CH709328A2 - Exhaust, timepiece movement and timepiece. - Google Patents

Abstract

The invention relates to an escapement, a timepiece movement, and a timepiece that aims to improve the efficiency of energy transfer, while ensuring stable operation. An escapement (1) includes a first impulse pallet (46 and a second impulse pallet (47) for inducing spiral balance energy, an anchor (40) which has an inlet pallet (48) and an output pallet (49), which is pivotally movable about an anchor rod (43), a first exhaust movable (10) which has a first escape wheel for the impulse (15), ) which comes into contact with the first pulse pallet (46), the energy being transmitted at this moment, and a second escape wheel (20) which has a second escape wheel for the pulse (25) which can come into contact with the second pulse pallet (47) and a stop exhaust wheel (26) which can engage with or separate from the entry pallet (48) and the pallet output (49), and which meshes with the first mobile escapement (10).

Description

BACKGROUND OF THE INVENTION

1. Field of the invention

[0001] The present invention relates to an escapement, a timepiece movement, and a timepiece.

2. Description of the prior art

[0002] A mechanical timepiece includes an escapement for controlling the rotation of a movement barrel, and a center mobile, a third mobile, and a second mobile which constitute a cog train. Generally speaking, an escapement mainly includes an escapement mobile, a double roller disposed in a sprung balance moving pivotably about a balance shaft, and an anchor pivotably movable around a rod. anchor.

[0003] The double roller includes a drive pin which contacts the anchor, and which pivotally moves with the sprung balance using the energy stored in the balance spring. The anchor includes an inlet vane and an outlet vane that can engage with or separate from the exhaust spindle teeth. The energy of the spiral spring is transferred by the impulse pin so that the anchor moves pivotally around the anchor rod.

[0004] In the prior art, different types of exhaust have been proposed in order to improve the efficiency and durability of the exhaust.

[0005] For example, the patent application JP-A-2012-168 172 (first patent document) discloses a timepiece escapement which comprises a first exhaust mobile and a second mobile which mesh with one another. with the other, and a first impulse vane and a second impulse vane to which pulses are alternately induced from the first exhaust mobile and the second mobile, and in which the first impulse vane and the second impulse vane are arranged in the impulse peg of the sprung balance. In the escapement disclosed in the first patent document, the energy induced from the balance spring of the movement barrel is transmitted directly from the first escape wheel set and the second escape wheel set to the first impulse vane and the second vane of the sprung balance (called the direct-impulse type escapement).

[0006] In addition, patent application JP-A-2004-53 592 (second patent document) discloses a timepiece escapement which comprises the first exhaust mobile and the second exhaust mobile which mesh together one with the other, and the anchor which can engage with or separate from the first exhaust mobile, the second mobile, and the double roller. In the escapement disclosed in the second patent document, the energy induced from the hairspring of the movement barrel is transmitted from the first escapement mobile and the second escape mobile to the double roller of the balance-spring through the anchor (called indirect impulse type escapement).

[0007] Fortuitously, according to the technology disclosed in the first patent document and the second patent document, the energy of the movement barrel is induced at the first mobile exhaust, then is induced at the second mobile exhaust via the first mobile d 'exhaust. A pallet (or a stop lever) of the anchor engages with and separates from the first mobile exhaust and the second mobile exhaust alternately. This causes the first escapement mobile and the second escapement to rotate and stop repeatedly, thereby causing the mechanical timepiece to measure time.

[0008] However, in the escapement disclosed in the prior art, the anchor vane engages with the first escapement mobile which is located on the more upstream side in the direction of energy transfer. When the first mobile exhaust is stopped, the second mobile exhaust is brought into a stopped state due to the meshing with the first mobile exhaust. In this case, and since the second escape mobile is separated from the anchor, a gap is generated in the gear with the first escape mobile, that is to say, a tremor corresponding to what one calls a lost path appears.

[0009] For this reason, if an external disturbance is introduced when the second mobile exhaust engages with or separates from the anchor, the second mobile exhaust vibrates unintentionally, thereby causing the possibility that the mechanical timepiece can be operated unstably. In addition, when a fairly large gear margin is ensured between the first exhaust mobile and the second exhaust mobile, taking into account the tremor corresponding to the lost path of the second escape mobile when the anchor engages with or separates from the second mobile exhaust (hereinafter, it will be referred to simply as the "tremor of the second mobile exhaust"), there is a possibility of significant loss in the transfer of energy and degradation in energy transfer efficiency.

[0010] In particular, in the prior art, the anchor separates from the second mobile escapement for a period of time from a vibration between the two vibrations in a cycle of the sprung balance. In other words, 50% of a period of time of operation of the mechanical timepiece is the period of time which remains in a state where the second mobile escapement separates from the anchor, that is, that is to say, a period of time when the tremor of the second exhaust mobile can occur. Therefore, it is desirable to improve the escapement in terms of shortening the quiver time period of the second escapement mobile.

SUMMARY OF THE INVENTION

[0011] Consequently, the invention is made in view of the circumstances described above, and its object is to provide an escapement, a timepiece movement, and a timepiece which can prevent degradation. efficiency of energy transfer, while ensuring stable operation by shortening the period of time of the quiver of the second mobile exhaust.

