CH709641B1 - Balance spring with coil spring, regulator, clockwork and clock. - Google Patents

Abstract

A balance spring with a spiral spring, a regulator, a clockwork and a clock are provided, which enable a reduction in thickness. There is provided a balance shaft 28, the two axial ends of which are rotatably supported by shock protection bearing units 5A and 5B and which is designed to rotate together with a balance wheel 20, a first connecting section 31 to which a spiral spring 16 is connected via a spiral roller 18, and a second connection section 32, to which a double roller 35 is connected, the first connection section 31 and the second connection section 32 being provided with a first recess 41 and a second recess 42, in each of which first tube sections 56a of the shock protection bearing units 5A and 5B are arranged . Both the first recess 41 and the second recess 42 are provided over the entire circumference in the circumferential direction of the balance shaft 28.

Description

description

Background of the Invention

1. Field of the Invention The present invention relates to a balance spring with a coil spring, a regulator, a clockwork and a clock.

2. Description of the Prior Art As is known in the art, a mechanical watch is provided with a controller for controlling the rotation of a clockwork barrel, a large-bottomed wheel with a drive, a small-bottomed wheel with a drive, and a second wheel with a drive form a front gear train. In general, the regulator is provided with a balance spring with a spiral spring, which consists of a balance wheel, a balance shaft around which the balance wheel rotates, a spiral spring which is designed in a spiral shape and is intended to rotate the balance wheel by expansion and contraction. a double roller, which is designed to rotate together with the balance wheel, and a spiral roller, with which the coil spring is attached to the balance shaft.

At both end portions of the balance shaft, a pair of shock protection bearing mechanisms (bearing units) are provided to receive pins. The pair of shock lock bearing mechanisms support the balance spring with a coil spring to enable it to rotate about the center axis of the balance shaft (see, for example, JP-A-2013-88 178 (patent literature 1)).

In addition to the function of the time display, a mechanical watch such as a wristwatch serves as an ornament. Therefore, depending on the user's taste, a reduction in the thickness of the clockwork is desirable. However, in the prior art, a pair of bearing units, a scroll roller and a double roller are arranged between the balance wheel and the bearing unit so that they are arranged in the axial direction, respectively. 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 still room for improvement in the form of further reducing the thickness of the clockwork and the clock.

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 balance spring, a regulator, a clockwork and a clock, which allow a reduction in thickness.

In order to achieve the above-mentioned object, a balance spring with a spiral spring of a watch is provided according to the present invention, which comprises: a shaft element in which at least one axial end of the same is rotatably supported by a bearing unit of the watch and which is together with rotates a balance wheel, and a connecting portion, which is provided on the balance wheel, with which a mechanical component is connected, which is provided for power transmission, a recess being arranged in the at least part of the bearing unit of the watch, on the inside in the radial direction on Connection section is provided, wherein the connection section and the bearing unit are arranged so that they partially overlap as seen in the radial direction of the shaft element, and wherein the distance between the balance wheel and the bearing unit is less than the thickness of the connection section.

According to the present invention, a recess is provided in the connecting section, in which at least a part of the bearing unit of the watch is arranged, so that by arranging a part of the bearing unit on the inside of the recess it is possible to arrange the connecting section and the bearing unit in such a way that 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 connecting portion, so that a reduction in the thickness of the clockwork and the clock compared to the prior art can be achieved when the spiral spring balance of the present invention is incorporated into the clockwork of the clock is.

[0008] Furthermore, the recess is provided such that it extends in the circumferential direction of the shaft element.

According to the present invention, it is possible to reliably arrange a part of the bearing unit in the recess. Therefore, the thickness of the clockwork and the watch can be reduced.

Further, a coil spring, which is provided on one side in the axial direction of the balance wheel and is designed to rotate the balance wheel, and a double roller is provided, which is provided on the other side in the axial direction of the balance wheel; the coil spring and the double roller are intended for power transmission; and the recess is provided at least either on the first connecting section to which the spiral spring is connected and / or on the second connecting section to which the double roller is connected.

According to the present invention, the recess is provided at least either on the first connecting section to which the coil spring is connected and / or on the second connecting section to which the double roller is connected, so that it is arranged on the inside by arranging a section of the bearing unit of the space area is possible to arrange at least either the first connecting section and / or the second connecting section in such a way

CH 709 641 B1 that, seen from the radial direction of the shaft element, it overlaps a section of the bearing unit. As a result, a reduction in the thickness of the clockwork and the clock compared to the prior art can be achieved when the balance spring of the present invention is incorporated in a clockwork of a clock.

Furthermore, a coil spring which is provided on one side in the axial direction of the balance wheel and configured to rotate the balance wheel, a spiral roller to which one end of the coil spring is attached, and a double roller provided on the other side is provided in the axial direction of the balance wheel, wherein the coil spring and the double roller are provided for power transmission; and the recess is provided at least either on the first connecting section to which the spiral spring is connected by the spiral roller and / or on the second connecting section to which the double roller is connected.

