JP5798434B2 - Watch bearings, movements, and watches - Google Patents

Description

  The present invention relates to an elastic support.

Conventionally, when fixing a fixed body to a frame or the like, a fixing method using an elastic body has been adopted.
Here, in FIG. 22, a watch bearing 510 shown in Non-Patent Document 1 includes a frame body 512 that is press-fitted and fixed to a balance 505 (not shown), and a hole stone 514 that restricts radial displacement of the tenon 522. The hole stone frame 511 in which the hole stone 514 is press-fitted and fixed to the inner peripheral surface, the stone 515 for restricting the displacement in the thrust direction of the tenon 522, the hole stone frame 511 and the stone receiving stone provided with the hole stone 514 in the frame body 512. It is comprised by the holding | suppressing spring 516 (elastic support body) which fixes 515, and restrict | limits the displacement of the tenon 522 to the radial direction and a thrust direction.

  The frame 512 is provided with a notch 512a for inserting the locking piece 516a of the pressing spring 516 and a groove 512b for containing the locking piece 516a of the pressing spring 516.

  The fixing spring 516 is fixed to the frame 512 by, for example, first including two locking pieces 516a provided in the pressing spring 516 in the groove 512b of the frame 512, and then the remaining one of the locking pieces 516a. This is done by inserting the book into the notch 512a and finally rotating the holding spring 516 relative to the center of the tenon 522 so that all the locking pieces 516a are included in the groove 512b. For removal, the above-described fixing operations are performed in reverse order.

  In FIG. 23, the timepiece bearing 206 of Patent Document 1 is different from that of Non-Patent Document 1 in the shape of the holding spring 205 (elastic support) and the frame 201. The holding spring 205 is formed in a direction in which the two arms 2101 face the center support portion 2091, and each arm 2101 branches into a connecting arm 2052 and an arc portion 2081, and a connecting arm 2054 and an arc portion 2082, and an arc portion 2081. , 2082 are formed with connecting arms 2051, 2053, respectively. Locking pieces 2071, 2072, 2073, and 2074 are provided at the ends of the connecting arms 2051, 2052, 2053, and 2054, respectively. Further, the frame body 201 is provided with a diametric cutout portion 2012, a parallel cutout portion 2013, and a concave portion 2014.

  In order to fix the pressing spring 205 to the frame body 201, for example, first, the locking pieces 2073 and 2074 of the pressing spring 205 are inserted into the notch portions 2012 in the diameter direction of the frame body 201 and hooked on the parallel notch portions 2013. Next, the connecting arms 2052 and 2053 are pinched with tweezers so as to fit in the concave portion 2014 of the frame body 201, and the connecting arms 2052 are displaced in the direction of approaching the distance between the connecting arms 2052 and 2053, and the connecting arm 2052 is changed to the diametric notch 2012. The locking piece 2072 is hooked on the parallel cutout portion 2013 through the insertion. Finally, the connecting arms 2051 and 2054 are pinched with tweezers so as to fit in the concave portion 2014 of the frame 201, and the connecting arm 2051 is moved to the diametric cutout portion 2012 in a state where the distance between the connecting arms 2051 and 2054 is displaced. This is done by inserting and hooking the locking piece 2071 onto the parallel cutout portion 2013. For removal, the above-described fixing operations are performed in reverse order.

US Patent Application Publication No. 2006/0215499

“Theory of Clock Theory-2-Wheels”, Second Seikosha, 1972, p124-126

  By the way, the fixing work of the holding spring 516 to the frame body 512 shown in Non-Patent Document 1 is a first stage of hooking the two locking pieces 516a into the groove 512b, and the second stage of the remaining one piece. The operation of inserting the locking piece 516a into the notch 512a and the rotation of the holding spring 516 for hooking the last locking piece 516a inserted through the groove 512b as the third step are required. There is a problem that it takes time and work time.

  In addition, the fixing work of the holding spring 205 of the watch bearing 206 shown in Patent Document 1 is also the first stage, the hooking operation of the two locking pieces 2073 and 2074 to the parallel notch 2013, and the second stage. The three steps of hooking the stopper piece 2072 to the parallel cutout portion 2013 and the hooking portion of the locking piece 2071 to the parallel cutout portion 2013 are required as the third step, which takes time and labor. There is a problem that becomes long.

Furthermore, in common with Non-Patent Document 1 and Patent Document 1, there is a problem that the holding springs 516 and 205 placed on a table or the like are difficult to pick up with tweezers.
Further, there is a problem that when the holding springs 516 and 205 are picked with tweezers, the holding springs 516 and 205 are detached from the tweezers, fly around and are lost.

  Furthermore, notches 512a and 2012 are required in the frame bodies 512 and 201 so that the locking pieces 516a and 2071 to 2074 of the holding springs 516 and 205 can be inserted, and the notches 512a and 2012 are formed. There is a problem that this leads to an increase in the number of machining steps, an associated increase in machining time, and an increase in machining costs.

  Therefore, the present invention has been made in view of the above-described circumstances, and can improve the assembly workability by allowing the pressing spring to be attached to or detached from the frame body in a single operation. It is an object of the present invention to provide an elastic support, a watch bearing, a movement and a watch.

