JP2017058248A - Pressing member, antishock bearing, movement, and timepiece - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pressing member, an antishock bearing, a movement, and a timepiece that are capable of improving shock resistance.SOLUTION: A pressing member 185 is provided in an antishock bearing 180 including: a jewel cap 184 disposed facing an end surface 21e in an axial direction of a balance staff 22; a mortise stone 183 through which coaks 21A, 21B of the balance staff 22 are inserted; a frame body 182 in which the jewel cap 184 and the mortise stone 183 are held; and a seat body 181 in which the frame body 182 is housed. The pressing member 185 is disposed outside the jewel cap 184 in an axial direction, holds the jewel cap 184, and is made of a viscoelastic material. A stationary portion of the pressing member 185 is provided on an inner surface of a locking frame portion 181d of the seat body 181, and an outer periphery 185a of the pressing member 185 is inserted to be fixed in a groove portion 181e.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a presser member, a vibration-proof bearing, a movement, and a timepiece.

  2. Description of the Related Art Conventionally, a rotating mechanical component such as a gear used for a mechanical timepiece such as a wristwatch is provided with a bearing so as to enclose an end portion of a shaft member. In particular, a so-called vibration-resistant bearing that can absorb an impact load from the outside that occurs, for example, at the time of dropping is used for the low-strength shaft (see, for example, Patent Document 1 and Patent Document 2).

  The vibration-proof bearings described in Patent Document 1 and Patent Document 2 are, for example, a hole stone into which a tenon of a shaft member such as a balance is inserted, a receiving stone formed so as to be capable of supporting an end of the tenon of the shaft member, A pressing spring (pressing member) that suppresses the movement of the stone in the axial direction outside. Hole stones, stones and presser springs are included in the frame. According to the vibration-proof bearings described in Patent Document 1 and Patent Document 2, since the presser spring that biases the stone receiving member toward the inner side in the axial direction is provided, the shaft member and the hole stone are displaced along the axial direction. Even in this case, the shaft member and the hole stone can be elastically supported and the impact load can be absorbed.

JP-A-52-38962 Japanese Patent No. 4598701

  However, in the prior art, for example, when a very large impact load generated during a fall is applied from the outside and the shaft member and the hole stone are greatly displaced along the axial direction, the displacement amount and the restoring force of the presser spring also increase. . At this time, the shaft member and the hole stone return vigorously, but an excessive load may be applied to the shaft member due to an excessive restoring force of the presser spring. In particular, when the shaft member is a spring, the spring is displaced in the axial direction and the radial direction due to an excessive restoring force of the presser spring, and the balance spring connected to the spring may be bent and plastically deformed. was there. Thus, in the prior art, a problem remains in terms of improving impact resistance.

  The present invention has been made in view of the above circumstances, and provides a presser member, a vibration-proof bearing, a movement, and a timepiece that can improve impact resistance.

  In order to solve the above-described problems, the presser member according to the present invention includes a stone that is opposed to the axial end surface of the shaft member, a hole stone through which an end of the shaft member is inserted, the stone, and the stone Provided in a vibration-proof bearing comprising a frame body that holds a hole stone and a seat body that accommodates the frame body, and at least a part thereof is disposed on the outer side in the axial direction than the stone; Is a holding member that is made of a viscoelastic material.

  According to the present invention, since the pressing member is made of a viscoelastic material, higher vibration damping performance can be obtained as compared with the prior art in which the pressing member is a metal spring. As a result, the presser member can absorb the displacement energy even if the stone is displaced due to an impact from the outside, etc., and can prevent the occurrence of excessive restoring force and the load applied to the stone and the shaft member. Can be suppressed. Therefore, by providing the pressing member according to the present invention in the vibration-proof bearing, it is possible to improve the impact resistance as compared with the conventional technique.

  Further, the vibration-proof bearing of the present invention holds a jewel that is opposed to the axial end surface of the shaft member, a hole stone through which the end of the shaft member is inserted, the stone and the hole stone. A frame body, a seat body in which the frame body is accommodated, and a pressing member at least a part of which is disposed on the outer side in the axial direction than the stone, and the stone is held. It is characterized by comprising a viscoelastic material.

