CH709641A2 - Balance wheel and hairspring, regulator, movement and clock. - Google Patents

Abstract

Provided are a balance spring with spiral spring, a regulator, a clockwork and a clock, which allow a reduction in thickness. There are provided a balance shaft 28, the both axial ends of which are rotatably supported by shock absorbing bearing units 5A and 5B and which is configured to rotate together with a balance wheel 20, a first connecting portion 31 to which a coil spring 16 is connected via a spiral roller 18, and a second connecting portion 32 to which a double pulley 35 is connected, wherein the first connecting portion 31 and the second connecting portion 32 are provided with a first space portion 41 and a second space portion 42, respectively, in which first pipe portions 56a of the shock absorbing bearing units 5A and 5B are arranged , Each of the first space area 41 and the second space area 42 is provided over the entire circumference in the circumferential direction of the balance shaft 28.

Description

BACKGROUND OF THE INVENTION

1. Field of the invention

The present invention relates to a balance spring with a spiral spring, a regulator, a movement and a clock.

2. Description of the Related Art

As is known in the art, a mechanical clock is provided with a controller for controlling the rotation of a clockwork spring house, a large floor wheel with drive, a Kleinbodenrad with drive and a second wheel with drive, which form a front wheel train. In general, the governor is provided with a balance-type balance spring composed of a balance wheel, a balance shaft about which the balance wheel rotates, a coil spring formed in a spiral shape and intended to turn the balance wheel by expansion and contraction. a double pulley designed to rotate together with the balance wheel and a spiral pulley that secures the coil spring to the balance shaft.

At both end portions of the balance shaft, a pair of shock preventive bearing mechanisms (bearing units) are provided to receive pins. The pair of shock-absorbing bearing mechanisms support the balance-type balance spring to allow it to rotate about the center axis of the balance wave (see, for example, JP-A-2013-88178 (Patent Literature 1)).

In addition to the function of the time display, a mechanical watch such as a wristwatch serves as a decorative piece. Therefore, depending on the taste of the user, a reduction in the thickness of the movement is desired. However, in the prior art, a pair of bearing units, a spiral roller and a double roller are disposed between the balance wheel and the bearing unit so as to be respectively disposed in the axial direction. Consequently, the distance between the balance wheel and the pair of bearing units is not less than the thickness of the spiral roller and the double roller. Therefore, there was room for improvement in terms of further reducing the thickness of the movement and the timepiece.

BRIEF SUMMARY OF THE INVENTION

The present invention has been made in view of the above problem; Accordingly, it is an object of the present invention to provide a spring with a spiral spring, a regulator, a clockwork and a clock, which allow a reduction in thickness.

In order to achieve the above object, according to the present invention, there is provided a balance type balance spring comprising: a shaft member in which at least one axial end thereof is rotatably supported by a bearing unit and which rotates together with a balance wheel; and a connecting portion to which is connected at least one mechanical member configured to effect the power transmission, the connecting portion being provided with a space portion in which at least a part of the bearing unit is arranged.

According to the present invention, a space portion is provided in the connecting portion, in which at least a part of the bearing unit is arranged, so that it is possible by arranging a part of the bearing unit on the inside of the space portion to arrange the connecting portion and the bearing unit such that they partially overlap, as seen in the radial direction of the shaft member. As a result, the distance between the balance wheel and the bearing unit is less than the thickness of the connection portion, so that a reduction in the thickness of the movement and the clock can be achieved compared to the prior art, when the coil spring balance of the present invention in the clockwork of the clock is installed.

Further, the space portion is provided so as to extend in the circumferential direction of the shaft member.

According to the present invention, it is possible to reliably arrange a part of the storage unit in the space area. Therefore, a reduction in the thickness of the movement and the clock can be achieved.

Further, a coil spring, which is provided on one side in the axial direction of the balance wheel and adapted to rotate the balance wheel, and a double roller provided on the other side in the axial direction of the balance wheel; the mechanical component comprises the coil spring and the double roller; and the space portion is provided at least at one of the first connecting portion to which the coil spring is connected and the second connecting portion to which the double pulley is connected.

According to the present invention, the space portion is provided at least at one of the first connecting portion to which the coil spring is connected and the second connecting portion to which the double pulley is connected, so that it is arranged by arranging a portion of the bearing unit on the Inside the space portion is possible to arrange at least one of the first connecting portion and the second connecting portion such that it, as seen from the radial direction of the shaft member, a portion of the bearing unit superimposed. As a result, a reduction in the thickness of the timepiece and the timepiece can be achieved as compared with the prior art when the coil spring balance of the present invention is incorporated in a timepiece of a timepiece.

Further, a coil spring provided on one side in the axial direction of the balance gear and configured to rotate the balance gear, a spiral roller to which one end of the coil spring is fixed, and a double roller provided on the is provided on the other side in the axial direction of the balance wheel, wherein the mechanical component comprises the coil spring and the double roller; and the space portion is provided at least at one of the first connecting portion to which the coil spring is connected by the spiral roller and the second connecting portion to which the double pulley is connected.

According to the present invention, the space is provided at least at one of the first connecting portion to which the spiral roller is connected and the second connecting portion to which the double roller is connected, so that it can be arranged by arranging a portion of the bearing unit on the Inside the space portion is possible to arrange at least one of the first connecting portion and the second connecting portion such that it, as seen from the radial direction of the shaft member, a portion of the bearing unit superimposed. As a result, the distance between the balance wheel and the bearing unit is less than the thickness of at least one of the spiral roller and the double roller, so that a reduction in the thickness of the movement and the clock compared to the prior art can be achieved when the balance spring with the Present invention is incorporated in a clockwork of a clock.

Furthermore, the controller is equipped according to the present invention with the balance described above with coil spring and a pair of storage units.

According to the present invention, a reduction in the thickness of a regulator can be achieved.

Further, at least one of the pair of bearing units is a shock-absorbing bearing unit designed to damp a shock acting on a bearing portion.

According to the present invention, even if, for example, an external shock is applied, the shock is damped and damage to the shaft member and the bearing portion can be prevented. Consequently, a regulator can be provided which can have a reduced thickness and is better in terms of its longevity.

