JP2012117842A - Bearing structure for timepiece, movement therefor, and timepiece - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing structure for a timepiece, a movement therefor, and a timepiece capable of effectively preventing a lubricating oil from leaking and scattering while preventing strength degradation of a tenon.SOLUTION: Bearing structure for a timepiece includes a shaft part 124a having a tenon 124c at an edge part 124f and a mortise stone 80 forming an insertion hole 81 to insert the tenon 124c into. The shaft part 124a is rotatably supported on the mortise stone 80 by inserting the tenon 124c into the insertion hole 81. A plurality of small grooves 83 are formed at least inside an outer diameter D3 of the shaft part 124a in a radial direction on an edge face 80a of the mortise stone 80.

Description

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

  Conventionally, a gear constituting a train wheel of a watch is rotatably supported via a rotating shaft by inserting a tenon formed at an end of a rotating shaft supporting the gear into a bearing. Yes. More specific description will be given below.

FIG. 9 is a partially enlarged cross-sectional view showing an example of a timepiece bearing structure used in a conventional wristwatch movement.
As shown in the figure, a wheel train 702 is incorporated in a movement 701 of a wrist watch 700, and a gear 703 constituting the wheel train 702 is fixedly fitted to a rotating shaft 704. The rotary shaft 704 is provided with a pinion 711 that meshes with another gear 703a, and tenons 705 that are reduced in diameter by a step from the shaft diameter of the rotary shaft 704 are integrally formed at both ends in the axial direction. The rotating shaft 704 configured as described above is rotatably supported by a train wheel bridge 706 and a bearing portion 708 provided on the main plate 707.

  Here, as the bearing portion 708, the train wheel bridge 706 and the base plate 707 are formed with insertion holes through which the tenon 705 can be directly inserted, and the train wheel bridge 706 and the base plate 707 are provided with a hole stone 709. For example, there is one in which an insertion hole 710 through which the tenon 705 can be inserted is formed in the hole stone 709 by being fixed by press fitting or the like. FIG. 9 shows a case where the insertion hole 710 is formed in the hole stone 709.

  A tenon 705 is inserted into the insertion hole 710 formed in the hole stone 709, and thereby the rotating shaft 704 is rotatably supported. Further, in order to smoothly rotate the rotation shaft 704, a gap S101 called tenon play is formed between the insertion hole 710 and the tenon 705, and the end of the rotation shaft 704 and the hole stone 709 are formed. A gap S102 called a postcard is formed between them.

  Thus, by forming the gaps S101 and S102 in the radial direction and the thrust direction with respect to the rotation shaft 704, the rotation shaft 704 can be smoothly rotated. Further, by lubricating the gap S101 with lubricating oil, the frictional resistance generated between the tenon 705 and the hole stone 709 is reduced, and the rotating shaft 704 is rotated more smoothly.

  Here, the operation of injecting the lubricating oil into the gaps S101 and S102 is performed before product shipment, and thereafter, for example, for several years until maintenance is performed, it is common to continue using the wristwatch without injecting the lubricating oil again. Is. For this reason, there exists a possibility that lubricating oil may flow out gradually from the clearance gap S101, or may be scattered. This will be described in detail below.

FIG. 10A and FIG. 10B are explanatory views showing the behavior of the lubricating oil accompanying the movement of the rotating shaft.
As shown in FIG. 10A, when the gap S102 is sufficiently secured, the lubricating oil J stays in the gap S101 due to the surface tension acting on the lubricating oil J.

On the other hand, as shown in FIG. 10 (b), the end of the rotating shaft 704 moves toward the hole 709 side (upper side in FIG. 10 (b)), and the gap S102 becomes a gap (tack). When it becomes narrower than S101, the lubricating oil J flows into the gap S102 due to capillary action. When the rotating shaft 704 moves from this state in a direction away from the hole stone 709 (downward in FIG. 10B), the lubricating oil J is pulled and the lubricating oil J further flows out.
Subsequently, when the rotating shaft 704 moves toward the hole 709 while the lubricating oil J stays in the gap S102, the lubricating oil J flows out or scatters. By repeatedly performing such a so-called pumping operation, the lubricating oil J injected into the gap S101 is reduced. As a result, the frictional resistance generated between the hole stone 709 and the tenon 705 is increased.

For this reason, various techniques have been proposed in order to prevent the lubricating oil J from flowing out and scattering.
For example, there is a case where an oil-repellent resin such as fluorine is formed on the surface of the tenon 705 and the hole stone 709 by immersion or vapor deposition to increase the contact angle of the lubricant and prevent the lubricant J from flowing out. is there.

In addition, a technique is disclosed in which a groove is formed over the entire circumference in the approximate center of the tenon in the axial direction (see, for example, Patent Document 1). By configuring in this way, a space for holding the lubricating oil is formed in the portion where the groove is formed, and an attempt is made to suppress the outflow of the lubricating oil.
Furthermore, a technique is disclosed in which a groove is formed in a rotating shaft or a hole stone, and an oil-repellent substance is attached to the groove (see, for example, Patent Document 2). With this configuration, it is intended to suppress the outflow of the lubricating oil.

Japanese Utility Model Publication No. 50-10264 Japanese Patent Publication No.49-22471

However, when oil repellent treatment is applied to the surface of tenon or hole stone as in the prior art described above, the oil repellent effect can be expected, but the oil repellent treatment is peeled off due to wear, or the oil repellent effect due to surface contamination. There exists a subject that there exists a possibility of reducing greatly.
Further, as in Patent Document 1, if a groove is formed around the tenon, the movement of the lubricating oil can be reduced. However, if severe vibration is applied, the number of movements of the rotating shaft also increases, preventing the lubricating oil from flowing out and scattering. There is a problem that it becomes difficult. Furthermore, when a groove is formed around the tenon, there is a problem that the strength of the tenon is lowered.

  Therefore, the present invention has been made in view of the above-described circumstances, and provides a timepiece bearing structure, a movement, and a timepiece that can effectively prevent the outflow and scattering of lubricating oil while preventing a tenon strength from being lowered. It is to provide.