In order to achieve the object described above, an escapement according to the invention comprises a first impulse vane and a second impulse vane for the induction of energy to the sprung balance, an anchor which has an entry vane and an exit vane, and which is pivotally movable about an anchor rod, a first escape wheel which has a first escape wheel for the impulse which can contact with the first impulse vane, the energy being transferred at this time, and a second escape wheel which has a second impulse escape wheel which can contact the second impulse vane, and an escape wheel for the stop which can engage with or separate from the input pallet and the output pallet, and which meshes with the first exhaust mobile.

According to the invention, there is provided the second escape mobile which has the escape wheel for the stop which can engage with or separate from the inlet pallet and the pallet of output, and which meshes with the first exhaust mobile. As a result, the second mobile exhaust can control the rotation and stopping of the first mobile exhaust and the second mobile exhaust. Here, in the second mobile escapement, each between the inlet vane and the outlet vane engages with the escapement wheel to stop. As a result, compared with the prior art technology, it is possible to shorten the period of time remaining in the state where the anchor separates from the second escapement runner. According to this constitution, it is possible to considerably shorten the period of time of tremor of the second mobile escapement. Therefore, it is possible to prevent the degradation of energy transfer efficiency, while ensuring stable operation of the exhaust.

[0014] In addition, the second escapement wheel for the impulse and the escapement wheel for the stop are formed in one piece to constitute the second mobile escapement.

[0015] According to the invention, it is possible to reduce the thickness of the second mobile exhaust. Therefore, it is possible to prevent the degradation of the energy transfer efficiency, while ensuring stable operation of the escapement by shortening the period of the shaking time of the second escapement rotor. In addition, it is possible to reduce the thickness of the exhaust.

[0016] In addition, the first impulse vane and the second impulse vane are disposed in the anchor.

According to the invention, the invention can be preferably selected for an escapement called an indirect pulse type escapement which induces the energy to the sprung balance via the first impulse vane and the second impulse vane of the anchor.

[0018] In addition, the first impulse vane and the second impulse vane are arranged in the sprung balance.

According to the invention, the invention can be preferably selected for an escapement called an escapement of the direct impulse type which induces the energy to the sprung balance in such a way that the first escapement mobile and the second mobile escapement collide with the first impulse vane and the second impulse vane of the sprung balance.

[0020] Furthermore, a timepiece movement according to the invention includes the escapement described above.

[0021] Further, a timepiece according to the invention includes the timepiece movement described above.

[0022] According to the invention, there is provided the exhaust which can considerably shorten the period of time of quivering of the second mobile exhaust, and which can prevent the degradation of the energy transfer efficiency, while ensuring stable operation. Therefore, it is possible to make available the timepiece movement and the timepiece which show high performance.

According to the invention, there is provided an exhaust including the second mobile exhaust which has the escape wheel for the stop which can engage with or separate from the inlet pallet and the outlet pallet, and which meshes with the first exhaust mobile. As a result, the second mobile exhaust can control the rotation and stopping of the first mobile exhaust and the second mobile exhaust. Here, in the second mobile escapement, each between the inlet vane and the outlet vane engages with the escapement wheel to stop. As a result, compared with the prior art technology, it is possible to shorten the period of time remaining in the state where the anchor separates from the second escapement runner. According to this constitution, it is possible to considerably shorten the period of time of quivering of the second mobile escapement. Therefore, it is possible to prevent the degradation of energy transfer efficiency, while ensuring stable operation of the exhaust.

BRIEF DESCRIPTION OF THE DRAWINGS

[0024] FIG. 1 is a plan view when a movement of a timepiece according to a first embodiment is viewed from the front side. Fig. 2 is a perspective view of an exhaust according to the first embodiment. Fig. 3 is a plan view of the exhaust according to the first embodiment. Fig. 4 is a view to illustrate the operation of the exhaust. Fig. 5 is a view to illustrate the operation of the exhaust. Fig. 6 is a view to illustrate the operation of the exhaust. Fig. 7 is a view to illustrate the operation of the exhaust. Fig. 8 is a view to illustrate the operation of the exhaust. Fig. 9 is a view to illustrate the operation of the exhaust. Fig. 10 is a view to illustrate the operation of the exhaust. Fig. 11 is a view to illustrate the operation of the exhaust. Fig. 12 is a plan view of an exhaust according to an example of modification of the first embodiment. Fig. 13 is a plan view of an exhaust according to a second embodiment.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0025] Hereinafter, embodiments according to the invention will be described with reference to the drawings.

[0026] In the following description, a mechanical timepiece according to the first embodiment will be described, and then, an escapement according to the first embodiment will be described in detail.

[0027] In general, the machine body comprising a drive unit for a timepiece is called a "movement". The finished product state, by attaching a dial and hands to the movement and placing the movement in a timepiece case is called a "complete assembly" of the timepiece. Between two sides of a main plate which constitutes the substrate of the timepiece, we call the side having the glass of the timepiece case, that is to say, the side having the dial the "side. back 'of movement. Between the two sides of the main plate, the side having the back of the case at the rear of the case of the timepiece is called the side opposite the dial the "front side" of the watch. movement.

[0028] FIG. 1 is a plan view when a movement 101 of a timepiece 100 (corresponding to a "timepiece movement" in the claims) is viewed from the front side. In fig. 1, a balance wheel 5a of a sprung balance 5 is illustrated by a double dotted line.

