, and portions other than the guide surface of the cage do not collide with the shaft body or the outer ring. Therefore, it is possible to suppress bearing loss when the shaft body is in rotational contact with the bearing, and it is possible to reduce torque fluctuation and rotation cycle fluctuation of the shaft body.

Further, the guide portion is formed on the inner peripheral surface of the cage, and is characterized in that it abuts on the outer peripheral surface of the shaft body at one or more places.
According to this configuration, by forming the guide portion guided by the shaft body on the inner peripheral surface of the cage, the spherical body is positioned in the circumferential direction around the shaft body when the shaft body rotates, and the shaft The inclination of the longitudinal direction of the central axis of the cage with respect to the longitudinal direction of the central axis of the body can be reduced, and the shaft body can be rotatably supported. As a result, the cage is guided by the shaft body by the guide surface, and does not collide with the shaft body or the outer ring at places other than the guide surface of the cage. Therefore, it is possible to suppress bearing loss when the shaft body is in rotational contact with the bearing, and it is possible to reduce torque fluctuation and rotation cycle fluctuation of the shaft body.

The shaft body includes a tip portion that is a straight portion and a shaft body portion that is larger than the diameter of the straight portion and is connected to the straight portion, and the guide portion is at least one of the tip portion and the shaft body portion. It is characterized by being substantially parallel to the above.
According to this configuration, the guide surface of the cage and at least one or more of the small shaft diameter portion and the medium shaft diameter portion are parallel or at an angle of 6 degrees at the maximum. At least one outer peripheral surface of the small shaft diameter portion and the medium shaft diameter portion is in contact with the entire surface or an area close to the entire surface. Therefore, the cage reduces the inclination of the longitudinal direction of the central axis of the cage with respect to the longitudinal direction of the central axis of the shaft body, and does not collide with the shaft body or the outer ring at places other than the guide surface of the cage. Therefore, the bearing loss when the shaft body is in rotational contact with the bearing can be suppressed, and the torque fluctuation of the shaft body and the fluctuation of the rotation cycle can also be reduced. Therefore, the balance with a balance has a stable and high swing angle, and the fluctuation of the rate is reduced.

In addition, any one of the contact surface of the guide portion with the outer peripheral surface of the shaft body or the outer peripheral surface of the shaft member that contacts the guide portion is provided with a concave portion or a convex portion.
According to this configuration, when the cage is guided by the shaft body, it is possible to reduce the contact area between the shaft small diameter portion and the shaft middle diameter portion and the guide portion of the cage, so that the solid frictional resistance due to contact is reduced. Can be reduced. Therefore, the energy loss in the guide portion can be suppressed while reducing the inclination of the cage with respect to the shaft body, so that the balance with the balance is stably high and the rate fluctuation is reduced.

Further, the guide portion is formed on the outer peripheral surface of the cage, and is characterized by abutting at one or more locations with the inner peripheral surface of the outer ring.
According to this configuration, by forming the guide portion guided by the outer ring on the outer circumferential surface of the cage, the spherical body is positioned in the circumferential direction around the shaft body when the shaft body rotates, and the center of the outer ring The inclination of the longitudinal direction of the central axis of the cage with respect to the longitudinal direction of the shaft can be reduced, and the shaft body can be rotatably supported. As a result, the cage is guided to the outer ring by the guide surface, and does not collide with the shaft body or the outer ring at locations other than the guide surface of the cage. Therefore, it is possible to suppress bearing loss when the shaft body is in rotational contact with the bearing, and it is possible to reduce torque fluctuation and rotation cycle fluctuation of the shaft body.

The outer ring includes a central inner peripheral portion that abuts against the guide portion of the cage on the distal end side of the shaft body, and the guide portion is substantially parallel to the central inner peripheral portion.
According to this configuration, the guide surface of the cage and the outer ring small-diameter portion are parallel or at an angle of 6 degrees at the maximum, so the guide surface of the cage and the outer ring small-diameter portion are entirely or entirely exposed during the guide. Abut in close area. Therefore, the cage reduces the inclination of the longitudinal direction of the central axis of the cage with respect to the longitudinal direction of the central axis of the outer ring, and does not cause a collision with the shaft body or the outer ring at places other than the guide surface of the cage. Therefore, the bearing loss when the shaft body is in rotational contact with the bearing can be suppressed, and the torque fluctuation of the shaft body and the fluctuation of the rotation cycle can also be reduced. Therefore, the balance with a balance has a stable and high swing angle, and the fluctuation of the rate is reduced.

The outer ring includes an outer edge inner peripheral portion that abuts against a guide portion of the cage on the shaft body side of the shaft body, and the guide portion is substantially parallel to the outer edge inner peripheral portion.
According to this configuration, the guide surface of the cage and the inner ring outer diameter portion are parallel or at an angle of 6 degrees at the maximum. Contact with an area close to the entire surface. Therefore, the cage reduces the inclination of the longitudinal direction of the central axis of the cage with respect to the longitudinal direction of the central axis of the outer ring, and does not cause a collision with the shaft body or the outer ring at places other than the guide surface of the cage. Therefore, the bearing loss when the shaft body is in rotational contact with the bearing can be suppressed, and the torque fluctuation of the shaft body and the fluctuation of the rotation cycle can also be reduced. Therefore, the balance with a balance has a stable and high swing angle, and the fluctuation of the rate is reduced.

In addition, either the contact surface of the guide portion with the inner peripheral surface of the outer ring or the inner peripheral surface of the outer ring that contacts the guide portion is provided with a concave portion or a convex portion.
According to this configuration, when the cage is guided by the outer ring middle diameter portion, the contact area between the outer ring middle diameter portion and the guide portion of the cage can be reduced, so that the solid frictional resistance due to contact is reduced. be able to. Therefore, the energy loss in the guide portion can be suppressed while reducing the inclination of the cage with respect to the shaft body, so that the balance with the balance is stably high and the rate fluctuation is reduced.

In addition, the material of the cage is a metal. The metal is preferably any of mild steel, brass, phosphor bronze, or stainless steel.
According to this configuration, cutting can be performed, and burr removal after processing can be easily performed. As a result, the processing time can be shortened and the shape accuracy can be improved. When the shape accuracy is improved, fluctuations in the pitch distance between the spheres and inclination of the cage with respect to the shaft body can be reduced, thereby reducing bearing resistance, improving the swing angle of the balance, and reducing rate fluctuations.

In addition, the material of the cage is a resin. The resin is preferably either an engineering plastic such as polyacetal, polyamide, fluororesin or polyether ether ketone, or a composite material such as glass fiber reinforced plastic or carbon fiber reinforced plastic.
According to this configuration, the weight of the cage can be reduced. When the weight of the cage is reduced, the solid friction resistance by the cage is reduced, so that the bearing resistance is reduced, the balance angle of the balance is improved, and the rate fluctuation is reduced.
Furthermore, since the resin material has a smaller hardness than the metal material, the cage is less likely to damage the shaft or outer ring when the cage formed of the resin material is guided by the shaft or outer ring formed of metal. . This makes it difficult for the shaft and outer ring to be scraped off due to the friction caused by the guide, and it is difficult for metal powder to be generated. If it becomes difficult for the metal powder to be generated, it is possible to reduce adverse effects such as damage to the part due to the metal powder and inhibition of ball rolling, and it is possible to improve the durability of the part and the timing accuracy.

The movement according to the present invention is a movement of a watch provided with a barrel, a watch wheel, a escape wheel, an ankle, and a balance, and the watch bearing unit of the present invention is used at least for the balance of the balance. It is characterized by being.
According to this configuration, since the timepiece bearing unit of the present invention is provided, it is possible to provide a movement with high timing accuracy by suppressing fluctuations in swing angle and rate.

In addition, a timepiece according to the present invention is characterized by including the above-described movement of the present invention and a casing containing the movement.
According to this configuration, since the movement according to the present invention is provided, it is possible to provide a timepiece having high timing accuracy by suppressing fluctuations in swing angle and rate.

According to the timepiece bearing unit according to the present invention, the inclination of the longitudinal direction of the central axis of the cage with respect to the longitudinal direction of the central axis of the shaft body or the outer ring can be reduced, and the shaft body is in a rotational contact with the bearing. The bearing loss can be suppressed, and the torque fluctuation of the shaft body and the fluctuation of the rotation cycle can be reduced.
According to the movement and timepiece of the present invention, it is possible to provide a movement and timepiece with high timing accuracy by suppressing fluctuations in swing angle and rate.