According to the present invention, the space is provided at least either at the first connecting section to which the spiral roller is connected and / or at the second connecting section to which the double roller is connected, so that it is arranged by arranging a section of the bearing unit on the inside of the cutout is possible to arrange at least one of the first connecting section and / or the second connecting section in such a way that, viewed from the radial direction of the shaft element, it overlaps a section of the bearing unit. As a result, the distance between the balance wheel and the bearing unit is less than the thickness of either the spiral roller and / or 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 spring Invention is built into a clockwork of a clock.

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

[0015] According to the present invention, a reduction in the thickness of a regulator can be achieved.

[0016] Furthermore, at least one of the pair of bearing units is a shock protection bearing unit which is designed to dampen an impact acting on a bearing section.

According to the present invention, even if, for example, an external impact is applied, the impact can be damped and damage to the shaft element and the bearing section can be prevented. As a result, a regulator can be provided which can have a reduced thickness and is better in terms of durability.

Furthermore, the pair of bearing units and the balance wheel face each other without any other components as intermediate members.

According to the present invention, no component is provided between the bearing units and the balance wheel so that a further reduction in the thickness of the regulator can be achieved by arranging the bearing units and the balance wheel as close as possible to one another.

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

According to the present invention can be achieved by providing the controller described above, a reduction in the thickness of a clockwork compared to the prior art.

Furthermore, a carrier unit is provided which is designed 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 controller about a predetermined axis by means of the carrier unit. The clockwork according to the present invention is thus equipped with a so-called tourbillon mechanism which can prevent a change in the oscillation cycle of the balance wheel with spiral spring depending on the direction of gravity, so that it is possible to provide a clockwork that is thinner and better May have timing accuracy.

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

[0025] According to the present invention, since a watch with reduced thickness is provided, a watch with better design properties can be provided.

According to the present invention, a recess is provided on the connecting portion, in which at least a portion of the bearing unit is provided, so that by arranging a portion of the bearing unit on the inside of the recess, it is possible to arrange the connecting portion and the bearing unit such that they are located , partially seen from the radial direction of the shaft element. 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 clockwork and the clock compared to the prior art can be achieved when installing the balance spring of the present invention in a clockwork of a watch is.

Brief Description of the Drawings [0027]

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

CH 709 641 B1

Fig. 2 is a plan view of a clockwork seen from the front.

FIG. 3 is a sectional view taken along line A-A of FIG. 2.

FIG. 4 is an enlarged view illustrating the shock protection storage unit of FIG. 3 and its surroundings.

5 is a sectional side view of a clockwork according to a modification of the first embodiment.

6 is a side sectional view of a clockwork according to a second embodiment.

7 is a side sectional view of a clockwork according to a third embodiment.

8 is a sectional side view of a clockwork according to a fourth embodiment.

Detailed Description of the Preferred Embodiments (First Embodiment) Hereinafter, the first embodiment of the present invention will be described with reference to the drawings.

In the following, a mechanical wristwatch (which corresponds to the "clock" mentioned in the patent claims; in the following it is simply referred to as "clock") and a clockwork incorporated in the clock, and then a balance spring with a spiral spring and a regulator which form the clockwork, described in detail.

(Clock) In general, the mechanical body comprising the drive part of the clock is referred to as the "clockwork". The complete product obtained by mounting a dial and hands on this movement and putting the whole in a watch case is called the "whole" of the watch. Of the two sides of a main plate that forms the carrier of the watch, the side on which the glass of the watch is located, that is, the side on which the dial is located, is referred to as the “back” of the movement. Furthermore, of the two sides of the main plate, the side on which the watch bottom of the watch case is located, that is to say the side opposite the dial, is referred to as the “front” of the movement.

Fig. 1 is an external view of a watch 1 according to a first embodiment.

As shown in Fig. 1, the whole of a watch 1 according to the present embodiment contains within a watch case 3 consisting of a watch bottom (not shown) and a glass 2, a movement 100, a dial 11 with divisions, etc., which relate to the time Display information and hands that include an hour hand 12 indicating the hour and a minute hand 13 indicating the minute. A day window 11 a, which shows numbers indicating the date, is open in the dial 11. As a result, watch 1 enables the date to be checked in addition to the time.

Fig. 2 is a plan view of the clockwork 100 of the watch 1 seen from the front. In Fig. 2, in order to facilitate understanding of the drawing, part of the components making up the clockwork 100 have been omitted, and each clock component is shown in a simplified form.

As shown in Fig. 2, the movement 100 of the mechanical watch has 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 which comprises an angle lever 103, a rocker 105, a rocker spring 107, an angle lever catch 109, etc.

[0035] When the elevator shaft 110 is rotated, an elevator drive 112 rotates through the rotation of a clutch wheel (not shown). The rotation of the elevator drive 112 rotates a crown wheel 114 and a ratchet wheel 116 one after the other, and a tension spring (not shown) accommodated in a clockwork spring housing 120 is wound up.