  In order to solve the above problems, a timepiece bearing structure according to the present invention includes a shaft body having a tenon at an end portion thereof, and a bearing body in which an insertion hole for inserting the tenon is formed, and the insertion In the timepiece bearing structure in which the shaft body is rotatably supported by the bearing body by inserting the tenon through the hole, the shaft body side end surface of the bearing body has at least an outer diameter of the shaft body. A first groove is formed at a position on the radially inner side.

With this configuration, even when the end of the shaft body is in contact with the bearing body, a space is secured at the location where the first groove is formed between the bearing body and the end of the shaft body. can do. For this reason, even when lubricating oil is injected into the insertion hole, the capillary phenomenon of the lubricating oil can be suppressed, and the outflow and scattering of the lubricating oil can be effectively prevented.
Further, unlike the prior art, it is not necessary to form a groove around the tenon, so that the tenon strength can be prevented from being lowered.

  In the timepiece bearing structure according to the present invention, the first groove is formed by radially forming a plurality of small grooves.

  By comprising in this way, the outflow and scattering to lubricating oil can be prevented more effectively.

  A timepiece bearing structure according to the present invention includes a shaft body having a tenon at an end thereof, and a bearing body provided at least on the tenon side of the shaft body and having an insertion hole for inserting the tenon. In the watch bearing structure in which the tenon is inserted into the insertion hole and the shaft body is rotatably supported by the bearing body, the tenon side end of the shaft body and the shaft body side of the bearing body A second groove communicating with the clearance between the tenon and the insertion hole is formed in at least one of the end faces.

By configuring in this way, even if the end of the shaft body abuts on the bearing body, a space is secured at the location where the second groove is formed between the bearing body and the end of the shaft body. can do. In addition, among the clearances formed between the tenon and the insertion hole, the opening area on the proximal end side of the tenon can be set larger than the opening area on the distal end side of the tenon. That is, when lubricating oil is poured into the insertion hole, the pressure received by the lubricating oil from the atmospheric pressure is higher on the base end side of the tenon than the pressure received on the tip side of the tenon. For this reason, the outflow and scattering of the lubricating oil can be effectively prevented.
Further, unlike the prior art, it is not necessary to form a groove around the tenon, so that the tenon strength can be prevented from being lowered.

  The timepiece bearing structure according to the present invention is characterized in that the second groove is formed by radially forming a plurality of small grooves.

  By comprising in this way, the outflow and scattering to lubricating oil can be prevented more effectively.

  The timepiece bearing structure according to the present invention is characterized in that the plurality of small grooves extend to the outside in the radial direction from the outer diameter of the shaft body.

  By configuring in this way, for example, even when the lubricating oil is excessively injected into the insertion hole, when the end of the shaft body comes into contact with the bearing body, A large contact area with the atmosphere can be set. That is, the pressure that the lubricating oil receives from the atmospheric pressure on the proximal end side of the tenon can be set larger. For this reason, generation | occurrence | production of a capillary phenomenon can be suppressed reliably and the outflow and scattering of lubricating oil can be prevented more effectively.

  The timepiece bearing structure according to the present invention is an opening formed by being surrounded by the end surface and the small groove in a state where the end portion of the shaft body and the end surface of the bearing body are in contact with each other. When the opening area of the opening formed on the tenon side is M, the number of the small grooves formed is N, and the sectional area of the clearance between the tenon and the insertion hole is C, the opening area M The number N of small grooves and the sectional area C of the clearance are set so as to satisfy M × N> C.

  By comprising in this way, the capillary phenomenon of lubricating oil can be prevented reliably.

  The timepiece bearing structure according to the present invention is characterized in that the small groove is formed so that the groove cross-sectional area gradually decreases toward the inner side in the radial direction.

By comprising in this way, lubricating oil can be collected near radial center by the capillary phenomenon of the lubricating oil which flowed out to the small groove. For this reason, the outflow and scattering of the lubricating oil can be further reliably prevented.
Further, since the lubricating oil can be retained near the radial center of the shaft body in the small groove, the frictional resistance generated between the end of the shaft body and the end surface of the bearing body can be reduced. For this reason, it becomes possible to rotate a shaft more smoothly.

  In the timepiece bearing structure according to the present invention, the small groove is formed at an inner small groove formed radially inward from an outer diameter of the shaft body, and at least the inner small groove is formed radially outward from the outer diameter of the shaft body. The outer small groove communicates with the inner small groove, and the groove sectional area of the outer small groove is set to be larger than the groove sectional area of the inner small groove.

  By comprising in this way, lubricating oil can be further retained between the edge part of a shaft body, and the end surface of a bearing body. For this reason, the frictional resistance generated between the end of the shaft body and the end surface of the bearing body is further reduced, so that the shaft body can be rotated more smoothly while preventing outflow and scattering of the lubricating oil. Become.

The timepiece bearing structure according to the present invention is characterized in that the first groove has an annular groove in an axial plan view.
In the timepiece bearing structure according to the invention, the second groove has an annular groove in an axial plan view.
With this configuration, when lubricating oil is injected into the insertion hole, the pressure received by the lubricating oil from the atmospheric pressure is higher on the base end side of the tenon than the pressure received on the tip side of the tenon. For this reason, even if the clearance between the bearing body and the end of the shaft body changes, the capillary action of the lubricating oil due to this clearance can be prevented. Therefore, it is possible to effectively prevent outflow and scattering of the lubricating oil.

  The movement according to the present invention is a movement of a clock provided with a barrel wheel, a watch wheel, a escape wheel, an ankle and a balance, and at least one of the barrel car, the ankle and the watch wheel, The timepiece bearing structure according to any one of Items 1 to 8 is used.

  By comprising in this way, the movement which can prevent the outflow and scattering of lubricating oil can be provided, preventing the tenon strength fall.

  A timepiece according to the present invention includes the movement described in claim 9.

  By comprising in this way, the timepiece which can prevent the outflow and scattering of lubricating oil can be provided, preventing the tenon strength fall.