  According to the present invention, since the pressing member is made of a viscoelastic material, higher vibration damping performance can be obtained as compared with the prior art in which the pressing member is a metal spring. As a result, the presser member can absorb the displacement energy even if the stone is displaced due to an impact from the outside, etc., and can prevent the occurrence of excessive restoring force and the load applied to the stone and the shaft member. Can be suppressed. Therefore, the shock resistance of the vibration-resistant bearing can be improved.

  In addition, an outer peripheral portion of the pressing member has a fixing portion that can be fixed to the seat body, and the pressing member is fixed to the fixing portion and disposed in a state of covering at least a part of the stone. It is characterized by.

  According to the present invention, by covering at least a part of the stone with the pressing member, it is possible to transmit the load generated when the stone is displaced by an external impact or the like to the pressing member. Therefore, the shock resistance of the vibration-resistant bearing can be improved.

  Further, the fixing portion is a groove portion provided on the inner surface of the seat body and being fixed by inserting an outer peripheral portion of the pressing member.

  According to the present invention, the presser member can be easily fixed to the seat body by simply inserting the outer peripheral portion of the presser member into the groove portion without providing a member for fixing. Therefore, a low-cost vibration-proof bearing that can improve the impact resistance can be obtained.

  Further, the fixing portion is an annular stopper that is screwed to the seat body and holds an outer peripheral portion of the pressing member.

  According to the present invention, after the pressing member is set on the seat body, the pressing member can be easily fixed by screwing the stopper as the fixing portion onto the seat body. Thereby, the assemblability and maintainability of the vibration-proof bearing can be improved.

  Further, the pressing member has a circular shape when viewed from the axial direction, and is arranged in a state of covering the entire surface of the stone.

  According to the present invention, since the entire surface of the stone can be covered with the pressing member, the load generated by the displacement of the stone due to an external impact or the like can be reliably transmitted to the pressing member. Therefore, the shock resistance of the vibration-resistant bearing can be significantly improved.

  The presser member has a polygonal shape when viewed from the axial direction, and a corner portion of the presser member is fixed to the seat body.

  According to the present invention, the pressing member can be easily fixed by fixing the corners of the outer peripheral portion of the pressing member to the seat body. Thereby, the assemblability and maintainability of the vibration-proof bearing can be improved.

  Moreover, the said pressing member is provided with the load absorption part interposed between the said frame and the said seat body in the radial direction of the said shaft member, It is characterized by the above-mentioned.

  According to the present invention, the load generated when the shaft member is displaced in the radial direction can be reliably absorbed by the load absorbing portion of the presser member. Therefore, the shock resistance of the vibration-resistant bearing can be significantly improved.

In addition, the movement of the present invention is characterized by including the vibration-proof bearing described above.
The timepiece of the present invention is characterized by including the above-described movement.

  ADVANTAGE OF THE INVENTION According to this invention, it can be set as the high performance movement and timepiece excellent in impact resistance.

  According to the present invention, since the pressing member disposed on the outer side in the axial direction than the stone is made of a viscoelastic material, higher vibration damping performance can be obtained as compared with the conventional technique in which the pressing member is a metal spring. . As a result, the presser member can absorb the displacement energy even if the stone is displaced due to an impact from the outside, etc., and can prevent the occurrence of excessive restoring force and the load applied to the stone and the shaft member. Can be suppressed. Therefore, by providing the pressing member according to the present invention in the vibration-proof bearing, it is possible to improve the impact resistance as compared with the conventional technique.

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. It is sectional drawing of the vibration-proof bearing which concerns on 1st embodiment. It is a top view of the vibration proof bearing concerning a first embodiment. It is a top view of the vibration-proof bearing which concerns on the modification of 1st embodiment. It is sectional drawing along the BB line of FIG. It is a top view of the vibration-proof bearing which concerns on 2nd embodiment. It is sectional drawing along CC line of FIG. It is sectional drawing of the vibration-proof bearing which concerns on 3rd embodiment.