The present invention provides the following means in order to solve the above-described problems.
A timepiece bearing according to the present invention includes a shaft body, a regulating member (hole stone, stone) for regulating movement of the shaft body in a radial direction and a thrust direction, a frame body for housing the regulating member, and a frame body And an elastic support that supports the vibration applied to the regulating member from the outside so as to absorb the vibration. The frame includes a groove used for attaching the elastic support, and the elastic The support body includes a plurality of locking pieces fitted in the groove and a plurality of gripping portions used to simultaneously move the plurality of locking pieces toward the shaft body. It is characterized in that it is fitted into the groove by being moved by. According to this configuration, in the assembly work of the timepiece bearing, a plurality of locking pieces provided on the elastic support can be moved at the same time, so that the attachment and detachment work of the elastic support to the frame can be facilitated. Work time can be shortened. In addition, since the outer diameter of the elastic support can be reduced, the notch portion of the frame for inserting the locking piece becomes unnecessary, and the machining time is shortened by omitting the machining process of the notch portion, In addition, the processing cost can be reduced. Further, by providing a plurality of gripping portions on the elastic support body, it is possible to easily pick up the elastic support body from a desktop or the like when a dedicated work jig is used, or to prevent it from coming off when gripped.

Further, the plurality of gripping portions are characterized by moving each of the plurality of locking pieces toward the rotation center of the shaft body.
According to this configuration, since the outer diameter of the locking piece in the elastic support can be reduced without any axial deformation, the locking piece of the elastic support can be inserted into the groove of the frame with a simple grip. Can be made.

Further, the plurality of gripping portions are characterized in that each of the plurality of locking pieces is deformed obliquely with respect to the orthogonal direction of the shaft body.
According to this configuration, since each of the locking pieces can be obliquely deformed with respect to the orthogonal direction of the shaft body, the locking piece of the elastic support body can be more easily inserted into the groove portion of the frame body.

In addition, each of the plurality of gripping portions is an opening provided in the elastic support.
According to this configuration, after gripping a plurality of gripping portions with a plurality of pins provided in the work jig, even when some pins are removed from the gripping portion, the remaining gripping pins are opened. Since it is contained in the (grip part), the elastic support body is restricted from moving in the plane direction. Therefore, since the elastic support does not fly around and falls in the direction of gravity that is not restricted by the opening, it is easy to find the dropped elastic support and prevent the elastic support from being lost. Can do.

Each of the plurality of gripping portions includes a plurality of connection portions connected to each of the plurality of locking pieces, and the plurality of connection portions are formed in an arc shape.
According to this configuration, the spring constant of the connecting portion connected to the locking piece can be further reduced in the direction perpendicular to the shaft body. Therefore, since the locking piece can be moved with a small force, the gripping force can be finely adjusted, and fatigue due to the gripping can be reduced, so that the assembly workability is improved.

The elastic support includes a thin portion that is thinner than the elastic support, and the plurality of gripping portions deform the locking pieces obliquely with respect to the orthogonal direction of the shaft body through the thin portions. It is characterized by being.
According to this configuration, since the spring constant in the thin portion is smaller than the spring constant of the portion other than the thin portion of the elastic support, it is small when the locking piece is deformed obliquely with respect to the orthogonal direction of the shaft body. It can be deformed by force.

Further, the plurality of gripping portions are characterized by having a taper at the end on the shaft body side.
According to this configuration, since the position of the force point of the grip portion can be shifted, it is possible to deform with a small force when the locking piece is deformed obliquely with respect to the orthogonal direction of the shaft body.

Further, the plurality of gripping portions are provided at equal intervals in the circumferential direction of the shaft body.
In addition, the plurality of gripping portions are provided at positions that are symmetric with respect to the shaft body.
According to these configurations, since the balance of the force to the elastic support body when the grip portion is gripped is symmetric with respect to the shaft body, the deformation of the elastic support body is also symmetric with respect to the shaft body. As a result, the elastic support is unlikely to be detached from the work jig during the assembly work, so that the assembly workability is improved.

In addition, the plurality of locking pieces are characterized by having a taper at an end portion that is fitted into the groove.
According to this configuration, the taper of the locking piece serves as a guide, and the locking piece of the elastic support body can be easily included in the groove of the frame, so that the assembly workability is improved.

Further, the plurality of gripping portions are characterized by including a notch portion on the shaft body side.
According to this configuration, the contact area and the contact location between the pin and the gripping portion can be increased by forming the notch portion that matches the shape of the pin of the work jig in the gripping portion. The frictional force to be increased increases, and the gripping force by the elastic support jig can be increased. As a result, the elastic support is unlikely to be detached from the jig, so that it is possible to prevent the elastic support from being removed from the jig or lost when the elastic support is handled.

The movement according to the present invention is a movement of a timepiece including a train wheel, an escapement, and a speed governor, and is used for at least one of the train wheel, the escapement, or the speed governor. It is characterized by the use of bearings.
According to this configuration, since the timepiece bearing of the present invention is provided, a movement with high assembling workability can be provided.

