CH717270A2 - Component of a timepiece, for example an escape wheel. - Google Patents

Abstract

The invention relates to a component of a timepiece, for example an escape wheel (26), comprising a body which rotates around an axis of rotation, a sliding surface (42) which faces a surface of contact (44) of an associated element, for example an anchor (28), is inclined with respect to this surface and slides on it due to a rotation of the component; and one or a plurality of grooves (46) which extend on the sliding surface (42) in a direction intersecting with a sliding direction and are capable of retaining the lubricating oil (48).

Description

BACKGROUND OF THE INVENTION

1. Field of the invention

The present patent application relates to a timepiece component, a movement and a timepiece.

2. Description of the prior art

As a component of a timepiece, one can use components including a sliding surface which faces a contact surface of an associated element and slides on the contact surface as it rotates.

[0003] For example, an exhaust mobile provided in a mechanical timepiece includes a sliding surface which slides on a pallet fixed to an anchor during its rotation. Since the vane is formed of a material having high hardness such as ruby or ceramic, a structure in which lubricating oil is retained on the sliding surface is provided in the related art so as to reduce the load. wear of the sliding surface.

[0004] Document JP-T-2007-506073 (PTL 1) discloses an exhaust mobile including a plurality of teeth arranged radially on a rim fixed to a hub, a finger of the tooth having a first portion which is arranged more close to the rim and a second portion which is disposed closer to an end of the finger and is thinner than the first portion, and a delimitation between these two portions is formed by a bending which constitutes an oil retaining portion.

[0005] Document JP-A-2016-176714 (PTL 2) discloses an electroformed component including a sliding part exhibiting high properties in terms of lubricating oil retention by forming fine irregularities in vertical bands extending along a direction perpendicular to a sliding direction on an electroformed surface of the sliding part.

[0006] Document JP-A-2010-91544 (PTL 3) discloses a timepiece component which is a precision mechanical component in which at least three layers are laminated, the precision mechanical component including a sliding part a portion of which substantially parallel to a rolling direction contacts other components, and at least a portion of the sliding portion has a recess.

[0007] In a timepiece component having a sliding surface which faces a contact surface of an associated member and slides over the contact surface as it rotates, it is desirable to reduce the wear of sliding surface and reduce the energy required to rotate the timepiece component. In the techniques described in the aforementioned patent literature, the wear of the sliding surface caused by friction between the sliding surface and the contact surface is reduced since the lubricating oil is retained on the sliding surface, but there is always has room for improvement to reduce the energy required for rotation.

SUMMARY OF THE INVENTION

[0008] An objective according to a first aspect of the present patent application is to, in a component of a timepiece comprising a sliding surface which faces a contact surface of an associated element and slides on the surface of contact when performing rotary motion, reduce the wear of the sliding surface and reduce the energy required to rotate a rotating body.

A timepiece component according to a first aspect includes: a rotating body which is rotatable about a rotating shaft; a sliding surface which is provided on the rotating body, is inclined with respect to a contact surface of an associated element, faces this surface and slides thereon as a result of the rotation of the rotating body; and one or a plurality of grooves which extend on the sliding surface in a direction intersecting with a sliding direction and can retain lubricating oil.

In the component of a timepiece, since the sliding surface provided on the rotating body is inclined relative to the contact surface of the associated element, and faces it, the sliding surface can be brought into line contact or point contact with the contact surface as the sliding surface slides over the contact surface due to the rotation of the rotating body.

[0011] In addition, the groove is disposed on the sliding surface in a direction orthogonal to the sliding direction, and the groove can retain the lubricating oil.

[0012] In this way, the sliding surface is brought into line or point contact with the contact surface, and the friction is reduced thanks to the lubricating oil retained in the groove, thereby reducing the resistance to sliding of the sliding surface. In other words, the wear of the sliding surface when the sliding surface slides on the contact surface can be reduced, and the energy required for rotating the rotating body can be reduced.

According to a second aspect, in accordance with the first objective, the sliding surface is inclined with respect to a central axis of rotation of the rotary body.

[0014] Therefore, a structure is obtained in which even when the rotating body is rotated, the sliding surface is moved in a circumferential direction of rotation while maintaining a state of inclination relative to the central axis of rotation.

According to a third aspect, according to the second aspect, an angle of inclination of the sliding surface in a plane including the central axis of rotation with respect to the central axis of rotation is between 1 degree and 5 degrees .