The clockwork barrel 120 has a barrel core, which serves as a shaft section, at both ends of which 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 barrel 120 is rotatably supported between the main plate 144 and the barrel bridge 134. A large bottom gear with pinion 124, a small bottom gear with pinion 126, a second wheel with pinion 128, and an escapement wheel with pinion 130 have journals (not shown) protruding from both ends of their respective shaft portions 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 train bridge 136.

When the clockwork barrel 120 is rotated by the restoring force of the tension spring, the large-bottomed wheel with drive 124, the small-sized wheel with drive 126, the second wheel with drive 128 and the escapement wheel with drive 130 are rotated in succession by the rotation of the clockwork spring 120. The clockwork spring barrel 120, the large bottom wheel with drive 124, the small bottom wheel with drive 126 and the second wheel with drive 128 form a front gear train.

CH 709 641 B1 When the large ground wheel with drive 124 rotates, a quarter tube (not shown) rotates at the same time due to the rotation, and the minute hand 13 attached to the quarter tube (see FIG. 1) 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 hand 12 attached to the hour wheel (see FIG. 1) indicates the “hour”.

A gear regulator 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?, Which comprises the balance with coil spring 10.

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

The regulator? consists of a balance with coil spring 10 and a shock protection bearing unit 5, which rotates the balance with coil spring 10. According to the present embodiment, the balance with spiral spring 10 is rotatably mounted between a balance bridge 104 and the main plate 144 by means of the shock protection bearing unit 5. The spiral spring balance 10 rotates back and forth at a fixed rate, causing one pallet 142a and the other pallet 142b of the armature fork 142 to alternately engage and disengage the teeth 132 of the escapement wheel 130 and them causes the escapement wheel with drive 130 to be released at a predetermined cycle. As far as the balance with coil spring 10 and the shock protection bearing unit 5 are concerned, these are described in detail below.

In this design, a tension spring (not shown) housed in the clockwork barrel 120 is wound using an elevator shaft 110; and then the clockwork barrel 120 is rotated by the torque when this tension spring is rewound. Rotation of the clockwork barrel 120 rotates the large bottom wheel with gear 124 which is in engagement with it. When the large bottom wheel with gear 124 rotates, the small bottom wheel with gear 126 which is in engagement with it rotates. When the small bottom wheel with gear 126 rotates, it rotates the engaging second gear 128. When the second gear 128 rotates, the speed controller 140 is driven. By driving the speed controller 140, the large floor wheel with the drive 124 is controlled in such a way that it executes one revolution per hour.

(Balance with spiral spring) Fig. 3 is a schematic sectional view along the line A-A of Fig. 2. For simplicity of the drawing, the components of the balance with spiral spring 10 in Fig. 3 are simplified.

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

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

As shown in Fig. 2, on the inside of the balance wheel main body portion 21, four arm portions 23 (23a to 23d) are provided along the radial direction toward the central axis O. The four arm portions 23a to 23d are formed at substantially equal intervals with a pitch of 90 degrees in the circumferential direction of the balance wheel main body portion 21. Time setting weights 22 are provided at the connection portions between the balance wheel 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; for example, they can be rotated about guide shafts parallel to the central axis O.

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

At the portion of the coupling portion 24 on the front of the movement 100 (the upper side in Fig. 3) and around the fitting engagement hole 24a, a first connecting portion 31 (which corresponds to the "first connecting portion" in the claims) is formed, which is coaxial with the Central axis is O. The first connecting portion 31 is formed as an annular projection that protrudes from the coupling portion 24 toward the front of the clockwork 100. A spiral roller 18 described below is attached to the first connecting section 31.

CH 709 641 B1 On the inside in the radial direction of the first connecting section 31, a first recess 41 (which corresponds to the “recess” in the claims) is provided. The first recess 41 is formed over the entire circumference of the balance shaft 28 on the front of the clockwork 100 with respect to the coupling section 24.

At the portion of the coupling portion 24 on the back of the movement 100 (the lower side in Fig. 3) and around the fitting engagement hole 24a, a second connecting portion 32 (which corresponds to the "second connecting portion" in the claims) is formed, which is coaxial with the Central axis is O. The second connecting section 32 is designed as an annular projection which protrudes from the coupling section 24 towards the rear of the clockwork 100. On the outside in the radial direction of the second connecting portion 32, a double roller 35 is arranged, which will be described later.

On the inside in the radial direction of the second connecting portion 32, a second recess 42 (which corresponds to the "recess" in the claims) is provided. The second recess 42 is formed over the entire circumference in the circumferential direction of the balance shaft 28 on the back of the clockwork 100 with respect to the coupling section 24.

The balance wheel 20 is equipped with the balance shaft 28 coaxial to the central axis O (which corresponds to the “shaft element” in the claims). The balance shaft 28 is a rod-like member made of a metal material such as iron.

The balance shaft 28 is provided at its two axial ends with conical pins 29 (29a and 29b). The pins 29a and 29b on both ends of the balance shaft 28 are carried by the shock protection bearing unit 5 described below in such a way that they can be rotated about the central axis O.

