JP2015222237A - Balance, speed governor, movement, and timepiece - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a balance, a speed governor, a movement and a timepiece, capable of reducing a thickness.SOLUTION: A balance includes: a balance staff 28 whose axial both ends are rotatably supported by vibration proof bearing units 5A, 5B, and which rotates together with a balance wheel 20; a first connection part 31 to which a balance spring 16 is connected through a collet 18; and a second connection part 32 to which a roller 35 is connected. In the first connection part 31 and the second connection part 32, provided are a first space part 41 and a second space part 42 in which each first cylindrical parts 56a of the vibration proof bearing units 5A, 5B is arranged, respectively. The first space part 41 and the second space part 42 are provided over the whole circumference in the circumferential direction of the balance staff 28.

Description

  The present invention relates to a balance with a balance, a speed governor, a movement, and a timepiece.

  It is known that the mechanical timepiece includes a speed governor for controlling the rotation of the barrel wheel, the second wheel, the third wheel and the fourth wheel constituting the front train wheel. A typical governor includes a balance wheel, a balance spring that is the center of rotation of the balance wheel, a balance spring that is formed in a spiral shape and rotates the balance wheel by expansion and contraction, a swinging seat that rotates together with the balance wheel, and a beard. A balance with a hair ball that truly fixes the mainspring to the balance is provided.

  A pair of vibration-resistant bearing mechanisms (bearing units) are provided at both ends of the balance so as to enclose the tenon. The pair of vibration-resistant bearing mechanisms support the balance with the balance of the balance about the center axis of the balance (see, for example, Patent Document 1).

JP 2013-88178 A

  Incidentally, a mechanical timepiece such as a wristwatch has a function as a decoration in addition to a function of displaying time. For this reason, depending on the user's preference, a thin movement is required. However, in the prior art, a pair of bearing units, a whisker and a swing seat are arranged between the balance wheel and the bearing unit so as to be aligned in the axial direction. For this reason, the separation distance between the balance wheel and the pair of bearing units is equal to or greater than the thickness of the whistle ball and the swing seat, respectively. Therefore, there is room for improvement in terms of further thinning the movement and the watch.

  Therefore, the present invention has been made in view of the above circumstances, and an object thereof is to provide a balance with a balance, a speed governor, a movement, and a timepiece that can be reduced in thickness.

  In order to solve the above-mentioned problems, the balance of the present invention is such that at least one end in the axial direction is rotatably supported by a bearing unit, and a shaft member that rotates together with the balance wheel and at least one mechanical component that transfers power are connected. And a space portion in which at least a part of the bearing unit is disposed is provided in the connection portion.

  According to the present invention, since the connection portion is provided with the space portion in which at least a portion of the bearing unit is disposed, by disposing a portion of the bearing unit inside the space portion, the radial direction of the shaft member can be increased. It can be arranged so that the connection portion and a part of the bearing unit overlap each other. As a result, the separation distance between the balance wheel and the bearing unit becomes shorter than the thickness of the connection part. Therefore, when the balance of the present invention is mounted on a movement for a watch, the movement and watch are made thinner compared to the conventional technology. can do.

  Moreover, the said space part is provided over the circumferential direction of the said shaft member, It is characterized by the above-mentioned.

  According to the present invention, a part of the bearing unit can be reliably arranged in the space. Therefore, the movement and the watch can be thinned.

  The balance spring is provided on one side in the axial direction from the balance wheel and rotates the balance wheel, and the swing seat is provided on the other side in the axial direction from the balance wheel. A mechanical part includes the hairspring and the swing seat, and the space portion includes a first connection portion to which the hairspring is connected and a second connection portion to which the swing seat is connected. It is characterized by being provided in at least one of them.

  According to the present invention, the space portion is provided in at least one of the first connection portion to which the hairspring is connected and the second connection portion to which the swing seat is connected. By disposing a part of the bearing unit, it is possible to dispose so that at least one of the first connection part and the second connection part overlaps a part of the bearing unit when viewed from the radial direction of the shaft member. Thereby, when the balance of the present invention is mounted on a movement for a timepiece, the movement and the timepiece can be made thinner as compared with the prior art.

  A balance spring which is provided on one side in the axial direction from the balance wheel and rotates the balance wheel; a hair ball to which one end of the balance spring is fixed; and the other in the axial direction from the balance wheel A swinging seat provided on a side, wherein the mechanical part includes the hairspring and the swinging seat, and the space portion is a first to which the hairspring is connected via the hairball. It is characterized by being provided in at least one of the connection part and the second connection part to which the swing seat is connected.

  According to the present invention, the space portion is provided in at least one of the first connection portion to which the whiskers are connected and the second connection portion to which the swing seat is connected. By disposing a part of the bearing unit, it is possible to dispose so that at least one of the first connection part and the second connection part overlaps a part of the bearing unit when viewed from the radial direction of the shaft member. As a result, the separation distance between the balance wheel and the bearing unit is shorter than the thickness of at least one of the ball and the swing seat. Therefore, when the balance of the present invention is mounted on a watch movement, it is compared with the prior art. Thus, the movement and the watch can be thinned.

  A speed governor according to the present invention includes the balance with the balance and the pair of bearing units.

  According to the present invention, the speed governor can be thinned.

  Further, at least one of the pair of bearing units is a vibration-resistant bearing unit that absorbs an impact acting on the bearing portion.

  According to the present invention, for example, even when an impact is applied from the outside, it is possible to absorb the impact and prevent the shaft member and the bearing portion from being damaged. Therefore, the speed governor can be thinned and has excellent durability.

  Further, the pair of bearing units and the balance wheel are opposed to each other without interposing other parts.

  According to the present invention, since no components are provided between the bearing unit and the balance wheel, the speed governor can be further reduced in thickness by arranging the bearing unit and the balance wheel as close as possible.

  The movement of the present invention is characterized by including the above-described speed governor.

  According to the present invention, by providing the speed governor described above, the movement can be made thinner as compared with the prior art.