Furthermore, the pair of bearing units and the balance wheel are opposite each other without other components as intermediate links.

According to the present invention, no component between the bearing units and the balance wheel is provided so that by the closest possible arrangement of the bearing units and the balance wheel together a further reduction in the thickness of the regulator can be achieved.

In addition, the movement according to the present invention is provided with the controller described above.

According to the present invention, by providing the above-described regulator, a reduction in the thickness of a movement as compared with the prior art can be achieved.

Furthermore, a carrier unit is provided which is configured to rotate the controller about a predetermined axis.

According to the present invention, it is possible to compensate for the influence of the direction of gravity by rotating the regulator about a predetermined axis by means of the carrier unit. The movement according to the present invention is thus equipped with a so-called tourbillon mechanism, which can prevent a dependent on the direction of gravity change in the vibration cycle of the balance spring with spiral spring, so that it is possible to provide a movement that has a smaller thickness and a can have better timing accuracy.

In addition, the clock is equipped according to the present invention with the above-described movement.

Since a watch is provided with a reduced thickness, according to the present invention, a watch with better design characteristics can be provided.

According to the present invention, a space portion is provided at the connecting portion, wherein at least a portion of the bearing unit is provided, so that it is possible by arranging a portion of the bearing unit on the inside of the space portion to arrange the connecting portion and the bearing unit such that they partially overlap, as seen from the radial direction of the shaft member. As a result, the distance between the balance wheel and the bearing unit is less than the thickness of the connecting portion, so that a reduction in the thickness of the movement and the clock compared to the prior art can be achieved when the coil spring balance of the present invention in a clockwork of a clock is installed.

BRIEF DESCRIPTION OF THE DRAWINGS

[0027] <Tb> FIG. 1 <SEP> is an external view of a timepiece according to a first embodiment. <Tb> FIG. 2 <SEP> is a plan view of a movement viewed from the front. <Tb> FIG. 3 <SEP> is a sectional view taken along the line A-A of FIG. 2. <Tb> FIG. FIG. 4 is a magnified view illustrating the shock absorbing bearing unit of FIG. 3 and its surroundings. FIG. <Tb> FIG. 5 <SEP> is a side sectional view of a timepiece according to a modification of the first embodiment. <Tb> FIG. 6 <SEP> is a side sectional view of a movement according to a second embodiment. <Tb> FIG. 7 <SEP> is a side sectional view of a movement according to a third embodiment. <Tb> FIG. 8 <SEP> is a side sectional view of a movement according to a fourth embodiment.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

(First Embodiment)

In the following, the first embodiment of the present invention will be described with reference to the drawings.

In the following, a mechanical wristwatch (corresponding to the "watch" referred to in the claims) will be referred to simply as a "watch") and a clockwork built into the watch, and then a spring with a spiral spring and a regulator form the movement, described in detail.

[Clock]

In general, the mechanical body comprising the driving part of the watch will be referred to as a "clockwork". The complete product obtained by fitting a dial and hand to this movement and inserting it into a watch case is called the "whole" of the watch. Of the two sides of a main plate forming the watch, the side on which the glass of the watch is located, that is the side on which the dial is located, is called the "back" of the movement. Furthermore, of the two sides of the main plate, the side on which the clock base of the watch case is located, that is, the side opposite the dial, referred to as the "front" of the movement.

FIG. 1 is an external view of a timepiece 1 according to a first embodiment. FIG.

As shown in Fig. 1, the whole of a clock 1 according to the present embodiment within a clock base (not shown) and a glass 2 existing watch case 3, a movement 100, a dial 11 with divisions, etc., which contains the Indicate time information, and pointers comprising an hour hand 12 indicating the hour and a minute hand 13 indicating the minute. A day window 11a showing numbers indicating the date is opened in the dial 11. As a result, clock 1 allows you to control the date in addition to the time.

FIG. 2 is a plan view of the timepiece 100 of the timepiece 1 as viewed from the front. In Fig. 2, in order to facilitate the understanding of the drawing, a part of the components constituting the movement 100 has been omitted, and each watch member is shown in a simplified form.

As shown in Fig. 2, the movement 100 of the mechanical watch on a main plate 144, which forms the carrier. An elevator shaft 110 is rotatably installed in an elevator shaft guide hole 102 of the main plate. The position in the axial direction of the elevator shaft 110 is determined by a switching device including an angle lever 103, a rocker 105, a rocker spring 107, an angle lever catch 109, and so forth.

When the elevator shaft 110 is rotated, an elevator gear 112 rotates by the rotation of a clutch wheel (not shown). By the rotation of the elevator gear 112, a crown wheel 114 and a ratchet wheel 116 are sequentially rotated, and a tension spring (not shown) accommodated in a clockwork spring house 120 is wound up.

The clockwork spring house 120 has a spring core, which serves as a shaft portion, at the two ends pins (not shown) are provided above; the pins are each rotatably supported by the main plate 144 and a barrel bridge 134, whereby the clockwork spring house 120 is rotatably mounted between the main plate 144 and the barrel bridge 134. A large-bottomed wheel with drive 124, a low-wheel with drive 126, a second wheel with drive 128 and an escapement wheel with drive 130 have pins (not shown) projecting from both ends of their respective shaft sections and rotatably supported by the main plate 144 and a gear train bridge 136 are, whereby these wheels are rotatably mounted with drives between the main plate 144 and the gear train bridge 136.

When the clockwork spring house 120 is rotated by the restoring force of the mainspring, the large floor wheel with drive 124, the low-floor wheel with drive 126, the second wheel with drive 128 and the escape wheel with drive 130 are rotated successively by the rotation of the clockwork spring house 120. The clockwork spring house 120, the large floor wheel with drive 124, the small floor wheel with drive 126 and the second wheel with drive 128 form a front wheel train.

At the same time, as the large bottom wheel rotates with drive 124, a quarter tube (not shown) rotates due to the rotation, and the minute hand 13 (see Fig. 1) attached to the quarter tube indicates the "minute". In addition, due to the rotation of the quarter tube, an hour wheel (not shown) is rotated by the rotation of a minute wheel (not shown), and an hour wheel 12 attached to the hour wheel (see Fig. 1) indicates the "hour".