According to the present invention, even when the end portion of the shaft body is in contact with the bearing body, a space is ensured at a location where the first groove is formed between the bearing body and the end portion of the shaft body. Can do. For this reason, even when lubricating oil is injected into the insertion hole, the capillary phenomenon of the lubricating oil can be suppressed, and the outflow and scattering of the lubricating oil can be effectively prevented.
Further, unlike the prior art, it is not necessary to form a groove around the tenon, so that the tenon strength can be prevented from being lowered.

According to the present invention, even when the end portion of the shaft body is in contact with the bearing body, a space is ensured at a location where the second groove is formed between the bearing body and the end portion of the shaft body. Can do. In addition, among the clearances formed between the tenon and the insertion hole, the opening area on the proximal end side of the tenon can be set larger than the opening area on the distal end side of the tenon. That is, when lubricating oil is poured into the insertion hole, the pressure received by the lubricating oil from the atmospheric pressure is higher on the base end side of the tenon than the pressure received on the tip side of the tenon. For this reason, the outflow and scattering of the lubricating oil can be effectively prevented.
Further, unlike the prior art, it is not necessary to form a groove around the tenon, so that the tenon strength can be prevented from being lowered.

It is a top view of the mechanical timepiece in the embodiment of the present invention. It is a schematic fragmentary sectional view which shows the part of the escape wheel from the barrel in the embodiment of the present invention. It is a general | schematic fragmentary sectional view which shows the part of the balance with the escape wheel in embodiment of this invention. The bearing structure in 1st embodiment of this invention is shown, (a) is sectional drawing of a bearing, (b) is sectional drawing which follows the XX line of Fig.4 (a). It is a top view of the bearing in 2nd embodiment of this invention. It is a top view of the bearing in 3rd embodiment of this invention. The bearing structure in 4th embodiment of this invention is shown, (a) is sectional drawing of a bearing, (b) is sectional drawing which follows the YY line of Fig.7 (a). The bearing structure in 5th embodiment of this invention is shown, (a) is sectional drawing of a bearing, (b) is sectional drawing which follows the ZZ line of Fig.8 (a). It is a partially expanded sectional view which shows an example of the bearing structure for timepieces used for the movement of the conventional wristwatch. The schematic sectional drawing of the conventional bearing part is shown, (a), (b) is explanatory drawing which shows the behavior of the lubricating oil accompanying the movement of a rotating shaft.

(First embodiment)
(Mechanical watch)
Next, a first embodiment of the present invention will be described with reference to FIGS.
FIG. 1 is a plan view of a mechanical timepiece using a timepiece bearing structure according to the present invention, FIG. 2 is a schematic partial sectional view showing a portion of an escape wheel from a barrel, and FIG. 3 is an escape wheel It is a general | schematic fragmentary sectional view which shows the part of Kara balance.
As shown in FIGS. 1 to 3, a mechanical timepiece 10 that is a wristwatch includes a movement 100 and a casing (not shown) that houses the movement 100, and a dial 104 is attached to the movement 100.

(Movement)
The movement 100 has a base plate 102 that constitutes a substrate.
Here, of the two sides of the main plate 102, the side on which the dial 104 is arranged (the lower side in FIG. 2) is referred to as the back side of the movement 100, and the opposite side of the side on which the dial 104 is arranged is the front side of the movement 100. Called. A train wheel incorporated on the front side of the movement 100 is referred to as a front train wheel, and a train wheel incorporated on the back side of the movement 100 is referred to as a back train wheel.

  A winding stem guide hole 102a is formed in the main plate 102, and a winding stem 110 is rotatably incorporated therein. The axial position of the winding stem 110 is determined by a switching device having a setting lever 190, a yoke 192, a yoke spring 194, and a back presser 196. Further, a chisel wheel 112 is rotatably provided on the guide shaft portion of the winding stem 110.

  Under such a configuration, the winding stem 110 is rotated in a state where the winding stem 110 is in the first winding stem position (0th stage) closest to the inside of the movement 100 along the rotation axis direction. Then, the hour wheel 112 is rotated through rotation of a not-shown pinion wheel. Then, as the chi-wheel 112 rotates, the round hole wheel 114 that meshes therewith rotates. Further, when the round hole wheel 114 rotates, the square hole wheel 116 that meshes with the circular hole wheel 114 rotates. As the square hole wheel 116 rotates, the mainspring 122 (see FIG. 2) accommodated in the barrel complete 120 is wound up. The barrel complete 120 forms a front train wheel.

The barrel complete 120 includes a barrel complete gear 120d, a barrel complete 120f, and a mainspring 122. The barrel complete 120f includes an upper shaft portion 120a and a tenon 120b that protrudes from a base plate 102 side end (a lower end in FIG. 2) that is an end opposite to the upper shaft portion 120a.
The tenon 120b is formed with a reduced diameter by a level difference from the barrel complete 120f. The barrel complete 120f is made of a metal such as carbon steel. The barrel gear 120d is formed of a metal such as brass.

  The front train wheel arranged on the front side of the movement 100 includes a second wheel 124, a third wheel 126 and a fourth wheel 128 in addition to the barrel complete 120. Further, on the front side of the movement 100, an escapement / regulator 40 for controlling the rotation of the front train wheel is disposed.

The center wheel & pinion 124 includes a shaft portion 124a, an abacus ball portion 124b provided on the ground plate 102 side of the shaft portion 124a, a tenon 124c projecting on the opposite side of the ground plate 102 of the shaft portion 124a, and a shaft portion. 124a has a pinion portion 124d provided between the abacus ball portion 124b and the tenon portion 124c, and a gear portion 124e provided between the tenon portion 124c and the pinion portion 124d. The kana portion 124c is configured to mesh with the barrel gear 120d.
The tenon 124c has a diameter smaller than that of the shaft portion 124a. The shaft portion 124a, the abacus ball portion 124b, and the tenon 124c are formed of a metal such as carbon steel. The gear portion 124e is formed of a metal such as nickel.