It is a top view of the movement front side of the mechanical timepiece in the embodiment of the present invention. It is a schematic fragmentary sectional view which shows the part of the escape wheel from the barrel in the embodiment of the present invention. It is a general | schematic fragmentary sectional view which shows the part of the balance with the escape wheel & pinion in embodiment of this invention. It is a perspective view which shows a balance and a bearing. FIG. 5 is an exploded perspective view showing the bearing of FIG. (A) It is a top view of the bearing body (1st Embodiment) in the A section of FIG. (B) It is sectional drawing in the cutting plane line Q-Q 'in the top view of (a). (A) It is a perspective view of the holder | retainer (1st Embodiment) with which the bearing body of FIG. 6 was equipped. (B) It is a top perspective view of (a). (C) It is sectional drawing in the upper surface perspective view cutting line B-B 'of (b). It is a figure explaining the inclination of the longitudinal direction of the central axis of a cage to the longitudinal direction of the central axis of a shaft object or an outer ring in a 1st embodiment of the present invention. (A) It is a top view of the bearing body in 2nd Embodiment of this invention. (B) It is sectional drawing (equivalent to FIG. 6) in the cutting | disconnection line D-D 'in the top view of (a). (A) It is a perspective view which shows the holder | retainer in 2nd Embodiment of this invention. It is a top perspective view of (b). (C) It is sectional drawing (equivalent to FIG. 7) in the cutting plane line E-E 'in the upper surface perspective view of (b). It is a figure explaining the inclination of the longitudinal direction of the center axis | shaft of a holder | retainer with respect to the longitudinal direction of the center axis | shaft of the shaft body or outer ring | wheel in 2nd Embodiment of this invention. (A) It is a top view of the bearing body in 3rd Embodiment of this invention. FIG. 7B is a cross-sectional view (corresponding to FIG. 6) taken along a cutting line R-R ′ in the top view of FIG. (A) It is a perspective view which shows the holder | retainer in 3rd Embodiment of this invention. (B) It is a top perspective view of (a). (C) It is sectional drawing (equivalent to FIG. 7) in the cutting plane line G-G 'in the upper surface perspective view of (b). It is a figure explaining the inclination of the longitudinal direction of the center axis | shaft of a holder | retainer with respect to the longitudinal direction of the center axis | shaft of the shaft or outer ring in 3rd Embodiment of this invention. (A) It is a top view of the bearing body in 4th Embodiment of this invention. (B) It is sectional drawing (equivalent to FIG. 6) in the cutting | disconnection line H-H 'in the top view of (a). (A) It is a perspective view which shows the holder | retainer in 4th Embodiment of this invention. (B) It is a top perspective view of (a). (C) It is sectional drawing (equivalent to FIG. 7) in the cutting plane line I-I 'in upper surface perspective drawing of (b). It is a figure explaining the inclination of the longitudinal direction of the center axis | shaft of a holder | retainer with respect to the longitudinal direction of the center axis | shaft of the shaft or outer ring in 4th Embodiment of this invention. (A) It is a top view of the bearing body in 5th Embodiment of this invention. (B) It is sectional drawing (equivalent to FIG. 6) in the cutting line J-J 'in the top view of (a). (A) It is a perspective view which shows the holder | retainer in 5th Embodiment of this invention. (B) It is a top perspective view of (a). (C) It is sectional drawing (equivalent to FIG. 7) in the cutting plane line K-K 'in upper surface perspective drawing of (b). It is a figure explaining the inclination of the longitudinal direction of the center axis | shaft of a holder | retainer with respect to the longitudinal direction of the center axis | shaft of the shaft or outer ring in 5th Embodiment of this invention. (A) It is centerline C passage sectional drawing of the timepiece bearing unit in 6th Embodiment of this invention. (B) (a) It is an enlarged view in the enlarged line S in a figure. (A) It is centerline C passage sectional drawing of the timepiece bearing unit in 7th Embodiment of this invention. (B) (a) It is an enlarged view in the enlarged line V in a figure. (A) It is centerline C passage sectional drawing of the timepiece bearing unit in 8th Embodiment of this invention. (B) (a) It is an enlarged view (b) in the enlarged line T in a figure. It is a general | schematic fragmentary sectional view which shows the structure of the conventional balance with a balance.

  Next, an embodiment of a timepiece bearing according to the present invention will be described with reference to the drawings.

(First embodiment)
(Mechanical watch)
FIG. 1 is a plan view of the movement front side of a mechanical timepiece, FIG. 2 is a schematic partial sectional view showing a portion of a escape wheel from a barrel, and FIG. 3 is a schematic portion showing a portion of a balance wheel from the escape wheel. It is sectional drawing. In FIG. 1, some components are omitted, and the receiving member is indicated by a virtual line.
As shown in FIGS. 1 to 3, the movement 100 of the mechanical timepiece has a base plate 102 that constitutes a substrate of the movement 100. A winding stem 110 is rotatably incorporated in the winding stem guide hole 102 a of the main plate 102. The dial 104 (see FIG. 2) is attached to the movement 100. In general, of both sides of the main plate 102, the side on which the dial plate 104 is disposed is referred to as the back side of the movement 100, and the opposite side of the side on which the dial plate 104 is disposed is referred to as the front side of the movement 100. A train wheel incorporated on the front side of the movement 100 is referred to as a front train wheel, and a train wheel incorporated on the back side of the movement 100 is referred to as a back train wheel. In addition, it is comprised as a portable timepiece by providing the movement 100 with a casing (not shown).

  The position of the winding stem 110 in the axial direction is determined by a switching device including the setting lever 190, the yoke 192, the yoke spring 194, and the back presser 196. The chisel wheel 112 is rotatably provided on the guide shaft portion of the winding stem 110. When the winding stem 110 is rotated in a state where the winding stem 110 is in the first winding stem position (0th stage) closest to the inside of the movement 100 along the rotation axis direction, the rotation of the handwheel is caused. The chic wheel 112 is rotated through. The round hole wheel 114 is rotated by the rotation of the chichi wheel 112. Further, the square hole wheel 116 is rotated by the rotation of the round hole wheel 114. As the square hole wheel 116 rotates, the mainspring 122 (see FIG. 2) accommodated in the barrel complete 120 is wound up.

  The center wheel & pinion 124 is rotated by the rotation of the barrel complete 120. The escape wheel & pinion 130 rotates through the rotation of the fourth wheel 128, the third wheel 126, and the second wheel 124. The barrel wheel 120, the second wheel 124, the third wheel 126, and the fourth wheel 128 constitute a front train wheel.

  The escapement and speed control device for controlling the rotation of the front train wheel includes a balance with hairspring 140, escape wheel 130, and ankle 142. Based on the rotation of the center wheel & pinion 124, the cylindrical pinion 150 (see FIG. 2) rotates simultaneously. The minute hand 152 attached to the cylindrical pinion 150 displays “minute”. The cylindrical pinion 150 is provided with a slip mechanism for the center wheel & pinion 124. Based on the rotation of the hour pinion 150, the hour wheel 154 rotates through the rotation of the minute wheel. An hour hand 156 attached to the hour wheel 154 displays “hour”.

  The barrel complete 120 includes a barrel complete gear 120d, a barrel complete 120f, and a mainspring 122. The barrel complete 120f includes an upper shaft portion 120a and a lower shaft portion 120b. The barrel complete 120f is made of a metal such as carbon steel. The barrel gear 120d is formed of a metal such as brass.

  The center wheel & pinion 124 includes an upper shaft portion 124a, a lower shaft portion 124b, a pinion portion 124c, a gear portion 124d, and an abacus ball portion 124h. The pinion portion 124c of the center wheel & pinion 124 is configured to mesh with the barrel gear 120d. The upper shaft portion 124a, the lower shaft portion 124b, and the abacus ball portion 124h are formed of a metal such as carbon steel. The gear portion 124d is formed of a metal such as nickel.

  The third wheel & pinion 126 includes an upper shaft portion 126a, a lower shaft portion 126b, a pinion portion 126c, and a gear portion 126d. The pinion 126c of the third wheel & pinion 126 is configured to mesh with the gear portion 124d.

  The fourth wheel & pinion 128 includes an upper shaft portion 128a, a lower shaft portion 128b, a pinion portion 128c, and a gear portion 128d. The pinion portion 128c of the fourth wheel & pinion 128 is configured to mesh with the gear portion 126d. The upper shaft portion 128a and the lower shaft portion 128b are formed of a metal such as carbon steel. The gear portion 128d is formed of a metal such as nickel.

  The escape wheel & pinion 130 includes an upper shaft portion 130a, a lower shaft portion 130b, a pinion portion 130c, and a gear portion 130d. The pinion 130c of the escape wheel & pinion 130 is configured to mesh with the gear portion 128d. The ankle 142 includes an ankle body 142d and an ankle true 142f. The ankle true 142f includes an upper shaft portion 142a and a lower shaft portion 142b.