In addition, a timepiece according to the present invention is characterized by including the above-described movement of the present invention and a casing that encloses the movement.
According to this configuration, since the movement of the present invention is provided, a timepiece having high assembling workability can be provided.

  According to the timepiece bearing according to the present invention, the attaching / detaching work of the elastic support body to the frame body can be facilitated, and the working time can be shortened. Moreover, the notch part of a frame becomes unnecessary, a process time can be shortened by omitting the process process of a notch part, and a process cost can be reduced. Furthermore, the elastic support can be easily picked up from a desktop or the like, and the elastic support can be made difficult to come off from the holding jig when grasped.

  According to the movement and timepiece of the present invention, it is possible to provide a movement and timepiece that facilitate the assembly and repair work of the bearing.

FIG. 1 is a plan view of the movement front side of a mechanical timepiece according to an embodiment of the present invention (some parts are omitted, and a receiving member is indicated by an imaginary line). FIG. 2 is a schematic partial cross-sectional view showing a portion of the escape wheel from the barrel in the embodiment of the present invention. FIG. 3 is a schematic partial cross-sectional view showing the portion from the escape wheel to the balance in the embodiment of the present invention. 4A is a top view of a timepiece bearing provided with an elastic support (pressing spring) in the first embodiment of the present invention, and FIG. 4B is a cross-sectional view taken along the cutting line AA ′ in FIG. It is. FIG. 5 is a top view (a) and a side view (b) of the elastic support (pressing spring) in the first embodiment of the present invention. FIG. 6 is a top view for explaining the deformation of the elastic support (pressing spring) in the first embodiment of the present invention. FIG. 7 is a cross-sectional view of a timepiece bearing for explaining the movement of the elastic support (pressing spring) when the elastic support (pressing spring) is attached to the frame in the first embodiment of the present invention. FIG. 8A is a top view of a timepiece bearing according to the second embodiment of the present invention, and FIG. 8B is a cross-sectional view taken along a cutting line G-G ′ in FIG. FIG. 9 is a top view of the elastic support (pressing spring) in the second embodiment of the present invention. FIG. 10 is a top view for explaining the deformation of the elastic support (pressing spring) in the second embodiment of the present invention. FIG. 11: is the top view (a) of the timepiece bearing in 3rd Embodiment of this invention, and sectional drawing (b) in (a) cutting line K-K '. FIG. 12 is a top view of the elastic support (pressing spring) in the third embodiment of the present invention. FIG. 13 is a top view for explaining the deformation of the elastic support (pressing spring) in the third embodiment of the present invention. FIG. 14 is a perspective view of an elastic support (pressing spring) in the fourth embodiment of the present invention. FIG. 15 is a sectional view (a) of the elastic support (pressing spring) according to the fourth embodiment of the present invention taken along the cutting line WW ′ in FIG. 14 before deformation of the pressing spring, and the principle of deformation of the pressing spring. It is the figure (b) to explain, and a sectional view (c) after the presser spring deformation referring to the cutting line WW ′. FIG. 16 is a perspective view of an elastic support (pressing spring) in the fifth embodiment of the present invention. FIG. 17 is a cross-sectional view (a) of the elastic support (pressing spring) according to the fifth embodiment of the present invention taken along the cutting line XX ′ in FIG. 16 before deformation of the pressing spring, and the principle of deformation of the pressing spring. It is sectional drawing (c) after the deformation | transformation of the holding | suppressing spring which refers the figure (b) demonstrated and the cutting | disconnection line XX '. FIG. 18 is a perspective view (a) and a top view (b) of an elastic support (pressing spring) in the sixth embodiment of the present invention. FIG. 19 is a side view (a) of the elastic support body (pressing spring) according to the sixth embodiment of the present invention before deformation of the pressing spring and a side view (b) after deformation of the pressing spring. FIG. 20 is a top view (a) of an elastic support (pressing spring) according to a seventh embodiment of the present invention, and a cross-sectional view (b) taken along a cutting line AB-AB ′ in FIG. FIG. 21 is a top view of an elastic support (pressing spring) according to the eighth embodiment of the present invention. FIG. 22 is a diagram showing Non-Patent Document 1, which is a prior art document. FIG. 23 is a diagram showing Patent Document 1 which is a prior art document.

Next, an embodiment of an elastic support according to the present invention will be described with reference to the drawings.
(First embodiment)
(Mechanical watch)
FIG. 1 is a plan view of the movement front side of the mechanical timepiece, FIG. 2 is a schematic partial sectional view showing a portion of the escape wheel from the barrel, and FIG. 3 is a schematic part showing a portion of the balance wheel from the escape wheel. It is sectional drawing. In FIG. 1, some components are omitted, and the receiving member is indicated by a virtual line.