(First embodiment)
Below, 1st embodiment of this invention is described using drawing.
In the following, a mechanical wristwatch (corresponding to “timepiece” in claims, hereinafter simply referred to as “timepiece”) and a movement incorporated in the timepiece will be described, and then details of the vibration-proof bearing according to the first embodiment 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, a minute hand 13 indicating the minute, and a second hand 14 indicating the second. 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 portion, 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 control device 140 for controlling the rotation of the front train wheel is constituted by the escape wheel 130, the ankle 142, and the balance with hairspring 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 is temporarily stopped with one pallet 142a of the ankle 142 engaged with the teeth 132 of the escape wheel 130.

  The balance with hairspring 10 is rotatably supported by the vibration-proof bearing 180 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 constant speed.

  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 speed adjusting device 140 is driven, the fourth wheel & pinion 128 is controlled to rotate once per minute, and the second wheel & pinion 124 is controlled to rotate once per hour.

(Tempo)
3 is a cross-sectional view taken along line AA in FIG.
As shown in FIG. 3, the balance with hairspring 10 includes a main balance wheel 20, a balance stem 22 (corresponding to a “shaft member” in the claims), and a hairspring 16. 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 a member formed in a substantially annular shape from a metal material such as iron, stainless steel, or brass, and is fitted and fixed to the balance stem 22.
The balance stem 22 is a cylindrical shaft member formed of a metal material such as iron, stainless steel, or brass. The balance stem 22 has tenons 21 (21A, 21B) (corresponding to “the end of the shaft member” in the claims) at both ends of the balance main body 22a. The central axis of the balance stem 22 coincides with the central axis O that is the center of rotation of the balance 10.

  The hairspring 16 is a spiral spring having a plurality of windings made of a metal material such as iron or nickel, or a resin material mainly composed of silicone resin or carbon. An inner end portion of the hairspring 16 is fixed to a hair ball 18 fixed to the balance stem 22. The outer end portion of the hairspring 16 is fixed to a hairspring 106 attached to the balance holder 104.

(Vibration resistant bearing)
FIG. 4 is a cross-sectional view of the vibration-proof bearing according to the first embodiment.
Anti-vibration bearings 180 (anti-vibration bearing 180A and anti-vibration bearing 180B) are provided at both ends in the axial direction of the balance with hairspring 10. The tenon 21 of the balance stem 22 is supported by the vibration-resistant bearing 180A and the vibration-resistant bearing 180B so as to be rotatable around the central axis O. One vibration-resistant bearing 180A and the other vibration-resistant bearing 180B have the same structure. In the following description, the vibration-resistant bearing 180A and the vibration-resistant bearing 180B are simply referred to as the vibration-resistant bearing 180 unless the vibration-resistant bearing 180B has to be distinguished.
As shown in FIGS. 3 and 4, the vibration-resistant bearing 180 includes a seat body 181, a frame body 182, a hole stone 183, a stone 184, and a pressing member 185.

As shown in FIG. 4, the seat body 181 includes a bottom 181 a having an insertion hole 181 h formed at the center, a cylindrical peripheral wall 181 b rising from the outer periphery of the bottom 181 a, and a bottom 181 a side of the peripheral wall 181 b. A receiving portion 181c that extends radially outward from the opposite end portion and a locking frame portion 181d that rises from the outer peripheral portion of the receiving portion 181c are integrally provided.
A tapered surface 181t is formed at the peripheral edge of the insertion hole 181h of the bottom 181a. The tapered surface 181t is formed so that the inner diameter dimension gradually decreases toward the bottom 181a.
In addition, a tapered surface 181s is formed at the corner between the peripheral wall portion 181b and the receiving portion 181c. The tapered surface 181s is formed such that the inner diameter dimension gradually decreases toward the bottom 181a.
On the inner surface of the locking frame portion 181d, a groove portion 181e is formed that is recessed in the radial direction over the entire circumference. The groove portion 181e functions as a fixing portion for fixing the outer peripheral portion 185a of the pressing member 185 to the seat body 181 as described later.

As shown in FIG. 3, the vibration-resistant bearing 180 </ b> A has a seat body 181 fitted to the balance holder 104. Further, the vibration-resistant bearing 180B has a seat body 181 fitted to the main plate 144.
As shown in FIG. 4, a spring main body 22 a of the spring stem 22 is inserted into the insertion hole 181 h of the seat body 181 so as to be rotatable around the central axis O.