  The barrel complete 120 is supported rotatably with respect to the main plate 102 and the barrel holder 160. That is, the upper shaft portion 120 a of the barrel complete 120 f is supported so as to be rotatable with respect to the barrel holder 160. The lower shaft part 120b of the barrel complete 120f is supported to be rotatable with respect to the main plate 102. The second wheel 124, the third wheel 126, the fourth wheel 128, and the escape wheel 130 are supported rotatably with respect to the main plate 102 and the train wheel bridge 162. That is, the upper shaft portion 124a of the center wheel & pinion 124, the upper shaft portion 126a of the third wheel & pinion 126, the upper shaft portion 128a of the fourth wheel & pinion 128, and the upper shaft portion 130a of the escape wheel & pinion 130 are And is rotatably supported. In addition, the lower shaft portion 124b of the center wheel 124, the lower shaft portion 126b of the third wheel 126, the lower shaft portion 128b of the fourth wheel 128, and the lower shaft portion 130b of the escape wheel 130 are defined with respect to the main plate 102. It is rotatably supported.

  The ankle 142 is rotatably supported with respect to the main plate 102 and the ankle receiver 164. That is, the upper shaft portion 142 a of the ankle 142 is supported so as to be rotatable with respect to the ankle receiver 164. The lower shaft portion 142b of the ankle 142 is rotatably supported with respect to the main plate 102.

  The bearing portion of the barrel holder 160 that rotatably supports the upper shaft portion 120a of the barrel complete 120f, the bearing portion of the train wheel ring 162 that rotatably supports the upper shaft portion 124a of the center wheel & pinion 124, and the third wheel & pinion 126 The bearing portion of the train wheel bridge 162 that rotatably supports the upper shaft portion 126a, the bearing portion of the train wheel bridge 162 that rotatably supports the upper shaft portion 128a of the fourth wheel & pinion 128, and the escape wheel 130 Lubricating oil is injected into the bearing portion of the train wheel bridge 162 that rotatably supports the upper shaft portion 130a and the bearing portion of the ankle receiver 164 that rotatably supports the upper shaft portion 142a of the ankle 142. Further, the bearing portion of the main plate 102 that rotatably supports the lower shaft portion 120b of the barrel complete 120f, the bearing portion of the main plate 102 that rotatably supports the lower shaft portion 124b of the center wheel & pinion 124, and the third wheel 126 A bearing portion of the main plate 102 that rotatably supports the lower shaft portion 126b, a bearing portion of the main plate 102 that rotatably supports the lower shaft portion 128b of the fourth wheel & pinion 128, and a lower shaft portion 130b of the escape wheel 130. Lubricating oil is injected into the bearing portion of the base plate 102 that is rotatably supported and the bearing portion of the base plate 102 that rotatably supports the lower shaft portion 142 b of the ankle 142. This lubricating oil is preferably a precision machine oil, particularly preferably a so-called watch oil.

  In order to improve the retention performance of the lubricating oil, the conical, cylindrical, or frustoconical oil sump is provided on each bearing portion of the main plate 102, the bearing portion of the barrel holder 160, and each bearing portion of the train wheel bridge 162. It is preferable to provide a part. Providing the oil reservoir can effectively prevent the oil from diffusing due to the surface tension of the lubricating oil. The main plate 102, the barrel holder 160, the train wheel bridge 162, and the ankle receiver 164 may be formed of metal such as brass, or may be formed of resin such as polycarbonate.

(Structure of balance)
Next, the structure of the balance of the present embodiment will be described.
As shown in FIG. 3, the balance with hairspring 140 includes a balance stem 140a and a hairspring 140c.

  The hairspring 140c is a thin leaf spring having a spiral shape having a plurality of winding numbers. An inner end portion of the hairspring 140c is fixed to a hairball 140d fixed to the balance stem (shaft main body portion) 140a, and an outer end portion of the hairspring 140c is rotatably attached to the balance holder 167. It is fixed by screwing through a beard 170a attached to 170. The frame body 166 including the bearing 180 has an outer peripheral portion fixed to the balance with hairspring 167. The slow / fast needle 168 is rotatably attached to the balance holder 167. Further, the balance with hairspring 140 is supported so as to be rotatable with respect to the main plate 102 and balance holder 167.

  Here, the balance with hairspring 140 is configured to be rotatable about the central axis C, and thin medium-diameter shaft portions 144 and 145 are formed at both ends of the shaft body 143 (the balance stem 140a). The lower (back side) medium-diameter shaft portion 144 is supported so as to be rotatable with respect to the main plate 102, and the upper (front-side) medium-diameter shaft portion 145 (small-diameter shaft portion 147) is rotatable with respect to the bearing 180a. It is supported by. The balance with hairspring 140 and the bearing 180a constitute a bearing unit (watch bearing unit) 105a.

(First embodiment)
Next, the bearing unit will be described. In the following description, the direction (thrust direction) along the central axis C which is the central axis of the bearing unit 105a in FIG. 3 is referred to as “axial direction”, and the direction orthogonal to the central axis C (radial direction) is “ “Radial direction”, and the direction around the central axis C is “circumferential direction”. Further, in FIG. 3, the bearing 180 a is depicted only on the medium diameter shaft portion 145 (small diameter shaft portion 147) side which is one end portion (upper end portion) of the shaft body 143, but the bearing 180 a is provided at both ends of the shaft body 143. Also good. Further, regarding the shaft body 143, the direction where the balance holder 167 and the main plate 102 are provided is defined as the “outside” axial direction, and the direction provided with the balance wheel 171 is defined as the “inside” axial direction.

  As shown in FIG. 3, the bearing 180 a indicated by part A is provided in the bearing unit 105 a together with the shaft body 143, and is a medium-diameter shaft that is one end portion (upper end portion) of the shaft body 143 that rotates about the central axis C. A bearing body 181a that is provided on the side of the portion 145 (small-diameter shaft portion 147) and restricts movement of the shaft body 143 in the axial direction and radial direction; an elastic body 182 that restricts movement of the bearing body 181a in the axial direction; A frame body 166 that includes 181a and an elastic body 182.

  FIG. 4 is a perspective view showing a balance and a bearing, and FIG. 5 is an exploded perspective view showing the bearing of FIG. 6A is a top view of the bearing body 181a and the shaft body 143, and FIG. 6B is a cross section taken along the cutting line QQ ′ in FIG. FIG. QQ ′.

  As shown in FIGS. 3 to 5, the elastic body 182 is configured by a leaf spring member made of metal, for example. The elastic body 182 is supported and fixed on the outer side in the axial direction of the bearing body 181a in the frame body 166. The elastic body 182 has a biasing force F that biases the bearing body 181a in the direction of the shaft body 143 (inward in the axial direction). In a state where no impact is applied to the bearing unit 105a, the biasing force F is Energizing force that causes the spherical body 183 of the body 181a and the second support surface 206 provided in the medium diameter shaft portion 145 (small diameter shaft portion 147) to abut and the shaft body 143 can rotate around the central axis C. have. That is, the elastic body 182 is configured as a pressurizing mechanism.

  As shown in FIGS. 3 to 6, the bearing body 181 a includes a plurality of (for example, four) spherical bodies 183 arranged along the circumferential direction so as to be able to contact the second support surface 206 of the shaft body 143. The outer ring 185 that holds the sphere 183 in a rollable manner, and the holder 201 a that is arranged along the circumferential direction of the second support surface 206 of the shaft body 143 and encloses the plurality of spheres 183.

  As shown in FIGS. 3 to 5, the frame body 166 is formed in a substantially cylindrical shape, and a third through hole 188 capable of containing the bearing body 181 a and the elastic body 182 is formed. In addition, a groove portion 189 is formed on the inner peripheral surface 166a of the frame body 166 along the circumferential direction so that the peripheral portion of the elastic body 182 is fitted and supported. Furthermore, the outer peripheral surface 166c of the frame 166 is configured to be press-fitted and fixed to the inner peripheral surface of the balance with hairspring 167 (see FIG. 3).

  Here, the configuration of the elastic body 182 and the configuration for supporting and fixing the elastic body 182 to the frame body 166 will be described using an example. For example, as shown in FIGS. 4 and 5, the elastic body 182 is formed with a plurality of inner ring portions 182a that are substantially in contact with the outer end surface 181l of the bearing body 181a and radially outward from the inner ring portion 182a. Spring portion 182b. 4 and 5, three spring portions 182b are formed at substantially equal intervals in the circumferential direction. Further, a plurality of cutout portions 166f that can be inserted through the tip of the spring portion 182b of the elastic body 182 are formed on one surface 166e of the frame 166 in accordance with the shape of the spring portion 182b. And this notch part 166f and the groove part 189 formed in the internal peripheral surface 166a of the frame 166 are connected. That is, the tip of the spring portion 182b can be disposed in the groove portion 189 by inserting the tip of the spring portion 182b in accordance with the position of the notch 166f. In this state, the elastic body 182 is rotated in the circumferential direction with respect to the frame body 166 and the tip of the spring part 182b is supported and fixed to the groove part 189, whereby the spring part 182b of the elastic body 182 is supported and fixed to the frame body 166. Can be done.