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

The spiral spring 16 is a spiral leaf spring made of thin sheet metal, which is formed from a metal material such as iron, nickel or niobium and is arranged on the front of the clockwork 100 with respect to the balance wheel 20. Viewed from the axial direction, the spiral spring 16 is designed in such a way that it extends 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 16b of the coil spring 16 is fastened to a shoulder 106 which projects from the balance bridge 104 towards the rear of the clockwork 100. The coil spring 16 expands and contracts while the outer end portion 16b is fixed to the boss 106, thereby rotating the balance wheel 20.

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

The double roller 35, like the balance wheel 20, is a ring-like member made of a metal material such as stainless steel or brass and is arranged on the outside in the radial direction of the second connecting portion 32. The double roller 35 according to the present embodiment is formed in one piece with the balance wheel 20 at the corner section between the coupling section 24 of the balance wheel 20 and the second connecting section 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 from ruby. The lever block 26 projects from the coupling section 24 of the balance wheel 20 to the rear of the clockwork 100. The lever block 26 can be attached to and detached from a pallet box 143a, which is formed on the inside of an input 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 can also be provided on the double roller 35.

On the double roller 35, a shoulder 35a is formed, which is set back in the radial direction from the outside to the inside in a position corresponding to the lever block 26 and one step lower than the second connecting portion 32. When the armature 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 armature fork 142 from coming into contact with the double roller 35.

(Regulator) Fig. 4 is an enlarged view of the shock protection bearing units 5 in Fig. 3 and its periphery.

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

As shown in FIG. 4, the shock protection bearing units 5A and 5B carry the pins 29a and 29b provided on both axial ends of the balance shaft 28 such that they can rotate about the central axis O. The two shock protection bearing units 5A and 5B are attached to the balance bridge 104 and the main plate 144, respectively.

CH 709 641 B1 The shock protection bearing units 5A and 5B primarily have a bearing section 50, a shock protection bushing 56 and a shock protection spring 59. The components of the shock protection bearing units 5 are described below. The one anti-lock bearing unit 5A on the balance bridge 104 side and the other anti-lock bearing unit 5B on the main plate 144 side have the same structure. Therefore, the one anti-lock bearing unit 5A on the balance bridge 104 side will be described in detail below, and a detailed description of the other anti-lock bearing unit 5B on the main plate 144 side will be omitted.

The bearing section 50 is equipped with a guide bush 53, a perforated brick 51 and a cover brick 52.

The guide bush 53 is a tubular member made of a metal material such as iron or brass and has a first pipe section 53a and a second pipe section 53b.

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

The second pipe section 53b is arranged on the front of the clockwork 100 with respect to the first pipe section 53a and has a larger diameter than the first pipe section 53a. The cover stone 52 is arranged on the inside of the second pipe section 53b. The second pipe section 53b has a second beveled surface 54b at the outer corner section of the connecting section between it and the first pipe section 53a. The second tapered surface 54b is formed, for example, over the entire circumference of the second pipe section 53b and gradually inclined from the inside to the outside in the radial direction.

The perforated brick 51 is a substantially circular element in plan view, which is made of ruby, for example, and has a through hole 51a in the middle. The inside diameter of the through hole 51a of the perforated brick 51 is sufficiently large to enable the pin 29a to be inserted. Furthermore, the perforated brick 51 is designed in a size that enables it to be fastened by pressing into the first tube section 53 a of the guide bush 53.

The cap stone 52 is an element with a substantially circular shape in plan view, which is made of ruby or the like. The cover stone 52 is arranged on the front of the clockwork 100 with respect to the perforated stone 51 and lies opposite the axial end face of the pin 29a. Furthermore, the cover stone 52 is arranged at the end section of the first pipe section 53a on the inside of the second pipe section 53b and closes the opening of the first pipe section 53a. The main surface of the cover stone facing the front of the clockwork 100 is designed with a convexly curved surface design.

The guide bushing 53 is accommodated in a shock protection bushing 56. The shock-proofing bushing 56 is an element such as a tube closed at the bottom with an opening 58 on the outside in the axial direction and made of a metal material such as iron or brass. The shock protection bushing 56 is installed, for example, in a mounting hole in the balance bridge 104. The shock protection bushing 56 has a first pipe section 56a and a second pipe section 56b.

The first tube section 56a largely encloses the guide bush 53. A first tapered surface 57a and a second tapered surface 57b are respectively formed on the inner surface of the first tube portion 56a and in positions corresponding to the first tapered surface 54a and the second tapered surface 54b of the guide bush 53. The first beveled surface 57a and the second beveled surface 57b of the shock-proofing bushing 56 are in flat contact with the first beveled surface 54a and the second beveled surface 54b of the guide bushing 53.

The second pipe section 56b is arranged on the front of the clockwork 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 tube portion 56b. At the opening 58 of the second pipe section 56b, the flange section 58a protrudes on the inside in the radial direction.