  In addition, a carriage unit that rotates the governor around a predetermined axis is provided.

  According to the present invention, the influence of the direction of gravity can be leveled by rotating the speed governor around a predetermined axis by the carriage unit. In other words, the movement of the present invention has a so-called tourbillon mechanism that can suppress a change in the vibration cycle of the balance with the direction of gravity, so that the movement can be reduced in thickness and has excellent timing accuracy. Can do.

  The timepiece of the present invention is characterized by including the above-described movement.

  According to the present invention, by providing the above-described thinned movement, a timepiece having excellent design can be obtained.

  According to the present invention, since the connection portion is provided with the space portion in which at least a portion of the bearing unit is disposed, by disposing a portion of the bearing unit inside the space portion, the radial direction of the shaft member can be increased. It can be arranged so that the connection portion and a part of the bearing unit overlap each other. As a result, the separation distance between the balance wheel and the bearing unit becomes shorter than the thickness of the connection part. Therefore, when the balance of the present invention is mounted on a movement for a watch, the movement and watch are made thinner compared to the conventional technology. can do.

It is an external view of the timepiece according to the first embodiment. It is a top view when the movement of the timepiece is viewed from the front side. It is sectional drawing along the AA line of FIG. FIG. 4 is an enlarged view around a vibration-proof bearing unit in FIG. 3. It is side surface sectional drawing of the movement of the timepiece which concerns on the modification of 1st embodiment. It is side surface sectional drawing of the movement of the timepiece which concerns on 2nd embodiment. It is side surface sectional drawing of the movement of the timepiece which concerns on 3rd embodiment. It is side surface sectional drawing of the movement of the timepiece which concerns on 4th embodiment.

(First embodiment)
Below, 1st embodiment of this invention is described using drawing.
In the following, a mechanical wristwatch (corresponding to “Clock” in the claims, hereinafter simply referred to as “Clock”) and a movement incorporated in the clock will be described, and then the details of the balance and speed governor constituting the movement will be described. explain.

(clock)
In general, a machine body including a driving part of a timepiece is referred to as a “movement”. A state in which a dial and hands are attached to the movement, and put into a watch case to form a finished product, is referred to as “complete” of the watch. Of the two sides of the base plate constituting the watch substrate, the side of the watch case with the glass, that is, the side with the dial is referred to as the “back side” of the movement. Of the two sides of the main plate, the side of the watch case with the case back, that is, the side opposite to the dial is referred to as the “front side” of the movement.

FIG. 1 is an external view of a timepiece 1 according to the first embodiment.
As shown in FIG. 1, a complete timepiece 1 according to the present embodiment includes a movement 100 and a dial 11 having a scale indicating time information in a timepiece case 3 made of a case back cover and glass 2 (not shown). And a pointer including an hour hand 12 indicating the hour and a minute hand 13 indicating the minute. The dial 11 has a date window 11a for clearly indicating a number representing a date. Thereby, the timepiece 1 can check the date in addition to the time.

FIG. 2 is a plan view of the movement 100 of the timepiece 1 when viewed from the front side. In FIG. 2, in order to make the drawing easy to see, some of the timepiece components constituting the movement 100 are not shown, and each timepiece component is shown in a simplified manner.
As shown in FIG. 2, the movement 100 of the mechanical timepiece has a base plate 144 that constitutes a substrate. A winding stem 110 is rotatably incorporated in the winding stem guide hole 102 of the main plate 144. The position of the winding stem 110 in the axial direction of the winding stem 110 is determined by a switching device including the setting lever 103, the yoke 105, the yoke spring 107, and the back presser 109.
When the winding stem 110 is rotated, the hour wheel 112 is rotated through the rotation of the clutch wheel (not shown). The round hole wheel 114 and the square hole wheel 116 are sequentially rotated by the rotation of the hour wheel 112, and the mainspring (not shown) accommodated in the barrel complete 120 is wound up.

In the barrel 120, tenons (not shown) projecting from both ends of the barrel barrel, which is a shaft, are pivotally supported by the ground plate 144 and the barrel holder 134, respectively. It is supported in a rotatable manner. In the second wheel 124, the third wheel 126, the fourth wheel 128, and the escape wheel 130, tenons (not shown) protruding from both ends of the respective shaft portions are respectively connected to the base plate 144 and the train wheel bridge 136. By being pivotally supported, the base plate 144 and the train wheel bridge 136 are rotatably supported.
When the barrel wheel 120 is rotated by the restoring force of the mainspring, the second wheel 124, the third wheel 126, the fourth wheel 128, and the escape wheel 130 are sequentially rotated by the rotation of the barrel wheel 120. The barrel wheel 120, the second wheel 124, the third wheel 126, and the fourth wheel 128 constitute a front wheel train.

When the center wheel & pinion 124 is rotated, a cylindrical pinion (not shown) is simultaneously rotated based on the rotation, and a minute hand 13 (see FIG. 1) attached to the cylindrical pinion indicates “minute”. .
Further, the hour wheel (not shown) is rotated through the rotation of the minute wheel (not shown) based on the rotation of the hour pinion, and the hour hand 12 (see FIG. 1) attached to the hour wheel is “hour”. Is displayed.

The escapement speed governor 140 for controlling the rotation of the front train wheel is constituted by the escape wheel 130, the ankle 142, and the speed governor 7 including the balance 10.
Teeth 132 are formed on the outer periphery of the escape wheel & pinion 130. The ankle 142 is rotatably supported between the main plate 144 and the ankle receiver 138, and includes a pair of stones 142a and 142b. The escape wheel 130 temporarily stops in a state where one pallet 142a of the ankle 142 is engaged with the teeth 132 of the escape wheel 130.
The governor 7 includes a balance 10 and a vibration-resistant bearing unit 5 that holds the balance 10 rotatably. The balance with hairspring 10 is rotatably supported by the vibration-proof bearing unit 5 according to this embodiment between the balance holder 104 and the main plate 144. The balance with hairspring 10 is reciprocally rotated at a constant period to alternately engage and release the one pallet 142a and the other pallet 142b of the ankle 142 with the teeth 132 of the escape wheel 130, and thereby the escape wheel. 130 is escaped at a predetermined cycle. The details of the balance with hairspring 10 and the vibration-proof bearing unit 5 will be described later.