  The frame body 182 holds the hole stone 183 and the stone 184 inside. The frame body 182 includes a base portion 182a having an insertion hole 182h into which the tenon 21 of the balance stem 22 is inserted, a cylindrical peripheral wall portion 182b rising from the outer peripheral portion of the base portion 182a, and the peripheral wall portion 182b. A receiving portion 182c spreading outward in the radial direction and a frame portion 182d rising from the outer peripheral portion of the receiving portion 182c are integrally provided.

A tapered surface 182t that contacts the tapered surface 181t of the seat body 181 is formed on the outer peripheral surface of the base portion 182a.
A tapered surface 182s that contacts the tapered surface 181s of the seat body 181 is formed on the outer peripheral portion of the receiving portion 182c.
The frame body 182 is accommodated inside the peripheral wall portion 181b of the seat body 181.

The hole stone 183 is made of a light-transmitting material such as ruby, for example. The hole stone 183 is a member having a substantially circular shape in a plan view, and a through hole 183h is formed at the substantially center in the plan view. The tenon 21 of the balance stem 22 is inserted through the through hole 183h. As for the hole stone 183, the outer peripheral surface 183a is press-fitted and fixed to the peripheral wall portion 182b of the frame body 182.
The balance stem 22 is restricted from moving in the radial direction by inserting the tenon 21 through the through hole 183h of the hole 183.

The stone 184 is a member having a substantially circular shape in a plan view and formed of a light-transmitting material such as a ruby. The receiving stone 184 has an axially inner surface as a flat portion 184f and an axially outer surface as a curved surface 184w bulging outward.
The stone 184 is disposed on the outer side in the axial direction than the hole stone 183. The receiving stone 184 has an end face 21e in the axial direction of the tenon 21 opposed to the central portion of the flat portion 184f on the side facing the balance 22. The receiving stone 184 is placed on the receiving portion 182c of the frame body 182 at the outer periphery of the flat surface portion 184f. The curved surface 184w of the stone 184 protrudes outward in the axial direction from the frame portion 182d of the frame body 182.
The end face 21e in the axial direction of the balance stem 22 is disposed so as to face the flat portion 184f of the stone 184. The movement of the balance stem 22 in the axial direction is restricted by the axial end surface 21e coming into contact with the flat surface portion 184f of the stone 184.

(Presser member)
FIG. 5 is a plan view of the vibration-proof bearing according to the first embodiment.
As shown in FIG. 5, the pressing member 185 has a circular shape in plan view, and has a plate shape having a certain thickness. The outer peripheral portion 185a of the pressing member 185 is placed on the receiving portion 181c of the seat body 181 over the entire circumference and is held by being pressed by the locking frame portion 181d.

  As shown in FIG. 4, the presser member 185 is curved when the surface 185f on the side facing the stone 184 is along the entire curved surface 184w of the stone 184, and the center portion is pivoted from the locking frame portion 181d. It bulges outward in the direction. The pressing member 185 is held by the seat body 181 by inserting the outer peripheral portion 185a into the groove portion 181e of the locking frame portion 181d.

The pressing member 185 is formed of a viscoelastic material having vibration damping performance. In other words, the presser member 185 has low resilience and high attenuation, attenuates displacement due to impact or the like input through the stone 184, and prevents the presser member 185 from generating excessive restoring force. To do. The pressing member 185 is formed of a viscoelastic material such as a rubber material or a silicone material.
The presser member 185 is preferably formed of a permeable material so that the stone 184 can be seen through. Thereby, the outstanding design property of the balance with hairspring 10 is ensured.

(Function)
The vibration-resistant bearing 180 acts as follows when an impact load is applied to the timepiece 1 from the outside, for example.
When the balance stem 22 is displaced in the axial direction by a load from the outside, the balance stem 22 and the catch stone 184 are displaced outward in the axial direction with the tenon 21 of the balance stem 22 in contact with the catch stone 184. Subsequently, the presser member 185 is elastically deformed so as to bulge outward in the axial direction due to the displacement of the receiving stone 184 outward in the axial direction. The holding member 185 absorbs the load from the receiving stone 184, elastically suppresses the displacement of the receiving stone 184 and the balance stem 22, and restores the shape of the holding member 185 while attenuating the vibration of the balance stem 22. Therefore, the balance stem 22 can return to the position before the displacement.