  The third wheel & pinion 126 includes a shaft portion 126a, tenons 126b and 126c projecting from both ends of the shaft portion 126a, a pinion portion 126d provided between the tenons 126b and 126c of the shaft portion 126a, and a gear portion 126e. And have. The kana portion 126d is configured to mesh with the gear portion 124e of the center wheel & pinion 124. Further, the tenons 126b and 126c are formed to have a reduced diameter by a step rather than the shaft portion 126a.

The fourth wheel & pinion 128 includes a shaft portion 128a, tenons 128b and 128c protruding from both ends of the shaft portion 128a, a pinion portion 128d provided between the tenons 128b and 128c of the shaft portion 128a, and a gear portion 128e. And have. The kana portion 128d is configured to mesh with the gear portion 126e of the third wheel & pinion 126.
The shaft portion 128a and both tenons 128b and 128c are formed of a metal such as carbon steel. The gear portion 128e is formed of a metal such as nickel. Further, the tenon 128b, 128c is formed to have a reduced diameter by a step rather than the shaft portion 128a.

  The escapement and speed control device 40 includes an escape wheel 130, an ankle 142, and a balance with hairspring 140 so that the pinion kana 150 (see FIG. 2) rotates simultaneously based on the rotation of the center wheel & pinion 124. It has become. The minute hand 152 attached to the cylindrical pinion 150 displays “minute”. The cylindrical pinion 150 is provided with a slip mechanism for the center wheel & pinion 124. Based on the rotation of the hour pinion 150, the hour wheel 154 rotates through the rotation of the minute wheel. An hour hand 156 attached to the hour wheel 154 displays “hour”.

The escape wheel & pinion 130 includes a shaft portion 130a, tenons 130b and 130c protruding from both ends of the shaft portion 130a, a pinion portion 130d provided between the tenons 130b and 130c of the shaft portion 130a, and a gear portion. 130e. The kana portion 130d is configured to mesh with the gear portion 128e of the fourth wheel & pinion 128.
The ankle 142 includes an ankle body 142d and an ankle true 142f. The pallet fork 142f has tenons 142a and 142b at both ends, respectively.

  The balance with hairspring 140 includes a balance stem 140a and a hairspring 140c. The hairspring 140c is a thin leaf spring having a spiral shape having a plurality of winding numbers. An inner end portion of the hairspring 140c is fixed to a hairball 140d fixed to the balance stem 140a. On the other hand, the outer end portion of the hairspring 140c is fixed by screw tightening via a whisker 170a attached to a whisker holder 170 rotatably attached to the balance holder 167. The slow / fast needle 168 is rotatably attached to the balance holder 167.

  Here, the balance with hairspring 140 is configured to be rotatable about the shaft body 143. The shaft body 143 includes a balance stem 140a configured as a shaft main body, and tenons 144 and 145 having diameters smaller than those of the balance stem 140a at both axial ends of the balance stem 140a. The tenons 144 and 145 are inserted through bearings 180 provided on the main plate 102 and the balance holder 167, and are rotatably supported. Thereby, the shaft body 143 is rotatably supported, and the balance with hairspring 140 is rotatable.

  The barrel complete 120 is supported rotatably with respect to the main plate 102 and the barrel holder 160. That is, the upper shaft portion 120a of the barrel complete 120f is rotatably supported with respect to the barrel holder 160, while the tenon 120b of the barrel complete 120f is rotatably supported by the bearing portion 181 provided on the main plate 102. Has been.

Further, the second wheel 124, the third wheel 126, the fourth wheel 128, and the escape wheel 130 are supported rotatably with respect to the main plate 102 and the train wheel bridge 162.
That is, the tenon 124c of the center wheel & pinion 124 is connected to the bearing portion 182 provided on the train wheel bridge 162, and the tenon 126b of the third wheel & pinion 126 is connected to the bearing portion 183 provided to the wheel train wheel 162. The tenon 128b of the wheel 128 is rotatably supported by a bearing part 184 provided on the train wheel bridge 162, and the tenon 130b of the escape wheel 130 is rotatably supported by a bearing part 185 provided on the wheel train bridge 162. Yes.

  The shaft 124 a of the center wheel 124 is connected to the bearing portion 186 provided on the main plate 102, and the tenon 126 c of the third wheel 126 is connected to the bearing portion 187 provided on the base plate 102. The tenon 128c is rotatably supported by a bearing portion 188 provided on the main plate 102, and the tenon 130c of the escape wheel 130 is rotatably supported by a bearing portion 189 provided on the main plate 102.

Further, the ankle 142 is rotatably supported with respect to the main plate 102 and the ankle receiver 164. That is, the tenon 142a of the ankle 142 is rotatably supported with respect to the ankle receiver 164, while the tenon 142b is rotatably supported with respect to the main plate 102.
The main plate 102, the barrel holder 160, the train wheel holder 162, and the ankle receiver 164 may be formed of metal such as brass, or may be formed of resin such as polycarbonate.

  Under such a configuration, after winding the mainspring 122 accommodated in the barrel complete 120 using the winding stem 110, the barrel complete 120 is rotated by the rotational force when the mainspring 122 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 / regulator 40 is driven. When the escapement and speed control device 40 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.

  Here, at least each of the bearing portions 181 to 189 provided in the main plate 102 and the train wheel bridge 162 has a structure in which lubricating oil J (see FIG. 4) such as precision machine oil is injected. Below, each bearing part 181-189 is demonstrated in detail. Since the bearing portions 181 to 189 are all in the same mode, only the bearing portion 182 that rotatably supports the tenon 124c of the shaft portion 124a constituting the center wheel & pinion 124 will be described in the following description. Description of the other bearing portions 181, 183 to 189 is omitted.

(Bearing structure)
4A and 4B show a bearing structure, in which FIG. 4A is a cross-sectional view of the bearing, and FIG. 4B is a cross-sectional view taken along line XX in FIG.
As shown in FIGS. 4A and 4B, the bearing portion 182 has a hole stone 80 that is fitted and fixed to the train wheel bridge 162. The hole stone 80 is formed in a substantially disc shape by a transparent material such as ruby, for example, and is inserted through the tenon 124c protruding from the end portion 124f of the shaft portion 124a at the substantially radial center. A hole 81 is formed.