  As shown in FIGS. 1 to 3, the movement 100 of the mechanical timepiece has a base plate 102 that constitutes a substrate of the movement 100. A winding stem 110 is rotatably incorporated in the winding stem guide hole 102 a of the main plate 102. The dial 104 (see FIG. 2) is attached to the movement 100. In general, of both sides of the main plate 102, the side on which the dial plate 104 is disposed is referred to as the back side of the movement 100, and the opposite side of the side on which the dial plate 104 is disposed is referred to as the front side of the movement 100. A train wheel incorporated on the front side of the movement 100 is referred to as a front train wheel, and a train wheel incorporated on the back side of the movement 100 is referred to as a back train wheel. In addition, it is comprised as a portable timepiece by providing the movement 100 with a casing (not shown).

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

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

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

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

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

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

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

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

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

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

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

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

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

  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 whistle ball 140d fixed to a balance stem (shaft body portion) 140a, and an outer end portion of the hairspring 140c is attached to a balance holder 167 so as to be rotatable. It is fixed by screwing through a beard 170a attached to 170. The outer periphery of the frame body 312 provided in the timepiece bearing 310 is fixed to the balance receiver 167 and the main plate 102. The slow / fast needle 168 is rotatably attached to the balance receiver 167. Further, the balance 140 is rotatably supported with respect to the main plate 102 and the balance receiver 167.

  Here, the balance 140 is configured to be rotatable about the central axis C, and tenons 321 and 322 are formed at both ends of the balance stem 140a. The lower (rear) tenon 321 and the upper (front) tenon 322 are rotatably supported by the watch bearing 310.

(Vibration resistance function)
In FIG. 3, when an external force such as an impact is applied to the movement 100, the balance 140 applies a force to the hole stone 314 or the stone 315 in the watch bearing 310 via the tenon 321 or the tenon 322. At this time, the hole stone 314 or the stone 315 attempts to be displaced by the applied force, but is pushed back to a predetermined position by the elastic force of the holding spring 316. Due to the above-described behavior, even if an external force such as an impact is applied to the movement 100, the hole stone 314 or the stone 315 can escape in the direction in which the force acts, so that an excessive force is applied to the tenons 321 and 322. It is possible to prevent the timing from stopping. The aforementioned function is called a vibration proof function.

(Structure of elastic support)
Next, the structure of the elastic support body of this embodiment is demonstrated.
The elastic support in the present embodiment is a presser spring 316.

  FIG. 4 is a top view (a) of a timepiece bearing provided with an elastic support (pressing spring) in the present embodiment, and a cross-sectional view (b) along the cutting line AA ′ in FIG. FIG. 5 is a top view (a) and a side view (b) of the elastic support body (pressing spring) in the present embodiment, and FIG. 6 illustrates deformation of the elastic support body (pressing spring) in the present embodiment. FIG. 7 is a cross-sectional view of a timepiece bearing for explaining the movement of the elastic support (pressing spring) when the elastic support (pressing spring) in this embodiment is attached to the frame. .

  In FIG. 4, a watch bearing 310 includes a frame body 312 that is press-fitted and fixed to a balance holder 167 (not shown), a cobblestone frame 311, and a cobblestone 314 that is press-fitted and fixed to the inner peripheral surface of the cobblestone frame 311. , Stones 315, and hole spring frames 311 and retaining stones 315 for fixing the stones 315 to the frame body 312.

  The holding spring 316 comes into contact with the upper surface 315a of the stone 315 by the contact portion 316c, and the locking portion 316a is included in the groove 312b of the frame body 312 so that the stone 315, the hole stone 314, and the hole stone frame are included. 311 is fixed to the frame 312.

  In FIG. 5, the holding spring 316 has a planar shape, a locking portion 316 a included in the groove 312 b of the frame body 312, a holding portion 316 d used when holding the holding spring 316 with a jig, It is comprised by the contact part 316c contacted with 315, and the elastic part 316e elastically deformed. The thickness H of the holding spring 316 is preferably within a range of 0.01 to 1 mm.

  In FIG. 6, the shape of the pressure spring 316f before deformation is indicated by a broken line, and the shape of the pressure spring 316g after deformation is indicated by a solid line. The holding spring 316f has an outer diameter D. When the pins 356 are inserted into the holding portions 316d and the holding portions 316d are moved toward the shaft center I by the pins 356, the elastic portions 316e are formed on the plane where the holding springs 316 are located. Is elastically deformed, and the locking portion 316a is also moved toward the axial center I to become a holding spring 316g having an outer diameter D ′ (<D).

Further, when the pin 356 is pulled out from the presser spring 316g, it returns to the presser spring 316f.
The outer diameter D of the presser spring 316 is preferably in the range of 1 to 5 mm.

  Moreover, the outer diameter D should just be the same as the diameter of the groove part 312b, or several micrometers smaller than the outer diameter of the groove part 312b. By minimizing the clearance between the outer diameter of the groove 312b and the outer diameter D, the center position of the pressing spring 316 can be brought closer to the shaft center I. Therefore, it is possible to prevent the stone 315, the hole stone 314, and the hole stone frame 311 from being inclined with respect to the axial direction of the tenon 321 (322).