[0016] When the angle of inclination is 1 degree or more, for example, even when the central axis of rotation is inclined relative to, for example, a design value, the state in which the surface of slip is in line or point contact with the contact surface and glides over it can be reliably maintained.

[0017] When the tilt angle is 5 degrees or less, any variation in position of a pointed end of the sliding surface, i.e., a portion which contacts and slides over the contact surface, is prevented, and any relative positional relationship between the sliding surface and the contact surface can be maintained.

According to a fourth aspect, in accordance with one of the preceding aspects - from the first to the third - the depth of the groove with respect to the sliding surface is between 0.1 μm and 3.0 μm.

When the depth of the groove is 0.1 µm or more, the lubricating oil can be reliably retained.

[0020] Further, when the depth of the groove is 3.0 µm or less, the groove is not excessively deep, so that the amount of the lubricating oil which remains in the groove and is thus "wasted" in the course of use can be reduced.

In a fifth aspect, according to one of the first to fourth aspects above, the width of the groove in the direction orthogonal to the direction of extension of the sliding surface is between 1 μm and 20 μm.

When the groove width of the groove is 1 µm or more, the lubricating oil can be reliably retained.

Further, when the groove width of the groove is 20 µm or less, a state can be obtained that the sliding surface slides smoothly on the contact surface.

A movement according to a sixth aspect includes: the timepiece component according to one of the first to fifth aspects; and the associated element including the contact surface. A part of the sliding surface slides on the contact surface in a line or point contact mode with the contact surface following the rotation of the rotating body.

Since the movement includes the timepiece component according to one of the first to fifth aspects, the wear of the sliding surface can be prevented and an energy required for the rotation can be reduced when the part of the Sliding surface slides on the contact surface while making line or point contact with the contact surface due to the rotation of the rotating body.

A timepiece according to a seventh aspect includes the movement according to the sixth aspect.

The timepiece includes the movement according to the sixth aspect, and the movement includes the timepiece component according to one of the first to fifth aspects. Therefore, when a part of the sliding surface slides on the contact surface while the mutual contacting takes place by line or by point with the contact surface as a result of the rotation of the rotating body, the wear of the sliding surface can be reduced and the energy required for the rotation drive can also be reduced accordingly.

In the present patent application, the wear of the sliding surface can be reduced and the energy required for the rotation of the rotary body can thus be reduced.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a plan view showing a movement including an escape wheel set and an anchor according to a first embodiment. FIG. 2 is a sectional view showing the exhaust mobile and a bearing according to the first embodiment. Fig. 3 is a plan view showing a state where a sliding surface of the exhaust mobile and a contact surface of an anchor finger according to the first embodiment face each other. Fig. 4 is an enlarged plan view showing a state where the sliding surface of the exhaust mobile and the contact surface of the anchor finger according to the first embodiment face each other. FIG. 5 is an enlarged perspective view showing the exhaust mobile according to the first embodiment near the sliding surface. Figure 6 is a sectional view taken along a line 6-6 in Figure 4 showing a state where the sliding surface of the exhaust mobile and the contact surface of the anchor finger according to the first mode of achievement face each other. FIG. 7 is an enlarged view taken in the direction of arrow 7 in FIG. 5 showing the exhaust mobile according to the first embodiment near the sliding surface. FIG. 8 is an enlarged sectional view taken along line 8-8 of FIG. 7 showing the exhaust mobile according to the first embodiment in proximity to the sliding surface. FIG. 9 is an enlarged explanatory view showing a tip end of the exhaust mobile of the exhaust mobile according to the first embodiment. FIG. 10 is an enlarged explanatory view showing an exhaust mobile tip end of the exhaust mobile according to the first embodiment. Fig. 11 is a graph showing a relationship between the backlash 8 of the exhaust mobile and the angle of inclination of the rotation shaft according to the first embodiment. Fig. 12 is a graph showing a relationship between the dimensions of the exhaust mobile and the inclination angle of the sliding surface according to the first embodiment. Fig. 13 is a graph showing a relationship between the groove width and the depth of the surface of the oil film in a groove of the exhaust mobile according to the first embodiment. Fig. 14 is a front view showing a timepiece of the technology of the present disclosure.

DESCRIPTION OF EMBODIMENTS

A timepiece component according to a first embodiment and a timepiece 22 using the timepiece component will be described in detail with reference to the figures.