  Here, when an external impact is applied to the bearing unit 105 a, the bearing body 181 a tends to move in the axial direction with respect to the frame body 166. The radial movement of the bearing body 181a is restricted because the first guide surface 185b and the second guide surface 166b are formed. At this time, since the elastic body 182 is disposed on the outer side in the axial direction of the bearing body 181a, the amount of movement of the bearing body 181a in the axial direction is restricted. When the impact on the bearing unit 105a is settled, the biasing force F (illustrated in FIG. 3) of the elastic body 182 and the first guide surface 185b are guided by the second guide surface 166b, so that the bearing body 181a is in its original position. Return to.

 As shown in FIG. 6, the outer ring 185 is a substantially disc-shaped member, and a first through hole 186 that penetrates along the axial direction is formed at the center in the radial direction. On the first inner peripheral surface 215 (second inner peripheral surface 216) of the first through hole 186, a first support surface 187 having a concave shape toward the radially outer side is formed along the circumferential direction. The 1st support surface 187 is formed in the curved surface shape which spreads toward the other end side (lower end side) from the axial direction one end side (upper end side). Further, the outer ring 185 can be manufactured using a machining process such as cutting, forging or punching, or a photolithography technique that is one of the MEMS (Micro Electro Mechanical Systems) techniques.

  The medium-diameter shaft portion 145 is formed at one end portion of the shaft body 143 so as to protrude outward in the axial direction, and is formed as a concave surface from the end portion of the medium-diameter shaft portion 145 toward the radially inner side. A small-diameter shaft portion 147 with a small shaft diameter is provided via the surface 206.

  The spherical body 183 abuts on the first support surface 187 of the outer ring 185 and the second support surface 206 provided on the medium-diameter shaft portion 145 (shaft body 143), and a plurality of third through holes provided on the cage 201a. It is held in a state enclosed in the hole 205. That is, the respective spheres 183 are arranged at equal intervals along the circumferential direction, and are held so as to freely roll. 3 to 6, the number of the spheres 183 is four, but the number is not limited to this, and the number of the spheres 183 may be any number as long as it is three or more.

  7A is a perspective view of the cage 201a of FIGS. 3 to 6, FIG. 7B is a top perspective view thereof, and FIG. 7C is a cross-sectional view in FIG. It is sectional drawing BB 'cut | disconnected by line BB'.

  6 and 7, the cage 201a is a rotationally symmetric member in which the first outer peripheral surface 203 is formed by a substantially inclined surface, and a second through hole penetrating along the axial direction in the radial center portion thereof. 202 is formed. A medium diameter shaft portion 145 (small diameter shaft portion 147) is inserted into the second through hole 202. Further, a plurality of third through holes 205 penetrating from the first outer peripheral surface 203 to the third inner peripheral surface 204 are formed at equal intervals along the circumferential direction. Each third through-hole 205 contains a sphere 183. A second gap 210 is provided between the third through hole 205 and the sphere 183 to allow the sphere 183 to roll. In addition, a third guide surface 207a is provided on the third inner peripheral surface 204 forming the second through hole 202. The third guide surface 207a and the second outer peripheral surface 208 of the small diameter shaft portion 147 are formed in parallel. A first gap 209 is provided between the third guide surface 207a and the second outer peripheral surface 208 to allow the cage 201a and the medium diameter shaft portion 145 (small diameter shaft portion 147) to rotate. Yes. The first gap 209 is preferably larger than 0 μm and up to about 20 μm.

  In FIG. 3, in the bearing 180 a configured as described above, the shaft body 143 (medium-diameter shaft portion 145) normally rotates around the central axis C. At this time, since the spherical body 183 is disposed on the bearing body 181a, the medium-diameter shaft portion 145 can smoothly rotate about the shaft center.

Further, in the present embodiment, the cage is constituted by the third guide surface 207a provided on the third inner circumferential surface 204 of the cage 201a and the second outer circumferential surface 208 of the medium diameter shaft portion 145 (small diameter shaft portion 147). 201a is guided by the medium-diameter shaft portion 145 (small-diameter shaft portion 147), and the sphere 183 is enclosed in the third through hole 205 of the retainer 201a to support the medium-diameter shaft portion 145 (small-diameter shaft portion 147). A configuration is adopted in which the roller 206 is held so as to be freely rollable in the circumferential direction along the surface 206.
According to this configuration, when the shaft body 143 rotates, the sphere 183 rolls in a state of being included in the third through holes 205 provided at equal intervals in the cage 201a. It can roll stably in the circumferential direction along the second support surface 206 of the medium diameter shaft portion 145 (small diameter shaft portion 147) while being held at a distance.

  FIG. 8 is a diagram showing the relationship between the inclination θ1 between the center line C in FIG. 3 and the center axis L of the cage 201a in FIG.

  As described above, since the cage 201a is guided by the medium diameter shaft portion 145 (small diameter shaft portion 147), the inclination θ1 can be reduced. In detail, the inclination θ1 can be set to 0 ° or more and 6 ° or less. As a result, the cage 201a does not collide with the shaft body 143 or the outer ring 185 at locations other than the third guide surface 207a. Therefore, the bearing loss when the shaft body 143 is in rotational contact with the bearing 180a can be suppressed, and torque fluctuations and fluctuations in the rotation cycle of the shaft body 143 can be reduced. Therefore, it is possible to stabilize the timing accuracy of the movement 100 (portable watch) by suppressing fluctuations in the swing angle and the rate.

(Second Embodiment)
Next, a second embodiment of the present invention will be described. 9A is a top view of the bearing body 181b and the shaft body 143, and FIG. 9B is a cross-sectional view D cut along a cutting line DD ′ in FIG. 9A. -D '. FIG. 10A is a perspective view of the cage 201b of FIG. 9, FIG. 10B is a top perspective view thereof, and FIG. 10C is a cross-sectional view in FIG. It is sectional drawing EE 'cut | disconnected by line EE'. Since the structure of the bearing body 181b is basically the same as that of the first embodiment of the present invention, only the parts different from the first embodiment will be described in the following description.

  The cage 201b is a rotationally symmetric member in which the first outer peripheral surface 203 is formed of an inclined surface, and a second through-hole 202 penetrating along the axial direction is formed in the central portion in the radial direction. A medium diameter shaft portion 145 (small diameter shaft portion 147) is inserted into the second through hole 202. A plurality of third through holes 205 penetrating from the first outer peripheral surface 203 to the third inner peripheral surface 204 are provided at equal intervals along the circumferential direction. A spherical body 183 is included in each third through hole 205. In addition, a second gap 210 is provided between the third through hole 205 and the sphere 183 to allow the sphere 183 to roll in the third through hole 205. Further, the third inner peripheral surface 204 forming the second through hole 202 is provided with a third guide surface 207a and a fourth guide surface 207b. The third guide surface 207a and the fourth guide surface 207b, the second outer peripheral surface 208 of the small diameter shaft portion 147, and the third outer peripheral surface 211 of the medium diameter shaft portion 145 are formed in parallel. Further, between the third guide surface 207a and the fourth guide surface 207b and the second outer peripheral surface 208 of the small diameter shaft portion 147 and the third outer peripheral surface 211 of the medium diameter shaft portion 145, the cage 201b and the medium diameter shaft A first gap 209 and a third gap 212 are provided to allow rotation of the portion 145 (small diameter shaft portion 147). The first gap 209 and the third gap 212 are preferably larger than 0 μm and up to about 20 μm.

  3 and 9, in a bearing 180b (not shown) provided with a bearing body 181b provided with a cage 201b, a shaft body 143 (medium-diameter shaft portion 145) usually rotates around a central axis C. . At this time, since the spherical body 183 is disposed on the bearing body 181b, the medium-diameter shaft portion 145 can smoothly rotate about the axis.

Further, in the present embodiment, the third guide surface 207a and the fourth guide surface 207b provided on the third inner peripheral surface 204 of the cage 201b, the second outer peripheral surface 208 of the small diameter shaft portion 147, and the medium diameter shaft portion 145. The third outer peripheral surface 211 of the retainer 201b is guided by the medium diameter shaft portion 145 (small diameter shaft portion 147), and the sphere 183 is included in the third through hole 205 of the retainer 201b, and the medium diameter shaft portion. It was set as the structure hold | maintained so that rolling in the circumferential direction is possible along the outer peripheral surface of 145 (small diameter shaft part 147).
According to this configuration, when the shaft body 143 rotates, the sphere 183 rolls while being enclosed in the third through holes 205 provided at equal intervals in the cage 201b. It can roll stably in the circumferential direction along the second support surface 206 of the medium diameter shaft portion 145 (small diameter shaft portion 147) while being held at a distance.