  As the pin 356, a work jig dedicated to tweezers and a holding spring 316 is used, and the work can be facilitated by using a pin jig simulating the structure of a pin vise, which is a tool for precision machinery. In particular, if the pin 356 of the dedicated jig is formed parallel to the thickness direction of the presser spring 316, the contact area between the pin 356 and the presser spring 316 increases and friction increases, so that the presser spring 316 is being gripped during gripping. It becomes easy to prevent falling or flying.

  FIG. 7 shows three states before, during, and after the holding spring 316 is attached to the watch bearing 310. The pressure spring 316 before installation is referred to as a pressure spring 316h, the pressure spring 316 being installed is referred to as a pressure spring 316i, and the pressure spring after attachment is referred to as a pressure spring 316j.

  Since the outer diameter of the holding spring 316h outside the frame 312 is D, the inner diameter B of the frame 312 having a smaller diameter than D cannot be inserted. Therefore, the holding portion 316d of the holding spring 316h is held by the pin 356, and the holding portion 316d is moved in the axial center I direction, thereby displacing the locking portion 316a in the axial center I direction and reducing the outer diameter D ′. The state of the holding spring 316i is as follows.

  The holding spring 316i can be inserted through the inner diameter B of the frame 312 having a diameter larger than the outer diameter D '. When the pin 356 is released from the presser spring 316i after the presser spring 316i is inserted through the inner diameter B of the frame 312, the outer diameter of the presser spring 316j is returned to D by the elastic force of the elastic part 316e, and the locking part 316a is Enclosed in the groove 312 b of the frame 312, the holding spring 316 j is fixed to the frame 312. Further, when removing the presser spring 316j from the frame body 312, the above-described mounting operations are performed in reverse order.

  Although the present embodiment has been described with a shape having two locking portions 316a, gripping portions 316d, and elastic portions 316e in the holding spring 316, each of the locking portions 316a and the gripping portions 316d has two or more elastic portions 316e. If one or more are provided, various shapes can be adopted without departing from the contents of the present embodiment.

  As described above, the elastic support (pressing spring 316) in this embodiment can be handled by tweezers or a dedicated jig, and in particular, the pressing spring 316 is less likely to come off when using the dedicated jig than when using the tweezers. Thus, handling of the holding spring 316 can be facilitated. In addition, when the pressing spring 316 is attached to and detached from the frame body 312, the insertion operation of the locking portion 316 a into the groove portion 312 b can be performed at a time, so the attaching and detaching operation of the pressing spring 316 is facilitated and the working time can be shortened. Furthermore, since the notch 512a, which is conventionally required for the frame body 312, is not necessary, the number of processing steps can be reduced. Further, since the clearance between the outer diameter of the groove 312b and the diameter D of the holding spring 316 can be minimized, the stone 315, the hole stone 314, and the hole stone frame 311 are in the axial direction of the tenons 321 and 322. It is possible to suppress tilting with respect to.

(Second Embodiment)
FIG. 8 is a top view (a) of the timepiece bearing according to the second embodiment of the present invention and a cross-sectional view (b) along the cutting line GG ′ in FIG. FIG. 10 is a top view of the presser spring in the embodiment, and FIG. 10 is a top view for explaining deformation of the presser spring.

  As shown in FIGS. 8 and 9, the holding spring 317 includes three gripping portions 317 d, locking portions 317 a, and elastic portions 317 e. The holding spring 317 is different from the holding spring 316 in the number of gripping portions, locking portions, and elastic portions. As described in the first embodiment, the holding spring 317 can take various shapes without departing from the content of the present invention.

  As shown in FIG. 10, the holding spring 317f is moved in the direction of the axial center I by the three pins 356 by moving the gripping portion 317d, so that the locking portion 317a is also moved in the direction of the axial center I. The deformation to 317g is possible. That is, the pressing spring 317 can reduce the outer diameter D of the pressing spring 317f to the outer diameter D ′ of the pressing spring 317g. Therefore, the pressing spring 317 can be inserted through the inner diameter B of the frame body 312, and the pressing spring 317 can be attached to and detached from the frame body 312. Since the number of pins 357 used for the deformation of the presser spring 317 is three, a working jig dedicated to the presser spring 317 is used instead of tweezers.

  As described above, the elastic support (pressing spring 317) in the present embodiment has three gripping portions 317d, three locking portions 317a, and three elastic portions 317e, and a dedicated treatment in which three pins 357 are formed. Use tools. When the holding spring 317 is picked up, carried, or deformed, the holding spring 317 can be gripped at three locations. Therefore, the holding spring 317 is less likely to be detached from the dedicated jig, and the holding of the holding spring 317 is easier.

(Third embodiment)
FIG. 11 is a top view (a) of a timepiece bearing according to a third embodiment of the present invention, and a rotational sectional view (b) taken along a cutting line KK ′ in (a), and FIG. 12 is an elastic support. FIG. 13 is a top view (a) and a side view (b) of the (pressing spring), and FIG. 13 is a top view for explaining deformation of the elastic support (pressing spring).