  When the balance 22 is displaced in the radial direction by an external load, when the displacement of the hole 183 is transmitted to the frame body 182, the frame body 182 is moved to the tapered surface 181 t and the tapered surface 181 s of the seat body 181. Displace while sliding along. At this time, the frame 182 is displaced radially outward and axially outward along the tapered surface 181t and the tapered surface 181s. Thereby, the stone 184 held by the frame body 182 is displaced outward in the radial direction and outward in the axial direction. Subsequently, the presser member 185 is elastically deformed so as to bulge outward in the axial direction due to the displacement of the receiving stone 184 in the radially outer side and the axially outer side. As a result, the presser member 185 absorbs the load from the jewel 184, elastically suppresses the displacement of the jewel 184 and the balance stem 22, and reduces the vibration of the balance stem 22 while reducing the shape of the presser member 185. Restore. Therefore, the balance stem 22 can return to the position before the displacement.

  According to this embodiment, since the presser member 185 disposed on the axially outer side than the stone 184 is made of a viscoelastic material, the vibration damping performance is higher than that of the conventional technique in which the presser member 185 is a metal spring. Can be obtained. As a result, the holding member 185 can absorb the displacement energy even if the stone 184 is displaced due to an external impact or the like, and also prevents the excessive stones 184 and the balance stone from being generated. The load applied to 22 can be suppressed. Therefore, by providing the pressing member 185 according to the present embodiment in the vibration-resistant bearing 180, it is possible to improve the impact resistance as compared with the conventional technique.

  Further, by covering the stone 184 with the holding member 185, the load generated when the stone 184 is displaced due to an external impact or the like can be transmitted to the holding member 185. Therefore, the shock resistance of the vibration-resistant bearing 180 can be improved.

  Moreover, it can fix simply by providing the outer peripheral part 185a of the pressing member 185 in the groove part 181e of the seat 181 without providing the member for fixing to the seat 181. Therefore, the vibration-resistant bearing 180 can be manufactured at a low cost that can improve the impact resistance.

  In addition, since the movement 100 and the timepiece 1 of the present embodiment include the vibration-resistant bearing 180 described above, the high-performance movement 100 and timepiece 1 having excellent impact resistance can be obtained.

(Modification of the first embodiment)
Next, a modification of the first embodiment is shown.
In the first embodiment, the presser member 185 is formed in a circular shape in plan view (see FIG. 5), but is not limited thereto.
FIG. 6 is a plan view of a vibration-proof bearing according to a modification of the first embodiment, and FIG. 7 is a cross-sectional view taken along line BB in FIG.
As shown in FIGS. 6 and 7, the pressing member 185 </ b> B can have a substantially triangular shape when viewed from the central axis O direction. The pressing member 185B is held by inserting a corner portion 185z corresponding to the outer peripheral portion 185a into the groove portion 181e of the locking frame portion 181d of the seat body 181.
In addition, the planar shape of the pressing member 185B is not limited to a substantially triangular shape. For example, the planar shape may be a substantially rectangular shape or a substantially pentagonal shape.

  According to the modification of the first embodiment, the pressing member 185B can be easily fixed by fixing the corner portion 185z of the outer peripheral portion 185a of the pressing member 185B to the seat body 181. Thereby, the assembly property and maintenance property of the vibration-proof bearing 180 can be improved.

(Second embodiment)
FIG. 8 is a plan view of the vibration-proof bearing according to the second embodiment, and FIG. 9 is a cross-sectional view taken along the line CC of FIG.
Next, a second embodiment of the vibration-proof bearing according to the present invention will be described.
In the first embodiment, the holding member 185 constituting the vibration-proof bearing is held by being inserted into the groove portion 181e of the locking frame portion 181d of the seat body 181 (see FIG. 4).
On the other hand, as shown in FIGS. 8 and 9, the vibration-proof bearing 280 of the second embodiment is different from the first embodiment in that the presser member 185 is fixed by an annular stopper 286. In addition, in 2nd embodiment demonstrated below, about the structure similar to 1st embodiment, while attaching | subjecting a same sign, the description is abbreviate | omitted.