  Under such a configuration, after winding the mainspring (not shown) accommodated in the barrel complete 120 using the winding stem 110, the barrel complete 120 is rotated by the rotational force when the mainspring is rewound. As the barrel wheel 120 rotates, the second wheel 124 engaged therewith rotates. When the center wheel & pinion 124 rotates, the center wheel & pinion 126 that meshes with the center wheel rotates. When the third wheel & pinion 126 rotates, the fourth wheel & pinion 128 meshing therewith rotates. When the fourth wheel & pinion 128 rotates, the escapement governor 140 is driven. When the escapement governor 140 is driven, the center wheel & pinion 124 is controlled to make one rotation in one hour.

(Tempo)
FIG. 3 is a schematic cross-sectional view along the line AA in FIG. In FIG. 3, each component of the balance with hairspring 10 is simplified for easy understanding of the drawing.
As shown in FIG. 3, the balance with hairspring 10 includes a main balance wheel 20, a hairspring 16 (corresponding to “mechanical part” in the claims), a balance stem 28, and a swing seat 35 (“mechanical part in the claim”). ”). In the following description of the balance with hairspring 10, the center of rotation when the balance 10 is reciprocally rotated is referred to as the central axis O, the direction along the central axis O is referred to as the axial direction, and the direction orthogonal to the central axis O is referred to as the radial direction. The direction around the central axis O is referred to as the circumferential direction. In FIG. 3, the upper side of the paper surface with the base plate 144 interposed therebetween is the front side of the movement 100, and the lower side of the paper surface with the base plate 144 interposed therebetween is the back side of the movement 100.

The balance wheel 20 is made of a metal material such as beryllium copper or brass, and includes a balance wheel main body 21 formed in a ring shape. The central axis of the balance wheel main body 21 coincides with the central axis O which is the center of rotation of the balance 10.
As shown in FIG. 2, four arm portions 23 (23 a to 23 d) are provided inside the balance wheel main body portion 21 along the radial direction toward the central axis O. The four arm portions 23 a to 23 d are formed at substantially equal intervals so as to have a 90 ° pitch in the circumferential direction of the balance wheel main body portion 21. In addition, time adjustment weights 22 are respectively provided at connection portions between the balance wheel main body 21 and the arm portions 23a to 23d. The time adjusting weight 22 is a weight provided for adjusting the balance and moment of inertia of the balance wheel 20 and is rotatable around a guide axis parallel to the central axis O, for example.

As shown in FIG. 3, a fitting hole 24 a coaxial with the central axis O is formed in the connecting portion 24 of the four arm portions 23 a to 23 d inside the balance wheel main body portion 21.
On the front side of the movement 100 in the connecting portion 24 (upper side in FIG. 3), around the fitting hole 24a, a first connecting portion 31 coaxial with the central axis O (“first connecting portion” in the claims) Equivalent). The first connecting portion 31 is an annular convex portion that protrudes from the connecting portion 24 toward the front side of the movement 100. The first connecting portion 31 is fitted with a ball 18 described later.
A first space portion 41 (corresponding to a “space portion” in the claims) is provided inside the first connecting portion 31 in the radial direction. The first space portion 41 is formed over the entire circumference in the circumferential direction of the balance stem 28 on the front side of the movement 100 with respect to the connecting portion 24.

A second connecting portion 32 (the “second connecting portion” in the claims) on the back side of the movement 100 in the connecting portion 24 (the lower side in FIG. 3) and around the fitting hole 24 a is coaxial with the central axis O. Is equivalent). The second connecting portion 32 is an annular convex portion that protrudes from the connecting portion 24 toward the back side of the movement 100. A swing seat 35 described later is disposed on the outer side in the radial direction from the second connection portion 32.
A second space portion 42 (corresponding to a “space portion” in the claims) is provided on the inner side in the radial direction of the second connection portion 32. The second space portion 42 is formed over the entire circumference in the circumferential direction of the balance stem 28 on the back side of the movement 100 with respect to the connecting portion 24.

The balance wheel 20 includes a balance stem 28 (corresponding to a “shaft member” in the claims) coaxial with the central axis O. The balance stem 28 is a rod-shaped member made of a metal material such as iron.
The balance stem 28 includes tenons 29 (29a, 29b) that are tapered at both ends in the axial direction. Tensels 29a and 29b at both ends of the balance stem 28 are supported so as to be rotatable around the central axis O by vibration-proof bearing units 5 described later.
The balance wheel 20 is fixed to the balance stem 28 by, for example, external fitting press-fitting. Thereby, the balance wheel 20 and the balance stem 28 are integrated.

The hairspring 16 is a thin spiral spring formed of a metal material such as iron, nickel, or niobium, and is disposed on the front side of the movement 100 with respect to the balance wheel 20. The hairspring 16 is formed along a so-called Archimedes curve as viewed in the axial direction.
The inner end 16a of the hairspring 16 is connected to the balance wheel 20 via a hair ball 18 described later. Further, the outer end portion 16 b of the hairspring 16 is fixed to a beard 106 that protrudes from the balance 104 to the back side of the movement 100. The hairspring 16 rotates the balance wheel 20 by expanding and contracting in a state where the outer end portion 16 b is fixed to the whiskers 106.