  In FIG. 11, the watch bearing 310 b includes a frame body 312, a cobblestone frame body 311, a cobblestone 314 that is press-fitted and fixed to the inner peripheral surface of the cobblestone frame 311, a stone 315, a cobblestone frame 311, and A holding spring 318 for fixing the jewel 315 to the frame body 312 is provided. The holding spring 318 presses the upper surface 315a of the stone 315 by the contact portion 318c, and the locking portion 318a is included in the groove 312b of the frame body 312 so that the stone 315, the hole stone 314, and the hole stone frame 311 are included. Is fixed to the frame 312.

  In FIG. 12, the holding spring 318 has a planar shape, includes an abutting portion 318 c, a circular stone receiving holding portion 318 h centering on the shaft center I, and a locking portion included in the groove portion 312 b of the frame body 312. 318a, a gripping portion 318d, and an elastic portion 318e that connects the stone holding portion 318h, the locking portion 318a, and the gripping portion 318d.

In FIG. 13, the holding spring 318 can reduce the outer diameter D to the outer diameter D ′ by elastic deformation of the elastic portion.
In FIG. 13, the pressure spring 318f before deformation is indicated by a broken line, and the pressure spring 318g after deformation is indicated by a solid line.

  The holding spring 318f of the outer diameter D inserts a pin 356 that is a dedicated jig into each of the gripping portions 318d, moves the pin 356 toward the axis center I, the elastic portion 318e is elastically deformed, and the pin 356 is an arrow. By moving only by P, the gripping portion 318d and the locking portion 318a are moved accordingly, so that the diameter is reduced to the pressing spring 318g having the outer diameter D ′. Further, when the pin 356 is pulled out from the presser spring 318g, it returns to the presser spring 318f.

In the radial clearance between the holding spring 318 and the groove 312b, the outer diameter D may be the same as the outer diameter of the groove 312b or smaller by several μm.
By minimizing the clearance between the outer diameter of the groove 312 b and the outer diameter D, the center position of the pressing spring 318 can be brought closer to the shaft center I. Therefore, it is possible to suppress the stone 315, the hole stone 314, and the hole stone frame 311 from being inclined with respect to the rotation axis directions of the tenons 321 and 322.

  As described above, with the shape of the holding spring 318, since only one elastic portion 318e is provided for one gripping portion 318d and the locking portion 318a, the force of the pin 356 is distributed to a plurality of elastic portions. Therefore, the holding spring 318 can be reduced in diameter with a small force. Further, the elastic deformation of the elastic portion 318e can be more easily performed by adjusting the spring constant of the elastic portion 318e at the time of design.

(Fourth embodiment)
FIG. 14 is a perspective view of an elastic support (pressing spring) according to the fourth embodiment of the present invention, and FIG. 15 is a pressing spring taken along a cutting line WW ′ in FIG. 14 of the elastic support (pressing spring). They are sectional drawing (a) before a deformation | transformation, the figure (b) explaining the principle of a deformation | transformation of a pressing spring, and sectional drawing (c) after a pressing spring deformation | transformation which refer to the cutting line WW '.

  In FIG. 14, the difference of the elastic support body of 4th Embodiment from 1st Embodiment is that the screen 319l is provided and the thin part 319b is provided in the elastic part 319e. The screen 319l is formed on the surface on the side where the pressing spring 319 of the elastic portion 319e contacts the stone receiving upper surface 315a.

In FIG. 15A, the maximum depth Y of the screen 319l is located at the center of the elastic portion 319e. The maximum depth Y is preferably in the range of 0 <Y ≦ H * 4/5 with respect to the height H of the holding spring 319. Further, the outer diameter of the holding spring 319 before deformation is the outer diameter D.
In FIG. 15B, the point Q indicates the center point of the gripping portion 319d, the point R indicates the midpoint of the line segment QQ ′, and the point S indicates the position of the center of gravity of the presser spring 319 after the formation of the screen 319l.

  The center of gravity S is a fulcrum, the points Q and Q ′ are load points, the vector Z1 is a gripping force vector for gripping the grip portion 319d with a pin 356 (not shown), and the vector Z1 is a fulcrum from the load points Q and Q ′. It is decomposed into a vector Z2 directed to S and a vector Z3 directed perpendicularly to the vector Z2 and directed to the point R.

Since the vector Z3 is a vector perpendicular to the line segments SQ and SQ ′ connecting the fulcrum S and the load points Q and Q ′, a moment for rotating the points Q and Q ′ about the fulcrum S is generated. The holding spring 319 is bent around a straight line connecting the center of gravity S and the position where the maximum depth Y of the slidable 319l in the elastic portion 319e is present.
Further, the elastic portion 319e is also deformed on the same curved surface as the presser spring 319.

  In FIG. 15 (c), the holding spring 319 that is bent and has a reduced diameter has an outer diameter D ′, and can communicate with the inner diameter B of the frame body 312, so that the pressing spring 319 can be attached to and detached from the frame body 312. .

As described above, the pressing spring 319 can be deformed not only on the same plane of the pressing spring 319 but also by bending about the direction perpendicular to the rotation axis C of the balance stem 140a. The diameter can be reduced to the outer diameter D ′. Further, since the holding spring 319 is deformed by bending around a direction perpendicular to the rotation axis C, the engaging portion 319a can be easily inserted into the groove portion 312b of the frame body 312 and workability is improved.
In the present embodiment, various wiping shapes can be adopted without departing from the contents of the present embodiment.