A step surface 56c is formed on the outer circumferential surface of the shock protection bush 56 and on the connection portion between the second pipe section 56b and the first pipe section 56a. The step surface 56c is provided in such a way that it faces the forward end surface 31a of the first connecting section 31. A shock protection spring 59 is provided at the opening 58 of the shock protection bushing 56. The shock protection spring 59 is a flexible ring-like elastic member made of a metal material such as iron or nickel. The outer edge portion of the shock securing spring 59 is arranged on the inside in the axial direction with respect to the flange portion 58a. The shock protection spring 59 drives the cover block 52 and the guide bush toward the inside in the axial direction.

In the one shock lock bearing unit 5A on the balance bridge 104 side of the pair of the shock lock bearing units 5A and 5B constructed as described above, the first pipe portion 56a of the shock lock bushing 56 is disposed on the inside of the first recess 41.

CH 709 641 B1 In addition, the one shock protection bearing unit 5A and the balance wheel 20 face each other without any other components as intermediate members. The first tube section 56a of the shock protection bushing 56 of the one shock protection bearing unit 5A is therefore arranged on the inside of the first recess 41, as a result of which the shock protection bearing unit 5A, viewed from the radial direction of the balance wheel 20, is arranged such that the first connecting section 31 and a section of the one Shock protection bearing unit 5A overlap. As a result, the distance between the balance wheel 20 and the one anti-shock bearing unit 5A is less than the thickness of the first connecting portion 31 and the spiral roller 18.

In the other shock protection bearing unit 5B on the main plate 144 side, the first pipe portion 56a of the shock protection bushing 56 is arranged on the inside of the second recess 42. In addition, the other shock protection bearing unit 5B and the balance wheel 20 face each other without other components as intermediate members. The first tube section 56a of the shock protection bushing 56 of the other shock protection bearing unit 5B is thus arranged on the inside of the second recess 42, as a result of which the second connecting section 32 and a section of the other shock protection bearing unit 5B, as seen from the radial direction of the balance shaft 28, are arranged such that they overlay each other. As a result, the distance between the balance wheel 20 and the other shock protection 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 an impact 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 which supports the balance shaft 28 is also displaced along the axial direction. On the other hand, the shock protection spring 59 is provided on the outside in the axial direction of the bearing section 50, which drives the bearing section 50 in the direction of the inside in the axial direction, so that the bearing section 50 is elastically supported even in the event of displacement of the bearing section 50 along the axial direction and the shock load is dampened. Furthermore, for example, even when a large shock load is applied against the compressive force of the shock protection spring 59, striking occurs either between the step surface 56c of the shock protection bushing 56 and the forward end face 31a of the first connecting section 31 or between the step surface 56c of the shock protection bushing 56 and the forward end surface 32a of the second connecting portion 32, thereby regulating the movement of the balance wheel 20 and the balance shaft 28 along the axial direction and damping the shock load.

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 that supports 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 bushing 53 are respectively in flat contact with the first tapered surface 57a and the second tapered surface 57b of the shock-proofing bushing 56. Accordingly, the guide bushing 53 becomes oblique toward the outside in the axial direction and the radial direction that it moves along the first tapered surface 57a and the second tapered surface 57b of the shock lock bushing 56. On the other hand, the shock-absorbing spring 59 is provided on the outside in the axial direction of the guide bush 53 and drives the guide bush 53 in the direction of the inside in the axial direction, so that even in the event of the guide bush 53 being displaced in the axial direction and in the direction of the outside in FIG the radial direction, the guide bush 53 is elastically supported and the shock load is damped. Furthermore, for example, even if a large shock load is applied against the compressive force of the shock protection spring 59, striking occurs at least either between the first pipe section 56a of the shock protection bush 56 and the inner circumferential surface 31b of the first connecting section 31 or between the first pipe section 56a of the shock protection bush 56 and the inner peripheral surface 32b of the second connecting portion 32, thereby regulating the movement of the balance ring 20 and the balance shaft 28 in the radial direction and damping the shock load.

(Effects of the First Embodiment) According to the present embodiment, the first connection portion 31 and the second connection portion 32 are provided with the first recess 41 and the second recess 42, respectively, in which a part of the shock protection bearing unit 5 is arranged, so that by arranging a part of the anti-lock bearing units 5A and 5B on the inside of the first recess 41 and the second recess 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, are a part of the anti-lock bearing units 5A and 5B overlay. As a result, the distance between the balance wheel 20 and the one anti-lock bearing unit 5A is less than the thickness of the first connecting portion 31 and the spiral roller 18. Furthermore, the distance between the balance wheel 20 and the other anti-lock bearing unit 5B is less than the thickness of the second connecting portion 32 and the double roller 35. Therefore, compared to the prior art, it is possible to achieve a reduction in the thickness of the balance with coil spring 10, the regulator 7, the clockwork 100 and the clock 1.

Furthermore, the first recess 41 and the second recess 42 are provided in the circumferential direction of the balance shaft 28, so that even when the balance wheel 20 rotates, there is a disturbance between the revolutions

CH 709 641 B1 side walls of the first recess 41 and the second recess 42 and the shock protection bearing units 5A and 5B to prevent. Therefore, it is possible to achieve a reduction in the thickness of the clockwork 100 and the clock 1 while ensuring their timekeeping accuracy.