The whisker ball 18 is a C-ring-shaped member made of a metal material such as iron, stainless steel, or brass, and is fitted and fixed to the first connection portion 31. The inner end 16a of the hairspring 16 is fixed to the hair ball 18 by welding or the like, for example.
Like the balance wheel 20, the swing seat 35 is a ring-shaped member formed of a metal material such as stainless steel or brass, and is disposed on the outer side in the radial direction than the second connection portion 32. The swing seat 35 of the present embodiment is integrally formed with the balance wheel 20 at the corner portion between the connecting portion 24 and the second connection portion 32 of the balance wheel 20. In FIG. 3, the boundary between the swing seat 35 and the balance wheel 20 is indicated by a two-dot chain line.

On the outer side in the radial direction from the swing seat 35, for example, a rock stone 26 formed of ruby or the like is provided. The pendulum 26 protrudes from the connecting portion 24 of the balance wheel 20 toward the back side of the movement 100. The gangue 26 can be engaged and disengaged with respect to the ankle hook 143 a formed inside the stag 143 of the ankle 142. The pendulum 26 of the present embodiment is provided on the arm portion 23 a of the balance wheel 20, but may be provided on the swing seat 35.
The swing seat 35 is formed with a relief 35 a that is recessed from the radially outer side to the inner side at a position corresponding to the rock stone 26 and that is lowered by one step from the second connection portion 32. Tsukigata 35a functions as an escape portion that prevents the sword tip 143b of the ankle 142 from coming into contact with the swing seat 35 when the ankle 142 and the rocking stone 26 are engaged.

(Governor)
FIG. 4 is an enlarged view around the vibration-proof bearing unit 5 in FIG.
The governor 7 includes the balance 10 described above and a pair of vibration-resistant bearing units 5 (5A, 5B).
As shown in FIG. 4, the vibration-proof bearing units 5 </ b> A and 5 </ b> B support tenons 29 a and 29 b provided at both ends in the axial direction of the balance 28 so as to be rotatable around the central axis O. The pair of vibration-resistant bearing units 5 </ b> A and 5 </ b> B are fixed to the balance holder 104 and the main plate 144, respectively.

  The vibration-resistant bearing units 5 </ b> A and 5 </ b> B mainly include a bearing portion 50, a vibration-resistant bushing 56, and a vibration-resistant spring 59. Below, each component of the vibration-proof bearing unit 5 is demonstrated. In addition, one vibration-proof bearing unit 5A on the balance holder 104 side and the other vibration-proof bearing unit 5B on the base plate 144 side have the same structure. Therefore, in the following, one vibration-resistant bearing unit 5A on the balance receiver 104 side will be described in detail, and detailed description on the other vibration-resistant bearing unit 5B on the base plate 144 side will be omitted.

The bearing unit 50 includes a guide bush 53, a hole 51, and a receiving stone 52.
The guide bush 53 is a cylindrical member formed of, for example, a metal material such as iron or brass, and includes a first cylindrical portion 53a and a second cylindrical portion 53b.
A hole 51 is disposed inside the first cylinder portion 53a. A first taper surface 54a is formed in the first tube portion 53a at the outer corner of the opening. The first tapered surface 54a is formed, for example, over the entire circumference of the first cylindrical portion 53a, and is gradually inclined from the inner side to the outer side in the radial direction.

  The 2nd cylinder part 53b is arrange | positioned at the front side of the movement 100 rather than the 1st cylinder part 53a, and has a larger diameter than the 1st cylinder part 53a. A jewel 52 is disposed inside the second cylindrical portion 53b. A second tapered surface 54b is formed in the second cylindrical portion 53b at the outer corner of the connection portion with the first cylindrical portion 53a. The second tapered surface 54b is formed, for example, over the entire circumference of the second cylindrical portion 53b, and is gradually inclined from the inner side to the outer side in the radial direction.

  The hole stone 51 is a substantially circular member in plan view formed of, for example, ruby and has a through hole 51a at the center. The inner diameter of the through hole 51a of the hole 51 is large enough to allow the tenon 29a to be inserted. The hole 51 is formed in a size that can be press-fitted and fixed to the first tube portion 53 a of the guide bush 53.

  The receiving stone 52 is a member having a substantially circular shape in a plan view formed of, for example, ruby. The stone 52 is disposed on the front side of the movement 100 with respect to the hole 51, and is opposed to the end face in the axial direction of the tenon 29a. The stone 52 is placed on the end portion of the first cylinder portion 53a on the inner side of the second cylinder portion 53b, and closes the opening of the first cylinder portion 53a. A main surface facing the front side of the movement 100 in the stone 52 is formed in a convex curved surface shape.

  The guide bushing 53 is accommodated in a vibration-proof bushing 56. The vibration-proof bushing 56 is a bottomed cylindrical member having an opening 58 on the outer side in the axial direction, and is formed of a metal material such as iron or brass, for example. The vibration-proof bushing 56 is fitted into the attachment hole of the balance holder 104, for example. The vibration-proof bushing 56 has a first cylinder part 56a and a second cylinder part 56b.

  The first cylindrical portion 56 a mainly surrounds the guide bush 53. A first tapered surface 57a and a second tapered surface 57b are formed on the inner surface of the first cylindrical portion 56a at positions corresponding to the first tapered surface 54a and the second tapered surface 54b of the guide bush 53, respectively. The first taper surface 57a and the second taper surface 57b of the vibration-proof bushing 56 are in surface contact with the first taper surface 54a and the second taper surface 54b of the guide bush 53, respectively.

  The 2nd cylinder part 56b is arrange | positioned at the front side of the movement 100 rather than the 1st cylinder part 56a, and has a larger diameter than the 1st cylinder part 56a. A flange 58a is formed in the opening 58 of the second cylindrical portion 56b. The flange portion 58a is formed so as to project radially inward in the opening portion 58 of the second cylindrical portion 56b.

  On the outer peripheral surface of the vibration-proof bushing 56, a step surface 56c is formed at a connection portion between the second tube portion 56b and the first tube portion 56a. The step surface 56 c is provided so as to face the front end surface 31 a of the first connection portion 31.