(Fifth embodiment)
FIG. 16 is a perspective view of an elastic support (pressing spring) in the fifth embodiment of the present invention, and FIG. 17 is a pressing spring taken along a cutting line XX ′ in FIG. 16 of the elastic support (pressing spring). They are sectional drawing (a) before a deformation | transformation, the figure (b) explaining the principle of a deformation | transformation of a pressing spring, and sectional drawing (c) after a pressing spring deformation | transformation which refer to cutting line XX '.

  In FIG. 16, the difference from the first embodiment of the elastic support of the fifth embodiment is that a tapered portion 320 m is formed, and the height F of the gripping portion 320 d is smaller than the height H of the holding spring 320. . The tapered portion 320m is formed at one edge of the grip portion 320d.

In FIG. 17A, the height F of the tapered portion 320m is preferably in the range of 0 <F ≦ 0.5H with respect to the height H of the pressing spring 319. In addition, the outer diameter of the presser spring 320 before deformation is the outer diameter D.
In FIG. 17B, points U and U ′ indicate the center point of the grip portion 320d, point V indicates the midpoint of the line segment U-U ′, and point T indicates the position of the center of gravity of the pressing spring 320.

  The center of gravity T is a fulcrum, the points U and U ′ are load points, the vector Z′1 is a gripping force vector for gripping the gripper 320 with a pin 356 (not shown), and the vector Z′1 is the load point U, A vector Z′2 that goes from U ′ to the fulcrum T and a vector Z′3 that goes perpendicular to the vector Z′2 and goes to the point V are decomposed.

Since the vector Z′3 is a vector that intersects perpendicularly with the line segments TU and TU ′ connecting the fulcrum T and the load points U and U ′, the moment for rotating the points U and U ′ around the fulcrum T is The holding spring 320 is bent around a straight line connecting the center of gravity T and the center of the elastic portion 320e.
Further, the elastic portion 320e is deformed even on the same curved surface as the pressing spring 320.

  In FIG. 17C, the outer diameter of the holding spring 320 that is bent and reduced in diameter is the outer diameter D ′, and the inner diameter B of the frame body 312 can be communicated, and the pressing spring 320 is attached to the frame body 312. It can be removed.

  As described above, the positions of the load points U and U ′ with respect to the center of gravity T serving as a fulcrum shift in the direction in which the balance with the balance with the axial balance 140 of the tenon 321 (322) is bent. A moment is generated, and not only on the same plane of the holding spring 320 but also deformation by bending about the direction perpendicular to the rotation axis C of the balance stem 140a can be performed, and the outer diameter D to the outer diameter D ′ can be easily performed. The diameter can be reduced. Further, since the holding spring 320 performs bending deformation around the direction perpendicular to the rotation axis C, the locking portion 320a can be easily inserted into the groove portion 312b of the frame body 312 and workability is improved.

In addition, in this embodiment, the method of providing the height F of the holding part 320d in the range which does not deviate from the content of a present Example can be taken variously. For example, the tapered portion 320m may be provided with a notch or a screen.
Moreover, this embodiment can make a bending deformation easier by combining with 4th Embodiment, and can make diameter reduction of a pressing spring easier.

(Sixth embodiment)
18 is a perspective view (a) and a top view (b) of an elastic support (pressing spring) in the sixth embodiment of the present invention, and FIG. 19 is an elastic support in the sixth embodiment of the present invention. It is the side view (a) before the presser spring deformation | transformation of (presser spring), and the side view (b) after a presser spring deformation | transformation.
18A and 18B, the holding spring 360 includes a locking portion 360a, an elastic portion 360e, and a gripping portion 360d.

  In FIG. 19A, the pressure spring before deformation has an outer diameter D. In addition, the gripping portion 360d has an inclination of an angle θ from a plane where the elastic portion 360e and the locking portion 360a are provided. For example, the range of the angle θ is desirably 30 ° ≦ θ ≦ 60 °. When the gripping portion 360d is displaced in the directions of arrows AA and AA ′ by tweezers or a pin 356 (not shown) of a dedicated jig, the elastic portion 360e is elastically deformed, and the locking portion 360a connected to the gripping portion 360d is also displaced. To do.

  In FIG. 19B, the outer diameter of the deformed pressure spring 360n is D ', and the inner diameter B of the frame 312 can be inserted. Thereby, the holding spring 360 can be attached to and detached from the frame body 312.

  As described above, the holding spring 360 can be bent and deformed around the direction perpendicular to the rotation axis C of the stem 140a, and can be easily reduced from the outer diameter D to the outer diameter D '. In addition, the holding spring 360 can be easily bent into the groove 312b of the frame 312 by bending the holding spring 360 around the direction perpendicular to the rotation axis C, thereby improving the workability. Furthermore, since the gripping part 360d has an inclination of an angle θ from the plane where the elastic part 360e and the locking part 360a are located, it is easy to pick up with the pin 356 of tweezers or a dedicated jig.

