JP5975618B2 - Vibration-proof bearing mechanism for balance, balance with balance and watch with the balance - Google Patents

Description

  The present invention relates to a vibration-proof bearing mechanism for a balance, a balance equipped with the balance, and a timepiece equipped with the balance.

  Axial direction (direction parallel to the true extension direction) or lateral direction (perpendicular to the true extension direction) applied to the balance of the watch fitted to the wrist due to a sudden movement of the wrist of the watch user. The tenons at both ends of the balance are supported by vibration-proof bearing mechanisms so that the impact in the right direction is reduced. As this type of vibration-proof bearing mechanism, a stone receiving stone, a hole stone, a hole stone frame that supports the hole stone, a vibration-resistant seat body that supports the hole stone frame, and a stone receiving stone between the vibration-resistant seat body and the hole stone frame. A vibration-proof bearing mechanism having a presser spring that presses against a hole stone frame is known (Patent Document 1 and Patent Document 2).

  More specifically, this type of vibration-resistant bearing mechanism 101 has, for example, a structure as shown in FIGS. 10 and 11 (a) and 11 (b), and a stone 110 that functions as a thrust bearing, and a journal bearing. A working hole stone 117, a cylindrical portion 121, and an enlarged diameter portion 122 on the opening end 121 a side thereof, and the stone diameter 120 that supports the stone 110 in the cylindrical portion 121 while supporting the stone 110 in the enlarged diameter portion 122, The vibration-resistant seat body 130 that supports the hole stone frame 120 and the vibration-receiving seat body 130 that is disposed between the hole stone frame 120 and the stone holder 110 are pressed against the opening end 121 a of the cylindrical portion 121 of the hole stone frame 120. And an anti-vibration spring 137 to be attached.

  The anti-vibration seat body 130 holds the entire components such as the anti-vibration holding spring 137, the anti-vibration stone 110, and the anti-vibration hole stone frame 120. More specifically, the vibration-resistant presser spring 137 holds the vibration-resistant receiving stone 110 and the vibration-resistant hole stone frame 120 to absorb the impact force to the balance 103, and the movement of the stone receiving stone 110 and the hole stone frame 120 when the shock is received ( Displacement) and help restore to the original position. The anti-vibration stone 110 supports the balance stem 140 against the forces in the extending directions (axial directions) A1 and A2 of the central axis C of the balance stem 140 of the balance 103. The anti-vibration hole stone frame 120 is a movable frame that is movable against the anti-vibration seat body when it is elastically pressed against the anti-vibration seat body 130 by the holding spring 137 and receives a force in the radial direction B. The stone 117 is accommodated inside and supported.

  The vibration-proof bearing mechanism 101 supports the balance stem 140 at the small diameter tenon portions 141F and 141R at both ends of the balance stem 140 of the balance 103 of the mechanical timepiece 102. In the following description, the vibration-resistant bearing mechanisms 101F and 101R and their components or elements are indicated by adding the suffix F or R after the same reference numerals. When the two are not distinguished or collectively referred to, the subscripts F and R are omitted.

  The tenon receiving surfaces or thrust bearing surfaces 111F and 111R of the stones 110F and 110R are flat. Anti-vibration bearing mechanism (so-called balance wheel upper bearing) 101F supporting the tenon portion 141F of the balance stem 140 on the back cover side of the watch 102 and the balance receiving portion 101R and the tenon portion 141R of the balance stem 140 on the dial side of the watch 102. The bearing mechanism (the so-called balance balance bearing) 101R is actually configured in the same manner.

  Here, in addition to the upper and lower vibration-resistant bearings 101F and 101R in the form of the vibration-resistant bearing mechanism 101, the balance 103 includes a balance stem 140, a balance 150, and a hairspring 155. The balance receiver 105F on the back cover side has a balance 105. Installed on. The balance holder 105 and the vibration-proof bearing 101R on the dial side are attached to the main plate 108, respectively. The hairspring 155 has a spiral shape around the central axis C of the balance stem 140 and is attached to the whisker ball 143 at the inner peripheral end of the spiral spring, and has a whisker (not shown) at the outer peripheral end of the spiral spring. It is attached and the effective length of the spiral (spring) is adjusted by a slow and quick needle (not shown).

  The controlled escapement 104 including the balance 103 includes an ankle 106 and a escape wheel 107 supported by the main plate 108 in addition to the balance 103. The ankle 106 is engaged with the swing stone 144 of the swing seat at the hook tip 161, and is engaged with the escape tooth 162 of the escape wheel 107 with an entering pallet and an exit pallet (not shown). The escape wheel & pinion 107 is meshed with the fourth wheel & pinion 170 at the kana portion 164. A fourth wheel & pinion 170 that operates the governor escapement 104 with the power of the mainspring (not shown) is intermittently rotated at a predetermined rotation speed by a escape wheel & pinion 107 that is intermittently rotated at a speed defined by the balance 103. The

  In the conventional timepiece 102 having the conventional balance 103 having the conventional vibration-proof bearing mechanisms 101F and 101R configured as described above, the balance 103 is in an appropriate state as shown in FIGS. 13 (a) and 13 (b). When in PS0, watch 2 operates appropriately. That is, the anti-vibration bearing mechanisms 101F and 101R on the back cover side and the dial side and the mechanisms so that the flat tenon receiving surfaces 111F and 111R of the stones 110F and 110R are perpendicular to the central axis C of the balance stem 140. When the receiving stones 110F and 110R of 101F and 101R are arranged and the central axis C of the balance stem 140 is not actually inclined, the vibration-proof bearing mechanism 101F on the back cover side is positioned on the vibration-proof bearing mechanism 101R on the dial side. Even if the flat posture PP1 is adopted, even if the dial-side vibration-proof bearing mechanism 101R adopts the back-flat posture PP2 in which the dial-side vibration-proof bearing mechanism 101R is positioned on the back cover-side vibration-proof bearing mechanism 101F, the balance stem 140 is located on the lower side. Anti-vibration bearing mechanism 1 on the dial side or back cover side located below the positions C0R and C0F through which the center axis C actually passes among the end surfaces 145R and 145F of the portions 141R and 141F. 1R, 101F of endstone 110R, tenon 110F receiving surface 111R, 111F abuts, is to be rotated the position C0R, the C0F the center. Therefore, the balance with hairspring 103 can actually operate in the same manner regardless of the postures PP1 and PP2 of the timepiece 102, and the difference in posture can be minimized.

  However, in the conventional timepiece 102 having the conventional balance 103 having the conventional vibration-resistant bearing mechanisms 101F and 101R, the orientation or posture in which the vibration-resistant bearing mechanism 101F on the back cover side is positioned on the vibration-resistant bearing mechanism 101R on the dial side. (Hereinafter, also referred to as “flat posture”) When the watch 102 is disposed on the PP1 and in the orientation or posture in which the anti-vibration bearing mechanism 101R on the dial side is positioned on the anti-vibration bearing mechanism 101F on the back cover side (hereinafter, The balance of the balance 103 may be different from the case where the timepiece 102 is disposed on the PP2.