The timepiece 22 shown in Figure 14 is a mechanical self-winding watch, and it comprises a movement 24 shown in Figure 1. The movement 24 includes an escapement mobile 26 and an anchor 28. The escapement mobile 26 is here an example of a timepiece component, and the anchor 28 is an example of an associated element.

The exhaust mobile 26 comprises a plurality of arms 32 which extend obliquely and radially around a rotation shaft 30. The plurality of arms 32 is arranged at a constant angular spacing in a circumferential direction of the rotation shaft 30. In each of these arms 32, a surface extending towards the tip is a sliding surface 42.

As shown in Figure 2, the rotation shaft 30 is inserted through a bearing 34 provided in the timepiece 22. As a result, the exhaust mobile 26 is rotatably held according to the arrow of direction R1 shown in Figure 1.

As shown in Figure 1, the anchor 28 is held pivotally about an anchor axis 36 along the direction arrow Y1 and the direction arrow Y2 opposite to the direction arrow Y1. Then, the anchor 28 oscillates in a repeated rotation of a predetermined angle according to the direction arrow Y1 and a rotation of a predetermined angle according to the direction arrow Y2 via an impulse vane (not shown).

The anchor 28 includes two corner pieces 38, and an inlet pallet 40A is held in a corner part 38 and an outlet pallet 40B is held in the other corner part 38. Ci -after, when the entry pallet 40A and the exit pallet 40B are not distinguished, the entry pallet 40A and the exit pallet 40B are simply described as being the anchor pallet 40.

As shown in Figures 3 and 4, the anchor pallet 40 is provided with a contact surface 44. The contact surface 44 is a surface whose sliding surface 42 of one of the arms 32 can face, as a function of an angle of rotation of the exhaust mobile 26.

The exhaust mobile 26 receives a rotational driving force of an energy source (not shown) in the direction of arrow R1. The rotation of the exhaust mobile 26 in the direction of the arrow R1 is temporarily prevented by one of the arms 32 adjoining the inlet pallet 40A or the outlet pallet 40B. For example, as shown in Fig. 1, a state where the rotation in the direction of the arrow R1 is prevented when one of the arms 32 adjoins the output pallet 40B can be obtained. Here, when the anchor 28 is rotated in the direction of the arrow Y1 by an impulse vane (not shown), the outlet vane 40B is separated from the arm 32, and the exhaust mobile 26 can rotate in the direction of arrow R1.

When the output pallet 40B separates from the arm 32, the exhaust mobile 26 rotates while the sliding surface 42 slides on the contact surface 44 of the output pallet 40B.

The anchor 28 rotates by a predetermined angle in the direction of the arrow Y1 while the exhaust mobile 26 rotates in the direction of the arrow R1, and the level of rotation of the exhaust mobile 26 reaches a predetermined angle. In this state, the inlet vane 40A adjoins the arm 32 (an arm different from the arm with which the outlet vane 40B is in contact) of the exhaust mobile 26. Therefore, a rotation of the exhaust mobile 26 is at again prevented. Then, since the inlet pallet 40A is separated from the arm 32 when the anchor 28 rotates in the direction of arrow Y2, the exhaust mobile 26 can again rotate in the direction of arrow R1.

In this way, even when the entry pallet 40A is separating from the arm 32, the exhaust mobile 26 rotates while the sliding surface 42 slides on the contact surface of the entry pallet 40A facing him.

When the exhaust mobile 26 is rotated at a predetermined angle in the direction of arrow R1, the output pallet 40B adjoins the arm 32 (a different arm from the arm with which the input pallet 40A was in contact) of the exhaust mobile 26, thereby preventing the rotation of the exhaust mobile 26. The exhaust mobile 26 is a component of a timepiece which allows a certain time to be counted down by performing such an intermittent rotation. (rotation by a certain angle and stop rotation).

According to the technique disclosed in the context of the present invention, as shown in Figures 5, 6, 9 and 10, the sliding surface 42 of the exhaust mobile 26 is inclined at an angle of inclination θ1 with respect to to a central axis of rotation CL-1. Here, as shown in Fig. 5, a PL plane including the central axis of rotation CL-1 is considered, and an angle of the sliding surface 42 in the plane PL with respect to the central axis of rotation CL-1 (a reference line CL-2 parallel to the central axis of rotation CL-1 in Fig. 5) is defined as the inclination angle θ1 of the sliding surface 42. In the present embodiment, l The tilt angle θ1 is 1 degree or more and 5 degrees or less. In Figures 6, 9 and 10, the tilt angle θ1 is shown larger than an actual tilt angle to make the tilt of the sliding surface 42 clearer.