As illustrated in FIG. 1, the timepiece 100 includes the movement 101. The movement 101 has a main plate 102 constituting the substrate. A winding stem guide hole 103 is formed in the main plate 102. A winding stem 104 is rotatably inserted into the winding stem guide hole 103. On the front side (front side from the surface of the watch face). sheet in Fig. 1) of the movement 101, a second mobile 106, a third mobile 107, a center mobile 108, and a movement barrel 110 which constitute a gear train 105 are arranged, and an escapement 1 which controls the rotation of the gear train 105 is also arranged.

[0030] The movement barrel 110 has inside a mainspring 111 serving as a source of energy for the timepiece 100. The mainspring 111 is armed by turning the winding stem 104. Then, a configuration is adopted so that the movement barrel 110 is rotated by a rotational force generated when the mainspring 111 is disarmed, and then the center wheel 108 is rotated.

[0031] The center mobile 108 meshes with the third mobile 107. If the center mobile 108 is rotated, the third mobile 107 is formed to be rotated.

The third mobile 107 meshes with the second mobile 106. If the third mobile 107 is rotated, the second mobile 106 is formed to be rotated.

[0033] The second mobile 106 is rotated, thereby prompting the exhaust 1 and a speed regulator 2 to be driven. Exhaust 1 will be described in detail later.

The speed regulator 2 is a mechanism for regulating the speed of the escapement 1, and includes the balance spring 5 and a balance spring (not shown).

The sprung balance 5 has a balance shaft 31 serving as an axis of rotation, a balance wheel 5a which is inserted externally and which is fixed to the balance shaft 31, a double roller 30 (will be described later), and a hairspring (not shown).

Then, the exhaust 1 and the speed regulator 2 are driven, in this way controlling the second mobile 106 so that it rotates once per minute, and controlling the center mobile 108 so that it rotates once. per hour.

(Exhaust)

[0037] FIG. 2 is a perspective view of the exhaust 1 according to the first embodiment. In fig. 2, the upper side of the sheet surface represents the front side of movement 101, and the lower side of the sheet surface represents the back side of movement 101.

[0038] FIG. 3 is a plan view of the exhaust 1 according to the first embodiment. In fig. 3, the front side of the sheet surface represents the front side of movement 101, and the rear side of the sheet surface represents the back side of movement 101. FIG. 3 illustrates only a front conical face 39 and a drive pin 36 in the double roller 30 (which will be described later).

[0039] Here, FIGS. 2 and 3 illustrate the state where anchor 40 (which will be described later) is located in an intermediate section within the range of pivot movement. In this case, the angle of oscillation of the double roller 30 (i.e., the sprung balance 5) is 0 °.

As illustrated in FIGS. 2 and 3, the escapement 1 according to the present embodiment mainly includes the double roller 30, the anchor 40, the first escape mobile 10, and the second escape mobile 20. Hereinafter, each component constituting the exhaust 1 will be described in detail.

As illustrated in FIG. 2, the double roller 30 is disposed in the sprung balance 5 (see fig. 1) which moves in a pivotal manner around the balance shaft 31. The double roller 30 is a constituent component of the speed regulator 2 (cf. Fig. 1) and is a constituent component of the escapement 1. The double roller 30 is a member formed in a circular shape in a plan view, and is externally inserted and fixed to the shaft. balance beam 31. For example, the double roller 30 is a member formed of a metallic material or of a material having a crystalline orientation such as monocrystalline silicon, and is formed by carrying out electroplating treatment or the LIGA, DRIE and MIM process which use an optical method such as photolithography technology. The method of manufacturing the double roller 30 is not limited to the methods described above. For example, the double roll 30 can be formed by performing mechanical treatment on a metallic material.

[0042] The double roller 30 has a rear taper face 32 and the front taper face 39 formed on the rear side (lower side of the sheet surface in Fig. 2) of the movement 101 seen from the rear taper face 32 .

The rear conical face 32 is an element having a disc shape, and having a through hole 33 penetrating in an axial direction of the rear conical face 32. For example, the impulse pin 36 is fitted and fixed in the through hole 33.

[0044] For example, the pulse peg 36 is formed of ruby, has a flat surface on the outer radial side when viewed in the axial direction, and is formed in a semi-circular shape having an arcuate surface on the inner radial side. The impulse peg 36 is disposed along the axial direction, and protrudes from the rear taper face 32 towards the rear side of the movement 101. The impulse peg 36 can contact the anchor 40 (which will be described later).

The front conical face 39 is a member having a disk shape, and is formed to have a diameter which is smaller than that of the rear conical face 32. A crescent-shaped curved portion 39a which is recessed from radially inward manner is formed at a position corresponding to the impulse peg 36 on the outer peripheral surface of the front taper face 39. When the anchor 40 (which will be described later) and the impulse peg 36 engage with each other, the crescent shaped portion 39a functions as an escape portion which prevents a stinger 44b of the anchor 40 from contacting the forward conical face 39. In addition, the stinger 44b of the anchor 40 may come into sliding contact with a partial area on both sides through the crescent-shaped portion 39a in the circumferential direction, in the outer peripheral surface of the front conical face 39.

Anchor 40 includes an elongated anchor body 41 extending along the radial direction of double roller 30, a pallet holding portion 42 disposed in an end portion of anchor body 41, an anchor rod 43 pivotally supporting the anchor body 41, and a plurality of paddles (the first impulse vane 46, the second impulse vane 47, the inlet vane 48, and the outlet vane 49 ).

The anchor rod 43 is disposed in an end portion of the anchor body 41. The anchor rod 43 pivotally supports the anchor body 41 so that it is pivotally movable around a central axis P of the anchor rod 43.