  For example, as shown in FIGS. 14 (a) and 14 (b), the stone holder 110F on the balance holder side or the back cover side is tilted slightly (for example, about 1 degree) by the presser spring 137F and the hole stone frame 120F. In the state PS1 attached to the watch, as shown in FIG. 14A, the timepiece 102 is arranged in a flat posture PP1 in which the vibration-proof bearing mechanism 101F on the back cover side is positioned on the vibration-proof bearing mechanism 101R on the dial side. And the case where the timepiece 102 is arranged in the back flat posture PP2 where the vibration-proof bearing mechanism 101R on the dial side is positioned on the vibration-proof bearing mechanism 101F on the back cover side as shown in FIG. Now, the balance 103 is in a different state. The inclination of the stone 110F typically occurs when the hole stone frame 120F is inclined with respect to the vibration-proof seat body 130F.

  In the state PS1 in which the balance stone 110F on the balance holder 105 side is tilted and attached, the vibration-proof bearing mechanism 101R on the dial side is positioned on the lower side as shown in FIG. In the flat posture PP1 in which the mortar 110R receives the end face of the tenon 141R of the balance stem 140 at its tenon receiving surface 111R, the balance stem 140 is the same as in FIGS. 13 (a) and 13 (b). The tenon face 111R of the stone 110R of the anti-vibration bearing mechanism 101R on the dial plate side located below the end face 145R of the tenon part 141R located on the side at the position C0R that actually passes through the center axis C, It is rotated around the position C0R.

  On the other hand, the timepiece 102 is inverted, and the anti-vibration bearing mechanism 101F on the balance 105 side (back cover side) is positioned on the lower side as shown in FIG. In the posture PP2 in which the mortar 110F receives the end surface of the tenon 141F of the balance stem 140 at the tenon receiving surface 111F, unlike the cases of FIGS. 13 (a) and 13 (b) and FIG. 140 is apart from the central axis C, and on the side of the balance 105 located on the lower end edge CaF of the end surface 145F of the tenon portion 141F located on the lower side, which coincides with the inclination direction of the stone 110. It contacts with the tenon receiving surface 111F of the stone 110F of the vibration-proof bearing mechanism 101F. Therefore, the rotation center CaF of the balance stem 140 is different from the center axis C of the balance stem 140 at a point away from the center axis C by Δpr (a size corresponding to the radius of the tenon portion 141 and about several tens of μm). It becomes CaF (Ca) and the rotation axis is not stable.

  Therefore, in this state PS1, it is difficult to avoid a considerable difference in rate due to the operation of the balance with hairspring 103 being different when the timepiece 102 takes the flat posture PP1 and when the watch 102 takes the flat posture PP2.

  Further, for example, as shown in FIGS. 15A and 15B (particularly FIG. 15B), PS2 when the central axis C of the balance stem 140 is inclined in the back flat posture PP2, 14A and 14B, as with PS1, the balance stem 140 is separated from the central axis C, and the central axis C of the balance stem 140 of the end surface 145F of the tenon portion 141F located on the lower side is located. At the edge CaF on the side that coincides with the inclination direction, the tenon receiving surface 111F of the stone 110F of the anti-vibration bearing mechanism 101F on the balance 105 side located below the edge CaF. Therefore, the rotation center CaF of the balance stem 140 is different from the center axis C of the balance stem 140 at a point away from the center axis C by Δpr (a size corresponding to the radius of the tenon portion 141 and about several tens of μm). It becomes CaF (Ca) and the rotation axis is not stable.

  Even in this state PS2, it is difficult to avoid a significant difference in rate due to the difference in the operation of the balance with the balance 102 when the watch 102 takes the flat posture PP1 and when the watch 102 takes the flat posture PP2.

  The central axis C of the balance stem 140 may be inclined when, for example, the balance of the weight of the balance 150 in the circumferential direction is deviated. Strictly speaking, for example, the center axis of the balance stem 140 according to the torque being applied to the balance stem 140 via the hair ball 143 during the winding operation or unwinding operation of the spiral spring 155 in the form of a spiral spring. C tilts somewhat or fluctuates slightly.

  Further, as shown in FIGS. 16A and 16B, in the case of the state PS3 in which the end surface 145F of the tenon 141F on the balance 105 side is inclined with respect to the central axis C of the balance stem 140, In the flat posture PP2, the end edge CaF of the end face 145F that protrudes with the inclination comes into contact with the tenon receiving face 111F of the stone holder 110F of the vibration-proof bearing mechanism 101F on the balance holder 105 side located below the end edge CaF. Therefore, the rotation center CaF of the balance stem 140 is different from the center axis C of the balance stem 140 at a point away from the center axis C by Δpr (a size corresponding to the radius of the tenon portion 141 and about several tens of μm). It becomes CaF (Ca) and the rotation axis is not stable.

  Even in this state PS3, it is difficult to avoid a considerable difference in rate due to the operation of the balance with hairspring 103 being different when the timepiece 102 takes the flat posture PP1 and when the watch 102 takes the flat posture PP2.

  On the other hand, the tenon 141F of the balance stem 140 is to avoid an increase in the possibility of a difference in rate for various reasons as described above between when the watch 102 takes the flat posture PP1 and when the watch 102 takes the flat posture PP2. , 141R, instead of keeping the end surfaces 145F and 145R flat, it is also proposed to curve the end surfaces or tenons 145F and 145R in a convex shape.

  However, since the diameters of the tenons 141F and 141R are usually about 0.1 mm at most, it is difficult to keep the dimensional accuracy of the shape of the convex curved surface high. In other words, the tenon length varies with the variation in the shape of the convex curved surface. When the variation in the length of the balance stem 140 is increased, there is a high possibility that the shape of the hairspring 155 is different between the flat posture PP1 and the back flat posture PP2. Accordingly, in the case where the balance spring 155 which should originally extend in a spiral shape in a plane perpendicular to the central axis C of the balance stem 140 is, for example, when the watch is in the flat posture PP1 or in the reverse flat posture PP2. It is difficult to avoid the possibility that the shape of the spring becomes fluctuated to some extent and the spring characteristics fluctuate and a difference in yield occurs.

JP 2009-139180 A Japanese Patent No. 4598701

  The present invention has been made in view of the above-described points, and an object of the present invention is to provide a vibration-proof bearing mechanism for a balance capable of minimizing fluctuations in the operation of the balance due to fluctuations in the support state of the balance. The object is to provide a balance with a balance and a watch with the balance.

  In order to achieve the above object, the vibration-proof bearing mechanism of the balance of the present invention includes a stone that functions as a thrust bearing, a hole stone that functions as a journal bearing, a hole stone frame that accommodates the hole stone and supports the hole stone, A rock-resistant seat body that accommodates the hole stone frame and supports the hole stone frame and has an engaging portion on the opening end side of the large diameter, and a stone receiving stone on the inner circumferential side supported by the engaging portion of the vibration-resistant seat body on the outer peripheral side A vibration-resistant bearing mechanism of a balance having a holding spring that elastically presses and holds the hole against the hole stone frame, and is a surface that faces the end face of the shaft that is supported by the vibration-resistant bearing mechanism and is in contact with the end face of the shaft Consists of a convex surface curved so as to protrude outward.