In the present embodiment, various shapes and angles θ of the gripping portions 360d can be adopted without departing from the contents of the present embodiment.
Moreover, this embodiment can make a bending deformation easier by combining with 4th Embodiment, and can make diameter reduction of a pressing spring easier.

(Seventh embodiment)
FIG. 20 is a top view (a) of an elastic support (pressing spring) according to a seventh embodiment of the present invention, and a cross-sectional view (b) taken along a cutting line AB-AB ′ in FIG.

  The difference of the seventh embodiment from the first embodiment is that the locking portion 361a is provided with a tapered portion 360o. Since the presser spring 361 is provided with the taper portion 360o, the taper portion 360o serves as a guide to the groove portion 312b when attached to the frame body 312, and the locking portion 361a can be easily inserted into the groove portion 312b. It becomes.

As described above, since the locking portion 361a is provided with the tapered portion 360o, the insertion of the locking portion 361a into the groove portion 312b is facilitated, so that workability is improved.
Moreover, this embodiment can be more easily attached to the frame body 312 of the pressing spring by combining with each of the first to sixth embodiments.

(Eighth embodiment)
FIG. 21 is a top view of an elastic support (pressing spring) according to the eighth embodiment of the present invention.
A difference of the eighth embodiment from the first embodiment is that a notch 362p is provided in the grip 362d. The shape of the notch 362p is formed according to the shape of the pin 356 (not shown). Since the shape of the notch 362p is formed in accordance with the shape of the pin 356, when the holding spring 362 is gripped by the pin 356, the contact area between the notch 362p formed in the grip 362d and the pin 356 increases. As a result, the frictional resistance at the contact point increases, and the presser spring 362 is less likely to come off the pin 356.

As described above, since the notch portion 362p is provided in the gripping portion 362d, when the presser spring 362 is gripped by the pin 356, the presser spring 362 is less likely to be detached from the pin 356, so that workability is improved.
In addition, the present embodiment can be more easily performed by attaching and detaching the pressing spring to the frame 312 by combining with each of the first to seventh embodiments.

  The technical scope of the present invention is not limited to the above-described embodiments, and includes those in which various modifications are made to the above-described embodiments without departing from the spirit of the present invention. In other words, the configuration described in the above-described embodiment is merely an example, and can be changed as appropriate.

For example, the elastic support in each embodiment of the present invention is described using a bearing that receives the tenons 321 and 322 of the balance 140, but the elastic support in the present embodiment is other than the balance 140 (the governor). In addition, it can be used as appropriate for a train wheel or an escapement.
Moreover, you may combine each embodiment mentioned above suitably.

310, 310a, 310b ... watch bearings, 311 ... hole stone frame, 312 ... frame body, groove part ... 312b, 312c ... insertion hole, 314 ... hole stone, 315 ... stone receiving, 315a ... stone receiving upper surface, 316, 317, 318, 319, 320, 360, 361, 362 ... Presser spring, 316a, 317a, 318a, 319a, 320a, 360a, 361a, 362a ... Locking part, 316d, 317d, 318d, 319d, 320d, 360d, 361d, 362d ... gripping part, 316e, 317e, 318e, 319e, 320e, 360e, 361e, 362e ... elastic part, 321, 322 ... tenon, 323 ... balance, 356 ... pin

Claims (8)

A shaft,
A regulating member for regulating movement of the shaft body in a radial direction and a thrust direction;
A frame housing the regulating member;
An elastic support that is attached to the frame and supports the vibration applied to the regulating member from the outside so as to absorb the vibration,
The frame includes a groove used for attaching the elastic support,
The elastic support body includes a plurality of locking pieces fitted into the groove,
A plurality of gripping portions used to simultaneously move each of the plurality of locking pieces toward the shaft body,
The locking piece is fitted into the groove by being moved by the grip portion ,
The plurality of gripping portions are configured to obliquely deform each of the plurality of locking pieces with respect to the orthogonal direction of the shaft body,
The elastic support includes a thin portion that is thinner than the elastic support,
The timepiece bearing, wherein the plurality of gripping portions are configured to deform the locking pieces obliquely with respect to a direction orthogonal to the shaft body through the thin portion . 2. The timepiece bearing according to claim 1, wherein the plurality of gripping portions include a taper at an end portion on the shaft body side . Wherein the plurality of gripping portions, watch bearing according to claim 1 or 2, characterized in that provided at equal intervals in the circumferential direction of the shaft body. The timepiece bearing according to any one of claims 1 to 3, wherein the plurality of gripping portions are provided at positions symmetrical with respect to the shaft body . 5. The timepiece bearing according to claim 1 , wherein the plurality of locking pieces include a taper at an end portion to be fitted into the groove . The timepiece bearing according to claim 1 , wherein the plurality of gripping portions include a notch portion on the shaft body side . A timepiece movement comprising a train wheel, an escapement, and a speed governor, wherein at least one of the train wheel or the escapement or the speed governor is used for a timepiece according to claim 1. A movement characterized by the use of bearings . A timepiece comprising the movement according to claim 7 and a casing that encloses the movement .

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