  FIG. 11 is a diagram illustrating the relationship between the inclination θ2 between the center line C in FIG. 3 and the center axis M of the cage 201b in FIG.

  As described above, since the retainer 201b is guided by the medium diameter shaft portion 145 (small diameter shaft portion 147), the inclination θ2 can be reduced. In detail, the inclination θ2 can be set to 0 ° or more and 4 ° or less. As a result, a collision with the shaft body 143 or the outer ring 185 does not occur at locations other than the third guide surface 207a and the fourth guide surface 207b of the cage 207b. Therefore, bearing loss when the shaft body 143 is in rotational contact with the bearing 180b can be suppressed, and torque fluctuations and rotation cycle fluctuations of the shaft body 143 can be reduced. Therefore, it is possible to stabilize the timing accuracy of the movement 100 (portable watch) by suppressing fluctuations in the swing angle and the rate.

  Furthermore, since this embodiment has a larger number of guide surfaces formed on the holder 201b than the first embodiment, the inclination θ2 of the holder 201b can be reduced more than the inclination θ1 of the first embodiment. . Therefore, the cage 201b can rotate more freely in the circumferential direction along the outer peripheral surface of the medium diameter shaft portion 145 (small diameter shaft portion 147) more stably than the cage 201a of the first embodiment. Therefore, the bearing loss when the shaft body 143 is in rotational contact with the bearing 180b can be further suppressed, and the torque fluctuation and the rotation cycle fluctuation of the shaft body 143 can be further reduced. Therefore, the fluctuation of the swing angle and the rate can be further suppressed, and the timekeeping accuracy of the movement 100 (portable watch) can be further stabilized.

(Third embodiment)
Next, a third embodiment of the present invention will be described. 12A is a top view of the bearing body 181c and the shaft body 143, and FIG. 12B is a cross-sectional view R— taken along the cutting line RR ′ in FIG. R ′. FIG. 13A is a perspective view of the cage 201c of FIG. 12, FIG. 13B is a top perspective view, and FIG. 13C is a section line in FIG. It is sectional drawing GG 'cut | disconnected by GG'. Since the structure of the bearing body 181c is basically the same as that of the first embodiment of the present invention, only the portions different from the first embodiment will be described in the following description.

  The cage 201c is a rotationally symmetric member in which the first outer peripheral surface 203 is formed of an inclined surface, and a second through-hole 202 penetrating along the axial direction is formed in the central portion in the radial direction. A medium diameter shaft portion 145 (small diameter shaft portion 147) is inserted into the second through hole 202. A plurality of third through holes 205 penetrating from the first outer peripheral surface 203 to the third inner peripheral surface 204 are provided at equal intervals along the circumferential direction. A spherical body 183 is included in each third through hole 205. In addition, a second gap 210 is provided between the third through hole 205 and the sphere 183 to allow the sphere 183 to roll in the third through hole 205. A third guide surface 207 c is provided on the third inner peripheral surface 204 that forms the second through hole 202. The fifth guide surface 207c and the first inner peripheral surface 215 of the outer ring 185 are formed in parallel. Further, a fourth gap between the fifth guide surface 207c and the first inner peripheral surface 215 of the outer ring 185 for allowing rotation of the cage 201c and the medium diameter shaft portion 145 (small diameter shaft portion 147). 213 is provided. The fourth gap 213 is preferably larger than 0 μm and up to about 20 μm.

  3 and 12, in a bearing 180c (not shown) provided with a bearing body 181c provided with a cage 201c, a shaft body 143 (medium-diameter shaft portion 145) is usually rotated around a central axis C. . At this time, since the spherical body 183 is arranged on the bearing body 181c, the medium-diameter shaft portion 145 can smoothly rotate about the shaft center.

In the present embodiment, the cage 201c is guided to the outer ring 185 by the fifth guide surface 207c provided on the first outer circumferential surface 203 of the cage 201c and the first inner circumferential surface 215 of the outer ring 185, so that the spherical body 183 is included in the third through hole 205 of the cage 201c and is configured to be held so as to be freely rollable in the circumferential direction along the outer peripheral surface of the medium diameter shaft portion 145 (small diameter shaft portion 147).
According to this configuration, when the shaft body 143 rotates, the sphere 183 rolls while being enclosed in the third through holes 205 provided at equal intervals in the retainer 201c. It can roll stably in the circumferential direction along the second support surface 206 of the medium diameter shaft portion 145 (small diameter shaft portion 147) while being held at a distance.

  FIG. 14 is a diagram illustrating the relationship between the inclination θ3 between the center line C in FIG. 3 and the center axis N of the cage 201c in FIG.

  As described above, since the retainer 201c is guided by the outer ring 185, the inclination θ3 can be reduced. In detail, the inclination θ3 can be set to 0 ° or more and 6 ° or less. As a result, a collision with the shaft body 143 or the outer ring 185 does not occur at any place other than the fifth guide surface 207c of the cage 201c. Therefore, it is possible to suppress bearing loss when the shaft body 143 is in rotational contact with the bearing 180c, and it is possible to reduce torque fluctuation and rotation cycle fluctuation of the shaft body 143. Therefore, it is possible to stabilize the timing accuracy of the movement 100 (portable watch) by suppressing fluctuations in the swing angle and the rate.

 Further, in the present embodiment, the cage 201c is guided to the outer ring 185 by the fifth guide surface 207c provided on the first outer circumferential surface 203 of the cage 201c and the first inner circumferential surface 215 of the outer ring 185. Therefore, the diameter of the second through hole 202 of the cage 201c can be increased. Therefore, the processability for forming the second through hole 202 can be improved. Therefore, the processing process can be facilitated and the processing cost can be reduced.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described. FIG. 15A is a top view of the bearing body 181d and the shaft body 143, and FIG. 15B is a cross-sectional view taken along the cutting line HH ′ in FIG. H ′. 16A is a perspective view of the cage 201d in FIG. 15, FIG. 16B is a top perspective view, and FIG. 16C is a section line I in FIG. It is sectional drawing II 'cut | disconnected by -I'. Since the structure of the bearing body 181d is basically the same as that of the first embodiment of the present invention, only the portions different from the first embodiment will be described in the following description.

  The cage 201d is a rotationally symmetric member in which the first outer peripheral surface 203 is formed of an inclined surface, and a second through-hole 202 penetrating along the axial direction is formed at the center in the radial direction. A medium diameter shaft portion 145 (small diameter shaft portion 147) is inserted into the second through hole 202. A plurality of third through holes 205 penetrating from the first outer peripheral surface 203 to the third inner peripheral surface 204 are provided at equal intervals along the circumferential direction. A spherical body 183 is included in each third through hole 205. In addition, a second gap 210 is provided between the third through hole 205 and the sphere 183 to allow the sphere 183 to roll in the third through hole 205. The third inner peripheral surface 204 forming the second through hole 202 is provided with a fifth guide surface 207c and a sixth guide surface 207d at both ends of the first outer peripheral surface 203. . The fifth guide surface 207c and the sixth guide surface 207d and the first inner peripheral surface 215 and the second inner peripheral surface 216 of the first through hole 186 provided in the outer ring 185 are formed in parallel. Further, between the fifth guide surface 207c and the sixth guide surface 207d and the first inner peripheral surface 215 and the second inner peripheral surface 216, the cage 201d and the medium diameter shaft portion 145 (small diameter shaft portion 147). Are provided with a fourth gap 213 and a fifth gap 214 for allowing each rotation. The fourth gap 213 and the fifth gap 214 are preferably larger than 0 μm and up to about 20 μm.

  3 and 15, in a bearing 180d (not shown) provided with a bearing body 181d provided with a cage 201d, the shaft body 143 (medium-diameter shaft portion 145) normally rotates around the central axis C. . At this time, since the spherical body 183 is arranged on the bearing body 181d, the medium-diameter shaft portion 145 can smoothly rotate about the shaft center.

In the present embodiment, the fifth guide surface 207c and the sixth guide surface 207d provided on the first outer peripheral surface 203 of the cage 201d, and the first inner peripheral surface 215 and the second inner peripheral surface provided on the outer ring 185 are provided. Due to the surface 216, the retainer 201d is guided by the outer ring 185, and the sphere 183 is enclosed in the third through hole 205 of the retainer 201d, along the outer periphery of the medium diameter shaft portion 145 (small diameter shaft portion 147). It was set as the structure hold | maintained so that rolling in the circumferential direction was possible.
According to this configuration, when the shaft body 143 rotates, the sphere 183 rolls while being enclosed in the third through holes 205 provided at equal intervals in the cage 201d. It can roll stably in the circumferential direction along the second support surface 206 of the medium diameter shaft portion 145 (small diameter shaft portion 147) while being held at a distance.