  In the vibration-proof bearing mechanism of the balance of the present invention, `` consisting of a convex surface curved so that the surface facing the end surface of the shaft supported by the vibration-resistant bearing mechanism of the stone and contacting the end surface of the shaft protrudes outside. '' Even if the stone supported by the hole stone frame and the holding spring is tilted, the center axis (center of gravity) of the shaft is tilted, or the end surface of the shaft is tilted, As compared with the case where the “surface facing the end surface of the shaft and abutting against the end surface of the shaft” is a “plane”, the positional deviation of the rotation support portion due to the inclination is minimized. Therefore, for example, the influence of the watch posture on the rate can be minimized. Moreover, since “the surface of the stone (tenon receiving surface) is a convex surface curved so as to protrude outward”, it can be supported by actually contacting the end surface of the shaft to be rotated and supported at one point. Shaft rotation is easy to stabilize. In this case, since the end surface of the end of the shaft (balance) or the tip (tenon) of the end (tenon) to be supported by the vibration-proof bearing mechanism of the balance can be made flat, ) Can be minimized.

  In the vibration-proof bearing mechanism of the balance of the present invention, typically, the convex surface of the stone is made of a part of a spherical surface.

  In that case, the convex surface of the stone is easily formed with high accuracy. Note that the convex surface may have another shape if desired as long as it is a spheroid surface including a spherical surface in a broad sense. If the convex surface is an outwardly convex and smoothly curved shape, the convex surface may not have rotational symmetry. However, a partial spherical surface (part of a spherical surface) is used in order to minimize the influence (variation of movement) that the variation of the true support state such as the inclination of the stone receives on the movement of the balance such as the rate. It is preferable.

  In the vibration-proof bearing mechanism of a balance of the present invention, typically, the jewel has a convex lens-like shape, and the perforated stone frame includes a cylindrical portion and a diameter-expanded portion on the opening end side thereof. The holding spring is supported by the engaging portion of the vibration-proof seat body on the outer peripheral side and elastically presses and holds the receiving stone at the enlarged diameter portion of the hole stone frame on the inner peripheral side. Configured as follows.

  In such a case, even if the thickness of the vibration-proof bearing mechanism is minimized and the end face of the shaft facing the bearing mechanism is flat, fluctuations in the balance of the balance due to fluctuations in the true support state are minimized. The movement variation due to the posture difference such as the flat posture and the back flat posture can be suppressed to the minimum.

  In another typical example of the vibration-proof bearing mechanism of the balance of the present invention, the stone is made of a sphere.

  In this case, the stone is formed with high dimensional accuracy, and the fluctuation of the balance of the balance can be suppressed to the minimum.

  In the case of this other typical example, the spherical stone is arranged in the cylindrical region of the hole stone frame so as to be able to contact the hole stone, and the holding spring is provided on the outer peripheral side of the engaging portion of the vibration-resistant seat body. So that the stone is elastically pressed and held on the hole stone frame through the hole stone by pressing the stone on the opposite end surface of the hole stone in the cylindrical region of the hole stone frame on the inner peripheral side. It is configured.

  In that case, the advantage that the stone is a sphere (ball) can be enjoyed in a state where the increase in thickness due to the shape of the jewel is in the form of a sphere (ball) is minimized.

  Typically, in the vibration-proof bearing mechanism of a balance of the present invention, the portion of the hole stone frame that supports the tenon receiving surface of the stone is truncated cone.

  In this case, fluctuations in the balance operation can be minimized. A spherical shape may be used instead of the truncated cone shape.

  The balance with hairspring of the present invention has the vibration-proof bearing mechanism as described above in order to achieve the above object.

  In the balance of the present invention, the shaft supported by the vibration-proof bearing mechanism is made of the balance stem, and the end surface of the tenon portion having a diameter smaller than that of the main body portion of the balance stem is actually planar.

  In this case, the length of the balance can be obtained with high dimensional accuracy, and as a result, fluctuations in the rate depending on whether the watch is in a flat posture or a back flat posture can be minimized.

  The timepiece of the present invention has the vibration-proof bearing mechanism as described above or the balance with hairspring as described above in order to achieve the object.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional explanatory view showing a part of a timepiece according to a preferred embodiment of the present invention having a balance with a vibration resistant bearing mechanism according to a preferred embodiment of the present invention. The vibration-proof bearing mechanism of the balance of FIG. 1 is shown, (a) is a plane explanatory view, (b) is a cross-sectional explanatory view. Cross-sectional explanatory drawing which showed the state which the one end part including the tenon part of a true balance was fitted in the vibration-proof bearing mechanism of the balance of FIG. 1 shows a case where the balance receiving stone on the balance of the balance of the balance of the timepiece of FIG. 1 is tilted. FIG. 1 (a) shows the balance of the balance of the balance and the balance of the balance in the timepiece in the flat position. The cross-sectional explanatory drawing which showed the both ends containing a part, (b) is the cross-sectional explanatory drawing which showed the both ends containing the vibration-proof bearing mechanism of a balance with a balance tenon in the timepiece in a back flat posture. FIG. 1 shows a case where the true tenon portion is tilted when the timepiece is in the back flat position in the vibration-proof bearing mechanism of the timepiece of FIG. 1, wherein (a) is a balance in the timepiece in the flat position. The cross-sectional explanatory drawing which showed the both ends including the tenon part of a vibration-proof bearing mechanism and a balance of a balance of the balance, (b) showed both ends including the vibration-proof bearing mechanism of a balance and the tenon of a balance in a watch in a back-flat position. Cross-sectional explanatory drawing. FIG. 1 shows a case where the end face of the balance receiving side of the balance of the balance of the balance of the balance of the balance of the timepiece of FIG. 1 is in an inclined state. FIG. The cross-sectional explanatory drawing which showed the both ends including the tenon part of a vibration-proof bearing mechanism and a balance of a balance of the balance, (b) showed both ends including the vibration-proof bearing mechanism of a balance and the tenon of a balance in a watch in a back-flat position. Cross-sectional explanatory drawing. The vibration-proof bearing mechanism of another preferable one Example of this invention is shown, (a) is plane explanatory drawing, (b) is sectional explanatory drawing. Sectional explanatory drawing which showed a part of balance with another preferable Example of this invention which showed the state which the one end part containing a true tenon part fitted in the vibration-proof bearing mechanism of FIG. FIG. 7 shows the degree of positional deviation of the rotation center under various conditions in the balance with the vibration-proof bearing mechanism of FIG. 7, and (a) shows the reference case in which the balance and the stone are in a predetermined state. Cross-sectional explanatory drawing, (b) is a cross-sectional explanatory view showing the case where the stone is tilted, (c) is a cross-sectional explanatory view showing the case where the balance is tilted. Cross-sectional explanatory drawing which showed a part of conventional timepiece which has the conventional balance with the conventional vibration-proof bearing mechanism. FIG. 11 shows a conventional vibration-proof bearing mechanism of the timepiece of FIG. 10, wherein (a) is a plane explanatory view and (b) is a cross-sectional explanatory view. Cross-sectional explanatory drawing which showed the state which the one end part containing the tenon part of a true balance was fitted in the vibration-proof bearing mechanism of the balance of FIG. FIG. 11 shows a state in which the vibration-proof bearing mechanism of the balance of the timepiece of FIG. 10 can operate properly, and (a) shows both ends of the balance with the balance of the balance of the balance and the tenon of the balance in the timepiece in a flat position. FIG. 4B is a cross-sectional explanatory view showing both ends including a vibration-proof bearing mechanism of the balance and the tenon of the balance in a timepiece in a flat back position. 10 shows a case where the balance receiving stone on the balance of the balance of the balance of the timepiece of FIG. 10 is tilted. FIG. 10 (a) shows the balance of the balance of the balance and the balance of the balance in the timepiece in the flat position. The cross-sectional explanatory drawing which showed the both ends containing a part, (b) is the cross-sectional explanatory drawing which showed the both ends containing the vibration-proof bearing mechanism of a balance with a balance tenon in the timepiece in a back flat posture. FIG. 10 shows a case where the true tenon portion is tilted when the watch is in the back flat position in the vibration-proof bearing mechanism of the timepiece of FIG. 10, and (a) the balance with the balance in the watch in the flat position. The cross-sectional explanatory drawing which showed the both ends including the tenon part of a vibration-proof bearing mechanism and a balance of a balance of the balance, (b) showed both ends including the vibration-proof bearing mechanism of a balance and the tenon of a balance in a watch in a back-flat position. Cross-sectional explanatory drawing. 10 shows a case where the end face of the balance portion of the balance of the balance in the balance of the balance of the balance of the balance of the timepiece of FIG. 10 is tilted. FIG. The cross-sectional explanatory drawing which showed the both ends including the tenon part of a vibration-proof bearing mechanism and a balance of a balance of the balance, (b) showed both ends including the vibration-proof bearing mechanism of a balance and the tenon of a balance in a watch in a back-flat position. Cross-sectional explanatory drawing.