The vibration-resistant bearing 280 includes a seat body 281, a frame body 182, a hole stone 183, a stone 184, a pressing member 185, and a stopper 286.
A female screw part 281e is formed on the inner surface of the support frame part 281d of the seat body 281.
The stopper 286 is attached to the inside of the support frame portion 281d of the seat body 281. The stopper 286 is formed in an annular shape from, for example, a resin material or a metal material. On the outer peripheral surface of the stopper 286, a male screw portion 286e that is screwed into the female screw portion 281e of the support frame portion 281d is formed. Further, a tool engagement groove 286t for engaging a tool such as a screwdriver is formed on the outer surface in the axial direction of the stopper 286.

  As shown in FIG. 9, the pressing member 185 made of a viscoelastic material is disposed inside the support frame portion 281 d of the seat body 281. The pressing member 185 is fixed by pressing the outer peripheral portion 185a against the receiving portion 181c of the seat body 281 by screwing the stopper 286 inside the support frame portion 281d. The pressing member 185 bulges outward in the axial direction in a curved state by abutting against the curved surface 184 w of the stone 184.

  According to the second embodiment, after the presser member 185 is set on the seat body 281, the presser member 185 can be easily fixed by screwing the stopper 286 as a fixing portion onto the seat body 281. Thereby, the assemblability and maintenance property of the vibration-resistant bearing 280 can be improved.

(Third embodiment)
FIG. 10 is a cross-sectional view of the vibration-proof bearing according to the third embodiment.
Next, a third embodiment of the vibration-proof bearing according to the present invention will be described.
In the first embodiment and the second embodiment, the pressing member 185 is provided on the outer side in the axial direction with respect to the stone 184 (see FIGS. 4 and 7).
On the other hand, as shown in FIG. 10, in the third embodiment, the press member 385 includes an outer peripheral wall portion 385 w located on the outer peripheral side of the frame body 382. This is different from the embodiment. In addition, in 3rd embodiment demonstrated below, about the structure similar to 1st embodiment and 2nd embodiment, while attaching | subjecting a same sign, the description is abbreviate | omitted.

As shown in FIG. 10, the vibration-resistant bearing 380 includes a seat body 381, a frame body 382, a hole stone 183, a stone 184, a pressing member 385, and a stopper 286.
The frame body 382 includes a base portion 382a having an insertion hole 382h, a cylindrical peripheral wall portion 382b that rises from the outer peripheral portion of the base portion 382a to one side, and a receiving portion 382c that is formed inside the distal end portion of the peripheral wall portion 382b. And a frame portion 382d rising from the outer peripheral portion of the receiving portion 382c.
A tapered surface 382t that abuts against the tapered surface 181t of the seat body 381 is formed on the outer peripheral surface of the base portion 382a.

The pressing member 385 has a plate-like portion 385p having a constant thickness in a circular shape in plan view, and an outer peripheral wall portion 385w erected from the outer peripheral portion of the plate-like portion 385p toward the bottom portion 181a of the seat body 381. In the bottomed cylindrical shape integrally with the load absorbing portion.
The plate-like portion 385p of the pressing member 385 is provided along the stone 184. Further, the outer peripheral wall portion 385 w of the pressing member 385 is provided so as to be positioned between the peripheral wall portion 382 b of the frame body 382 and the peripheral wall portion 181 b of the seat body 381 in the radial direction.

  When the balance stem 22 is displaced in the axial direction by a load from the outside, the balance stem 22 and the catch stone 184 are displaced outward in the axial direction with the tenon 21 of the balance stem 22 in contact with the catch stone 184. The presser member 385 absorbs the load from the stone 184 and elastically suppresses the displacement of the stone 184 and the balance stem 22 and restores the shape of the presser member 385 while attenuating the vibration of the balance stem 22. Therefore, the balance stem 22 can return to the position before the displacement.