  FIG. 17 is a diagram illustrating the relationship between the inclination θ4 between the center line C in FIG. 3 and the center axis O of the cage 201d in FIG.

  As described above, since the cage 201d is guided by the outer ring 185, the inclination θ4 can be reduced more than the inclination θ3. In detail, the inclination θ4 can be set to 0 ° or more and 4 ° or less. As a result, a collision with the shaft body 143 or the outer ring 185 does not occur at locations other than the fifth guide surface 207c and the sixth guide surface 207d of the cage 201d. Therefore, it is possible to suppress bearing loss when the shaft body 143 is in rotational contact with the bearing 180d, and it is possible to reduce torque fluctuations and rotation cycle fluctuations of the shaft body 143. Therefore, it is possible to stabilize the timing accuracy of the movement 100 (portable watch) by suppressing fluctuations in the swing angle and the rate.

  Furthermore, since the number of guide surfaces of the holder 201d is larger than that of the third embodiment, the inclination θ4 of the holder 201d can be reduced more than the inclination θ3 of the third embodiment. Therefore, the cage 201d can rotate more freely in the circumferential direction along the outer peripheral surface of the medium diameter shaft portion 145 (small diameter shaft portion 147) more stably than the cage 201c of the third embodiment. Therefore, the bearing loss when the shaft body 143 is in rotational contact with the bearing 180d can be further suppressed, and the torque fluctuation of the shaft body 143 and the fluctuation of the rotation cycle can be further reduced. Therefore, the fluctuation of the swing angle and the rate can be further suppressed, and the timekeeping accuracy of the movement 100 (portable watch) can be further stabilized.

  Further, in the present embodiment, the fifth guide surface 207c and the sixth guide surface 207d provided on the first outer peripheral surface 203 of the cage 201d, and the first inner peripheral surface 215 and the second inner peripheral surface provided in the outer ring 185 are used. Since the cage 201d is guided by the outer ring 185 by the surface 216, the diameter of the second through hole 202 of the cage 201d can be increased. Therefore, the processability for forming the second through hole 202 can be improved. Therefore, the machining process can be facilitated and the machining cost can be reduced.

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described. 18A is a top view of the bearing body 181e and the shaft body 143, and FIG. 18B is a cross-sectional view J cut along a cutting line JJ ′ in FIG. -J '. FIG. 19A is a perspective view of the cage 201e of FIG. 18, FIG. 19B is a top perspective view, and FIG. 19C is a section line in FIG. It is sectional drawing KK 'cut | disconnected by KK'. Since the structure of the bearing body 181e is basically the same as that of the first embodiment of the present invention, only the portions different from the first embodiment will be described in the following description.

  The cage 201e is a rotationally symmetric member in which the first outer peripheral surface 203 is formed of an inclined surface, and a second through-hole 202 penetrating along the axial direction is formed at the center in the radial direction. A medium diameter shaft portion 145 (small diameter shaft portion 147) is inserted into the second through hole 202. A plurality of third through holes 205 penetrating from the first outer peripheral surface 203 to the third inner peripheral surface 204 are provided at equal intervals along the circumferential direction. A spherical body 183 is included in each third through hole 205. Further, a second gap 210 is provided between the third through hole 205 and the sphere 183, and the rotation of the sphere 183 in the third through hole 205 is allowed. The third inner peripheral surface 204 and the first outer peripheral surface 203 are provided with a fourth guide surface 207b and a fifth guide surface 207c. The fourth guide surface 207b and the fifth guide surface 207c, the third outer peripheral surface 211 of the medium diameter shaft portion 145, and the first inner peripheral surface 215 of the first through hole 186 provided in the outer ring 185 are formed in parallel. ing. Further, between the fourth guide surface 207b and the fifth guide surface 207c and the third outer peripheral surface 211 and the first inner peripheral surface 215, a cage 201e and an intermediate diameter shaft portion 145 (small diameter shaft portion 147) are provided. A third gap 212 and a fourth gap 213 for allowing each rotation are provided. The third gap 212 and the fourth gap 213 are preferably larger than 0 μm and up to about 20 μm.

  3 and 18, in a bearing 180e (not shown) provided with a bearing body 181e provided with a cage 201e, a shaft body 143 (medium-diameter shaft portion 145) is usually rotated around a central axis C. . At this time, since the spherical body 183 is arranged on the bearing body 181e, the medium-diameter shaft portion 145 can smoothly rotate about the shaft center.

Furthermore, in the present embodiment, the fourth outer peripheral surface 204 and the fifth outer peripheral surface 203 provided on the third inner peripheral surface 204 and the first outer peripheral surface 203 of the cage 201e, and the third outer peripheral surface of the medium diameter shaft portion 145. 211 and the first inner peripheral surface 215 of the first through hole 186 provided in the outer ring 185, the retainer 201 e is guided to the medium diameter shaft portion 145 and the outer ring 185, and the sphere 183 is the third of the retainer 201 e. It is included in the through-hole 205 and is configured to be held so as to be rollable in the circumferential direction along the outer periphery of the medium diameter shaft portion 145 (small diameter shaft portion 147).
According to this configuration, when the shaft body 143 rotates, the sphere 183 rolls while being enclosed in the third through holes 205 provided at equal intervals in the cage 201e. It can roll stably in the circumferential direction along the second support surface 206 of the medium diameter shaft portion 145 (small diameter shaft portion 147) while being held at a distance.

  FIG. 20 is a diagram illustrating a relationship between the inclination θ5 of the center line C in FIG. 3 and the center axis P of the cage 201e in FIG.

  As described above, the cage 201e is guided by the medium-diameter shaft portion 145 and the outer ring 185, so that the inclination θ5 can be reduced. In detail, the inclination θ5 can be set to 0 ° or more and about 4 ° or less. Thereby, the collision with the shaft body 143 or the outer ring 185 does not occur at any place other than the fourth guide surface 207b and the fifth guide surface 207c of the cage 201e. Therefore, it is possible to suppress bearing loss when the shaft body 143 is in rotational contact with the bearing 180e, and it is possible to reduce torque fluctuation and rotation cycle fluctuation of the shaft body 143. Therefore, it is possible to stabilize the timing accuracy of the movement 100 (portable watch) by suppressing fluctuations in the swing angle and the rate.

  Furthermore, since this embodiment has a larger number of guide surfaces of the holder 201e than the first or third embodiment, the inclination θ5 of the holder 201e is set to be larger than the inclinations θ1 and θ3 of the first or third embodiment. Can be reduced. Therefore, the cage 201e rotates more stably in the circumferential direction along the outer peripheral surface of the medium-diameter shaft portion 145 (small-diameter shaft portion 147) than the cages 201a and 201c of the first or third embodiment. can do. Therefore, it is possible to further suppress bearing loss when the shaft body 143 is in rotational contact with the bearing 180e, and to further reduce torque fluctuation and rotation cycle fluctuation of the shaft body 143. Therefore, the fluctuation of the swing angle and the rate can be further suppressed, and the timekeeping accuracy of the movement 100 (portable watch) can be further stabilized.

  Further, in the present embodiment, the fourth guide surface 207b and the fifth guide surface 207c provided on the third inner peripheral surface 204 and the first outer peripheral surface 203 of the cage 201e, and the third outer peripheral surface of the medium diameter shaft portion 145 are provided. 211 and the first inner peripheral surface 215 of the first through hole 186 provided in the outer ring 185, the retainer 201 e is configured to be guided by the medium-diameter shaft portion 145 and the outer ring 185. The diameter on the fifth guide surface 207 c side in the central axis P of the two through holes 202 can be increased. Therefore, the processability for forming the second through hole 202 can be improved. Therefore, the machining process can be facilitated and the machining cost can be reduced.

(Sixth embodiment)
Next, a sixth embodiment of the present invention will be described. FIG. 21 is a cross-sectional view (a) passing through the center line C of the bearing body according to the sixth embodiment of the present invention, and an enlarged view (b) taken along the enlarged line S in FIG. Since the basic structure of the bearing body 181f is the same as that of the first embodiment, only the portions different from the first embodiment will be described in the following description.

21, the cage 201f has a structure that is guided by the third guide surface 207a of the cage 201f with respect to the second outer peripheral surface 208 of the small-diameter shaft portion 147. Concave portions 221 are formed in the third guide surface 207a in the circumferential direction.
Here, the axial length AA of the concave portion 221 is smaller than the axial length AB of the third guide surface 207a before the concave portion 221 is formed.
The radial depth AC of the recess 221 is a depth at which the recess 221 does not penetrate the first outer peripheral surface 203 and the third through hole 205.
Moreover, the number of the recessed parts 221 should just be one or more in an axial direction and the circumferential direction, respectively. However, when the number of the concave portions 221 is one in the circumferential direction, it is desirable that they are connected over the entire circumference. In addition, when there are a plurality of recesses 221 in the circumferential direction, it is desirable to make the distance between pitches of adjacent recesses 221 equal.
In addition, when the third guide surface 207a is divided into a plurality of portions by the recess 221, it is desirable that the recess 221 is in a position where each of the plurality of third guide surfaces 207a contacts the second outer peripheral surface 208 of the small diameter shaft portion 147. .