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

  FIG. 1 shows a part of a timepiece 2 of a preferred embodiment of the present invention having a balance 3 of a preferred embodiment of the present invention equipped with a vibration-proof bearing mechanism 1 of a preferred embodiment of the present invention. 2 (a) and 2 (b) show an enlarged view of the vibration-proof bearing mechanism 1 of the timepiece 2, and FIG. 3 shows an enlarged one end side portion of the balance of the balance 3 including the vibration-resistant bearing mechanism 1. ing.

  In the mechanical timepiece 2, the speed control escapement 4 includes a balance 3, an ankle 6, and a escape wheel 7. These timepiece parts 3, 6, 7 constituting the governor escapement 4 are supported by a main plate 8. The pallet fork 6 is engaged with the swing stone 44 of the swing seat at the box tip 61, and is engaged with the escape tooth 62 of the escape wheel 7 by an entrance pallet and an exit pallet (not shown). The escape wheel 7 is meshed with the fourth wheel 70 at the kana portion 64. The fourth wheel & pinion 70 for operating the escape wheel 7 of the speed control escapement 4 with the power of the mainspring (not shown) is predetermined by the escape wheel 7 that is intermittently rotated at a speed defined by the balance 3. It is intermittently rotated at the rotation speed.

  The balance with hairspring 3 has a balance stem 40, a balance 50, and a hairspring 55, and the balance stem 40 is a vibration-proof bearing at tenon portions 41 </ b> F and 41 </ b> R which are small-diameter end portions on the upper and lower sides (back cover side and dial side). The upper and lower vibration-proof bearings in the form of the mechanism are supported rotatably by the balance upper bearing 1F and balance lower bearing 1R. The end faces 45F and 45R of the tenon portions 41F and 41R are actually planes perpendicular to the central axis C. Accordingly, the tenon length can be accurately formed as compared with the case where the end surface or tenon of the tenon is curved in a convex shape. Therefore, it is easy to accurately form the length and shape of the balance 40, and the tenon tip. The variation in the assembled state can be minimized.

  In the following description, the vibration-resistant bearing mechanisms 1F and 1R and the components and elements thereof are indicated by adding the suffix F or R to the same reference numeral. When the two are not distinguished or collectively referred to, the subscripts F and R are omitted.

  The balance bearing 1 </ b> R on the lower balance or the dial side is attached to the main plate 8, and the balance bearing 1 </ b> F on the upper or back cover side is attached to the base plate 8 via the balance 5. The balance stem 40 also has end shafts 42F and 42R which are larger in diameter than the tenon portions 41F and 41R but smaller in diameter than the other portions of the balance stem 40 on the intermediate side of the tenon portions 41F and 41R. Have. The hairspring 55 has a spiral shape around the central axis (center of gravity axis) C of the balance stem 40, is attached to the whisker ball 43 at the inner peripheral side end of the spiral, and has a whisker at the outer peripheral side end of the spiral ( The effective length of the spiral (spring) is adjusted by a slow and quick needle (not shown).

  Since the upper and lower vibration-resistant bearings 1F and 1R have the same structure and shape in practice, the vibration-resistant bearing mechanism or vibration-resistant bearing 1 will be described unless it is necessary to distinguish between the two.

  A set of balance bearings or a set of anti-vibration bearings, that is, anti-vibration bearing mechanism 1 includes a stone or vibration-resistant stone 10 that functions as a thrust bearing, a hole stone 17 that functions as a journal bearing, and a hole stone frame or vibration-resistant hole stone frame 20 that supports the hole stone 17. And a vibration-resistant seat 30 that supports the stone 10 and the hole stone frame 20, and a pressing spring or a vibration-resistant pressing spring 37.

  The vibration-resistant bearing mechanism 1 supports the balance stem 40 at the small diameter tenon portions 41F and 41R at both ends of the balance 40 of the balance 3 of the mechanical timepiece 2. The tenon receiving surface or thrust bearing surface 11F, 11R of the stones 10F, 10R is a partial spherical surface (a part of a spherical surface having a large radius). The tenon receiving surfaces 11F and 11R of the stones 10F and 10R need not be partial spherical surfaces (parts of spherical surfaces having large radii) as long as they are curved surfaces (convex surfaces) that are smoothly curved outwardly and have rotational symmetry. Good.

  The stone 10 has partial spherical end faces 11 and 12 like the convex lens as described above. When the partial spherical surfaces of the end surfaces 11 and 12 are the same, it is not necessary to identify the front and back when assembling. However, the end surface 12 may have a partial spherical shape with different diameters, or may have another shape such as a flat shape instead of the partial spherical shape. The anti-vibration stone 10 receives a force in the extending direction (axial direction) A1, A2 of the central axis C of the balance 40 of the balance 3 (A direction when not distinguished or generically referred to as A direction).

  The hole stone 17 is generally disc-shaped, has a mortise 18 at the center, and the outer peripheral surface 17a is cylindrical. On one end surface 17b, a guide recess 17c to the mortise 18 is formed. The other end face 17d is typically planar. However, depending on the case, it may be curved in a concave shape so as to easily maintain an appropriate gap between the convex surface 11 of the stone 10.