[0048] A kite-shaped part 44 formed in a U-shape in a plan view is disposed in the other end part of the anchor body 41 which is the side opposite to the anchor rod 43. An inner side of the kite-shaped part 44 is adapted to serve as a pallet bridge 44a whose impulse pin 36 can engage or separate by the pivoting movement of the double roller 30.

In addition, the dart 44b projecting towards the front conical face 39 of the double roller 30 is disposed on the inner side of the kite-shaped part 44. When the double roller 30 is pivotally moved , a distal end of the stinger 44b comes in sliding contact with a partial area on both sides through the crescent-shaped portion 39a in the circumferential direction, in the outer peripheral surface of the front conical face 39. This can prevent the anchor 40 to be pivotally moved even when the impulse pin 36 separates from the pallet bridge 44a.

The paddle holding portion 42 is disposed in an end portion of the anchor body 41. The paddle holding portion 42 has a pair of impulse paddle holding portions 42a and 42b (the first impulse pallet holding part 42a and the second impulse pallet holding part 42b) arranged to widen towards the side opposite to the double roller 30, an entry pallet holding part 42c disposed between the first impulse vane holding part 42a and the second impulse vane holding part 42b, and an outlet vane holding part 42d disposed between the anchor body 41 and the second vane holding part d pulse 42b.

The first impulse paddle holding part 42a is disposed on the side of the first exhaust mobile 10 (which will be described later) relative to the central axis P of the anchor rod 43. The second impulse pallet holding part 42b, the inlet pallet holding part 42c, and the outlet pallet holding part 42d are arranged on the side of the second exhaust mobile 20 (which will be described later ) with respect to the central axis P of the anchor rod 43.

Slots are formed in the first impulse vane holding part 42a, the second impulse vane holding part 42b, the inlet vane holding part 42c, and the holding part of the impulse vane, respectively. 42d output pallet.

[0053] The first impulse vane 46 is inserted into and held by the slot in the first impulse vane holding portion 42a. The first impulse vane 46 is disposed to protrude from the first impulse vane holding portion 42a. An impulse surface 46a which can collide with the first exhaust mobile 10 (which will be described later) is disposed in a protrusion portion of the first impulse vane 46. The impulse surface 46a of the first impulse vane 46 is shaped to be flat, and is arranged to face the direction of rotation of the first exhaust mobile 10. For example, the thickness of the first impulse vane 46 is equal to the thickness of the anchor 40.

[0054] The second impulse vane 47 is inserted into and held by the slot in the second impulse vane holding portion 42b. The second impulse vane 47 is arranged to protrude from the second impulse vane holding portion 42b. An impulse surface 47a which can collide with the second exhaust mobile 20 (which will be described later) is disposed in a projecting part of the second impulse vane 47. The impulse surface 47a of the second impulse vane 47 is formed to be flat, and is arranged to face the direction of rotation of the second exhaust mobile 20. For example, the thickness of the second impulse vane 47 is equal to the thickness of the anchor 40.

[0055] The entry pallet 48 is inserted into and held by the slot in the entry pallet holding portion 42c. The entry pallet 48 is disposed to protrude from the entry pallet holding portion 42c. An engaging-disengaging surface 48a which can engage with or separate from the second exhaust mobile 20 is provided in a protruding portion of the entry vane 48. The engaging-disengaging surface 49a of the vane inlet 48 is formed to be flat, and is arranged to face the direction of rotation of the second exhaust mobile 20. For example, the thickness of the inlet vane 48 is thinner than the inlet vane 48. thickness of the first impulse vane 46. The input vane 48 protrudes towards the rear side (lower side in Fig. 2) of movement 101 as seen from the first impulse vane 46.

The outlet pallet 49 is inserted into and held by the slot in the outlet pallet holding portion 42d. The exit pallet 49 is arranged to protrude from the exit pallet holding portion 42d. An engagement-disengagement surface 49a which can engage with or separate from the second exhaust mobile 20 is provided in a protruding portion of the outlet vane 49. The engagement-disengagement surface 49a of the exhaust vane. outlet 49 is formed to be flat, and is disposed so as to face the direction of rotation of the second exhaust mobile 20. For example, the thickness of the outlet vane 49 is thinner than the thickness of the outlet. second impulse vane 47. The output vane 49 protrudes on the rear side (lower side in Fig. 2) of movement 101 as seen from the second impulse vane 47.

[0057] As illustrated in FIG. 3, a pair of tilt pins 45a and 45b (illustration omitted in Fig. 2) are provided on both sides of anchor 40. Tilt pins 45a and 45b rise from main stage 102 of movement 101. Anchor 40 is pivotally moved, thereby bringing the anchor body 41 into contact with the tilt pins 45a and 45b. This adjusts the amount of pivotal movement of anchor 40.

[0058] As illustrated in FIG. 2, for example, the first exhaust mobile 10 and the second exhaust mobile 20 are members formed respectively of a metallic material or of a material having a crystalline orientation such as monocrystalline silicon, and are formed by performing processing. by electroplating or Lithographie Galvanoformung Abformung (LIGA), Deep Reactive Ion Etching (DRIE), and Metal Injection Molding (MIM) process which use an optical method such as photolithography technology.

The first exhaust mobile 10 is a disc-shaped gear member having a central axis Q1, and it includes a first wheel 11, an exhaust pinion 12, and the first escape wheel for the 'impulse 15.