On the other hand, as shown in Figure 6, the contact surface 44 of the anchor finger 40 is parallel to the central axis of rotation CL-1 of the exhaust mobile 26. Therefore, the sliding surface 42 of the escapement mobile 26 faces the contact surface 44 of the anchor 28 as a function of the angle of rotation of the exhaust mobile 26, but in such a state of confrontation, the sliding surface 42 is inclined relative to the contact surface 44.

In the state where the sliding surface 42 faces the contact surface 44, a pointed end of the exhaust mobile 26T terminating the sliding surface 42 is brought into contact with the contact surface 44. When the exhaust mobile 26 rotates in the direction of arrow R1 in this state of contact, the sliding surface 42 slides on the contact surface 44 according to a mode of contact by line or by point with the contact surface 44.

As shown in Figures 4 to 8, a plurality of grooves 46 is formed on the sliding surface 42. Each of the grooves 46 is oriented in a direction intersecting with the sliding direction (direction arrow S1) of the sliding surface 42 relative to the contact surface 44. In particular, in the present embodiment, as shown in Fig. 7, when the sliding surface 42 is viewed from the front, the direction of extension of the groove 46 coincides with the thickness direction (direction arrow T1) of the exhaust mobile 26, and is orthogonal to the sliding direction (direction arrow S1).

As shown in Figure 6, since the sliding surface 42 is inclined relative to the contact surface 44, a wedge-shaped space WG is formed between the sliding surface 42 and the contact surface 44 while the surface of The slip 42 is sliding on the contact surface 44. A lubricating oil 48 is applied to the sliding surface 42. The lubricating oil 48 may be temporarily stored in the WG space while the tip end of the exhaust mobile 26T terminating the sliding surface 42 comes into contact with the contact surface 44. The lubricating oil 48 has the effect of reducing the friction when the sliding surface 42 slides on the contact surface 44.

As shown in Figure 8, part of the lubricating oil 48 applied to the sliding surface 42 is retained in the grooves 46. In other words, the groove 46 is a recess provided to allow the lubricating oil 48 to be retained in this manner. Even when an amount of the lubricating oil 48 is reduced as a result of the repeated sliding of the sliding surface 42 on the contact surface 44, the state where the lubricating oil 48 is retained in the groove 46 is. maintained.

[0048] The term "retention" of the lubricating oil 48 used herein means that the lubricating oil 48 is maintained in a state where it remains in the groove 46 without escaping from the groove 46 due to viscosity, surface tension, or the like. Therefore, for example, when the lubricating oil 48 retained in the groove 46 is discontinuous with the lubricating oil 48 on the sliding surface 42 (including a case where the lubricating oil on the sliding surface 42 is exhausted), a state where the lubricating oil 48 does not escape from the groove 46 is maintained regardless of the orientation of the sliding surface 42. Even when the lubricating oil 48 flows vertically downward. in the groove 46 due to gravity, the lubricating oil 48 does not escape from the groove 46. On the other hand, in the state that the lubricating oil 48 retained in the groove 46 is continuous with lubricating oil 48 on the sliding surface 42, part of the lubricating oil 48 inside the groove 46 and on the sliding surface 42 can be replaced, but even then the oil lubricant 48 retained is not completely removed from the groove 46.

[0049] In practice, part of the lubricating oil 48 may be slightly lifted from the groove 46 due to the surface tension described above, and a lens 48A of convex shape may be formed as illustrated by the line dotted line in Fig. 8. In this case, as the sliding surface 42 slides over the contact surface 44, the lubricating oil 48 reliably adheres to the anchor end tip 28T of the vane. anchor 40.

On the other hand, the lubricating oil lens 48 formed in the groove 46 may be a concave lens 48B recessed into the groove 46, as represented by a continuous line in FIG. 8, and corresponding here to a shape meniscus. Even then, when the anchor end point 28T (see Figure 4) of the anchor finger 40 slightly enters the groove 46, the lubricating oil 48 will adhere to the anchor end point. 28T of the anchor pallet 40.

As shown in Figures 7 and 8, the groove 46 has a predetermined groove width W1 in the direction of sliding. In the present embodiment, the groove width W1 is 1 µm or more and 20 µm or less.

Further, the groove 46 has a predetermined groove depth D1 with respect to the sliding surface 42. In the present embodiment, the groove depth D1 is 0.1 µm or more and 3.0 µm. or less.