  Here, the inner diameter D1 of the insertion hole 81 is set slightly larger than the outer diameter D2 of the tenon 124c, and a desired clearance (tenon backlash) C1 is formed between the insertion hole 81 and the tenon 124c. . Lubricating oil J is injected into the clearance C1.

Further, a clearance C <b> 2 (postcard) is also formed between the end portion 124 f of the shaft portion 124 a and the end surface 80 a of the hole stone 80 on the shaft portion 124 a side. By forming this clearance C2, the shaft portion 124a can move slightly in the axial direction.
A two-dot chain line shown in FIG. 4A indicates a state in which the end portion 124f of the shaft portion 124a is farthest from the end surface 80a of the hole stone 80. By allowing the shaft portion 124a to move slightly in the axial direction, it is possible to prevent an unnecessary frictional resistance from being generated between the end surface 80a of the hole 80 and the end portion 124f of the shaft portion 124a. For this reason, the shaft part 124a can be smoothly rotated.

  The clearance C1 between the insertion hole 81 and the tenon 124c is set to about 5 μm, for example. The clearance C2 between the end of the shaft portion 124a and the hole stone 80 is set to about 20 to 30 μm, for example.

Further, a recess 82 is formed at a position corresponding to the insertion hole 81 on the end surface 80b of the hole stone 80 opposite to the shaft portion 124a. The recess 82 functions as a tray for injecting the lubricating oil J into the clearance C1.
Furthermore, a plurality of (for example, eight in the first embodiment) small grooves 83 are radially formed around the insertion hole 81 on the end surface 80a of the hole stone 80 on the shaft portion 124a side. The small groove 83 is formed so that the groove width tapers from the radially inner side toward the radially outer side.

Further, the small groove 83 extends so that the base end side (radially inner side) communicates with the clearance C1 and the distal end side (radial outer side) extends radially outward from the outer diameter D3 of the shaft portion 124a. It is formed to do. That is, in a state where the end portion 124f of the shaft portion 124a is in contact with the end surface 80a of the hole stone 80 (see the solid line portion in FIG. 4B), the tip that is radially outward of the small groove 83 has a diameter larger than that of the shaft portion 124a. It is formed so as to protrude outward in the direction.
Thereby, regardless of the state of the shaft portion 124a, the opening on the shaft portion 124a side (the lower side in FIG. 4A) of the clearance C1 is always in contact with the atmosphere A through the small groove 83.

Here, in the state where the end portion 124f of the shaft portion 124a is in contact with the end surface 80a of the hole stone 80, the tenon 124c side of the opening portion surrounded by the end portion 124f of the shaft portion 124a and the small groove 83 is formed. When the opening area of the opening K1 formed in is defined as M1, the opening area M1 is defined by the groove width W1 (see FIG. 4B) and the groove depth H1 (see FIG. 4B) on the radially inner side of the small groove 83. It can be obtained based on the product with FIG. That is, the opening area M1 can be expressed by the following formula (1).
M1≈W1 × H1 (1)

The cross-sectional area C of the clearance C1 can be obtained based on the inner diameter D1 of the insertion hole 81 and the outer diameter D2 of the tenon 124c. That is, the cross-sectional area C can be expressed by the following formula (2).
^{C = π (D1-D2)} 2/4 ··· (2)

The opening area M1 and the cross-sectional area C thus obtained are as follows, where N is the number of small grooves 83 formed:
M1 × N> C (3)
It is set to satisfy.
When the opening area M1, the cross-sectional area C, and the number N of formed small grooves 83 satisfy the formula (3), the lubricant oil J can be prevented from flowing out and scattering.

  More specifically, as shown in FIG. 4A, the lubricating oil J injected into the clearance C1 receives the pressure of the atmosphere A on the recess 82 side of the hole stone 80, and on the end face 80a side of the hole stone 80. Subject to atmospheric pressure A. At this time, the area of the lubricating oil J that contacts the atmosphere A on the recess 82 side of the hole stone 80 is a cross-sectional area C, and the area of the lubricating oil J that contacts the atmosphere A on the end face 80a side of the hole stone 80 is an opening. This is the product of the area M1 and the number N of small grooves 83 formed.

Since the opening area M1, the cross-sectional area C, and the number N of small grooves 83 are set so as to satisfy the expression (3), the lubricating oil J is more concentrated on the hole stone 80 than on the recess 82 side of the hole stone 80. The end face 80a side receives a larger pressure. In addition, in a state where the end portion 124f of the shaft portion 124a is in contact with the end surface 80a of the hole stone 80 (see the solid line portion in FIG. 4B), the tip of the small groove 83 protrudes radially outward from the shaft portion 124a. Therefore, the shaft 124a side of the lubricating oil J is always in contact with the atmosphere A.
For this reason, even when the clearance C2 between the end portion 124f of the shaft portion 124a and the end surface 80a on the shaft portion 124a side of the hole stone 80 is smaller than the clearance C1, the capillary phenomenon of the lubricating oil J is suppressed. The

(effect)
Therefore, according to the first embodiment described above, the plurality of small grooves 83 are formed in the end face 80a of the hole stone 80, so that the lubricating oil J injected into the clearance C1 is the base portion 124a on the proximal end side of the tenon 124c. Can be prevented from flowing out to the end portion 124f side. For this reason, it is possible to prevent the lubricant oil J from flowing out and scattering even if the shaft portion 124a is repeatedly moved in the axial direction by the clearance C2 referred to as agitation.
Moreover, since it is not necessary to form a groove for preventing the scattering of the lubricating oil J around the tenon 124c as in the prior art, the strength of the tenon 124c can be prevented from being lowered.