The first wheel 11 includes several parts of teeth 11a on an outer peripheral surface. The tooth portion 11a of the first wheel 11 meshes with a tooth portion 21a of a second wheel 21 of the second mobile escapement 20 (which will be described later).

The exhaust pinion 12 meshes with the second mobile 106 (see FIG. 1) constituting the gear train 105. The energy of the mainspring 111 inside the movement barrel 110 is transferred to the pinion. exhaust 12 by the center mobile 108, the third mobile 107, and the second mobile 106 (see Fig. 1 for everything). This causes the first exhaust mobile 10 to rotate clockwise about the central axis Q1.

The first escape wheel for the impulse 15 is disposed at a position corresponding to the first impulse vane 46 of the anchor 40 in the axial direction of the central axis Q1, which is the rear side ( lower side in Fig. 2) of the movement 101 which is further from the escape pinion 12, and the first impulse vane 46 can contact the first escape wheel for the impulse 15. The first impulse wheel exhaust for the pulse 15 has several first portions of pulse teeth 15a. Among the first impulse tooth portions 15a, a surface in the direction of rotation (in the clockwise direction in Fig. 3) on the side of the first exhaust mobile 10 is adapted to be a. contact surface 15b which comes into contact with the impulse surface 46a of the first impulse vane 46 of the anchor 40.

The second mobile escapement 20 is a disc-shaped gear member having a central axis Q2, and it includes the second wheel 21, a second escape wheel for the impulse 25, and a wheel d 'exhaust for stop 26.

The second wheel 21 includes several parts of teeth 21a on an outer peripheral surface. The tooth portion 21a of the second wheel 21 meshes with the tooth portion 11a of the first wheel 11 of the first mobile exhaust 10. The energy of the mainspring 111 inside the movement barrel 110 is transferred to the motor. second wheel 21 by the center mobile 108, the third mobile 107, the second mobile 106, and the first exhaust mobile 10 (cf. FIG. 1 for everything). This prompts the second mobile escapement 20 to rotate counterclockwise around the central axis Q2.

The second escape wheel for the impulse 25 is disposed at a position corresponding to the second impulse vane 47 of the anchor 40 in the axial direction of the central axis Q2, and the second vane of impulse 47 may contact the second impulse escape wheel 25. The second impulse escape wheel 25 has several second impulse tooth portions 25a. In the second pulse tooth portions 25a, a surface in the direction of rotation (in the counterclockwise direction in Fig. 3) on the side of the second exhaust mobile 20 is adapted to be. a contact surface 25b which comes into contact with the impulse surface 47a of the second impulse vane 47 of the anchor 40.

The escape wheel for the stop 26 is arranged on the rear side (lower side in Fig. 2) of the movement 101 seen from the second escape wheel for the impulse 25, and the paddle. The inlet 48 and the outlet vane 49 may alternately engage with or separate from the stop escape wheel 26. The stop escape wheel 26 has several parts of stop teeth 26a. In the teeth portions for the stop 26a, a surface in the direction of rotation (in the counterclockwise direction in Fig. 3) on the side of the second exhaust mobile 20 is adapted to be. an engage-disengage surface 26b which can engage with or separate from the engage-disengage surface 48a of the input pallet 48 and the engage-disengage surface 49a of the output pallet 49 of anchor 40.

(Operation)

[0067] Figs. 4 to 11 are views to illustrate the operation of the exhaust 1.

Subsequently, the operation of the exhaust 1 configured as described above will be described with reference to FIGS. 4 to 1.

Hereinafter, the operation during two vibrations in a cycle in which the double roller 30 is pivotally moved counterclockwise about a central axis O in response to free vibrations of the Spring balance 5 and hereinafter is pivotally moved in a clockwise direction will be described sequentially. Further, in the state of the start of operation in the following description, as shown in fig. 4, the anchor body 41 of the anchor 40 is in contact with the tilting pin 45b on the side of the second mobile exhaust 20, and the outlet pallet 49 of the anchor 40 engages with the wheel exhaust for stopping 26 of the second exhaust mobile 20. At this moment, the rotation is stopped in the second exhaust mobile 20 and the first exhaust mobile 10 which mesh with the second exhaust mobile 20 .

As illustrated in FIG. 4, if the double roller 30 is pivotally moved counterclockwise, the pallet bridge 44a of the anchor 40 engages with the impulse pin 36. At this time, the pin d The impulse 36 contacts the inner surface of a pallet bridge 44a (right side in Fig. 4). In this way, the rotational force (i.e., the spring force of the balance spring 5) of the double roller 30 acts on the anchor 40.

Then, as illustrated in FIG. 5, if the double roller 30 is pivotally moved further counterclockwise, the drive pin 36 presses the inner surface of the pallet bridge 44a. In this way, the anchor 40 and the first impulse vane 46, the second impulse vane 47, the entry vane 48, and the exit vane 49 which are to be held in the anchor 40 are moved by pivotally clockwise about a central axis P of the anchor rod 43. Here, the crescent-shaped part 39a is formed in the front conical face 39. In this way, when the The anchor 40 and the impulse pin 36 engage with each other, the front conical face 39 and the stinger 44b of the anchor 40 do not contact each other. As a result, the rotational force of the double roller 30 can be transferred efficiently to the anchor 40 without hindering the pivoting movement of the anchor 40.