The anti-vibration seat 30 includes an end flange-like portion including a small-diameter cylindrical portion 31, a large-diameter cylindrical portion 32, and an end-shaft receiving hole 33a into which the end shaft portion 42 of the balance 40 is loosely fitted. 33, a connecting flange-shaped portion 34, an inclined surface portion 35a (an example of the first inclined surface portion of the present invention ) , 35b ( an example of the second inclined surface portion of the present invention) , a radially inward engagement portion 36, Have The end flange-shaped portion 33 is formed at one end of the small-diameter flange-shaped portion 31, and the large-diameter tubular portion 32 has a larger diameter than the small-diameter tubular-shaped portion 31. The other end of the shape portion 31 is connected. The radially inward engagement portion 36 is formed on the other end side of the large diameter cylindrical portion 32.
The end shaft receiving hole 33 a is slightly larger than the diameter of the end shaft 42 of the balance 40. The inclined surface portions 35a and 35b are each in the form of an outer peripheral surface of a truncated cone, and typically both inclined surface portions 35a and 35b are similarly formed so as to form a part of the outer peripheral surface of the same virtual truncated cone. And they are arranged in a straight line. The inclined surface portion 35 a is formed at one end of the end shaft receiving hole 33 a of the end flange-shaped portion 33, and the inclined surface portion 35 b is formed in the vicinity of the connecting flange-shaped portion 34 in the small diameter cylindrical portion 31.

The hole stone frame 20 is loosely fitted with a small-diameter cylindrical portion 21, a large-diameter cylindrical portion 22 as an enlarged diameter portion, an annular plate-like end flange-like portion 23, and an end shaft portion 42 of the balance stem 40. A frustoconical end flange-like portion 24 having an end shaft receiving hole 24a, a connecting flange-like portion 25, and an inclined surface portion 26a (an example of a third inclined surface portion of the present invention ) , 26b (of the present invention ) An example of a fourth inclined surface portion) . The inner peripheral surface 21 a of the small diameter cylindrical portion 21 is cylindrical, and the hole stone 17 is fitted into the small diameter cylindrical portion 21. The annular plate-like end flange-like portion 23 is formed at one end of the small-diameter cylindrical portion 21, and the truncated cone-like end flange-like portion 24 is the radial end of the annular plate-like end flange-like portion 23 at its large-diameter side end. It is connected to the inner end and extends to the end shaft receiving hole end that defines the end shaft receiving hole 24a. The inner end surface 23a of the annular plate-shaped end flange-shaped portion 23 is flat and supports the perforated stone 17 by abutting against the end surface 17b of the perforated stone 17 fitted to the small-diameter cylindrical portion 21. The large-diameter cylindrical portion 22 has a larger diameter than the small-diameter cylindrical portion 21 and is connected to the other end of the small-diameter cylindrical portion 21 via a connection flange-shaped portion 25 on one end side. The inner surface 25a of the connecting flange-shaped portion 25 as the opening end portion of the cylindrical portion 21 is in the shape of a truncated cone, and is outside the partially spherical end surface 11 like a convex lens that is the tenon receiving surface 11 of the stone 10. The stone 10 is supported by the partial spherical end face 11 in contact with the part. The end shaft receiving hole 24 a is slightly larger than the diameter of the end shaft 42 of the balance 40. The inclined surface portions 26a and 26b are each in the form of an outer peripheral surface of a truncated cone, and typically both inclined surface portions 26a and 26b are similarly formed so as to form a part of the outer peripheral surface of the same virtual truncated cone. Moreover, when the perforated frame 20 is disposed at a predetermined position in the vibration-proof seat body 30, it is in contact with the inclined surface portions 35 a and 35 b of the vibration-proof seat body 30. The inclined surface portion 26 a is formed on the outer peripheral surface of the truncated cone-shaped end flange-shaped portion 24, and the inclined surface portion 26 b is formed on the outer peripheral surface of the end portion in the vicinity of the connecting flange-shaped portion 25 in the large-diameter cylindrical portion 22. .

  The anti-vibration spring 37 has a shape like a three-leaf clover, and is engaged with the radially inward engaging portion 36 of the anti-vibration seat 30 by engaging portions 38 a, 38 a, 38 a protruding from the large-diameter portion 38. The U-shaped engaging portions 39, 39, 39 extending inward in the radial direction are engaged with the outer end surface 12 of the stone 10, and the stone 10 is connected to the inner surface 25 a of the connecting flange-shaped portion 25 of the hole stone frame 20. Press on. As a result, the hole frame 20 is pressed against the inclined surface portions 35a and 35b of the vibration-proof seat body 30 at the inclined surface portions 26a and 26b through the stone 10. In addition, as long as the anti-shock spring 37 can hold the stone 10, another shape may be used instead of a shape like a three-leaf clover.

  Accordingly, the vibration-resistant presser spring 37 elastically holds the vibration-resistant stone 10 and the vibration-resistant hole stone frame 20 to absorb the impact force to the main body of the balance 3, and the stone 10 and the hole stone frame 20 when receiving the shock. Move and restore. When an impact in the axial direction is applied to the balance stem 40 due to a sudden movement of the wrist of the user while the watch 2 in the form of a wrist watch is worn on the wrist, the axial force (impact) acting on the balance stem 40 is received. The stone 10 receives the force in the A direction from the end face (tenon tip) 45 of the tenon 41 at the tenon receiving surface 11 and allows the stone 10 to be displaced in the A direction to absorb the impact and protect the tenon portion 41. In addition, the impact in the lateral direction (perpendicular to the axial direction) is applied to the balance 40 by the sudden movement of the wrist of the user, and the force (impact) in the direction in which the balance 40 is perpendicular to the central axis C. When the force is received, the force in the direction acts from the tenon portion 41 to the tenon hole 18, so that the perforated frame 20 resists the spring force of the presser spring 37 and the slopes 26 a and 26 b of the perforated frame 20 and the vibration-proof seat 30. Are displaced along the engagement surfaces with the inclined surfaces 35a, 35b, the impact is absorbed, and the tenon portion 41 is protected. In either case, when the impact disappears, the original position is restored to some extent by the force of the holding spring.

  In the mechanical timepiece 2 of the preferred embodiment of the present invention having the balance 3 of the preferred embodiment of the present invention having the vibration-proof bearing mechanisms 1F and 1R of the preferred embodiment of the present invention configured as described above, When the watch 2 is arranged in a “flat position” P1 in which the vibration-proof bearing mechanism 1F on the back cover side is positioned on the vibration-proof bearing mechanism 1R on the dial plate, and the vibration-proof bearing mechanism 1R on the dial plate side 4 (a) and 4 (b) regarding whether or not there is a difference from the case where the timepiece 2 is disposed in the “back flat posture” P2 positioned on the vibration-proof bearing mechanism 1F on the back cover side. This will be described in detail with reference to FIGS. 5A and 5B and FIGS. 6A and 6B.

  When the receiving stones 10F and 10R are arranged substantially perpendicular to the central axis C of the balance 40 of the balance 3 and the partially spherical receiving surfaces 11F and 11R are rotationally symmetrical around the central axis C Since the balance state of the balance 3 of the balance 3 is practically the same when the watch 2 takes the flat posture P1 and when it takes the back flat posture P2, the difference in rate between the flat posture P1 and the back flat posture P2 is as follows. What is not practical is as usual. In the balance 3, the tenon receiving surfaces 11F and 11R of the stones 10F and 10R are partially spherical, and the tenon receiving surfaces 11F and 11R are the end surfaces 45F and 45R of the tenon portions 41F and 41R of the balance stem 40. However, the rotation of the balance stem 40 is likely to be stabilized.