A speed controller 140 for controlling the rotation of the front gear train consists of the escapement wheel with drive 130, an anchor fork 142 and a regulator 7, which includes the balance spring with coil spring 10.

On the outer periphery of the escape wheel with drive 130 teeth 132 are formed. The anchor fork 142 is rotatably supported between the main plate 144 and an armature bridge 138 and provided with a pair of pallets 142a and 142b. In the state in which a pallet 142a of the anchor fork 142 engages a tooth 132 of the escapement wheel with drive 130, the escapement wheel with drive 130 temporarily stops.

The controller 7 consists of a balance with coil spring 10 and a shock-absorbing bearing unit 5, which rotatably holds the balance with coil spring 10. According to the present embodiment, the balance with coil spring 10 is rotatably supported between a balance bridge 104 and the main plate 144 by means of the shock-absorbing bearing unit 5. The balance spring 10 rotates at a fixed rate, causing the one pallet 142a and the other pallet 142b of the armature fork 142 to alternately engage and disengage the teeth 132 of the escapement sprocket 130 and disengage them causes the escape wheel with drive 130 to be released at a predetermined rate. As for the balance-type balance spring 10 and the shock-proofing bearing unit 5, they will be described below in detail.

In this design, a housed in the clockwork spring house 120 tension spring (not shown) mounted using a winding shaft 110; and then the clockwork spring house 120 is rotated by the rotational force when this tension spring is rewound. The rotation of the clockwork spring housing 120 rotates the large floor gear with drive 124 engaged therewith. As the floorboard wheel 124 rotates, the low floor gear with turn 126 rotates therewith. When the minor floor gear rotates with drive 126, it rotates the second wheel with drive 128 engaged therewith. As the second wheel with drive 128 rotates, the speed control 140 is driven. By driving the gear regulator 140, the large bottom wheel with drive 124 is controlled so that it performs one revolution per hour.

[Balance with spiral spring]

FIG. 3 is a schematic sectional view taken along the line A-A of FIG. 2. FIG. For ease of clarity of the drawing, the components of the balance with coil spring 10 in Fig. 3 are simplified.

As shown in Fig. 3, the balance spring with spiral spring 10 mainly comprises a balance wheel 20, a coil spring 16 (corresponding to the "mechanical component" in the claims), a balance shaft 28 and a double roller 35 (the "mechanical component »In the claims). In the following description of the balance-type balance spring 10, it should be understood that the center of rotation about which the balance-type balance spring 10 rotates is the center axis O; the direction along the center axis O is referred to as the axial direction, a direction orthogonal to the center axis O is referred to as the radial direction, and the direction along which the rotation about the center axis O is made is referred to as the circumferential direction. In FIG. 3, the upper side in the drawing plane with respect to the main plate 144 is the front side of the movement 100, and the lower side with respect to the main plate 144 is the back side of the movement 100.

The balance wheel 20 is formed of a metal material such as beryllium bronze or brass and provided with a balance main body portion 21 formed with a ring-like shape. The center axis of the balance main body portion 21 coincides with the center axis O, which is the center of rotation of the balance-type balance spring 10.

As shown in FIG. 2, on the inside of the balance gear main body portion 21, four arm portions 23 (23 a to 23 d) are provided along the radial direction toward the center axis O. The four arm portions 23 a to 23 d are formed at substantially equal intervals with a pitch of 90 degrees in the circumferential direction of the balance gear main body portion 21. Timing weights 22 are provided at the connecting portions between the balance main body portion 21 and the arm portions 23a to 23d. The timing weights 22 are weights intended to adjust the balance and moment of inertia of the balance wheel 20; they are rotatable, for example, around the central axis O parallel guide shafts.

As shown in Fig. 3, on a coupling portion 24 of the four arm portions 23a to 23d on the inside of the balance wheel main body portion 21 a to the central axis O coaxial mating engagement bore 24a is formed.

At the portion of the coupling portion 24 on the front side of the movement 100 (the upper side in Fig. 3) and around the fitting engagement hole 24a, a first connection portion 31 (corresponding to the "first connection portion" in the claims) is formed which is coaxial with Center axis O is. The first connecting portion 31 is formed as an annular protrusion projecting from the coupling portion 24 toward the front of the movement 100. On the first connecting portion 31, a spiral roller 18 described below is attached.

On the inside in the radial direction of the first connection portion 31, a first space portion 41 (corresponding to the "space portion" in the claims) is provided. The first space area 41 is formed over the entire circumference of the balance shaft 28 on the front side of the movement 100 with respect to the coupling portion 24.

At the portion of the coupling portion 24 on the back side of the movement 100 (the lower side in FIG. 3) and around the fitting engagement hole 24a, there is formed a second connection portion 32 (corresponding to the "second connection portion" in the claims) which is coaxial with Center axis O is. The second connection portion 32 is formed as an annular projection projecting from the coupling portion 24 toward the rear of the movement 100. On the outside in the radial direction of the second connecting portion 32, a double roller 35 is arranged, which will be described below.

On the inner side in the radial direction of the second connecting portion 32, a second space area 42 (corresponding to the "space area" in the claims) is provided. The second space area 42 is formed over the entire circumference in the circumferential direction of the balance shaft 28 on the back of the movement 100 with respect to the coupling portion 24.

The balance wheel 20 is equipped with the center shaft O coaxial balance shaft 28 (which corresponds to the "wave element" in the claims). The balance shaft 28 is a rod-like member formed of a metal material such as iron.

The balance shaft 28 is provided at its two axial ends with conical pins 29 (29 a and 29 b). The pins 29a and 29b at both ends of the balance shaft 28 are supported by the shock absorbing bearing unit 5 described later so as to be rotatable about the center axis O.

The balance wheel 20 is attached to the balance shaft 28 by, for example, it is attached to it. As a result, the balance wheel 20 and the balance shaft 28 are integrated with each other.