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

In addition, the pair of shock protection bearing units 5A and 5B and the balance wheel 20 face each other without any other components as intermediate members. No component is therefore provided between the shock protection bearing units 5A and 5B and the balance wheel 20, so that the fact that the shock protection bearing units 5A and 5B and the balance wheel 20 are arranged as close as possible to one another further reduces the thickness of the regulator 7 to achieve.

[0086] Furthermore, according to the present embodiment, it is possible to provide a watch 1 with better design properties by producing the watch mechanism 100 with reduced thickness.

(Modification of the First Embodiment) A modification of the first embodiment will be described below.

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

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

In contrast, as shown in Fig. 5, the modification of the first embodiment differs from the first embodiment in that the scroll roller 18 is fixed to the balance bridge 104 and in that the scroll roller 106 is fixed to the balance wheel 20. In the following, description of the same structure as in the first embodiment is omitted.

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

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

In addition, the inner portion of the spiral roller 18 formed with a ring-like shape forms the first recess 41. In the first recess 41, the first tube section 56a of the shock protection bushing 56 of the one shock protection bearing unit 5A is arranged. As a result, the scroll roller 18 and a portion of the one anti-lock bearing unit 5A, as seen from the radial direction of the balance shaft 28, are arranged to overlap each other. Furthermore, the distance between the balance wheel 20 and the one shock protection bearing unit 5A is less than the thickness of the spiral roller 18.

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

(Effect of Modification of First Embodiment) Even in the modification of the first embodiment, the same effect as that of the first embodiment can be obtained. That is, according to the present modification, the spiral roller 18 itself forms the first connecting section 31 and has a first recess 41, in which the first tube section 56a of the shock protection bushing 56 of the shock protection bearing unit 5A is arranged, so that the spiral roller 18 and a section of the one shock protection bearing unit 5A , viewed from the radial direction of the balance shaft 28, are arranged such that they overlap one another. Therefore, the distance between the balance wheel 20 and the one anti-lock bearing unit 5A is less than the thickness of the spiral roller 18 with the first connecting portion 31. Furthermore, the distance between the balance wheel 20 and the other anti-lock bearing unit 5B is less than the thickness of the second connecting portion 32 and the double roller 35. Therefore, compared to the prior art, it is possible to achieve a reduction in the thickness of the balance with coil spring 10, the regulator 7, the clockwork 100 and the clock 1.

(Second Embodiment) The second embodiment will be described below.

CH 709 641 B1 Fig. 6 is a side cross sectional view of the clockwork of a watch 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 attached to it.

In contrast, the second embodiment, as shown in FIG. 6, differs from the first embodiment in that the spiral roller 18 is fastened to the coupling section 24 of the balance wheel 20.

In the following, a description of the same structure as in the first embodiment is omitted.

[0101] A fitting engagement cutout 25 is formed on the coupling section 24 of the balance wheel 20. The fitting engagement recess 25 is formed by recessing in the axial direction. The fit engagement recess 25 can extend through the balance wheel 20.

The spiral roller 18 has a fitting engagement projection 18a. If the spiral roller 18 is arranged coaxially to the central axis O, the mating engagement projection 18a is pressed into a mating engagement recess 25 of the balance wheel 20. As a result, the scroll roller 18 is fixed to the portion of the coupling portion 24 of the balance wheel 20 which is located on the front of the movement 100.

The inner end portion 16a of the coil spring 16 is connected to the coil roller 18. As in the modification of the first embodiment, the spiral roller 18 itself, to which the inner end portion 16a of the spiral spring is fastened, also forms the first connecting portion 31 in the second embodiment. Furthermore, the inner portion of the spiral roller 18 forms the first recess 41 The scroll roller 18 and a portion of the one anti-shock bearing unit 5A are arranged so as to overlap each other when viewed from the radial direction of the balance shaft 28. The distance between the balance wheel 20 and the one shock protection bearing unit 5A is less than the thickness of the spiral roller 18.

According to the second embodiment, it is possible to achieve the same effect as that of the first embodiment. Compared to the previously known technology, it is therefore possible to achieve a reduction in the thickness of the balance with coil spring 10, the regulator 7, the clockwork 100 and the clock 1.

(Third Embodiment) The third embodiment will be described below.

Fig. 7 is a sectional side view of a clockwork 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 attached to it.

In contrast, the third embodiment, as shown in FIG. 7, differs from the first embodiment in that the spiral roller 18 is formed in one piece with the balance wheel 20.

In the following, a description of the same structure as in the first embodiment is omitted.