  As shown in FIGS. 4 (a) and 4 (b), the stone holder 10F on the balance holder 5 side or back cover side is attached to the hole stone frame 20F by the holding spring 37F in a state where it is slightly inclined (for example, about 1 degree). Strictly speaking, in the state S1, the timepiece 2 takes the flat posture P1 as shown in FIG. 4A, and the timepiece 2 is in the reverse flat posture as shown in FIG. 4B. In the case of taking P2, the balance 3 is in a slightly different state. The inclination of the stone 10F typically occurs when the hole frame 20F is inclined with respect to the vibration-resistant seat 30F by being shifted with respect to the inclined surfaces 35a and 35b of the vibration-resistant seat 30F at the inclined surfaces 26a and 26b. . Note that this (the balance of the balance is different between the case where the watch takes a flat posture and the case where the watch takes a flat back posture) itself is a conventional balance having a conventional balance 103 having vibration-proof bearing mechanisms 101F and 101R. Although the timepiece 102 is the same as that described with reference to FIGS. 14A and 14B, the difference in the balance state between the flat posture and the back flat posture is the same as that of the watch 2. It differs from the conventional watch 102.

  That is, in the timepiece 2, when the stone holder 10F on the balance holder 5 side is in the tilted state S1, the vibration-proof bearing mechanism 1R on the dial side is positioned on the lower side as shown in FIG. In the flat posture P1 in which the receiving stone 10R on the dial side receives the end surface 45R of the tenon 41R of the balance stem 140 at the tenon receiving surface 11R, the balance stem 40 of the end surface 45R of the tenon portion 41R located below is provided. Among them, the center axis C is in contact with the partially spherical tenon receiving surface 11R of the stone 10R of the anti-vibration bearing mechanism 1R on the dial side located at the lower position C0R through which the central axis C passes. Is rotated in the same manner as in FIG. 14A. That is, in this range, there is no influence due to the stone holder 10F on the balance holder 5 side or the back cover side being attached to the hole stone frame 20F by the pressing spring 37F in a state where it is slightly inclined (for example, about 1 degree). Is substantially the same as the case of FIG. Strictly speaking, however, in the timepiece 2, the tenon receiving surface 11R of the stone 10R is curved in a convex shape. Therefore, in the case of the timepiece 102, the C0R surely becomes the center of rotation when it coincides with the central axis C. And can be different.

  On the other hand, the timepiece 2 is inverted, and the anti-vibration bearing mechanism 1F on the balance 5 side (back cover side) is positioned on the lower side as shown in FIG. In the back flat posture P2 where the tenon receiving surface 11F receives the end face 45F of the tenon 41F of the balance 40, even if a slight deviation occurs in the outline of the tenon receiving surface 11F in the vicinity of the central axis C, FIG. ), The contour of the tenon receiving surface 11F is substantially the same as before the inclination of about 1 degree occurs. Particularly, a portion CaV in which the tangent line is perpendicular to the central axis C in the tenon receiving surface 11F with the inclination of the receiving stone 10F approximately 1 degree almost coincides with the position where the receiving surface 11F intersects the central axis C. That is, if the inclination of the stone 10F is caused by the displacement of the hole stone frame 20F with respect to the vibration-proof seat 30 (the displacement of the surfaces 26a and 26b with respect to the surfaces 35a and 35b), the tenon receiving surface 11F becomes 1 according to one rotation. Even if it rotates approximately in the circumferential direction by a certain degree, the orientation of the tangential plane at the portion C0F where the central axis C intersects in the tenon receiving surface 11F can be kept substantially constant. The portion CaV where is perpendicular to the central axis C is hardly displaced from the position C0F where the receiving surface 11F intersects the central axis C. Accordingly, the balance stem 40 has the stone 10F of the vibration-proof bearing mechanism 1F on the dial side located below the point CaV in the vicinity of the position through which the central axis C passes in the end face 45F of the tenon portion 41F located on the lower side. Is contacted with the partially spherical tenon receiving surface 11F and rotated about the center axis C around the position CaV. The situation is the same even if the tenon receiving surface 11F is displaced along the frustoconical inner surface 25a of the connecting flange-shaped portion 25 of the hole stone frame 20F.

  That is, in the mechanical timepiece 2 having the balance 3 having the vibration-proof bearing mechanisms 1F and 1R having the partially spherical convex curved tenon receiving surfaces 11F and 11R, as shown in FIGS. 4 (a) and 4 (b). In addition, in a state S1 in which the stone holder 10F on the balance holder side or the back cover side is tilted slightly (for example, about 1 degree) and is attached to the hole stone frame 20F by the presser spring 37F, it is shown in FIG. Thus, strictly speaking, the balance 3 is slightly different between the case where the watch 2 takes the flat posture P1 and the case where the watch 2 takes the back flat posture P2 as shown in FIG. 4B. Actually, even if the flat posture P2 is adopted, the portion where the partially spherical convex curved tenon receiving surface 11F of the vibration-proof bearing mechanism 1F is in contact with the end surface 45F of the tenon portion 1F of the balance stem 40 is , Approximately at a position CaV on the central axis C. Therefore, in the flat posture P1 and the back flat posture P2, the balance with hairspring 3 can actually operate in the same manner, and the difference in the rate is considerably smaller than in the cases of (a) and (b) of FIG.

  On the other hand, as shown in FIGS. 5A and 5B (particularly, FIG. 5B), the center axis C of the balance stem 40 is slightly (for example, about 0.2 degrees) in the back flat posture P2. ) When tilted S2, the stone 10F of the anti-vibration bearing mechanism 1F on the side of the balance 5 that the end face 45F of the tenon portion 41F of the balance 40 is positioned below the portion Cb slightly away from the central axis C of the balance 40 Abuts with the mortise receiving surface 11F. Here, the part Cb corresponds to a part where the tangent plane of the tenon receiving surface 11F of the jewel 10F is parallel to the end face 45F of the tenon portion 41F of the balance stem 40 having the inclined central axis C (part that can coincide). To do.

  Accordingly, the rotation center Cb of the balance stem 40 is different from the central axis C of the balance stem 40 by Δr (about 10 μm as a fraction of the radius of the tenon portion 41) from the portion through which the center axis C passes. However, the balance stem 40 rotates around the point Cb.

  In this state S2, the operation of the balance 4 is actually different between the timepiece 2 taking the flat posture P1 and the back flat posture P2, and it is difficult to avoid a slight difference in rate. However, the deviation from the center C of the center position Cb when taking the back flat posture P2 is about a fraction of the radius of the tenon portion 41 of the balance stem 40, and is about the radius of the tenon portion 41 of the balance stem 40. As compared with the conventional watch 102, the difference in the rate between the back flat posture P2 and the flat posture P1 can be greatly reduced.