  A vibration-resistant spring 59 is provided in the opening 58 of the vibration-proof bushing 56. The vibration-resistant spring 59 is a flexible ring-shaped elastic member made of a metal material such as iron or nickel. The anti-vibration spring 59 has an outer edge portion disposed on the inner side in the axial direction than the flange portion 58a. The vibration-resistant spring 59 urges the stone 52 and the guide bush 53 toward the inner side in the axial direction.

Of the pair of anti-vibration bearing units 5A and 5B configured as described above, one anti-vibration bearing unit 5A on the balance support 104 side has the first cylindrical portion 56a of the anti-vibration bush 56 disposed inside the first space portion 41. Has been.
Furthermore, one vibration-proof bearing unit 5A and the balance wheel 20 are opposed to each other without interposing other parts. That is, by arranging the first cylindrical portion 56a of the vibration-proof bushing 56 in one vibration-proof bearing unit 5A inside the first space portion 41, the vibration-proof bearing unit 5A is first viewed from the radial direction of the balance 28. It arrange | positions so that the connection part 31 and a part of one vibration-proof bearing unit 5A may overlap. Thereby, the separation distance between the balance wheel 20 and the one vibration-proof bearing unit 5 </ b> A is shorter than the thickness of the first connection portion 31 and the whisker ball 18.

  In the other vibration-proof bearing unit 5 </ b> B on the ground plate 144 side, the first cylinder portion 56 a of the vibration-proof bushing 56 is disposed inside the second space portion 42. Furthermore, the other vibration-proof bearing unit 5B and the balance wheel 20 are opposed to each other without any other components. That is, by arranging the first cylindrical portion 56a of the vibration-proof bushing 56 in the other vibration-resistant bearing unit 5B inside the second space portion 42, the second connecting portion 32 and the other connection portion 32 are seen from the radial direction of the balance stem 28. It arrange | positions so that a part of vibration-proof bearing unit 5B may overlap. Thereby, the separation distance between the balance wheel 20 and the other vibration-proof bearing unit 5 </ b> B is shorter than the thickness of the second connection portion 32 and the swing seat 35.

By the way, when an impact load is applied from the outside, the position of the balance stem 28 may be displaced in the axial direction and the radial direction.
For example, when an impact load is applied to the balance stem 28 along the axial direction, the balance stem 28 is displaced along the axial direction, and the bearing portion 50 that supports the balance stem 28 also extends along the axial direction. Displace. On the other hand, since the vibration-resistant spring 59 that urges the bearing portion 50 toward the inner side in the axial direction is provided outside the bearing portion 50 in the axial direction, the bearing portion 50 is displaced along the axial direction. Even in this case, the bearing portion 50 is elastically supported and an impact load is absorbed. Further, for example, even when a large impact load against the urging force of the vibration-resistant spring 59 is applied, the step surface 56 c of the vibration-proof bushing 56, the tip surface 31 a of the first connection portion 31, and the step surface of the vibration-proof bushing 56 When 56c and one of the front end surfaces 32a of the second connection portion 32 abut, the movement of the balance wheel 20 and the balance stem 28 along the axial direction is restricted, and an impact load is absorbed.

  Further, for example, when an impact load is applied along the radial direction to the balance stem 28, the balance stem 28 is displaced along the radial direction, and the bearing portion 50 that supports the balance stem 28 also extends in the radial direction. Displaces along. Here, the first tapered surface 54a and the second tapered surface 54b of the guide bush 53 are in surface contact with the first tapered surface 57a and the second tapered surface 57b of the vibration-proof bushing 56, respectively. Therefore, the guide bush 53 is displaced obliquely toward the outside in the axial direction and the radial direction along the first tapered surface 57a and the second tapered surface 57b of the vibration-proof bushing 56. In contrast, a vibration-resistant spring 59 that biases the guide bush 53 in the axial direction is provided outside the guide bush 53 in the axial direction, so that the guide bush 53 extends outward in the axial direction and the radial direction. Even when it is displaced obliquely, the guide bush 53 is elastically supported and an impact load is absorbed. Further, for example, even when a large impact load that resists the biasing force of the vibration-resistant spring 59 is applied, the first cylindrical portion 56 a of the vibration-resistant bushing 56, the inner peripheral surface 31 b of the first connection portion 31, and the vibration-resistant bushing 56. When the first cylindrical portion 56a and at least one of the inner peripheral surfaces 32b of the second connecting portion 32 come into contact with each other, the movement along the radial direction of the balance wheel 20 and the balance stem 28 is restricted and the impact load is absorbed. .

(Effects of the first embodiment)
According to the present embodiment, the first connection portion 31 and the second connection portion 32 are provided with the first space portion 41 and the second space portion 42 in which a part of the vibration-proof bearing unit 5 is disposed, respectively. By arranging a part of the vibration-proof bearing units 5A and 5B inside the first space portion 41 and the second space portion 42, the first connection portion 31 and the second connection portion 32 are seen from the radial direction of the balance stem 28. And the vibration-proof bearing units 5A and 5B can be arranged so as to overlap each other. Thereby, the separation distance between the balance wheel 20 and the one vibration-proof bearing unit 5 </ b> A is shorter than the thickness of the first connection portion 31 and the whistle ball 18. Further, the separation distance between the balance wheel 20 and the other vibration-resistant bearing unit 5B is shorter than the thickness of the second connection portion 32 and the swing seat 35. Therefore, the balance 10, the speed governor 7, the movement 100, and the timepiece 1 can be reduced in thickness as compared with the prior art.

  Moreover, since the 1st space part 41 and the 2nd space part 42 are provided over the circumferential direction of the balance stem 28, even when the balance wheel 20 rotates, the 1st space part 41 and the 2nd space part It is possible to prevent interference between the peripheral wall 42 and the vibration-proof bearing units 5A and 5B. Therefore, the movement 100 and the timepiece 1 can be reduced in thickness while ensuring the timing accuracy.