  Further, each small groove 83 extends so that the base end side (radial inner side) communicates with the clearance C1 and the distal end side (radial outer side) extends radially outward from the outer diameter D3 of the shaft portion 124a. It is formed to exist. For this reason, even when the end portion 124f of the shaft portion 124a is in contact with the end surface 80a of the hole stone 80, the opening on the shaft portion 124a side (the lower side in FIG. 4A) of the clearance C1 forms the small groove 83. Through the atmosphere A. Therefore, for example, even when the lubricating oil J is excessively injected into the insertion hole 81, the capillary phenomenon of the lubricating oil J can be reliably suppressed, and the lubricating oil J can be effectively discharged and scattered. Can be prevented.

  Of the openings surrounded by the end portion 124f of the shaft portion 124a and the small groove 83, the opening area of the opening K1 formed on the tenon 124c side is M1, the sectional area C of the clearance C1, and The number N of small grooves 83 formed is set so as to satisfy Expression (3). For this reason, the lubricating oil J injected into the clearance C <b> 1 receives a larger pressure on the end surface 80 a side of the hole stone 80 than on the recess 82 side of the hole stone 80. Therefore, the capillary phenomenon of the lubricating oil J can be more reliably suppressed.

  In the above-described first embodiment, the case where the small groove 83 is formed so that the tip extends to the outside in the radial direction from the outer diameter D3 of the shaft portion 124a has been described. However, the present invention is not limited to this, and it is sufficient that a groove is formed at least on the radially inner side of the outer diameter D3 of the shaft portion 124a. Thereby, the pressure which the lubricating oil J exposed to the end surface 80a side of the hole stone 80 receives from air | atmosphere A can be enlarged compared with the case where the groove | channel is not formed in the conventional hole stone 80. FIG. For this reason, compared with the past, the outflow and scattering of the lubricating oil J can be suppressed.

  In the first embodiment described above, the case where the small groove 83 is formed in the end surface 80a of the hole stone 80 has been described. However, the present invention is not limited to this, and it is sufficient that the small groove 83 is formed in at least one of the end surface 80a of the hole stone 80 and the end portion 124f of the shaft portion 124a.

(Second embodiment)
Next, a second embodiment of the present invention will be described based on FIG. 5 with reference to FIGS.
FIG. 5 is a plan view of the bearing in the second embodiment. In addition, the same aspect as 1st embodiment is attached | subjected and demonstrated (it is the same also about the following embodiment).
In this second embodiment, the train wheel 100 and the escapement / speed control device 40 of the movement 100 of the mechanical timepiece 10 are rotatably supported by bearing parts 180 to 189 provided on the main plate 102 and the train wheel bridge 162. At least the bearing portions 181 to 189 have hole stones 80, and tenons 120b to 142b for rotatably supporting the train wheel and the escapement / speed control device 40 are inserted into the hole stones 80. Basic structure such as a point in which the insertion hole 81 is formed, and a structure in which the lubricating oil J is injected into the clearance (tenon backlash) between the insertion hole 81 and the tenons 120b to 142b. Is the same as that of the first embodiment described above (the same applies to the following embodiments).

  Since each of the bearing portions 181 to 189 has the same mode, in the following description, similarly to the first embodiment described above, the tenon 124c of the shaft portion 124a constituting the second wheel & pinion 124 is rotatably supported. Only the bearing portion 182 to be described will be described, and description of the other bearing portions 181, 183 to 189 will be omitted (the same applies to the following embodiments).

Here, as shown in FIG. 5, the difference between the second embodiment and the first embodiment described above is that a plurality of ends formed on the end surface 80 a on the shaft portion 124 a side in the hole stone 80 of the second embodiment. Located in the small groove 84.
The plurality of small grooves 84 are formed radially around the insertion hole 81 of the hole stone 80. In addition, the small groove 84 extends so that the proximal end, which is radially inner, communicates with the clearance C1, and the distal end, which is radially outer, extends to the radially outer side than the outer diameter D3 of the shaft portion 124a. Is formed.

  Further, the small groove 84 is formed so that the groove width gradually becomes wider from the proximal end side which is radially inward toward the distal end side, and the groove width on the distal end side is larger than the groove width W2 on the proximal end side of the small groove 84. W3 is set large. A semicircular groove 84 a having a substantially semicircular shape in plan view and communicating with the small groove 84 is formed at the tip of the small groove 84. Under such a configuration, the small groove 84 has a gradually decreasing groove sectional area toward the proximal end side.

  Here, in FIG. 5, the scale of each part is appropriately changed in order to make the shape of the small groove 84 easy to understand. That is, the groove width W2 on the proximal end side of the small groove 84 is set to be substantially the same as the groove width W1 (see FIG. 4B) of the small groove 83 in the first embodiment described above. In the state where the end portion 124f of the shaft portion 124a is in contact with the end surface 80a of the hole stone 80, the opening portion surrounded by the end portion 124f of the shaft portion 124a and the small groove 84 is formed on the radially inner side. The opening area M2 of the opening K2 formed on the tenon 124c side is set to be substantially the same as the opening area M1 in the first embodiment described above. For this reason, it is difficult for the lubricating oil J to flow out into the small groove 84.

  Even if the lubricating oil J flows out to the small groove 84, the small groove 84 has a gradually decreasing groove cross-sectional area toward the proximal end side, so that the capillary phenomenon acts on the lubricating oil J and lubricates. Oil J stays in the small groove 84 near the center in the radial direction where the groove width is narrow.

(effect)
Therefore, according to the second embodiment described above, in addition to the same effects as those of the first embodiment described above, even if the lubricant oil J flows out into the small groove 84, the lubricant oil J stays in the center in the radial direction. Therefore, the lubricating oil J can be prevented from flowing out and scattering more reliably.
Further, since the lubricating oil J stays near the radial center in the end portion 124f of the shaft portion 124a, the frictional resistance generated between the end portion 124f and the end surface 80a of the hole stone 80 can be reduced. For this reason, it becomes possible to rotate the axial part 124a more smoothly.