  The central axis C of the balance stem 40 is inclined for various causes. That is, when a phenomenon occurs in which the central axis C of the balance stem 40 is tilted, it is possible to reduce the possibility of a large difference in rate compared to the conventional timepiece 102 regardless of the position of the timepiece 2. . As such an example, for example, there is a case where the balance of the weight of the balance 50 is broken and the balance 50 is inclined. Strictly speaking, for example, when the spiral of the hairspring 55 is wound or unwound, the force applied to the hairspring 40 from the hairspring 55 through the hairball 43 is caused by the central axis C of the spring 40. The axis can be tilted somewhat. Even in such a case, in the balance 3 provided with the vibration-proof bearing mechanisms 1 and 1 at both ends of the balance stem 40, unlike the conventional balance 102, the tenon receiving surface 111 is a flat tenon receiving surface. Since 11 is a partial spherical surface, a portion in the vicinity of the center axis C of the end surface 45 is not a side edge of the end surface 45 of the tenon portion 41 of the balance 40, but a portion of the tenon receiving surface 11 corresponding to the inclined tangential plane Can abut. Therefore, the extent to which the center of rotation of the balance stem 40 deviates from the central axis C can be minimized.

  Further, as shown in FIGS. 6A and 6B, in the state S3 where the end face 45F of the tenon 41F on the balance 5 side is inclined with respect to the central axis C of the balance 40, the back flat posture In P2, the inclined end surface 45F is a portion Cd where the inclination of the tenon receiving surface 11F of the stone receiving surface 10F of the vibration-proof bearing mechanism 1F on the balance receiving 5 side coincides with the inclination of the end surface 45F, and the tenon receiving surface 11F of the receiving stone 10F. Abut. This portion Cd is a portion that substantially matches the portion Cb shown in FIG.

  That is, even in this state S3, the operation of the balance with hairspring 103 is different between the time when the watch 02 takes the flat posture P1 and the time when the watch 02 takes the back flat posture P2. This is the same as in the case of (b), and the rate difference between the back flat posture P2 and the flat posture P1 is significantly reduced as compared with the conventional timepiece 102 shown in FIGS. 16 (a) and 16 (b). Can be done.

  Therefore, the rotation center Cd of the balance stem 40 is different from the center axis C of the balance stem 40, and is approximately a point Cd away from the center axis C by Δr (a fraction of the radius of the tenon portion 41 is about 10 μm). Will rotate around.

  As described above, in the timepiece 2, since the receiving surface 11 of the stone 10 is formed in a partial spherical shape, even if there are various inclinations or the like, the amount of deviation in which the center of rotation deviates from the center C of the balance 40 is large. Therefore, the fluctuation in the rate of the timepiece 2 due to the postures such as the flat posture P1 and the back flat posture P2 can be minimized.

  Further, in this timepiece 2, the part-spherical shape is not the end faces 45F, 45R of the tenon portions 41F, 41R of the balance stem 40 but the tenon-receiving faces 11F, 11R of the stone 10 and the partial spherical surface Since the diameter is large, the length of the balance 40 and other amounts are less likely to vary greatly.

  Instead of the stone receiving surface having a partially spherical tenon receiving surface, the stone receiving stone 10 </ b> A may be composed of a spherical body 13 as shown in FIGS. 7A and 7B and FIG. 8. The balance 3A provided with the vibration-proof bearing structure 1A shown in FIGS. 7A and 7B and FIG. 8 is the same as the elements of the balance 3 provided with the vibration-proof bearing structure 1 shown in FIGS. The same reference numerals are given to the elements of, and the subscript A is attached to the elements that correspond but are different. In addition, when there is a subscript “F” indicating that it is on the back cover side or the hair-sheet receiving side and a subscript “R” indicating that it is on the dial side, the subscript A is added before the subscripts F and R. The

  In the vibration-proof bearing structure 1A of the balance with hairspring 3A, the jewel 10A is composed of the spheres 13, so that the dimensional accuracy of the jewel 10A is easily increased. Further, in the vibration-proof bearing structure 1A of the balance with hairspring 3A, the size of the timepiece 2A in the thickness direction is large because the stone 10A is composed of the spherical body 13, so the vibration-proof seat 30A is a large-diameter cylindrical shape of the vibration-proof seat 30. Except for having a large-diameter cylindrical portion 32A having an axial length larger than that of the portion 32, it is configured in substantially the same manner as the vibration-proof seat body 30.

  Further, in the vibration-proof bearing structure 1A, the stone 10A is composed of the sphere 13 and the size of the timepiece 2A in the thickness direction is large. Therefore, unlike the case of the vibration-resistant bearing structure 1, the stone 10A is the hole stone frame 20A. Instead, it is supported in the axial direction by the hole stone 17A. Accordingly, the end surface 17dA of the hole stone 17A is a truncated cone surface that receives the spherical surface 14 of the stone 10A. The tenon receiving surface 11A is an inner side of the annular region of the spherical surface portion 14 that contacts the frustoconical end surface 17dA of the hole stone 17A in the stone 10A.

  The holding spring 37A is engaged with the engaging portion 36 of the vibration-proof seat 30A at the outer peripheral side engaging portions 38a, 38a, 38a, and the spherical body 13 is connected at the inner U-shaped engaging portions 39, 39, 39. The region 12A located on the opposite side of the diametrical direction from the tenon receiving surface 11A of the shaped stone 10A is pressed.

  As long as attention is paid to the outer peripheral surface portion, the hole stone frame 20 </ b> A is configured in substantially the same manner as the hole stone frame 20. It has an outer circular truncated cone-shaped connection flange-shaped portion 25A corresponding to the diameter cylindrical portion 22A and the connection flange-shaped portion 25 connecting these. However, since the jewel 10A is composed of a sphere 13 having a small diameter so as to suppress the thickness unlike the jewel 10, the jewel 10A has a cylindrical inner peripheral surface 27 that is substantially the same as the cylindrical inner peripheral surface 21a of the hole stone frame 20A. Placed inside. The cylindrical inner peripheral surface 27 is the inner peripheral surface of the outer peripheral large-diameter cylindrical portion 22A.

In the vibration-proof bearing structure 1A configured as described above, as shown in FIG. 8, the tenon portion 41 of the balance 40 of the balance 3 is fitted into the tenon hole 18 of the hole 17A and serves as a journal bearing. The end surface 45 of the tenon portion 41 is supported by the peripheral surface of the hole 18 and is in contact with the tenon receiving surface portion 11A of the receiving stone 10A that functions as a thrust bearing in the form of the sphere 13 and is supported by the tenon receiving surface portion 11A.

  FIG. 9 shows the degree of misalignment of the center of rotation under various conditions in the balance with the vibration-proof bearing mechanism of FIG. 7, and FIG. The case of the reference | standard in a predetermined state is shown. In this case, the tenon portion 41 of the balance stem 40 contacts the tenon receiving surface 11A of the stone 10A in the form of the sphere 13 at the position C0 of the end surface 45 thereof. This position corresponds to C0R in FIG. 4 and is on the central axis C of the balance stem 40.