The spiral spring 16 is a spiral-shaped leaf spring made of thin sheet metal, which is formed from a metal material such as iron, nickel or niobium and arranged on the front of the movement 100 relative to the balance wheel 20. As seen from the axial direction, the coil spring 16 is formed such that it expands into a so-called Archimedean spiral.

The inner end portion 16a of the coil spring 16 is connected to the balance wheel 20 via a spiral roller 18 described below. The outer end portion 16 b of the coil spring 16 is attached to a projection 106 which projects from the balance bridge 104 to the rear of the movement 100 out. The coil spring 16 expands and contracts while the outer end portion 16 b is fixed to the boss 106, thereby rotating the balance gear 20.

The spiral roller 18 is a C-ring-shaped member formed of a metal material such as iron, stainless steel or brass and attached to the first connecting portion 31. The inner end portion 16a of the coil spring 16 is fixed to the spiral roller 18 by welding or the like.

The double pulley 35 is, like the balance wheel 20, a ring-like member made of a metal material such as stainless steel or brass and disposed on the outside in the radial direction of the second connecting portion 32. The double pulley 35 according to the present embodiment is formed integrally with the balance wheel 20 at the corner portion between the coupling portion 24 of the balance wheel 20 and the second connecting portion 32. In Fig. 3, the boundary between the double roller 35 and the balance wheel 20 is indicated by a double dashed chain line.

On the outside in the radial direction of the double roller 35, a lever block 26 is provided, which is formed for example of ruby. The lever block 26 projects from the coupling portion 24 of the balance wheel 20 toward the rear of the movement 100. The lever block 26 may be attached to and detached from a pallet box 143 a formed on the inside of an entrance claw 143 of the anchor fork 142. Although the lever block 26 according to the present embodiment is provided on an arm portion 23a of the balance wheel 20, it may be provided on the double roller 35 as well.

On the double roller 35, a shoulder 35a is formed, which is recessed in the radial direction from the outside to the inside in a position corresponding to the lever block 26, and a step lower than the second connecting portion 32. When the anchor fork 142 and the lever block 26 are engaged with each other, the shoulder 35a acts as a relief portion which prevents a safety pin 143b of the anchor fork 142 from coming into contact with the double roller 35.

[Regulator]

Fig. 4 is an enlarged view of the shock-absorbing bearing units 5 in Fig. 3 and its peripheral area.

The regulator 7 is equipped with the above-described balance having a coil spring 10 and a pair of shock preventive bearing units 5 (Figs. 5A and 5B).

As shown in FIG. 4, the shock-absorbing bearing units 5A and 5B support the pins 29a and 29b provided at both axial ends of the balance-shaft 28 so as to be able to rotate about the center axis O. The two shock-absorbing bearing units 5A and 5B are attached to the balance bridge 104 and the main plate 144, respectively.

The shock-absorbing bearing units 5A and 5B mainly include a bearing portion 50, a shock-absorbing bushing 56 and a shock-absorbing spring 59. Hereinafter, the components of the shock-absorbing bearing units 5 will be described. The one shock absorbing bearing unit 5A on the side of the balance bridge 104 and the other shock absorbing bearing unit 5B on the side of the main plate 144 have the same structure. Therefore, a shock absorbing bearing unit 5A on the side of the balance bridge 104 will be described in detail below, and a detailed description of the other shock absorbing bearing unit 5B on the main plate 144 side will be omitted.

The bearing portion 50 is equipped with a guide bush 53, a perforated brick 51 and a cap stone 52.

The guide bushing 53 is a tubular member formed of a metal material such as iron or brass and has a first pipe portion 53a and a second pipe portion 53b.

The perforated brick 51 is disposed on the inside of the first tubular portion 53a. The first pipe section 53a has a first tapered surface 54a at the outer corner portion of the opening. The first tapered surface 54a is formed, for example, over the entire circumference of the first pipe portion 53a, and gradually inclined from the inside to the outside in the radial direction.

The second pipe section 53b is disposed on the front side of the movement 100 relative to the first pipe section 53a and has a larger diameter than the first pipe section 53a. The cover brick 52 is disposed on the inside of the second pipe section 53b. The second pipe portion 53b has a second tapered surface 54b at the outer corner portion of the connecting portion between itself and the first pipe portion 53a. The second tapered surface 54b is formed, for example, over the entire circumference of the second pipe portion 53b, and gradually inclined from the inside to the outside in the radial direction.

The perforated brick 51 is a substantially circular in plan view element, which is formed for example of ruby, and has a through hole 51 a in the middle. The inner diameter of the through hole 51a of the hole 51 is sufficiently large to allow the insertion of the pin 29a. Furthermore, the perforated brick 51 is formed in a size that allows the fastening by pressing into the first pipe section 53 a of the guide bushing 53.

The cap stone 52 is a member having a substantially circular shape in plan view, which is formed of ruby or the like. The cap stone 52 is arranged on the front side of the movement 100 relative to the perforated brick 51 and lies opposite the axial end face of the pin 29a. Further, the cap stone 52 is disposed at the end portion of the first pipe portion 53a on the inside of the second pipe portion 53b and closes the opening of the first pipe portion 53a. The front surface of the movement 100 facing the main surface of the cover stone 52 is formed with a convex curved surface design.

The guide bushing 53 is housed in a shock-absorbing bushing 56. The shock absorber bushing 56 is a tube-closed type member having an outer-side opening 58 in the axial direction and formed of a metal material such as iron or brass. The shock absorber bush 56 is installed, for example, in a mounting hole of the balance bridge 104. The shock absorber bush 56 has a first pipe section 56a and a second pipe section 56b.

The first tube section 56a encloses the guide bushing 53 largely. On the inner surface of the first pipe portion 56a and in positions corresponding to the first tapered surface 54a and the second tapered surface 54b of the guide bush 53, a first tapered surface 57a and a second tapered surface 57b are respectively formed. The first tapered surface 57a and the second tapered surface 57b of the anti-shock bushing 56 are each in plan contact with the first tapered surface 54a and the second tapered surface 54b of the guide bushing 53.