  Further, since the vibration-proof bearing units 5A and 5B that absorb the impact acting on the bearing portion 50 are provided, for example, even when an impact is applied from the outside, the balance 28 and the bearing portion 50 are capable of absorbing the impact. It can be prevented from being damaged. Therefore, the speed governor 7 can be reduced in thickness and excellent in durability.

  In addition, the pair of vibration-resistant bearing units 5A and 5B and the balance wheel 20 are opposed to each other without interposing other parts. That is, since no parts are provided between the vibration-proof bearing units 5A and 5B and the balance wheel 20, the vibration-proof bearing units 5A and 5B and the balance wheel 20 are arranged as close as possible to further increase the speed of the speed governor 7. Thinning can be achieved.

  In addition, according to the present embodiment, by providing the movement 100 that is thinned, the timepiece 1 having excellent design can be obtained.

(Modification of the first embodiment)
Then, the modification of 1st embodiment is demonstrated.
FIG. 5 is a side cross-sectional view of a movement of a timepiece according to a modification of the first embodiment, and is a cross-sectional view corresponding to a cross section taken along the line AA of FIG.
In the first embodiment described above, the whisker ball 18 is fixed to the first connection part 31 of the balance wheel 20, and the whisker 106 is fixed to the balance holder 104.
On the other hand, as shown in FIG. 5, in the modified example of the first embodiment, the first embodiment is that the whisker ball 18 is fixed to the balance with hairspring 104 and the whiskers 106 are fixed to the balance wheel 20. It is different from the form. In the following, description of the same configuration as in the first embodiment is omitted.

The hair ball 18 is fixed to the balance with hairspring 104 through the vibration-proof bearing unit 5A. Specifically, the ball 18 is fixed to the first cylindrical portion 56a of the vibration-proof bushing 56 in the vibration-proof bearing unit 5A on the balance receiver 104 side by, for example, press-fitting or bonding.
The inner end portion 16 a of the hairspring 16 is connected to the hairball 18. That is, in the present modification, the whistle ball 18 itself to which the inner end portion 16 a of the hairspring 16 is fixed serves as the first connection portion 31.
The inner portion of the whistle ball 18 formed in a ring shape is a first space portion 41. In the first space portion 41, the first cylindrical portion 56a of the vibration-proof bushing 56 in one vibration-proof bearing unit 5A is disposed. Thereby, when viewed from the radial direction of the balance stem 28, the whistle ball 18 and a part of one vibration-proof bearing unit 5A are arranged so as to overlap each other. Further, the separation distance between the balance wheel 20 and the one vibration-proof bearing unit 5 </ b> A is shorter than the thickness of the whistle ball 18.

  The whisker 106 is fixed to the arm portion 23 a of the balance wheel 20. The outer end portion 16 b of the hairspring 16 is fixed to the balance wheel 20 via a whisker 106. The hairspring 16 rotates the balance wheel 20 by expanding and contracting in a state where the inner end portion 16a is fixed to the hairball 18.

(Effects of Modification of First Embodiment)
Also in the modification of the first embodiment, the same effect as that of the first embodiment can be obtained. That is, according to this modification, the whistle ball 18 itself is the first connection portion 31 and has the first space portion 41 in which the first cylindrical portion 56a of the vibration-proof bushing 56 in the vibration-proof bearing unit 5A is disposed. As seen from the radial direction of the balance stem 28, the whistle ball 18 and a part of one vibration-proof bearing unit 5A are arranged so as to overlap each other. Therefore, the separation distance between the balance wheel 20 and the one vibration-proof bearing unit 5 </ b> A is shorter than the thickness of the whistle ball 18 having the first connection portion 31. Further, the separation distance between the balance wheel 20 and the other vibration-resistant bearing unit 5B is shorter than the thickness of the second connection portion 32 and the swing seat 35. Therefore, the balance 10, the speed governor 7, the movement 100, and the timepiece 1 can be reduced in thickness as compared with the prior art.

(Second embodiment)
Next, the second embodiment will be described.
FIG. 6 is a side sectional view of the movement of the timepiece according to the second embodiment.
In the first embodiment described above, the whisker ball 18 is externally fitted and fixed to the first connection part 31 of the balance wheel 20.
On the other hand, as shown in FIG. 6, the second embodiment is different from the first embodiment in that the whistle ball 18 is fixed to the connecting portion 24 of the balance wheel 20.
In the following, description of the same configuration as in the first embodiment is omitted.

A fitting recess 25 is formed in the connecting portion 24 of the balance wheel 20. The fitting recess 25 is recessed in the axial direction. The fitting recess 25 may penetrate the balance wheel 20.
A fitting projection 18 a is formed on the whistle ball 18. The fitting convex portion 18 a is press-fitted into the fitting concave portion 25 of the balance wheel 20 when the whistle ball 18 is arranged coaxially with the central axis O. Accordingly, the whistle ball 18 is fixed to the front side of the movement 100 in the connecting portion 24 of the balance wheel 20.

The inner end portion 16 a of the hairspring 16 is connected to the hairball 18. That is, in the second embodiment, similarly to the modified example of the first embodiment, the hair ball 18 itself to which the inner end portion 16 a of the hairspring 16 is fixed serves as the first connection portion 31. Further, the inner portion of the whistle ball 18 is a first space portion 41. As seen from the radial direction of the balance stem 28, the whistle ball 18 and a part of one vibration-proof bearing unit 5A are arranged to overlap each other. The separation distance between the balance wheel 20 and the one vibration-proof bearing unit 5 </ b> A is shorter than the thickness of the whistle ball 18.
According to the second embodiment, the same effect as the first embodiment can be obtained. That is, the balance 10, the speed governor 7, the movement 100, and the timepiece 1 can be reduced in thickness as compared with the prior art.

(Third embodiment)
Next, a third embodiment will be described.
FIG. 7 is a side sectional view of the movement of the timepiece according to the third embodiment.
In the first embodiment described above, the whisker ball 18 is externally fitted and fixed to the first connection part 31 of the balance wheel 20.
On the other hand, as shown in FIG. 7, the third embodiment is different from the first embodiment in that the ball 18 is integrally formed with the balance wheel 20.
In the following, description of the same configuration as in the first embodiment is omitted.