If the anchor 40 is pivotally moved, the output pallet 49 is moved in the direction away from the second exhaust mobile 20. In this way, the output pallet 49 and the wheel. exhaust for stopping 26 of the second exhaust mobile 20 separate from each other, and the second exhaust mobile 20 and the first exhaust mobile 10 which mesh with the second exhaust mobile 20 become respectively pivotally movable. Fig. 5 illustrates the state immediately before the outlet pallet 49 is separated from the second mobile exhaust 20, and FIG. 6 illustrates the state after the outlet pallet 49 is separated from the second mobile exhaust 20.

At this time, the energy of the mainspring 111 inside the movement barrel 110 is transferred to the first exhaust mobile 10 via the center mobile 108, the third mobile 107, and the second mobile 106, and the first exhaust mobile 10 rotates in the direction of clockwise (cf. fig. 1 for everything). In addition, the energy of the mainspring 111 inside the movement barrel 110 is transferred to the second exhaust mobile 20 which meshes with the first exhaust mobile 10 via the first exhaust mobile 10, and the second exhaust mobile 20 rotates in an anti-clockwise direction (see fig. 1 for everything).

[0074] In addition, as illustrated in FIG. 6, if the second escape wheel 20 rotates counterclockwise, the second pulse tooth part 25a of the second escape wheel for the pulse 25 collides with the second vane pulse 47. In this way, the energy of the mainspring 111 inside the movement barrel 110 (cf. for the whole of FIG. 1) is induced by the double roller 30 by the second exhaust mobile 20 and anchor 40 as the rotational force of double roller 30 (i.e., sprung balance 5), and double roller 30 is further pivotally moved counterclockwise. 'a watch. Additionally, if anchor 40 is pivotally moved, inlet pallet 48 is moved in the direction approaching second mobile exhaust 20.

[0075] Then, as illustrated in FIG. 7, the inlet vane 48 moving close to the second mobile exhaust 20 and the stop escapement wheel 26 of the second mobile exhaust 20 contact each other. Fig. 7 illustrates the state immediately before the inlet vane 48 and the second mobile exhaust 20 engage with each other. Hereinafter, as illustrated in fig. 8, the inlet pallet 48 and the escape wheel for stopping 26 of the second escape mobile 20 engage with each other, and the anchor body 41 and the tilting pin 45 come into contact with each other. In this way, the rotation of the second mobile exhaust 20 is stopped, and the rotation of the first mobile exhaust 10 which meshes with the second mobile exhaust 20 is also stopped.

After the amount of anti-clockwise pivoting movement (i.e. the angle of oscillation) of the double roll 30 is maximized, the direction of pivoting movement of the double roll 30 is changed in an anti-clockwise direction.

[0077] Then, as illustrated in FIG. 9, if the double roller 30 is pivotally moved in a clockwise direction, as shown in fig. 10, the inlet pallet 48 and the escape wheel for stopping 26 of the second exhaust mobile 20 separate from each other so that the first exhaust mobile 10 is turned in the direction clockwise, and that the second exhaust mobile 20 meshing with the first exhaust mobile 10 is rotated anti-clockwise. Fig. 9 illustrates the state immediately before the inlet pallet 48 is separated from the second mobile exhaust 20 (hereinafter referred to as the "first state"), and FIG. 10 illustrates the state after the inlet pallet 48 is separated from the second mobile exhaust 20.

If the first exhaust mobile 10 is rotated clockwise, the first pulse tooth portion 15a of the first escape wheel for the pulse 15 collides with the first impulse pallet 46. In this way, the energy of the mainspring 111 inside the movement barrel 110 (cf. for the whole of FIG. 1) is induced by the double roller 30 via the first mobile exhaust 10. and anchor 40 as the rotational force of the double roller 30 (i.e., the sprung balance 5), and the double roller 30 is further pivotally moved clockwise. 'a watch. Additionally, if anchor 40 is pivotally moved, outlet pallet 49 is moved in the direction approaching second mobile exhaust 20.

[0079] Then, as illustrated in FIG. 11, the outlet vane 49 moving close to the second mobile exhaust 20 and the stop escapement wheel 26 of the second rotating escapement mobile 20 contact each other. Fig. 11 illustrates the state immediately before the outlet vane 49 and the second mobile exhaust 20 engage with each other (hereinafter referred to as the "second state").

Hereinafter, as illustrated in FIG. 4, the outlet pallet 49 of the anchor 40 engages with the escape wheel for stopping 26 of the second escape mobile 20, and the anchor body 41 comes into contact with the tilting pin 45b , in this way stopping the rotation of the second exhaust mobile 20 and of the first exhaust mobile 10 which mesh with the second exhaust mobile 20.

[0081] Hereinafter, the operation described above is carried out repeatedly. In this way, the escapement 1 according to the first embodiment can be operated as an escapement called an escapement of the indirect impulse type 1 in which the second mobile escapement 20 engages alternately and repeatedly with or separates from it. the entry pallet 48 and the exit pallet 49, and which induces the energy to the sprung balance 5 via the anchor 40.

Incidentally, the vibration of the mechanical timepiece is generally expressed by the following expression, when the angle of oscillation of the sprung balance 5 is set to A0, the angle of rotation of the sprung balance 5 is set to θ, the angular frequency of the sprung balance 5 is set to ω, and the time is set to t.