In the second embodiment described above, the groove width W2 on the proximal end side of the small groove 84 is set to be substantially the same as the groove width W1 (see FIG. 4B) of the small groove 83 in the first embodiment described above. Explained the case. However, the present invention is not limited to this, and the groove width W2 of the small groove 84 may be set narrower than the groove width W1 of the small groove 83. For example, the groove width W3 on the distal end side of the small groove 84 may be set to be substantially the same as the groove width W1 of the small groove 83.
Even in such a case, the pressure received from the atmosphere A by the lubricating oil J that flows out to the tip end side of the small groove 84 is larger than the pressure that the lubricating oil that flows out from the conventional shaft end receives from the atmosphere. . For this reason, it becomes possible to suppress the outflow and scattering of the lubricating oil J as a result.

  Furthermore, in the second embodiment described above, the case where the small groove 84 is formed in the end surface 80a of the hole stone 80 has been described. However, the present invention is not limited to this, and it is only necessary that the small groove 84 be formed in at least one of the end surface 80a of the hole stone 80 and the end portion 124f of the shaft portion 124a.

  In the second embodiment described above, the case where the tip of the small groove 84 is formed to extend to the outside in the radial direction from the outer diameter D3 of the shaft portion 124a has been described. However, the present invention is not limited to this, and it is sufficient that a groove is formed at least on the radially inner side of the outer diameter D3 of the shaft portion 124a. Thereby, the pressure which the lubricating oil J exposed to the end surface 80a side of the hole stone 80 receives from air | atmosphere A can be enlarged compared with the case where the groove | channel is not formed in the conventional hole stone 80. FIG. For this reason, compared with the past, the outflow and scattering of the lubricating oil J can be suppressed.

  In the second embodiment described above, the case where the semicircular groove 84a is formed in communication with the tip of the small groove 84 has been described. However, the small groove 84 may have a substantially isosceles triangular shape in plan view without forming the semicircular groove 84a.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIG.
FIG. 6 is a plan view of a bearing in the third embodiment.
In this third embodiment, the point that a plurality of small grooves 85 are formed radially on the end surface 80a of the hole stone 80 is the same as in the second embodiment described above.

  Here, as shown in FIG. 6, the difference between the third embodiment and the second embodiment is that the small groove 84 of the second embodiment has a distal end side that is radially outward from a proximal end side that is radially inner. The small groove 85 of the third embodiment is formed such that the inner groove 85a formed on the inner side in the radial direction and the outer side in the radial direction of the inner small groove 85a are formed. In addition, the outer small groove 85b formed wider than the inner small groove 85a has two grooves.

The inner small groove 85a is formed so as to communicate with the clearance C1, and the tip thereof extends to a portion corresponding to the outer diameter D3 of the shaft portion 124a.
On the other hand, the outer small groove 85b is formed so as to extend radially outward from the tip of the inner small groove 85a, and communicates with the inner small groove 85a.
Here, the groove width W4 of the inner small groove 85a is set to be substantially the same as the groove width W2 of the small groove 84 in the third embodiment described above. Further, the groove width W5 of the outer small groove 85b is set to be substantially the same as the groove width W3 of the small groove 84 in the third embodiment described above.

(effect)
Therefore, according to the above-described third embodiment, the same effects as those of the above-described second embodiment can be achieved. Further, since the inner small groove 85a is formed over the entire radial direction of the end portion 124f of the shaft portion 124a, the lubricating oil J can be retained more between the end portion 124f and the end surface 80a of the hole stone 80. it can. For this reason, the frictional resistance generated between the end portion 124f and the end surface 80a of the hole stone 80 can be further reduced, and the shaft portion 124a can be rotated more smoothly.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIG.
7A and 7B show a bearing structure according to the fourth embodiment. FIG. 7A is a sectional view of the bearing, and FIG. 7B is a sectional view taken along line YY in FIG.
As shown in FIGS. 7A and 7B, the difference between the fourth embodiment and the first embodiment is that a plurality of small grooves 83 are radially formed in the hole stone 80 of the first embodiment. On the other hand, the hole stone 80 of the fourth embodiment is formed with an annular groove 86 having a substantially annular shape in an axial plan view.

  The annular groove 86 is formed around the insertion hole 81 so as to communicate with the insertion hole 81. The outer diameter D4 of the annular groove 86 is set smaller than the outer diameter D3 of the shaft portion 124a. For this reason, the outer peripheral portion of the end portion 124f of the shaft portion 124a contacts the end surface 80a of the hole stone 80 even when the shaft portion 124a is moving toward the hole stone 80 (the state shown in FIG. 7A). Touch. Therefore, the space K3 is formed by the annular groove 86 and the end portion 124f of the shaft portion 124a.

(effect)
Therefore, according to the above-described fourth embodiment, the pressure received from the atmosphere A by the lubricating oil J injected into the insertion hole 81 is higher than the pressure received at the distal end side of the tenon 124c (the shaft portion 124a). Pressure at the end 124f side) increases. For this reason, there can exist an effect similar to the above-mentioned 1st embodiment. In addition to this, the variation of grooves that can be formed in the end face of the hole stone 80 can be increased.

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described with reference to FIG.
8A and 8B show a bearing structure according to the fifth embodiment, in which FIG. 8A is a sectional view of the bearing, and FIG. 8B is a sectional view taken along line ZZ in FIG.
As shown in FIGS. 8A and 8B, the difference between the fifth embodiment and the fourth embodiment is that the annular groove 86 formed in the hole stone 80 of the fourth embodiment is inserted. The annular groove 87 formed in the hole stone 80 of the fifth embodiment is in a state of being separated from the insertion hole 81 while being formed so as to communicate with the hole 81.

  More specifically, an annular groove 87 is formed on the end face 80 a of the hole stone 80 so as to surround the periphery of the insertion hole 81. The annular groove 87 is formed such that the inner peripheral surface thereof is separated from the insertion hole 81. Further, the outer diameter D5 of the annular groove 87 is set larger than the outer diameter D3 of the shaft portion 124a.