  When the balance 22 is displaced in the radial direction by an external load, if the displacement of the hole 183 is transmitted to the frame body 382, the frame body 382 slides along the tapered surface 181t of the seat body 381. It is displaced while. At this time, the frame body 382 is displaced radially outward and axially outward along the tapered surface 181t. At this time, the outer peripheral wall portion 385w of the pressing member 385 is elastically deformed in the thickness direction. As a result, the presser member 385 absorbs the load from the stone 184 and the frame body 382, elastically suppresses the displacement of the stone 184 and the balance 22, and attenuates the vibration of the balance 22 while holding the member 385. Restore the shape. Therefore, the balance stem 22 can return to the position before the displacement.

  According to the third embodiment, the load generated by the displacement of the balance stem 22 in the radial direction can be reliably absorbed by the outer peripheral wall portion 385 w of the pressing member 385. Therefore, the shock resistance of the vibration-resistant bearing 380 can be significantly improved.

The technical scope of the present invention is not limited to the above embodiment, and various modifications can be made without departing from the spirit of the present invention.
For example, in each embodiment, the vibration-resistant bearings 180, 280, and 380 that rotatably support the balance stem 22 constituting the balance 10 are described as examples. However, the application of the vibration-resistant bearings 180, 280, and 380 is described in each embodiment. It is not limited to. Therefore, for example, the vibration-proof bearings 180, 280, and 380 of the escape wheel & pinion 130 may be used, or the ankle true vibration-proof bearings 180, 280, and 380 that rotatably support the ankle 142 may be used.
The application of the vibration-resistant bearings 180, 280, 380 is not limited to a mechanical timepiece, and may be applied to a quartz type timepiece.

  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 10 ... Balance 21, 21A, 21B ... Tenon (end part) 22 ... Tenshin (shaft member) 180, 180A, 180B, 280, 380 ... Vibration-proof bearing 181, 281 , 381 ... Seat 181e ... Groove (fixed part) 281e ... Female thread (fixed part) 182, 382 ... Frame 183 ... Hole stone 184 ... Stone 185, 185B, 385: Pressing member 185a, 385a ... Outer peripheral portion 185z ... Corner portion 385w ... Outer peripheral wall portion (load absorbing portion)

Claims (10)

A receiving stone disposed opposite to the axial end surface of the shaft member;
A hole stone through which an end of the shaft member is inserted;
A frame for holding the stone and the hole stone;
A seat in which the frame is accommodated;
Provided in a vibration-proof bearing with
At least a part of the holding member that is disposed on the outer side in the axial direction than the receiving stone and holds the receiving stone,
A pressing member made of a viscoelastic material. A receiving stone disposed opposite to the axial end surface of the shaft member;
A hole stone through which an end of the shaft member is inserted;
A frame for holding the stone and the hole stone;
A seat in which the frame is accommodated;
At least a part of the holding stone that is disposed on the outer side in the axial direction than the stone and holds the stone;
With
The vibration-proof bearing, wherein the pressing member is made of a viscoelastic material. A fixing portion capable of fixing the outer periphery of the pressing member to the seat;
The vibration-proof bearing according to claim 2, wherein the pressing member is fixed to the fixing portion and is disposed in a state of covering at least a part of the stone.   The vibration-proof bearing according to claim 3, wherein the fixing portion is a groove portion that is provided on an inner surface of the seat body and is fixed by inserting an outer peripheral portion of the pressing member.   The vibration-proof bearing according to claim 3, wherein the fixing portion is an annular stopper that is screwed to the seat body and holds an outer peripheral portion of the pressing member.   6. The vibration proof according to claim 3, wherein the presser member has a circular shape when viewed from the axial direction and is disposed in a state of covering the entire surface of the stone. 6. bearing.   6. The presser member according to claim 3, wherein the presser member has a polygonal shape when viewed from the axial direction, and a corner portion of the presser member is fixed to the seat body. 6. Vibration-resistant bearing.   The said pressing member is provided with the load absorption part interposed between the said frame and the said seat body in the radial direction of the said shaft member, The any one of Claim 2 to 7 characterized by the above-mentioned. Vibration-resistant bearing.   A movement comprising the vibration-proof bearing according to claim 1.   A timepiece comprising the movement according to claim 9.

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