[Expression 1]

In addition, the time between the first state immediately before the inlet pallet 48 is separated from the second exhaust mobile 20 (see Fig. 9) and the state where the angle of rotation of the balance hairspring 5 becomes 0 ° (cf. fig. 3) is set to tR, and the angle of rotation of the sprung balance 5 in the first state is set to θR. Here, in the case of time t = 0, we obtain 0 = 0 °. Accordingly, the result is expressed by the following expression.

[Expression 2]

[0083]

[0084] Therefore, the time tR enters the first state and the state where the angle of rotation of the sprung balance 5 is 0 ° is expressed by the following expression.

[Expression 3]

[0085]

In addition, when the time between the state where the angle of rotation of the sprung balance 5 is 0 ° (cf. FIG. 3) and the second state immediately before the output pallet 49 engages with the second escapement mobile 20 (see fig. 11) is set to tL1, and the angle of rotation of the sprung balance 5 in the second state is set to θL1u, the time tL1 between the state where the angle of rotation of the sprung balance 5 is 0 ° and the second state is expressed by the following expression.

[Expression 4]

[0087]

Here, the sum of the time tRet of the time tL1est equivalent to the time during which the input pallet 48 and the output pallet 49 are separated from the second exhaust mobile 20, that is to say, the time in the state where the anchor 40 separates from the second escape mobile 20. The time in the state where the anchor 40 separates from the second escape mobile 20 appears once during the two vibrations in a cycle of the sprung balance 5. Consequently, a ratio rf in the state where the anchor 40 separates from the second escapement mobile 20 during the operation of the timepiece 100 (cf. FIG. 1) is expressed by the following expression.

[Expression 5]

[0089]

For example, when the angle of oscillation of the sprung balance 5 (A0 = 280 °), the angle of rotation of the sprung balance 5 in the first state (θR = 9 °), and the angle of rotation of the sprung balance 5 in the second state (θL1 = 11 °) are set, the ratio in the state where the anchor 40 separates from the second escape wheel 20 is expressed by rf = 1.14%. As described above, during the operation of the timepiece 100, the ratio of the period of time remaining in the state where the anchor separates from the second escapement mobile is 50% according to the prior art. . On the other hand, the ratio rf of the period of time remaining in the state where the anchor 40 separates from the second escapement mobile 20 is considerably reduced according to the present embodiment.

(Beneficial effect)

According to the first embodiment, there is provided the exhaust 1 comprising the second exhaust mobile 20 which has the escape wheel for the stop 26 which can engage with or separate from the inlet pallet 48 and the outlet pallet 49, and which meshes with the first exhaust mobile 10. Consequently, the second exhaust mobile 20 can control the rotation and stopping of the first exhaust mobile 10 and the second exhaust mobile 20. Here, in the second exhaust mobile 20, each between the inlet pallet 48 and the outlet pallet 49 engages with the escape wheel for stopping 26. In Consequently, in comparison with the prior art, it is possible to shorten the period of time remaining in the state where the anchor 40 separates from the second escape mobile 20. In this way, it is possible to shorten so the period of time of tremor of the second exhaust mobile 20. Consequently, degradation of energy transfer efficiency can be prevented, while ensuring stable operation of the exhaust 1.

In addition, the first impulse vane 46 and the second impulse vane 47 are disposed in the anchor 40. Accordingly, the invention can be preferably selected for the so-called exhaust type exhaust. indirect impulse 1 which induces energy to the sprung balance 5 via the first impulse vane 46 and the second impulse vane 47 of the anchor 40.

In addition, according to the movement 101 and the timepiece 100 of the first embodiment, the escapement 1 is made available which can considerably shorten the period of time of the tremor of the second mobile escapement 20, and which can prevent the degradation of energy transfer efficiency, while ensuring stable operation. Therefore, it is possible to provide the movement 101 and the timepiece 100 which show high performance.

In the first embodiment, the energy of the mainspring 111 inside the movement barrel 110 is transferred to the first exhaust mobile 10. However, the energy transferred to the first exhaust mobile 10 n is not limited to that. For example, a configuration can be adopted in which energy is transferred to the first mobile escapement 10 from the mainspring disposed in a different location from the movement barrel 110.

(Example of modification of the first embodiment)

[0095] FIG. 12 is a plan view of the exhaust 1 according to an example of modification of the first embodiment.

Next, the exhaust 1 according to the modification example of the first embodiment will be described.

In this embodiment, the second escape wheel 20 has the second escape wheel for the impulse 25 which can come into contact with the second impulse vane 47, and the escape wheel for the impulse. stop 26 which can engage with or separate from the input pallet 48 and the output pallet 49 (see Fig. 2).

On the other hand, as illustrated in FIG. 12, the modification example of the first embodiment is different from the embodiment in that the second escape wheel for impulse 25 and escape wheel for stop 26 are integrally formed as a second escape wheel 24. Hereinafter, the description will be omitted with respect to the configuration elements which are the same as those in the first embodiment.

The second escape wheel 20 includes the second escape wheel 24. For example, the second escape wheel 24 is formed of several second escape tooth portions 24a which are erected along the axial direction. . The second impulse vane 47 can contact the second escape tooth portions 24a of the second escape wheel 24, and the input vane 48 and the exit vane 49 can engage with or interlock with. separate second exhaust tooth portions 24a. That is, the second escape wheel 24 according to the modification example of the first embodiment is configured so that the second escape wheel for the impulse 25 and the escape wheel for the The stop 26 according to the first embodiment are integrally formed, and it functions as the second escape wheel for the impulse 25 and the escape wheel for the stop 26.