  The whistle ball 18 is integrally formed with the balance wheel 20 on the front side of the movement 100 in the connecting portion 24 of the balance wheel 20. The inner end portion 16 a of the hairspring 16 is connected to the hairball 18. That is, in the third embodiment, as in the modification of the first embodiment and the second embodiment, the ball 18 itself to which the inner end portion 16 a of the hairspring 16 is fixed becomes the first connection portion 31. Yes. According to the third embodiment, the same effect as the first embodiment can be obtained. That is, the balance 10, the speed governor 7, the movement 100, and the timepiece 1 can be reduced in thickness as compared with the prior art. Further, by integrally forming the whistle ball 18 and the balance wheel 20, the number of parts can be reduced.

(Fourth embodiment)
Next, a fourth embodiment will be described.
FIG. 8 is a side sectional view of the movement of the timepiece according to the fourth embodiment.
In the first embodiment described above, the speed governor 7 including the balance 10 and the vibration-proof bearing units 5A and 5B is fixed to the main plate 144 and the balance receiver 104.
On the other hand, as shown in FIG. 8, in the fourth embodiment, the speed governor 7 including the balance 10 and the vibration-proof bearing units 5A and 5B is mounted on the carriage unit 70 that can rotate around the central axis O. In the point which is carried out, it differs from the modification of 1st embodiment and 1st embodiment.
In addition, below, description is abbreviate | omitted about the structure similar to the modification of 1st embodiment and 1st embodiment.

  The carriage unit 70 includes an upper carriage 71 disposed on the front side (upper side in FIG. 8) of the movement 100 with respect to the base plate 144 and a lower carriage 72 disposed on the back side of the movement 100 with respect to the upper carriage 71 via the balance wheel 20. A connecting pin 73 that connects the upper carriage 71 and the lower carriage 72, and a ring-shaped fixed gear 76.

  Each of the upper carriage 71 and the lower carriage 72 is a frame-like member formed of a metal material such as stainless steel, iron, aluminum, titanium, or brass. The upper carriage 71 and the lower carriage 72 are fixed to each other by a connecting pin 73 and a bolt 73a with a predetermined gap therebetween. Between the upper carriage 71 and the lower carriage 72, the speed governor 7 including the balance 10 and the vibration-proof bearing units 5A and 5B is mounted.

The upper carriage 71 and the lower carriage 72 are formed with fixing holes 71a and 72a coaxial with the central axis O, respectively. The vibration-proof bearing units 5A and 5B are fitted and fixed in the fixing holes 71a and 72a, respectively.
Lower carriage teeth 72 b are formed on the outer peripheral edge of the lower carriage 72. The lower carriage tooth portion 72b meshes with the fourth intermediate wheel 129. The fourth intermediate wheel 129 constitutes a front wheel train together with the barrel wheel 120, the second wheel 124, the third wheel 126, and the fourth wheel 128 (all refer to FIG. 2). The fourth intermediate wheel 129 transmits the power from the barrel complete 120 to the lower carriage 72.

  Here, the hair ball 18 of the balance with hairspring 10 is fixed to the upper carriage 71 via the vibration-proof bearing unit 5A. The inner end portion 16 a of the hairspring 16 is connected to the hairball 18. That is, in the fourth embodiment, as in the modified example of the first embodiment, the hair ball 18 itself to which the inner end portion 16 a of the hairspring 16 is fixed serves as the first connection portion 31. Further, the inner portion of the whistle ball 18 is a first space portion 41. As seen from the radial direction of the balance stem 28, the whistle ball 18 and a part of one vibration-proof bearing unit 5A are arranged so as to overlap each other. The separation distance between the balance wheel 20 and the one vibration-proof bearing unit 5 </ b> A is shorter than the thickness of the whistle ball 18.

A escape wheel 130 is held between the upper carriage 71 and the lower carriage 72 via a bearing. The escape wheel & pinion 130 is rotatable around an axis P parallel to the central axis O.
A fixed gear 76 is disposed between the upper carriage 71 and the lower carriage 72. The fixed gear 76 is formed in a ring shape whose outer diameter is larger than the outer diameters of the upper carriage 71 and the lower carriage 72. A tooth portion 77 is formed on the inner peripheral surface of the fixed gear 76. The toothed portion 77 of the fixed gear 76 meshes with the escape hook 131 of the escape wheel 130.

A ring-shaped bearing 80 is arranged on the main plate 144 so as to be coaxial with the central axis O.
The bearing 80 includes an outer ring 81, an inner ring 82, and rolling elements 83 that allow the outer ring 81 and the inner ring 82 to rotate relative to each other. The inner diameter of the bearing 80 is larger than the outer diameter of the vibration-proof bearing units 5A and 5B.

The outer ring 81 is fixed to the bearing holding hole 145 formed in the base plate 144 with, for example, a bolt or the like.
A lower carriage 72 of the carriage unit 70 is fixed to the inner ring 82 via bolts or the like, for example.
The rolling elements 83 are spherical bodies, and a plurality of rolling elements 83 are disposed between the outer ring 81 and the inner ring 82. The inner ring 82 can rotate around the central axis O via the rolling elements 83 with respect to the outer ring 81 fixed to the main plate 144.
The carriage unit 70 is rotatable about a central axis O (corresponding to a “predetermined axis” in the claims) with respect to the base plate 144 via a bearing 80.