The scroll roller 18 is integrally formed with the balance wheel 20 at the portion of the connecting portion 24 of the balance wheel 20, which is located on the front of the clockwork 100. The inner end portion 16a of the coil spring 16 is connected to the coil roller 18. As in the modification of the first embodiment and in the second embodiment, the spiral roller 18 itself, to which the inner end section 16a of the coil spring 16 is fastened, forms the first connecting section 31 in the third embodiment as well. According to the third embodiment, it is possible to to achieve the same effect as in the first embodiment. Compared to the previously known technology, it is therefore possible to achieve a reduction in the thickness of the balance with coil spring 10, the regulator 7, the clockwork 100 and the clock 1. In addition, the number of components can be reduced by integrally forming the spiral roller 18 with the balance wheel 20.

(Fourth Embodiment) The fourth embodiment will be described below.

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

In the first embodiment described above, the regulator 7, which includes the balance spring 10 and the anti-lock bearing units 5A and 5B, is fixed to the main plate 144 and the balance bridge 104.

In contrast, the fourth embodiment, as shown in Fig. 8, differs from the first embodiment and the modification of the first embodiment in that the regulator?, Which includes the balance spring 10 and the shock protection bearing units 5A and 5B, to one Carrier unit 70 rotatable about the central axis O is mounted.

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

The carrier unit 70 is provided with an upper carrier 71, which is arranged with respect to the main plate 144 on the front of the movement 100 (the upper side in FIG. 8), with a lower carrier 72, which is related to the upper carrier

CH 709 641 B1 is arranged on the back of the clockwork 100, a connecting bolt 73, which connects the upper bracket 71 and the lower bracket 72 to each other, and a ring-like stationary gear 76.

[0117] The upper bracket 71 and the lower bracket 72 are frame-like members made of a metal material such as stainless steel, iron, aluminum, titanium or brass. The upper bracket 71 and the lower bracket 72 are fixed by a connecting bolt 73 and a screw 73a with a predetermined distance between them. The regulator 7, which includes the balance spring 10 and the shock protection bearing units 5A and 5B, is mounted between the upper bracket 71 and the lower bracket 72.

The upper support 71 and the lower support 72 each have mounting holes 71a and 72a which are coaxial with the central axis O. The shock protection bearing units 5A and 5B are respectively fitted by fitting engagement in the mounting holes 71a and 72a.

A serrated portion 72b of the lower bracket 72 is formed on the outer peripheral edge portion of the lower bracket 72. The toothed section 72b of the lower carrier is in engagement with a second idler gear 129. The second idler gear 129 forms a front gear train together with the clockwork barrel 120, the large bottom gear with drive 124, the small bottom gear with drive 126 and the second gear with drive 128 (see Fig . 2). The second idler gear 129 transfers the energy from the clockwork barrel 120 to the lower bracket 72.

Here, the spiral roller 18 of the balance with the spiral spring 10 is fastened to the upper support 71 via the shock protection bearing unit 5A. The inner end portion 16a of the coil spring 16 is connected to the coil roller 18. As in the modification of the first embodiment, the spiral roller 18 itself, to which the inner end portion 16a of the spiral spring 16 is fastened, also forms the first connecting portion 31 in the fourth embodiment. Furthermore, the inner portion of the spiral roller 18 forms the first recess 41. The spiral roller 18 and a portion of the one anti-shock bearing unit 5A are arranged so as to overlap each other when viewed from the radial direction of the balance shaft 28. The distance between the balance wheel 20 and the one shock protection bearing unit 5A is less than the thickness of the spiral roller 18.

Between the upper support 71 and the lower support 72, an escapement 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 arranged between the upper bracket 71 and the lower bracket 72. The fixed gear 76 is designed as a ring, the outer diameter of which 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 gear 131 of the escapement gear with gear 130.

A ring-like bearing 80 is arranged on the main plate 144 so that it is coaxial with the central axis O.

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

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

[0126] The lower bracket 72 of the bracket unit 70 is fixed to the inner ring 82 by a screw or the like.

The roller body 83 is a spherical body; and a plurality of rolling elements are arranged between the outer ring 81 and the inner ring 82. The inner ring 82 is rotatable about the central 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 (which corresponds to the “predetermined axis” mentioned in the claims).

The movement 100 constructed as described above operates as follows.

When the clockwork barrel 120 (see Fig. 2) is rotated by the restoring force of the tension spring, the energy is transmitted by the rotation of the clockwork barrel 120 and the second idler gear 129 rotates. Furthermore, it engages with the second idler gear 129 located lower bracket 72 together with the upper bracket 71 about the central axis O. With the rotation of the upper bracket 71 and the lower bracket 72, the escapement wheel with drive 130 also rotates about the center axis O. The escapement drive 131 is the The escapement wheel with drive 130 engages with the toothed section 77 of the fixed gear 76. The escapement wheel with drive 130 consequently rotates (circles) about the central axis O and it rotates about the axis P. As a result, the speed controller 140 (see FIG. 2 ) driven. The speed controller 140 rotates with the rotation of the upper bracket 71 and the lower bracket 72 about the central axis O. This means that the movement 100 of the fourth embodiment is equipped with the so-called carousel tourbillon mechanism 85, which causes the Speed controller 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, which makes it possible to compensate for the influence which depends on the direction of gravity. The clockwork 100 according to the fourth embodiment is therefore equipped with the so-called carousel tourbillon mechanism 85,

CH 709 641 B1, which can prevent a change in the oscillation cycle of the balance wheel with spiral spring 10 which is dependent on the direction of gravity, so that it is possible to provide a clockwork 100 which enables a reduction in thickness and has better timing accuracy.