The second pipe section 56b is disposed on the front side of the movement 100 with respect to the first pipe section 56a and has a larger diameter than the first pipe section 56a. A flange portion 58a is formed at the opening 58 of the second pipe portion 56b. At the opening 58 of the second pipe section 56b, the flange section 58a protrudes on the inner side in the radial direction.

A step surface 56c is formed on the outer peripheral surface of the shock absorbing bush 56 and the connecting portion between the second pipe portion 56b and the first pipe portion 56a. The step surface 56 c is provided so as to face the front end surface 31 a of the first connection portion 31.

A shock-absorbing spring 59 is provided at the opening 58 of the shock-absorbing bushing 56. The shock-absorbing spring 59 is a flexible ring-like elastic member formed of a metal material such as iron or nickel. The outer peripheral portion of the shock absorbing spring 59 is disposed on the inner side in the axial direction with respect to the flange portion 58a. The shock-absorbing spring 59 drives the cap stone 52 and the guide bush 53 toward the inside in the axial direction.

In the on the side of the balance bridge 104 a shock-absorbing bearing unit 5A of the pair of shock-absorbing bearing units 5A and 5B constructed as described above, the first tube portion 56a of the shock-absorbing bush 56 is disposed on the inside of the first space portion 41.

Moreover, the one shock-proof bearing unit 5A and the balance wheel 20 are opposed to each other without any other components than intermediate members. The first pipe portion 56a of the shock absorber bushing 56 of the one shockproofing unit 5A is thus disposed on the inside of the first space portion 41, whereby the shock absorbing bearing unit 5A, as seen from the radial direction of the balance wheel 20, is arranged such that the first connecting portion 31 and a portion of the one Surge bearing unit 5A superimpose each other. As a result, the distance between the balance wheel 20 and the shock absorbing bearing unit 5A is smaller than the thickness of the first connecting portion 31 and the spiral roller 18.

In the other shock absorbing bearing unit 5B on the side of the main plate 144, the first tube portion 56a of the shock absorbing sleeve 56 is disposed on the inside of the second space portion 42. In addition, the other shock-absorbing bearing unit 5B and the balance wheel 20 are opposed to each other without any other components than intermediate members. Thus, the first pipe portion 56a of the shock absorbing bushing 56 of the other shock absorbing bearing unit 5B is disposed on the inside of the second space portion 42, whereby the second connecting portion 32 and a portion of the other shock absorbing bearing unit 5B are arranged to be seen from the radial direction of the balance shaft 28 overlay each other. As a result, the distance between the balance wheel 20 and the other shock-absorbing bearing unit 5B is less than the thickness of the second connecting portion 32 and the double roller 35.

There is a fear that the position of the balance shaft 28 shifts in the axial direction and the radial direction when a shock load is applied from the outside.

For example, when a shock load is applied to the balance shaft 28 along the axial direction, the balance shaft 28 is displaced along the axial direction, and the bearing portion 50 supporting the balance shaft 28 is also displaced along the axial direction. On the other hand, on the outer side in the axial direction of the bearing portion 50, the shock-absorbing spring 59 is provided, which drives the bearing portion 50 toward the inside in the axial direction, so that even in the case of displacement of the bearing portion 50 along the axial direction, the bearing portion 50 is elastically supported is and the shock load is damped.

Further, for example, even if a large impact load is applied against the urging force of the shock-absorbing spring 59, striking occurs either between the step surface 56c of the shock-absorbing bush 56 and the front-end surface 31a of the first connecting portion 31 or between the step surface 56c of FIG Anti-shock bushing 56 and the forward end face 32a of the second connecting portion 32, whereby the movement of the balance wheel 20 and the balance shaft 28 along the axial direction is regulated and the shock load is damped.

Further, for example, when a shock load is applied to the balance shaft 28 along the radial direction, the balance shaft 28 is displaced along the radial direction, and the bearing portion 50 supporting the balance shaft 28 is also displaced along the radial direction. Here, the first tapered surface 54a and the second tapered surface 54b of the guide bush 53 are respectively in abutment with the first tapered surface 57a and the second tapered surface 57b of the shock absorber bushing 56. Thus, the guide bush 53 becomes oblique toward the outside in the axial direction and the radial direction to move along the first tapered surface 57 a and the second tapered surface 57 b of the shock absorbing bushing 56. On the other hand, on the outer side in the axial direction of the guide bush 53, the shock-absorbing spring 59 is provided, which drives the guide bushing 53 in the direction of the inner side in the axial direction, so that even in the case of displacement of the guide bush 53 in the axial direction and in the direction of the outside in the radial direction, the guide bush 53 is elastically mounted and the shock load is damped. Further, for example, even if a large impact load is applied against the urging force of the shock-absorbing spring 59, striking occurs at least either between the first tube portion 56a of the shock-absorbing sleeve 56 and the inner circumferential surface 31b of the first connecting portion 31 or between the first tube portion 56a of the shock-absorbing sleeve 56 and the inner peripheral surface 32b of the second connecting portion 32, thereby regulating the movement of the ram 20 and the balance shaft 28 in the radial direction and damping the shock load.

Effects of First Embodiment

According to the present embodiment, the first connection portion 31 and the second connection portion 32 are provided with the first space portion 41 and the second space portion 42, respectively, in which a part of the shock-absorbing bearing unit 5 is arranged, so that by arranging a part of the shock-absorbing bearing units 5A and 5B On the inner side of the first space area 41 and the second space area 42, such an arrangement can be accomplished that the first connecting portion 31 and the second connecting portion 32, as viewed from the radial direction of the balance shaft 28, overlap a part of the shock-absorbing bearing units 5A and 5B. As a result, the distance between the balance wheel 20 and the one shock mount unit 5A is smaller than the thickness of the first link portion 31 and the spiral roller 18. Further, the distance between the balance wheel 20 and the other shock mount unit 5B is smaller than the thickness of the second link portion 32 and the double roller 35. Therefore, it is possible over the prior art to achieve a reduction in the thickness of the balance with coil spring 10, the regulator 7, the movement 100 and the clock 1.