  Under such a configuration, when the shaft portion 124a moves toward the cobblestone 80, the radially inner side of the end surface 80a of the cobblestone 80 comes into contact with the end portion 124f of the shaft portion 124a. At this time, the capillary phenomenon of the lubricating oil J acts on the contacted portion, and the lubricating oil J flows out into the annular groove 87. However, since the outer diameter D5 of the annular groove 87 is set larger than the outer diameter D3 of the shaft portion 124a, the lubricating oil J flowing into the annular groove 87 comes into contact with the atmosphere A. In such a state, the lubricant oil J has a larger area in contact with the atmosphere A on the annular groove 87 side than the area in contact with the atmosphere A on the recess 82 side of the hole 80.

(effect)
Therefore, according to the fifth embodiment described above, in addition to achieving the same effects as those of the first embodiment described above, it is possible to further increase the variation of grooves that can be formed in the end face 80a of the hole stone 80a. Can do.

The present invention is not limited to the above-described embodiment, and includes various modifications made to the above-described embodiment without departing from the spirit of the present invention.
For example, in the above-described embodiment, the case where the bearings 181 to 189 having the bearing structure according to the present invention are provided in the movement 100 of the mechanical timepiece 10 that is a wristwatch has been described. However, the present invention is not limited to this, and the bearing portions 181 to 189 can be used for various watches.

  Further, in the above-described embodiment, the case has been described in which the hole stone 80 is provided in the main plate 102 or the train wheel bridge 162 and the insertion holes 81 into which the tenons 120b to 130c can be inserted are formed in the hole stones 80, respectively. However, the present invention is not limited to this, and the through hole 81 may be directly formed in the base plate 102 or the train wheel bridge 162 without providing the hole stone 80 in the base plate 102 or the train wheel bridge 162. In this case, the grooves 83 to 87 for suppressing the outflow or scattering of the lubricating oil J may be formed in the main plate 102 or the train wheel bridge 162.

Furthermore, in the above-described embodiment, a case has been described in which each of the bearing portions 181 to 189 has a structure in which lubricating oil J such as precision machine oil is injected and a structure having the grooves 83 to 87. However, the present invention is not limited to this, and it is only necessary that the grooves 83 to 87 are formed in at least one of the bearing portions 181 to 189.
Further, it is sufficient that at least one of the bearing portions 181 to 189 has a bearing structure to which the lubricating oil J is injected. In this case, it is only necessary that the grooves 83 to 87 are formed in the bearing portions 181 to 189 to which the lubricating oil J is injected.

  Furthermore, in the above-described embodiment, no surface treatment is applied to each of the grooves 83 to 87 formed in the hole stone 80, but it is desirable to apply an oil repellent treatment to each of the grooves 83 to 87. By comprising in this way, it becomes possible to suppress the outflow and scattering of the lubricating oil J more reliably.

10 Mechanical clock (clock)
80 hole stone (bearing body)
80a End face (shaft end face)
81 Insertion holes 83, 84, 85 Small groove 85a Inner small groove 85b Outer small groove 86, 87 Annular groove 100 Movement 120 Incense car 120b, 124c, 126b, 126c, 128b, 128c, 130b, 130c Tenon 120f Incandescent box true (shaft body)
124 Second car (car)
124a, 126a, 128a, 130a Shaft (shaft body)
124f End 126 Third wheel (number wheel)
128 4th car
130 escape wheel 140 balance 142 ankle 180-189 bearing C1 clearance D3 outer diameter

Claims (12)

A shaft having a tenon at the end;
A bearing body in which an insertion hole for inserting the tenon is formed,
In the timepiece bearing structure in which the shaft body is rotatably supported by the bearing body by inserting the tenon through the insertion hole.
The timepiece bearing structure according to claim 1, wherein a first groove is formed on the shaft body side end surface of the bearing body at a position that is at least radially inner than the outer diameter of the shaft body.   The timepiece bearing structure according to claim 1, wherein the first groove is formed by forming a plurality of small grooves in a radial pattern. A shaft having a tenon at the end;
A bearing body provided on at least the tenon side of the shaft body and having an insertion hole for inserting the tenon;
In the watch bearing structure in which the tenon is inserted into the insertion hole, and the shaft body is rotatably supported by the bearing body,
A second groove communicating with the clearance between the tenon and the insertion hole is formed in at least one of the tenon side end of the shaft body and the shaft body side end surface of the bearing body. A watch bearing structure characterized by   The timepiece bearing structure according to claim 3, wherein the second groove is formed by forming a plurality of small grooves radially.   5. The timepiece bearing structure according to claim 2, wherein the plurality of small grooves are formed so as to extend outward in the radial direction from the outer diameter of the shaft body. The opening of the opening formed on the tenon side is formed by being surrounded by the end surface and the small groove in a state where the end of the shaft body and the end surface of the bearing body are in contact with each other. When the area is M, the number of the small grooves is N, and the sectional area of the clearance between the tenon and the insertion hole is C,
The opening area M, the number N of small grooves, and the cross-sectional area C of the clearance are
M × N> C
6. The timepiece bearing structure according to claim 2, wherein the timepiece bearing structure is set so as to satisfy   The timepiece bearing structure according to any one of claims 2 and 4, wherein the small groove is formed so that a cross-sectional area of the groove gradually decreases toward a radially inner side. The small groove is composed of an inner small groove formed radially inward from the outer diameter of the shaft body, and an outer small groove formed at least radially outward from the outer diameter of the shaft body and communicating with the inner small groove,
7. The timepiece bearing structure according to claim 2, wherein a groove cross-sectional area of the outer small groove is set larger than a groove cross-sectional area of the inner small groove.   9. The timepiece according to claim 1, wherein the first groove has an annular groove in an axial plan view. Bearing structure.   The timepiece bearing structure according to any one of claims 3 to 8, wherein the second groove has an annular groove in an axial plan view. A watch movement with a barrel wheel, watch wheel, escape wheel, ankle and balance,
A timepiece bearing structure according to any one of claims 1 to 10, wherein the watch bearing structure according to any one of claims 1 to 10 is used in at least one of the barrel wheel, the ankle, and the wheel.   A timepiece comprising the movement according to claim 11.

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