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

The clockwork 100 according to the first embodiment and the modification of the first embodiment is provided with the first recess 41, which is formed on the first connecting portion 31, and the second recess 42, which is formed on the second connecting portion 32. In contrast, as in the fourth embodiment, it is also possible for the clockwork 100 to be provided only with the first recess 41 which is formed on the first connecting section 31.

Furthermore, there is also the possibility that the clockwork is only provided with the second recess, which is formed on the second connection section. This means that the clockwork according to the present invention only has to be provided with at least one connecting section and one recess.

[0135] Furthermore, it is also possible to combine the above embodiments with one another. For example, by combining the first embodiment with the fourth embodiment, a clockwork 100 can be provided, which is provided with the first recess 41 and the second recess 42 and is equipped with the carousel tourbillon mechanism 85.

[0136] Although a so-called Swiss anchor escapement is used in the embodiments described above, this should not be interpreted restrictively. For example, it is also possible to use an anchor escapement other than Swiss, 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 spiral spring 16 and the balance wheel 20 with the aid of MEMS (microelectromechanical systems), such as dry etching or galvanoforming, using a material which primarily contains silicon and silicon nitride.

[0138] Furthermore, in the above embodiments, the spiral roller 18 and the spiral spring 16 are formed separately. In contrast, the spiral roller 18 and the spiral spring 16 can be formed in one piece.

[0139] In the above embodiments, the double roller 35 and the balance wheel 20 are integrally formed. In contrast, the balance wheel 20 and the double roller 35 can be formed as separate components. Further, while the lever block 26 is fixed to the balance wheel 20 in the above embodiments, the lever block 26 may be fixed to the double roller 35.

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

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

Claims (10)

Claims 1. balance with coil spring (16) of a watch (1), comprising: a shaft element (28), in which at least one axial end thereof is rotatably mounted in a bearing unit (5) of the watch (1), the shaft element (28) rotating together with a balance wheel (20), and a connecting section (31, 32), which is provided on the balance wheel (20), to which a mechanical component is connected, which is provided for power transmission, a recess (41, 42) in which at least part of the bearing unit (5) is arranged, on which Is provided on the inside in the radial direction of the connecting section (31, 32), and wherein the connecting section (31, 32) and the bearing unit (5) are arranged such that they partially overlap when viewed in the radial direction of the shaft element (28), and wherein the distance between the balance wheel (20) and the bearing unit (5) is less than the thickness of the connecting section (31, 32). 2. balance spring with coil spring according to claim 1, wherein the recess (41,42) is provided such that it extends in the circumferential direction of the shaft element (28). 3. A balance spring with a coil spring according to claim 1 or 2, further comprising: the coil spring (16) which is provided in the axial direction of the balance wheel (20) on one side of the balance wheel (20) and is provided for rotating the balance wheel, and CH 709 641 B1 a double roller (35), which is provided in the axial direction of the balance wheel (20) on the other side of the balance wheel (20), the coil spring (16) and the double roller (35), as mechanical components, for power transmission are provided; and the recess is provided at least either on the first connecting section (31) to which the spiral spring (16) is connected and / or on the second connecting section (32) to which the double roller (35) is connected. 4. A balance spring balance spring according to claim 1 or 2, further comprising: the spiral spring (16) which is provided in the axial direction of the balance wheel (20) on one side of the balance wheel (20) and is provided for rotating the balance wheel, a spiral roller (18) to which one end of the spiral spring (16) is fastened, and a double roller (35) which is provided in the axial direction of the balance wheel (20) on the other side of the balance wheel (20), the coil spring (16) and the double roller (35) being provided as mechanical components for power transmission; and the recess is provided at least on the first connecting section (31) to which the spiral spring (16) is connected by the spiral roller (18) and / or on the second connecting section (32) to which the double roller (35) is connected. 5. Regulator comprising a balance with a spiral spring (10) according to claim 3 or 4, and a pair of bearing units (5a, 5b) by means of which the balance with a spiral spring (10) is rotatably mounted. 6. Controller according to claim 5, wherein at least one bearing unit of the pair of bearing units is a shock protection bearing unit (5a, 5b), which dampens an impact acting on a bearing section for supporting the shaft element (28). 7. Regulator according to claim 5 or 6, wherein the pair of bearing units and the balance wheel (20) face each other without other components as intermediate members. 8. Clockwork for a clock (1), which is equipped with a controller according to one of claims 5 to 7. 9. Clockwork according to claim 8, wherein a carrier unit (70) is provided, which is designed to rotate the controller (7) about a predetermined axis. 10. Clock (1), which is equipped with a clockwork according to claim 8 or 9.