Further, the first space portion 41 and the second space portion 42 are provided in the circumferential direction of the balance shaft 28, so that it is possible even when the balance wheel 20 rotates, interference between the peripheral walls of the first space portion 41 and second space area 42 and the shock-absorbing storage units 5A and 5B. Therefore, it is possible to achieve a reduction in the thickness of the movement 100 and the clock 1, while ensuring its timing accuracy.

Furthermore, the shock-absorbing bearing units 5A and 5B are provided which damp a shock applied to the bearing portion 50 so that it is possible to damp the shock and damage the balance-shaft 28 even if, for example, an external impact is applied and the bearing portion 50. Accordingly, a regulator 7 can be provided which enables a reduction in thickness and has a better durability.

In addition, the pair of shock-absorbing bearing units 5A and 5B and the balance wheel 20 are opposed to each other without any other components than intermediate members. Thus, no component is provided between the shock-absorbing bearing units 5A and 5B and the balance wheel 20, so that it is possible that the shock-absorbing bearing units 5A and 5B and the balance wheel 20 are arranged as close to each other as possible, further reducing the thickness of the regulator 7 to achieve.

Further, according to the present embodiment, it is possible to provide a timepiece 1 having better design characteristics by manufacturing the reduced-thickness movement 100.

[Modification of First Embodiment]

Hereinafter, a modification of the first embodiment will be described.

Fig. 5 is a side sectional view of a timepiece according to the modification of the first embodiment; It is a sectional view corresponding to a sectional view taken along the line A-A of Fig. 2.

In the first embodiment described above, the spiral roller 18 is fixed to the first connecting portion 31 of the balance wheel 20, and the boss 106 is fixed to the balance bridge 104.

As shown in Fig. 5, on the other hand, the modification of the first embodiment from the first embodiment differs in that the spiral roller 18 is fixed to the balance bridge 104 and in that the spiral roller 106 is fixed to the balance wheel 20. Hereinafter, a description of the same structure as in the first embodiment will be omitted.

The spiral roller 18 is attached to the balance bridge 104 via the shock-absorbing bearing unit 5A. More specifically, the spiral roller 18 is fixed to the first pipe portion 56a of the shock absorbing bushing 56 of the shock absorbing bearing unit 5A on the side of the balance bridge 104 by press-fitting, adhering, and the like.

The inner end portion 16 a of the coil spring 16 is connected to the spiral roller 18. In the present modification, therefore, the spiral roller 18 itself, to which the inner end portion 16 a of the coil spring 16 is fixed, forms the first connecting portion 31.

In addition, the inner portion of the spiral roll 18 formed with a ring-like shape forms the first space portion 41. In the first space portion 41, the first pipe portion 56a of the shock absorbing bush 56 of the one shockproofing unit 5A is disposed. As a result, the spiral roller 18 and a portion of the one shock-proofing bearing unit 5A, as viewed from the radial direction of the balance-of-shaft 28, are arranged so as to overlap each other. Furthermore, the distance between the balance wheel 20 and the one shock-absorbing bearing unit 5A is smaller than the thickness of the spiral roller 18.

The lug 106 is attached to the arm portion 23 a of the balance wheel 20. The outer end portion 16b of the coil spring 16 is fastened by the projection 106 on the balance wheel 20. The coil spring 16 expands and contracts while its inner end portion 16 a is fixed to the spiral roller 18, thereby rotating the balance gear 20.

[Effect of Modification of First Embodiment]

Also, in the modification of the first embodiment, the same effect as in the first embodiment can be obtained. That is, according to the present modification, the spiral roller 18 itself constitutes the first connecting portion 31 and has a first space portion 41 in which the first tube portion 56a of the shock absorbing bush 56 of the shock absorbing bearing unit 5A is disposed so that the spiral roller 18 and a portion of the one shockproofing bearing unit 5A, as seen from the radial direction of the balance shaft 28, are arranged so as to overlap each other. Therefore, the distance between the balance wheel 20 and the one shock mount unit 5A is smaller than the thickness of the spiral roll 18 having the first joint portion 31. Further, the distance between the balance wheel 20 and the other shock mount unit 5B is less than the thickness of the second joint portion 32 and the double roll 35. Therefore, it is possible over the prior art to achieve a reduction in the thickness of the balance with coil spring 10, the regulator 7, the movement 100 and the clock 1.

[Second Embodiment]

Next, the second embodiment will be described.

Fig. 6 is a side cross-sectional view of the movement of a timepiece according to the second embodiment.

In the first embodiment described above, the spiral roller 18 is fixed to the first connecting portion 31 of the balance wheel 20 by being fitted on it.

On the other hand, as shown in Fig. 6, the second embodiment differs from the first embodiment in that the spiral roller 18 is fixed to the coupling portion 24 of the balance wheel 20.

Hereinafter, a description of the same configuration as in the first embodiment will be omitted.

At the coupling portion 24 of the balance wheel 20, a fitting engagement recess 25 is formed. The fitting engagement recess 25 is formed by recessing in the axial direction. The mating engagement recess 25 may extend through the balance wheel 20.

The spiral roller 18 has a fitting engagement projection 18a. When the spiral roller 18 is disposed coaxially with the central axis O, the fitting engagement projection 18a is pressed into a fitting engagement recess 25 of the balance wheel 20. As a result, the spiral roller 18 is attached to the portion of the coupling portion 24 of the balance wheel 20, which is located on the front side of the movement 100.

The inner end portion 16a of the coil spring 16 is connected to the spiral roller 18. Thus, as in the modification of the first embodiment, even in the second embodiment, the spiral roller 18 itself to which the inner end portion 16a of the coil spring is fixed forms the first connecting portion 31. Further, the inner portion of the spiral roller 18 forms the first space portion 41 Spiral roller 18 and a portion of a shock-absorbing bearing unit 5A, as seen from the radial direction of the balance shaft 28, arranged so as to overlap each other. The distance between the balance wheel 20 and the one shock-absorbing bearing unit 5 A is less than the thickness of the spiral roller 18th

According to the second embodiment, it is possible to obtain the same effect as in the first embodiment. Compared to the prior art, it is possible to achieve a reduction in the thickness of the balance with coil spring 10, the controller 7, the movement 100 and the clock 1.

[Third Embodiment]

Next, the third embodiment will be described.