In what follows, the operation of the present embodiment will be described.

As illustrated in Figures 5 and 6, the sliding surface 42 of the exhaust mobile 26 is inclined at an angle of inclination θ1 relative to the central axis of rotation CL-1. On the other hand, the contact surface 44 of the anchor 28 is parallel to the central axis of rotation CL-1. Therefore, the sliding surface 42 is inclined at the inclination angle θ1 with respect to the contact surface 44 when the sliding surface 42 is in a state where it faces the contact surface 44. Further , when the sliding surface 42 slides on the contact surface 44 following the rotation of the exhaust mobile 26 in the direction of arrow R1 (see Figures 1 to 3), the sliding surface 42 slides on the surface of contact 44 while the type of contact with the contact surface 44 is a line contact or a point contact.

In addition, the lubricating oil 48 is retained in the grooves 46 provided on the sliding surface 42. The lubricating oil 48 reduces the frictional forces when the sliding surface 42 slides on the contact surface 44. , and thus reduces the slip resistance.

Thus, in the present embodiment, compared to a structure in which the sliding surface 42 is not inclined and a structure in which the lubricating oil 48 is not retained by the groove 46, the Wear of the sliding surface 42 can be reduced, and the energy required to rotate the exhaust mobile 26 can be reduced even when the sliding surface 42 slides over the contact surface 44.

According to the present embodiment, the sliding surface 42 is inclined at the predetermined angle of inclination θ1 with respect to the central axis of rotation CL-1 of the exhaust mobile 26. Consequently, even when the exhaust mobile 26 rotates, the sliding surface 42 can maintain a state of inclination according to the predetermined angle of inclination θ1 with respect to the central axis of rotation CL-1.

As shown in Figure 2, the rotation shaft 30 of the exhaust mobile 26 is inserted through the bearing 34 of the timepiece 22, and a GP spacing is formed between the outer periphery of the rotation shaft 30 and the inner periphery of bearing 34. The spacing is called a "backlash", and as indicated by the dotted line in Figure 2, the rotation shaft 30 can be tilted relative to the backlash. 'original central axis of rotation CL-1 of the exhaust mobile 26 due to the GP spacing. In the present embodiment, a lower limit value of the tilt angle θ1 is determined such that even when the rotating shaft 30, i.e., the actual rotating central axis CL -1 is inclined relative to a central axis of rotation as was desired during its design, the state where the sliding surface 42 is in line contact or in point contact with the contact surface 44 can be maintained.

FIG. 11 shows a relationship between an inclination of the rotation shaft 30 and the GP space (kickback) when an axial length L1 is 1 mm, 2 mm, 3 mm and 4 mm. As shown in Figure 2, in the rotation shaft 30, the axial length L1 is a full length of the rotation shaft 30.

More specifically, as can be seen in FIG. 11, in the exhaust mobile 26 of the timepiece 22, when the maximum value of the spacing GP is approximately 10 μm, and the value minimum of the axial length L1 of the bearing 34 is about 1 mm, the maximum angle of inclination of the rotation shaft 30 is 0.57 degrees. Even when the rotation shaft 30 is tilted in this way, the lower limit value of the tilt angle θ1 can be adjusted to 1 degree so as to maintain the state where the sliding surface 42 is brought into contact by. line or in point contact with the contact surface 44.

In this way, in order to maintain the state where the sliding surface 42 is in contact by line or by point with the contact surface 44, the upper limit value of the angle of inclination θ1 is not not limited. However, when the angle of inclination θ1 is too large, the thickness of the end point of the exhaust mobile 26T is thin, and its strength decreases. Consequently, in order not to make the end point of the exhaust mobile 26T too fragile, it is preferable to set an upper limit value for the angle of inclination θ1.

As shown in Figures 9 and 10, in the sliding surface 42, the end point of the exhaust mobile 26T may have a curved shape due to a manufacturing precision limit, and a radius of curvature R of the curved shape can vary within a range of 0 µm to 20 µm. In FIGS. 9 and 10, the end point of the exhaust mobile 26T represented by a continuous line has a relatively small radius of curvature R (R = R1), and the end point of the exhaust mobile 26T represented by a dotted line has a large radius of curvature R (R = R2). Fig. 9 shows a case where the inclination angle θ1 of the sliding surface 42 is relatively small, and Fig. 10 shows a case where the inclination angle θ1 of the sliding surface 42 is relatively large. In Figures 9 and 10, the tilt angle is shown larger in the drawing than the actual tilt angle.