The movement 100 configured as described above operates as follows.
When the barrel wheel 120 (see FIG. 2) rotates due to the restoring force of the mainspring, the power is transmitted by the rotation of the barrel wheel 120, and the fourth intermediate wheel 129 rotates. In addition, the lower carriage 72 that meshes with the fourth intermediate wheel 129 rotates with the upper carriage 71 about the center axis O as the center of rotation. Further, as the upper carriage 71 and the lower carriage 72 rotate, the escape wheel & pinion 130 rotates (revolves) around the central axis O. Here, the escape wheel 131 of the escape wheel & pinion 130 meshes with the tooth portion 77 of the fixed gear 76. Accordingly, the escape wheel & pinion 130 rotates (revolves) around the central axis O and rotates (rotates) around the axis P. As a result, the escapement governor 140 (see FIG. 2) is driven. Further, the escapement governor 140 rotates around the central axis O as the upper carriage 71 and the lower carriage 72 rotate. That is, the movement 100 of the fourth embodiment includes a so-called tourbillon mechanism 85 in which the escapement governor 140 rotates around the central axis O.

  According to the fourth embodiment, the influence of the direction of gravity can be leveled by rotating the speed governor 7 around the central axis O by the carriage unit 70. That is, the movement 100 according to the fourth embodiment includes a so-called tourbillon mechanism 85 that can suppress a change in the vibration period of the balance with the direction of gravity, so that the movement 100 can be reduced in thickness and has excellent timekeeping accuracy. Movement 100.

  The present invention is not limited to the above-described embodiment described with reference to the drawings, and various modifications can be considered within the technical scope thereof.

The movement 100 according to the first embodiment and the modification of the first embodiment includes a first space part 41 formed in the first connection part 31, a second space part 42 formed in the second connection part 32, and It was equipped with. On the other hand, it is good also as the movement 100 provided only with the 1st space part 41 formed in the 1st connection part 31 like 4th embodiment.
Moreover, it is good also as a movement provided only with the 2nd space part formed in the 2nd connection part. That is, the movement according to the present invention only needs to include at least one connection portion and space portion.
Moreover, you may combine each embodiment. Therefore, for example, by combining the first embodiment and the fourth embodiment, the movement 100 including the first space portion 41 and the second space portion 42 and the tourbillon mechanism 85 may be used.

  In each embodiment, the case of a so-called club tooth lever escapement has been described, but the present invention is not limited to a club tooth lever escapement. Accordingly, other types of escapement other than the club tooth lever escapement, such as a so-called detent escapement or coaxial escapement, may be used.

The material and manufacturing method for forming the hairspring 16 and the balance wheel 20 are not limited to the embodiments. Therefore, for example, the hairspring 16 and the balance wheel 20 may be formed by so-called MEMS (Micro Electro Mechanical Systems) such as dry etching or electroforming using a material mainly containing silicon or silicon nitride.
Moreover, in each embodiment, the beard ball 18 and the hairspring 16 are formed separately. On the other hand, the beard ball 18 and the hairspring 16 may be integrally formed.

  In each embodiment, the swing seat 35 is integrally formed with the balance wheel 20. On the other hand, the balance wheel 20 may be configured as a separate part from the swing seat 35. Further, in each embodiment, the rock stone 26 is fixed to the balance wheel 20, but the rock stone 26 may be fixed to the swing seat 35.

  In each embodiment, the balance 10 is rotatably supported by so-called vibration-resistant bearing units 5A and 5B. On the other hand, the bearing may be a normal bearing unit or a ball bearing that does not have a vibration proof function, instead of the vibration proof bearing units 5A and 5B.

  In the fourth embodiment, the tourbillon mechanism 85 is configured such that the carriage unit 70 rotates around the central axis O together with the speed governor 7. On the other hand, for example, the tourbillon mechanism 85 may be configured so that the carriage unit 70 rotates together with the speed governor 7 around a predetermined axis other than the central axis O.

  In addition, it is possible to appropriately replace the components in the above-described embodiments with known components without departing from the spirit of the present invention.

DESCRIPTION OF SYMBOLS 1 ... Clock 5,5A, 5B ... Vibration-resistant bearing unit (bearing unit) 7 ... Speed governor 10 ... Balance balance 16 ... Hairspring (machine part) 18 ... Beard ball 20. ··· balance wheel 28 · · · balance (shaft member) 31 · · · first connection portion (connection portion) 32 · · · second connection portion (connection portion) 35 · swing seat (mechanical parts) · · · .... First space part (space part) 42 ... Second space part (space part) 50 ... Bearing part 70 ... Carriage unit 100 ... Movement

Claims (10)

A shaft member that is rotatably supported by a bearing unit at least in one axial direction, and rotates with the balance wheel;
A connection part to which at least one machine part for transferring power is connected;
With
The balance with the connecting portion is provided with a space in which at least a part of the bearing unit is disposed.   The balance according to claim 1, wherein the space portion is provided in a circumferential direction of the shaft member. A balance spring provided on one side in the axial direction from the balance wheel and rotating the balance wheel;
A swing seat provided on the other side in the axial direction from the balance wheel;
With
The mechanical component includes the hairspring and the swing seat,
2. The space portion is provided in at least one of the first connection portion to which the hairspring is connected and the second connection portion to which the swing seat is connected. Or the balance according to 2. A balance spring provided on one side in the axial direction from the balance wheel and rotating the balance wheel;
A whistle ball to which one end of the hairspring is fixed;
A swing seat provided on the other side in the axial direction from the balance wheel;
With
The mechanical component includes the hairspring and the swing seat,
The space portion is provided in at least one of the first connecting portion to which the hairspring is connected via the whirling ball and the second connecting portion to which the swing seat is connected. The balance with hairspring according to claim 1 or 2, wherein the balance is characterized.   A speed governor comprising the balance according to claim 3 and the pair of bearing units.   The speed governor according to claim 5, wherein at least one of the pair of bearing units is a vibration-resistant bearing unit that absorbs an impact acting on the bearing portion.   The speed governor according to claim 5 or 6, wherein the pair of bearing units and the balance wheel are opposed to each other without interposing other parts.   A movement comprising the speed governor according to claim 5.   The movement according to claim 8, further comprising a carriage unit that rotates the governor around a predetermined axis.   A timepiece comprising the movement according to claim 8.

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