Fig. 7 is a side sectional view of a timepiece according to the third embodiment.

In the first embodiment described above, the spiral roller 18 is fixed to the first connecting portion 31 of the balance wheel 20 by being fitted on it.

On the other hand, as shown in FIG. 7, the third embodiment differs from the first embodiment in that the spiral roller 18 is formed integrally with the ratchet wheel 20.

Hereinafter, a description of the same structure as in the first embodiment will be omitted.

The spiral roller 18 is integrally formed with the balance wheel 20 at the portion of the connecting portion 24 of the balance wheel 20 located on the front side of the movement 100. The inner end portion 16 a of the coil spring 16 is connected to the spiral roller 18. Thus, as in the modification of the first embodiment and in the second embodiment, even in the third embodiment, the spiral roller 18 itself to which the inner end portion 16a of the coil spring 16 is fixed forms the first connection portion 31. According to the third embodiment, it is possible to use the first embodiment to achieve the same effect as in the first embodiment. Compared to the prior art, it is possible to achieve a reduction in the thickness of the balance with coil spring 10, the controller 7, the movement 100 and the clock 1. In addition, by integrally forming the spiral roller 18 with the balance wheel 20, the number of components can be reduced.

[Fourth Embodiment]

Next, the fourth embodiment will be described.

Fig. 8 is a side sectional view of a timepiece according to the fourth embodiment.

In the first embodiment described above, the regulator 7, which comprises the balance spring with coil spring 10 and the shock absorbing bearing units 5A and 5B, is fixed to the main plate 144 and the balance bridge 104.

On the other hand, as shown in Fig. 8, the fourth embodiment differs from the first embodiment and the modification of the first embodiment in that the regulator 7 comprising the balance spring with coil spring 10 and the shock-absorbing bearing units 5A and 5B is different mounted around the central axis O rotatable support unit 70 is mounted.

Hereinafter, a description of the same structure as in the first embodiment and the modification of the first embodiment will be omitted.

The support unit 70 is provided with an upper bracket 71, which is disposed relative to the main plate 144 on the front side of the movement 100 (the upper side in FIG. 8), a lower bracket 72 which is relative to the upper bracket 71 the back of the movement 100 is arranged, a connecting pin 73, which connects the upper support 71 and the lower support 72 together, and a ring-like stationary gear 76 equipped.

The upper bracket 71 and the lower bracket 72 are frame-like members formed of a metal material such as stainless steel, iron, aluminum, titanium or brass. The upper bracket 71 and the lower bracket 72 are fastened by a connecting bolt 73 and a screw 73a with a predetermined space between them. The regulator 7, which comprises the balance spring with coil spring 10 and the shock absorbing bearing units 5A and 5B, is mounted between the upper bracket 71 and the lower bracket 72.

The upper bracket 71 and the lower bracket 72 have fixing holes 71a and 72a respectively coaxial with the center axis O. The shock-absorbing bearing units 5A and 5B are respectively fitted by fitting engagement in the fixing holes 71a and 72a.

A toothed portion 72b of the lower bracket is formed on the outer peripheral edge portion of the lower bracket 72. The toothed portion 72b of the lower beam is engaged with a second intermediate gear 129. The second idler gear 129 together with the clockwork spring housing 120, the large-bottom wheel with drive 124, the low-order wheel with drive 126 and the second wheel with drive 128 form a front gear train (see FIG 2). The second intermediate gear 129 transmits the energy from the clockwork spring housing 120 to the lower support 72nd

Here, the spiral roller 18 of the balance with coil spring 10 via the shock-absorbing bearing unit 5A on the upper bracket 71 is attached. The inner end portion 16 a of the coil spring 16 is connected to the spiral roller 18. Thus, as in the modification of the first embodiment, even in the fourth embodiment, the spiral roller 18 itself to which the inner end portion 16a of the coil spring 16 is fixed forms the first connection portion 31. Further, the inner portion of the spiral roller 18 forms the first space portion 41. The spiral roller 18 and a portion of the one shock-proofing bearing unit 5A, as viewed from the radial direction of the balance-shaft 28, are disposed so as to overlap each other. The distance between the balance wheel 20 and the one shock-absorbing bearing unit 5 A is less than the thickness of the spiral roller 18th

Between the upper carrier 71 and the lower carrier 72, an escape wheel with drive 130 is held by a bearing. The escapement wheel with drive 130 is rotatable about an axis P parallel to the central axis O.

Furthermore, a fixed gear 76 is disposed between the upper bracket 71 and the lower bracket 72. The fixed gear 76 is formed as a ring whose outer diameter is larger than the outer diameter of the upper carrier 71 and the lower carrier 72. A toothed portion 77 is formed on the inner peripheral surface of the fixed gear 76. The toothed portion 77 of the fixed gear 76 is engaged with an escapement drive 131 of the escapement wheel 130.

A ring-like bearing 80 is disposed on the main plate 144 so as to be coaxial with the center axis O.

The bearing 80 is provided with an outer ring 81, an inner ring 82 and a rolling element 83, which allows the relative rotation between the outer ring 81 and the inner ring 82. The inner diameter of the bearing 80 is larger than the outer diameter of the shock-absorbing bearing units 5A and 5B.

The outer ring 81 is inserted into a bearing holding hole 145 formed in the main plate 144 and fixed in position with a screw or the like in this state.

The lower carrier 72 of the carrier unit 70 is fixed to the inner ring 82 by a screw or the like.

The rolling element 83 is a spherical body; and a plurality of rolling elements is disposed between the outer ring 81 and the inner ring 82. The inner ring 82 is rotatable about the center axis O by the rolling elements 83 relative to the outer ring 81 fastened to the main plate 144.

The support unit 70 is rotatable relative to the main plate 144 by the bearing 80 about the central axis O (corresponding to the "predetermined axis" mentioned in the claims).

The timepiece 100 constructed as described above operates as follows.