  In a bearing 180f (not shown) provided with a bearing body 181f provided with a cage 201f, the shaft body 143 (medium-diameter shaft portion 145) normally rotates around the central axis C. At this time, since the spherical body 183 is disposed on the bearing body 181f, the medium-diameter shaft portion 145 can smoothly rotate about the shaft center.

When the shaft body 143 rotates, the sphere 183 rolls while being enclosed in the third through holes 205 provided at equal intervals in the cage 201f, so that the sphere 183 is kept at a constant pitch distance. It is possible to stably roll in the circumferential direction along the second support surface 206 of the diameter shaft portion 145 (small diameter shaft portion 147).
Further, since the cage 201f is guided by the small diameter shaft portion 147, the inclination of the cage 201f with respect to the small diameter shaft portion 14 can be reduced. As a result, the cage 201f does not collide with the shaft body 143 or the outer ring 185 at locations other than the third guide surface 207a of the cage 201f. Therefore, it is possible to suppress the bearing loss when the shaft body 143 is in rotational contact with the bearing 180f, and it is possible to reduce the torque fluctuation and the rotation cycle fluctuation of the shaft body 143. Therefore, it is possible to stabilize the timing accuracy of the movement 100 (portable watch) by suppressing fluctuations in the swing angle and the rate.

  Further, in the present embodiment, the cage 201f is guided by the third guide surface 207a of the cage 210f with respect to the second outer peripheral surface 208 of the small diameter shaft portion 147, and the recess 221 is formed on the third guide surface 207a. It was set as the structure formed in the circumferential direction.

According to the configuration of the present embodiment, when the cage 210f is guided by the small diameter shaft portion 147, the third guide surface 207a excluding the concave portion 221 of the cage 210f is formed on the second outer peripheral surface 208 of the small diameter shaft portion 147. Contact.
In contact of the third guide surface 207a with the second outer peripheral surface 208, the contact area of the third guide surface 207a formed with the recess 221 is larger than that of the third guide surface 207a where the recess 221 is not formed. Therefore, the solid frictional resistance is reduced.
If the solid frictional resistance due to the contact at the time of guide becomes small, the energy loss at the bearing 180f caused by the cage 210f becomes small, and the reduction of the rotational energy of the balance with hairspring 140 is suppressed.
When the rotational energy of the balance with hairspring 140 is increased, the swing angle is increased, and the influence of the escapement error is reduced.
Therefore, since the inclination with respect to the small diameter shaft part 147 of the retainer 201f can be reduced while suppressing the energy loss at the bearing 180f, the rate variation can be further reduced, and the timekeeping accuracy of the movement 100 (portable watch) is reduced. Can be further stabilized.

In addition, although the present Example demonstrated the case where the recessed part 221 was one, when forming the several recessed part 221, the length of the axial direction of the several recessed part 221 may each differ. Similarly, when forming the plurality of recesses 221, the radial depths of the plurality of recesses 221 may be different from each other. However, in order to reduce the inclination of the cage 201f with respect to the small-diameter shaft portion 147, it is desirable that the radial depths of the plurality of concave portions 221 be equal.
In the description of the present embodiment, the concave portion 221 is provided on the cage 201f side and the small-diameter shaft portion 147 side is the second outer peripheral surface 208 as a simple surface, but conversely, the concave portion 221 is formed on the small-diameter shaft portion 147 side. It is good also considering the retainer 201f side as an inner peripheral surface as a simple one surface.

(Seventh embodiment)
Next, a seventh embodiment of the present invention will be described. FIG. 22 is a sectional view (a) passing through the center line C of the bearing body according to the seventh embodiment of the present invention, and an enlarged view (b) taken along the enlarged line V in the figure. Since the basic structure of the bearing body 181g is the same as that of the first embodiment, only the portions different from the first embodiment will be described in the following description.

As shown in FIG. 22, the cage 201g is structured to be guided by the fifth guide surface 207c of the cage 201g with respect to the first inner peripheral surface 215 of the outer ring 185. Moreover, the convex part 222 is formed in the circumferential direction on the 5th guide surface 207c.
Here, the axial length BA of the convex portion 222 is smaller than the axial length BB of the fifth guide surface 207 c before the convex portion 222 is formed.
Further, the height BC in the radial direction of the convex portion 222 is a height at which the gap BD is generated between the first inner peripheral surface 215 and the cage 201g in the bearing body 181g.
Moreover, the number of the convex parts 222 should just be one or more in an axial direction and the circumferential direction, respectively. However, when there is one convex portion 222 in the circumferential direction, it is desirable that the entire length is connected. In addition, when there are a plurality of convex portions 222 in the circumferential direction, it is desirable that the pitch distance between adjacent convex portions 222 be equal.
Further, when there are a plurality of convex portions 222 in the axial direction, it is desirable that all the plurality of convex portions 222 in the axial direction are in a position where they abut against the first inner peripheral surface 215 of the outer ring 185.

  In a bearing 180g (not shown) provided with a bearing body 181g provided with a cage 201g, a shaft body 143 (medium-diameter shaft portion 145) normally rotates around a central axis C. At this time, since the spherical body 183 is disposed on the bearing body 181g, the medium diameter shaft portion 145 can smoothly rotate about the axis.

When the shaft body 143 rotates, the sphere 183 rolls while being enclosed in the third through holes 205 provided at equal intervals in the cage 201g, so that the sphere 183 is kept at a constant pitch distance. It is possible to stably roll in the circumferential direction along the second support surface 206 of the diameter shaft portion 145 (small diameter shaft portion 147).
Further, since the cage 201g is guided by the outer ring 185, the inclination of the cage 201g with respect to the outer ring 185 can be reduced. As a result, the cage 201g does not collide with the shaft body 143 or the outer ring 185 at locations other than the convex portion 222 of the cage 201g. Therefore, it is possible to suppress bearing loss when the shaft body 143 is in rotational contact with the bearing 180g, and it is possible to reduce torque fluctuations and rotation cycle fluctuations of the shaft body 143. Therefore, it is possible to stabilize the timing accuracy of the movement 100 (portable watch) by suppressing fluctuations in the swing angle and the rate.

  Furthermore, in this embodiment, the cage 201g has a structure that is guided by the convex portion 222 of the cage 210g with respect to the first inner peripheral surface 215 of the outer ring 185. Further, the convex portion 222 is formed in the circumferential direction on the fifth guide surface 207c.

According to the configuration of the present embodiment, when the retainer 201g is guided by the outer ring 185, the convex portion 222 formed on the fifth guide surface 207c of the retainer 201g contacts the first inner peripheral surface 215 of the outer ring 185. To do.
In contact of the convex portion 222 with the first inner peripheral surface 215, the fifth guide surface 207c on which the convex portion 222 is formed is in contact with the fifth guide surface 207c on which the convex portion 222 is not formed. Since the area becomes smaller, the solid frictional resistance becomes smaller.
When the solid frictional resistance due to the contact at the time of guide becomes small, the energy loss at the bearing 180g caused by the cage 210g becomes small, and the rotational energy of the balance with hairspring 140 suppresses the reduction.
When the rotational energy of the balance with hairspring 140 is increased, the swing angle is increased, and the influence of the escapement error is reduced.
Therefore, the tilt energy of the retainer 201g with respect to the outer ring 185 can be reduced while suppressing the energy loss at the bearing 180g. Therefore, the rate variation can be further reduced, and the timekeeping accuracy of the movement 100 (portable watch) is further increased. It can be stabilized.

In the description of the present embodiment, the axial lengths of the plurality of convex portions 222 are the common length BA, but the axial lengths of the plurality of convex portions 222 may be different from each other. Moreover, although the height of the radial direction of the some convex part 222 was made into common height BC, the height of the radial direction of the some convex part 222 may each differ. However, in order to reduce the inclination of the retainer 201g with respect to the outer ring 185, it is desirable that the radial heights of the plurality of convex portions 222 be equal.
Further, in the description in the present embodiment, the convex portion 222 is provided on the cage 201g side and the outer ring 185 side is the first inner peripheral surface 215 as a simple one surface, but conversely, the convex portion is provided on the outer ring 185 side. The cage 201g side may be a simple outer peripheral surface.

(Eighth embodiment)
Next, an eighth embodiment of the present invention will be described. FIG. 23 is a sectional view (a) passing through the center line C of the bearing body according to the eighth embodiment of the present invention, and an enlarged view (b) taken along the enlarged line T in the figure. Since the basic structure of the bearing body 181h is the same as that of the first embodiment, only the portions different from the first embodiment are described in the following description.