  FIG. 9B shows a case where the stone is tilted. Even if the stone 10A in the form of the sphere 13 is slightly inclined (for example, about 1 degree), the stone 10A is Since the annular region 14 is supported by the frustoconical end surface 17dA of the hole stone 17, depending on the rotation, the contact position Cf between the stone 10A in the form of the sphere 13 and the end surface 45 of the tenon portion 41 of the balance stem 40. Is not changed and is actually maintained at the position C0. Therefore, even if the stone 10A is tilted, the balance 3A can be operated in the same manner regardless of whether it is in the flat posture P1 or the back flat posture P2, so that the influence of the posture on the rate can be minimized.

  FIG. 9C shows a case where the balance stem is tilted, and the end face 45 of the tenon portion 41 is tilted as the balance 40 is tilted. However, in the balance 3A provided with the vibration-resistant bearing mechanism 1A, the stone 10A of the vibration-resistant bearing mechanism 1A is composed of the sphere 13 having a relatively small diameter, so that the contact position is slightly shifted from the position C0 on the central axis C. Since the inclination of the tangential plane changes greatly, the portion that just contacts the end face 45 of the tenon portion 41 of the slightly bent stem 40 becomes Cg when slightly separated from the central axis C. As a result, the influence of the inclination of the balance 40 on the rotation of the balance 3A can be minimized.

DESCRIPTION OF SYMBOLS 1,1A Vibration-resistant bearing mechanism 2,2A Mechanical timepiece 3,3A Balance 4 Control escapement 5 Balance holder 6 Ankle 7 Spur wheel 8 Base plate 10, 10F, 10R, 10A Anti-vibration stone 11 Partial spherical end face Reception)
11F, 11R, 11A Tenon receiving surface 12 End surface 12A Region 13 Sphere 14 Spherical surface portion 17, 17F, 17R, 17A Hole stone 17a Outer peripheral surface 17b End surface 17c Guide recesses 17d, 17dA End surface 18 Mortise holes 20, 20F, 20R, 20A Stone frame 21 Small diameter cylindrical shape 21A Outer peripheral small diameter cylindrical portion 21a Inner peripheral surface 22 Large diameter cylindrical portion 22A Outer peripheral large diameter cylindrical portion 23 Annular plate-shaped flange-shaped portion 23a Inner end surface 24 Frustum-shaped end flange-shaped portion 24a End Shaft receiving hole 25 Connection flange-like portion 25A External frustoconical flange-like portion 25a (conical frustum-shaped) inner surfaces 26a, 26b Inclined surface portion 27 Cylindrical inner peripheral surfaces 30, 30F, 30R, 30A Vibration-resistant seat body 31 Small-diameter cylindrical shape Portions 32 and 32A Large-diameter cylindrical portion 33 End flange-like portion 33a End shaft portion receiving hole 34 Connecting flange-like portions 35a and 35b Inclined surface portion 36 Inward in the radial direction Engagement part 37, 37F, 37R, 37A Anti-vibration holding spring 38 Large diameter part 38a Engagement part 39 U-shaped engagement part 40 Tenshin 41, 41F, 41R Tenon part 42, 42F, 42R End shaft part 43 Whistle ball 44 Rotating stone 45, 45F, 45R End face 50 Spring 55 Hairspring 61 Scale tip 62 Spigot 64 Kana part 70 Fourth wheel A, A1, A2 Direction C True central axis C0R Contact position CaV Tilt is tilted Part where the tenon receiving surface is perpendicular to the central axis when the end face of the true tenon part is in contact with the tenon receiving surface of the stone of the vibration-proof bearing mechanism (rotation center)
Cd Site Cf, Cg where the inclined end surface of the tenon portion contacts the tenon receiving surface of the stone receiving portion C1 Region where the stone receiving stone in the form of a sphere contacts the end surface of the tenon portion P1 Flat posture P2 Back flat posture S1 Stone receiving stone on the balance receiving side Inclined and attached state S2 State in which the central axis of the scale is inclined S3 State in which the end face of the tenon is inclined with respect to the central axis of the truth Δr Distance from the central axis to the portion serving as the center of rotation

Claims (9)

A stone that works as a thrust bearing, a hole stone that works as a journal bearing, a hole stone frame that accommodates the hole stone and supports the hole stone, a hole diameter frame that accommodates the hole stone frame and supports the hole stone frame, and has a large diameter. A vibration-resistant seat body having an engaging portion on the opening end side, and a holding spring that is supported by the engaging portion of the vibration-resistant seat body on the outer peripheral side and elastically presses and holds the stone on the perimeter frame on the inner peripheral side. A vibration-proof bearing mechanism for balances,
Ri Do from convex surface facing the end face of the shaft to be supported by the vibration bearing mechanism end faces abutting surface of the shaft is curved so as to protrude to the outside of the jewel,
A first inclined surface portion and a second inclined surface portion arranged in a straight line so as to form a part of the outer peripheral surface of the virtual truncated cone are formed on the inner peripheral surface of the vibration-proof seat body,
On the outer peripheral surface of the hole stone frame, a third inclined surface portion and a fourth inclined surface portion arranged in a straight line so as to form a part of the outer peripheral surface of the virtual truncated cone are formed,
When the hole stone frame is disposed at a predetermined position of the vibration-proof seat body, the first inclined surface portion of the hole stone frame is placed on the third inclined surface portion of the vibration-proof seat body, and the second stone wall frame has a second inclined surface portion. An anti-vibration bearing mechanism for a balance with an inclined surface contacting the fourth inclined surface of the anti-vibration seat . The vibration-proof bearing mechanism for a balance according to claim 1 , wherein the convex surface of the stone is made of a part of a spherical surface. The stone has a convex lens-like shape,
The hole stone frame includes a cylindrical portion and an enlarged diameter portion on the opening end side thereof, and is configured to support the stone at the enlarged diameter portion,
Claim pressing spring is configured to hold the endstone at the enlarged diameter portion of the bore stone frame presses elastically in supported inner side engagement portion of the vibration seat body at the outer side 1 Or the vibration-proof bearing mechanism of the balance as described in 2 . The balance with vibration resistance of the balance according to claim 1 or 2 , wherein the stone is made of a spherical body. A spherical stone is placed in the cylindrical area of the hole stone frame so that it can come into contact with the hole stone,
The holding spring is supported by the engaging portion of the vibration-proof seat on the outer peripheral side and is received through the hole stone by pressing the stone against the opposite end surface of the hole stone in the cylindrical region of the hole stone frame on the inner peripheral side. The vibration-proof bearing mechanism for a balance according to claim 4 , wherein the balance is configured to elastically press and hold a stone against a hole stone frame. The vibration-proof bearing mechanism for a balance according to any one of claims 1 to 5 , wherein a portion of the hole stone frame that supports the tenon receiving surface of the receiving stone has a truncated cone shape. A balance having the vibration-proof bearing mechanism according to any one of claims 1 to 6 . 8. The balance according to claim 7 , wherein the shaft supported by the vibration-proof bearing mechanism is made of a balance stem, and the end surface of the tenon portion having a diameter smaller than that of the main body portion of the balance scale is actually flat. A timepiece having the vibration-proof bearing mechanism according to any one of claims 1 to 6 or the balance with a balance according to claim 7 or 8.

Images