When the clockspring spring 120 (see Fig. 2) is rotated by the restoring force of the tension spring, the energy is transmitted by the rotation of the clockwork spring house 120 and the second idler gear 129 rotates. Further, it engages with the second idler gear Further, with the rotation of the upper bracket 71 and the lower bracket 72, the escapement wheel with pulley 130 rotates (revolves) about the central axis O. Here, the escapement pinion 131 of FIG Escapement wheel with drive 130 in engagement with the toothed portion 77 of the fixed gear 76. The escapement wheel with drive 130 thus rotates (revolves) about the central axis O and it rotates about the axis P. As a result, the speed controller 140 (see FIG ). The speed controller 140 rotates with rotation of the upper bracket 71 and lower bracket 72 about the center axis O. That is, the movement 100 of the fourth embodiment is provided with the so-called carousel tourbillon mechanism 85 which causes the speed control 140 rotates about the central axis O.

According to the fourth embodiment, the controller 7 is rotated by the carrier unit 70 about the central axis O, whereby it is possible to compensate for the influence dependent on the direction of gravity. The movement 100 according to the fourth embodiment is thus equipped with the so-called carousel-tourbillon mechanism 85, which can suppress a change in the direction of gravity of the vibration cycle of the balance spring with spiral spring 10, so that it is possible to provide a movement 100, which allows a reduction in thickness and has better timing accuracy.

The present invention is not limited to the above embodiments described with reference to the drawings, but allows various modifications without departing from the technical scope thereof.

The movement 100 according to the first embodiment and the modification of the first embodiment is provided with the first space portion 41 formed on the first connection portion 31 and the second space portion 42 formed on the second connection portion 32. On the other hand, as in the fourth embodiment, it is also possible that the movement 100 is provided only with the first space portion 41 formed on the first connection portion 31.

Further, there is also a possibility that the movement is provided only with the second space portion formed on the second connection portion. This means that the movement according to the present invention only needs to be provided with at least one connecting section and spatial area.

Furthermore, it is also possible to combine the above embodiments with each other. For example, by combining the first embodiment with the fourth embodiment, a timepiece 100 provided with the first space portion 41 and the second space portion 42 and equipped with the carousel tourbillon mechanism 85 can be provided.

Although a so-called Swiss lever escapement is used in the above-described embodiments, it should not be construed as limiting. For example, it is also possible to use other than the Swiss lever escapement, such as a chronometer escapement or a co-axial escapement.

The material and the manufacturing method for the coil spring 16 and the balance wheel 20 are not limited to those of the above embodiments. For example, it is also possible to form the coil spring 16 and the balance wheel 20 by means of MEMS (microelectromechanical systems) such as dry etching or electroforming using a material containing predominantly silicon and silicon nitride.

Further, in the above embodiments, the spiral roller 18 and the coil spring 16 are formed separately. In contrast, the spiral roller 18 and the coil spring 16 may be integrally formed.

In the above embodiments, the double pulley 35 and the balance wheel 20 are integrally formed. In contrast, the balance wheel 20 and the double roller 35 may be formed as separate components. Further, while in the above embodiments the lever block 26 is fixed to the balance wheel 20, the lever block 26 may be fixed to the double roller 35.

In the above embodiments, the balance-type balance spring 10 is rotatably supported by the so-called shock absorbing units 5A and 5B. In contrast, it is also possible to use instead of the shock-absorbing bearing units 5A and 5B as a bearing ordinary bearing units or ball bearings without shock-absorbing function.

In the fourth embodiment, the carousel tourbillon mechanism 85 is formed such that the carrier unit 70 rotates together with the controller 7 about the central axis O. In contrast, the carousel-tourbillon mechanism 85 may also be designed such that, for example, the carrier unit 70 rotates together with the controller 7 about a different axis from the central axis O predetermined axis.

On the other hand, it is possible to conveniently replace the components of the above embodiments with other well-known components without departing from the scope of the gist of the present invention.

Claims (10)

1. balance with spiral spring (16), comprising: a shaft member (28) in which at least one axial end thereof is rotatably supported in a bearing unit (5) and which rotates together with a balance wheel (20), and a connecting portion (31, 32) to which at least one mechanical component is provided, which is intended for power transmission, wherein the connecting portion (31, 32) is formed with a space portion (41, 42) in which at least a part of the bearing unit (5) is arranged. 2. balance spring with coil spring according to claim 1, wherein the space portion (41, 42) is provided so as to extend in the circumferential direction of the shaft member (28). 3. balance with coil spring according to claim 1 or 2, further comprising: the spiral spring (16) provided in the axial direction of the balance wheel (20) on one side of the balance wheel (20) and provided for rotating the balance wheel, and a double roller (35) provided in the axial direction of the balance wheel (20) on the other side of the balance wheel (20), wherein the mechanical component comprises the coil spring (16) and the double roller (35); and the space portion is provided at least at one of a first connecting portion (31) to which the coil spring (16) is connected and a second connecting portion (32) to which the double roller (35) is connected. 4. balance with coil spring according to claim 1 or 2, further comprising: the spiral spring (16) provided in the axial direction of the balance wheel (20) on one side of the balance wheel (20) and provided for rotating the balance wheel, a spiral roller (18) to which one end of the coil spring (16) is fixed, and a double roller (35) provided in the axial direction of the balance wheel (20) on the other side of the balance wheel (20), wherein the mechanical component comprises the coil spring (16) and the double roller (35); and the space portion is provided at least at one of a first connecting portion (31) to which the coil spring (16) is connected by the spiral roller (18) and a second connecting portion (32) to which the double roller (35) is connected. 5. A regulator comprising a balance spring (10) with coil spring (16) according to claim 3 or 4 and a pair of bearing units (5a, 5b). A regulator according to claim 5, wherein at least one bearing unit of the pair of bearing units is a shock-absorbing bearing unit (5a, 5b) for damping a shock applied to a bearing portion for supporting the shaft member. 7. Regulator according to claim 5 or 6, wherein the pair of bearing units and the balance wheel (20) opposed to each other without other components as intermediate links. 8. movement, which is equipped with a controller (7) according to any one of claims 5 to 7. 9. A movement according to claim 8, wherein a support unit (70) is provided, which is designed for rotating the controller (7) about a predetermined axis. 10 o'clock, which is equipped with a movement according to claim 8 or 9.