23, the cage 201h is structured to be guided by the sixth guide surface 207d of the cage 201h with respect to the second inner peripheral surface 216 of the outer ring 185. In addition, convex portions 223 are formed on the second inner peripheral surface 216 in the circumferential direction.
Here, the length CA of the convex portion 223 in the surface direction with respect to the second inner peripheral surface 216 is smaller than the length CB in the axial direction of the second inner peripheral surface 216 before the convex portion 223 is formed.
Further, the height CC in the direction perpendicular to the surface of the second inner peripheral surface 216 of the convex portion 223 is such that when the retainer 201h is assembled into the bearing body 181h, a gap CD is formed between the sixth guide surface 207d. It is height.
Moreover, the number of the convex parts 223 should just be one or more in an axial direction and the circumferential direction, respectively. However, when there is only one convex part 223 in the circumferential direction, it is desirable that the entire circumference is connected. In addition, when there are a plurality of convex portions 223 in the circumferential direction, it is desirable that the pitch distance between adjacent convex portions 223 be equal.
Further, when there are a plurality of convex portions 223 in the axial direction, it is desirable that all of the plurality of convex portions 223 in the axial direction are in positions where they abut against the sixth guide surface 207d of the cage 201h.

  In a bearing 180h (not shown) provided with a bearing body 181h provided with a cage 201h, a shaft body 143 (medium-diameter shaft portion 145) normally rotates around the central axis C. At this time, since the spherical body 183 is arranged on the bearing body 181h, the medium-diameter shaft portion 145 can smoothly rotate about the axis.

When the shaft body 143 rotates, the sphere 183 rolls while being enclosed in the third through holes 205 provided at equal intervals in the cage 201h, so that the sphere 183 is held at a constant pitch distance. It is possible to stably roll in the circumferential direction along the second support surface 206 of the diameter shaft portion 145 (small diameter shaft portion 147).
Further, since the cage 201h is guided by the outer ring 185, the inclination of the cage 201h with respect to the outer ring 185 can be reduced. As a result, the cage 201h does not collide with the shaft body 143 or the outer ring 185 at locations other than the convex portion 223. Therefore, it is possible to suppress bearing loss when the shaft body 143 is in rotational contact with the bearing 180h, and it is possible to reduce torque fluctuations and rotation cycle fluctuations of the shaft body 143. Therefore, it is possible to stabilize the timing accuracy of the movement 100 (portable watch) by suppressing fluctuations in the swing angle and the rate.

  Furthermore, in the present embodiment, the cage 201h is structured to be guided by the convex portion 223 of the cage 201h with respect to the second inner peripheral surface 216 of the outer ring 185. Further, the second inner peripheral surface 216 has a configuration in which convex portions 223 are formed in the circumferential direction.

According to the configuration of the present embodiment, when the cage 201h is guided by the outer ring 185, the sixth guide surface 207d of the cage 201h contacts the convex portion 223 formed on the second inner peripheral surface 216 of the outer ring 185. To do.
In contact of the convex portion 223 with the sixth guide surface 207d, the second inner peripheral surface 216 formed with the convex portion 223 is compared with the second inner peripheral surface 216 where the convex portion 223 is not formed. Since the contact area is small, the solid frictional resistance is small.
When the solid frictional resistance due to the contact at the time of guide becomes small, the energy loss at the bearing 180h caused by the cage 210h becomes small, and the rotational energy of the balance with hairspring 140 suppresses the reduction.
When the rotational energy of the balance with hairspring 140 is increased, the swing angle is increased, and the influence of the escapement error is reduced.
Therefore, the tilt energy of the retainer 201h with respect to the outer ring 185 can be reduced while suppressing the energy loss at the bearing 180h, so that the rate variation can be further reduced, and the timekeeping accuracy of the movement 100 (portable watch) is further increased. Can be stabilized

In the description of the present embodiment, the length in the surface direction of the plurality of convex portions 223 relative to the second inner peripheral surface 216 is the common length CA, but the second inner peripheral surface 216 of the plurality of convex portions 223 is used. The lengths in the surface direction relative to may be different. Moreover, although the height of the direction perpendicular | vertical to the surface with respect to the 2nd internal peripheral surface 216 of the some convex part 223 was made into common height CC, it is perpendicular | vertical to a surface with respect to the 2nd internal peripheral surface 216 of the some convex part 223. The height in the direction may be different. However, in order to reduce the inclination of the cage 201h with respect to the outer ring 185, it is desirable that the radial heights of the plurality of convex portions 223 are equal.
Further, in the description in the present embodiment, the convex portion 223 is provided on the outer ring 185 side and the cage 201h side is the sixth guide surface 207d as a simple one surface, but conversely, the convex portion is provided on the cage 201h side. Thus, the outer ring 185 side may be a simple inner peripheral surface.

The technical scope of the present invention is not limited to the above-described embodiments, and includes those in which various modifications are made to the above-described embodiments without departing from the spirit of the present invention. In other words, the configuration described in the above-described embodiment is merely an example, and can be changed as appropriate. Moreover, you may combine each embodiment mentioned above suitably.
For example, a metal or a resin can be used as the material for the cage.

105a, 105b, 105c, 105d, 105e ... bearing unit 143 ... shaft body 144, 145 ... medium diameter shaft portion 147 ... small diameter shaft portion 180a, 180b, 180c, 180d, 180e ... bearings 181a, 181b, 181c, 181d, 181e ... Bearing body 183 ... Sphere 185 ... Outer ring 187 ... First support surface 201a, 201b, 201c, 201d, 201e ... Retainer 206 ... Second support surface 207a, 207b, 207c, 207d ... Third guide surface, fourth guide surface, 5th guide surface, 6th guide surface 203, 208, 211 ... 1st outer peripheral surface, 2nd outer peripheral surface, 3rd outer peripheral surface 204, 215, 216 ... 3rd inner peripheral surface, 1st inner peripheral surface, 2nd inner surface Circumference

Claims (12)

A shaft that rotates about its axis;
A bearing unit for a timepiece comprising a bearing for rotatably supporting the shaft body,
The bearing includes at least three or more spheres arranged along the circumferential direction of the shaft body so as to be able to contact the outer peripheral surface of the shaft body;
An outer ring that holds the sphere with the shaft,
A cage that is disposed along an outer peripheral surface of the shaft body between the shaft body and the outer ring and encloses the spheres at regular intervals;
The retainer includes a guide portion between the shaft body and the outer ring ,
The guide portion contacts the outer peripheral surface of the shaft body at one or more locations,
Either the contact surface of the guide portion with the outer peripheral surface of the shaft body or the outer peripheral surface of the shaft member in contact with the guide portion includes a concave portion or a convex portion. . The shaft body includes a tip portion of the shaft body that is a straight portion, and a shaft main body portion that is larger than the diameter of the straight portion and that is connected to the straight portion,
The timepiece bearing unit according to claim 1, wherein the guide portion is substantially parallel to at least one of the tip portion and the shaft main body portion . The timepiece bearing unit according to claim 1 , wherein the guide portion abuts on an inner peripheral surface of the outer ring at one or more locations . The outer ring includes a central inner peripheral portion that comes into contact with the guide portion of the cage on the distal end side of the shaft body,
The timepiece bearing unit according to claim 3 , wherein the guide portion is substantially parallel to the central inner peripheral portion . The outer ring includes an outer peripheral inner peripheral portion that comes into contact with a guide portion of the cage on the shaft main body side of the shaft body,
The timepiece bearing unit according to claim 3 , wherein the guide portion is substantially parallel to the outer peripheral inner peripheral portion . Contact surface between the inner peripheral surface of the outer ring of the guide portion, or either one of the inner peripheral surface of the outer ring abuts on the guide portion from claim 3, further comprising a concave or convex portion The timepiece bearing unit according to claim 5 . The timepiece bearing unit according to any one of claims 1 to 6 , wherein a material of the cage is a metal . The timepiece bearing unit according to claim 7 , wherein the metal is any one of mild steel, brass, phosphor bronze, and stainless steel . The watch bearing unit according to any one of claims 1 to 6 , wherein a material of the cage is resin . The said resin is either engineering plastics, such as a polyacetal, polyamide, a fluororesin, or polyetheretherketone, or composite materials, such as a glass fiber reinforced plastic or a carbon fiber reinforced plastic, The Claim 9 characterized by the above-mentioned. Watch bearing unit. A watch movement with a barrel, watch wheel, escape wheel, ankle and balance,
A timepiece bearing unit according to any one of claims 1 to 10 is used for at least the balance of the balance with a balance . The movement according to claim 11;
A timepiece comprising a casing containing the movement .

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