[0100] The shape of the first escapement wheel for the impulse 15 of the first mobile escapement 10 is not limited to that of the first embodiment. Therefore, as in the modification example of the first embodiment, the first pulse tooth part 15a of the first escape wheel for the pulse 15 can be erected along the axial direction, for example, similarly to the second escape tooth portion 24a of the second escape wheel 24.

[0101] In addition, as in the modification example of the first embodiment, a configuration can be adopted in which the amount of pivotal movement of the anchor 40 is adjusted by forming a long hole in the anchor 40 and simply inserting the tilt pin 45 into the long hole.

[0102] According to the modification example of the first embodiment, the second escape wheel for the impulse 25 and the escape wheel for the stop 26 which are formed in two layers in the first embodiment are formed in one piece. In this way, it is possible to reduce the thickness of the second exhaust mobile 20. Therefore, by shortening the period of the dither time of the second exhaust mobile 20, it is possible to further prevent the degradation of. the energy transfer efficiency, while ensuring stable operation of the exhaust 1. In addition, it is possible to reduce the thickness of the exhaust 1.

(Second embodiment)

[0103] Next, the exhaust 1 according to a second embodiment will be described.

[0104] FIG. 13 is a plan view of the exhaust 1 according to the second embodiment.

[0105] In the first embodiment, the first impulse vane 46 and the second impulse vane 47 are disposed in the anchor 40, thereby constituting the escapement called the indirect impulse type exhaust 1.

[0106] On the other hand, as illustrated in FIG. 13, the escapement 1 according to the second embodiment is different from that according to the first embodiment in that the first impulse vane 46 and the second impulse vane 47 are arranged in the double roller 30 to constitute the The so-called direct impulse type escapement 1. Hereinafter, description will be omitted with regard to the setting items which are the same as those in the first embodiment.

[0107] The second escape wheel 20 includes the second escape wheel 24. The second impulse vane 47 can come into contact with the second escape tooth portion 24a of the second escape wheel 24, and the inlet vane 48 and the outlet vane 49 can engage with or separate from the second exhaust tooth portion 24a. That is, the second escape wheel 24 is formed such that the second escape wheel for impulse 25 and escape wheel for stop 26 according to the first embodiment are formed. in one piece, and it functions as the second escape wheel for the impulse 25 and the escape wheel for the stop 26.

[0108] A pair of slots are formed in the rear conical face 32 of the double roller 30. The first impulse vane 46 and the second impulse vane 47 are respectively inserted into and secured to the pair of slits in the conical face. 32. The escapement 1 according to the second embodiment is operated as the escapement called direct-impulse type escapement 1 which induces energy to the sprung balance 5 in such a way that the first escapement wheel for the impulse 15 of the first escape wheel set 10 collides with the first impulse vane 46, and the second escape wheel 24 of the second escape wheel set 20 collides with the second impulse vane 47.

[0109] As in the second embodiment, a configuration can be adopted in which a through hole is formed in the anchor 40, and the inlet pallet 48 is inserted into and fixed to the through hole.

[0110] According to the second embodiment, the invention can be preferably selected for the escapement called direct-pulse type escapement 1 which induces energy to the sprung balance 5 in such a way that the first mobile exhaust 10 and the second escape wheel 20 collide with the first impulse vane 46 and the second impulse vane 47 of the spring balance 5.

[0111] The technical scope of this invention is not limited to the embodiments described above, and it can be additionally modified in various ways within a scope not departing from the spirit of the invention. 'invention.

[0112] The shapes or materials of the first exhaust mobile 10, the second exhaust mobile 20, the double roller 30, the anchor 40, the impulse pin 36, the first impulse paddle 46 , the second pulse vane 47, the input vane 48, and the output vane 49 are not limited to those according to the respective embodiments.

[0113] In addition, the methods of fixing the impulse pin 36, the first impulse vane 46, the second impulse vane 47, the entry vane 48, and the exit vane 49 are not limited to those according to the respective embodiments.

[0114] In addition, so that the field of application does not depart from the spirit of the invention, the configuration elements according to the embodiments described above can be suitably replaced by elements of known configuration.

Claims (6)

An exhaust (1) comprising: a first impulse pallet (46) and a second impulse pallet (47) for inducing spiral balance (5) energy; an anchor (40) which has an entry pallet (48) and an output pallet (49), and which is pivotally movable about an anchor rod (43); a first escape wheel (10) which has a first escape wheel for the pulse (15) which can contact the first pulse pallet (46), the energy being transferred at this moment; and a second escape wheel (20) which has a second escape wheel for the pulse (25) which can contact the second pulse pallet (47) and an escape wheel for stopping ( 26) which can engage with or separate from the entry pallet (48) and the output pallet (49), and which meshes with the first escape wheel (10). 2. The exhaust (1) according to claim 1, wherein the second escape wheel for the pulse (25) and the escape wheel for the stop (26) are formed in one piece to form a second wheel exhaust (24). The exhaust according to claim 1 or 2, wherein the first impulse pallet (46) and the second impulse pallet (47) are disposed in the anchor (40). 4. The exhaust according to claim 1 or 2, wherein the first impulse pallet (46) and the second impulse pallet (47) are disposed in the spiral balance (5). 5. A timepiece movement (101) (100) comprising: the exhaust (1) according to any one of claims 1 to 4. A timepiece (100) comprising: the timepiece movement (101) (100) according to claim 5.