As can be seen in Figures 9 and 10, the larger the radius of curvature R of the end point of the exhaust mobile 26T, the greater the influence on the dimension L2 of the exhaust mobile 26 is tall. As can be seen by comparing Figures 9 and 10, the wider the tilt angle θ1, the larger the dimension L2, and this tendency is more evident as the radius of curvature R becomes larger. The dimension L2 is a length measured between a position of the end point of the exhaust mobile 26T (see the reference line L3 shown in Figures 9 and 10) when the radius of curvature is zero (R = 0) in each arm 32 and the end point of the actual exhaust mobile 26T.

FIG. 12 represents a relationship between the dimension L2 and the angle of inclination θ1 when the radius of curvature R of the end point of the exhaust mobile 26T is 20 μm, 10 μm, 5 μm and 2 µm. Here, when the allowable value of variation of the dimension based on the radius of curvature R is set to 2 µm, as seen in figure 12, the tilt angle θ1 corresponding to the dimension L2 of 2 µm is 5.71 degrees when the radius of curvature R is 20 µm. Therefore, if the upper limit value of the tilt angle θ1 is 5 degrees, the variation of the dimension L2 can be reduced when the radius of curvature R is larger.

As illustrated in Figure 8, the width W1 of the groove 46, that is to say, the opening width of the groove 46 in a direction orthogonal to the direction of extension of the groove 46 n This is not limited as long as the lubricating oil 48 can be retained in the groove 46. However, when the groove width W1 is too wide, the anchor end point 28T is liable to fall into the groove 46. and abuts in the groove 46 as the sliding surface 42 slides over the contact surface 44, resulting in slip resistance. When the minimum value of the radius of curvature of the anchor end point 28T is set at 20 µm, the resistance when sliding the sliding surface 42 on the contact surface 44 can be reduced by setting the maximum value of the groove width W1 of the groove from 46 to 20 µm.

The groove depth D1 of the groove 46 relative to the sliding surface 42 is not limited as long as the lubricating oil 48 can be retained in the groove 46. For example, if the lower limit of the groove depth D1 is fixed at 0.1 µm, the lubricating oil 48 can be retained in the groove 46.

However, when the groove 46 is too deep, the lubricating oil 48 accumulates in the groove 46 near the bottom 46B thereof, and the amount of lubricating oil 48 which is not available. between the sliding surface 42 and the contact surface 44 increases. For example, as shown in Fig. 8, when the lubricating oil lens 48B 48 ("the meniscus") in the groove 46 has a concave shape, the lubricating oil 48 cannot be used within the materialized range. by the interior space surrounded by the bold dotted line N1.

[0068] Fig. 13 shows a relationship between the groove width W1 and the depth of the surface of the oil film D2 of the lubricating oil 48 retained in the groove 46. As shown in Fig. 8, the depth of the surface of the oil film D2 is a depth of the deepest part measured from the sliding surface 42 in the concave lens 48B of the lubricating oil 48 retained in the groove 46. The deepest part appears in a central position in the range of the groove width W1.

[0069] The sliding surface 42 may be subject to a process called an oil retaining process. The oil retaining method is a method of increasing a contact angle θ2 (see Figure 8) of the lubricating oil 48 on the sliding surface 42 (including the groove 46), and the oil Lubricant 48 is readily retained on sliding surface 42 (including groove 46) by the oil retaining process. As an example, the contact angle θ2 when the oil retaining process is performed is 70 degrees, while the contact angle θ2 when the oil retaining process is not performed is 30 degrees.

As described above, the maximum value of the groove width W1 of the groove 46 can be set at 20 μm with regard to the contact surface 44 of the anchor pallet 40. In this case, as as can be seen in figure 13, the depth of the oil film surface is 2.7 µm. In other words, even when the groove depth D1 of the groove 46 is larger than 2.7 µm, lubricating oil 48 which cannot be used is generated. Taking this into account, if the upper limit value of the groove depth D1 of the groove 46 is set at 3 µm, the amount of the lubricating oil 48 which cannot be used can be reduced.

In the art of the present disclosure, the number of grooves 46 is not limited, and, for example, a single groove 46 can be formed on the sliding surface 42. In the above description, as shown in FIG. 7, although an example is given in which the direction of extension of the groove 46 is a direction along the direction of the thickness (direction arrow T1) of the exhaust mobile 26 when the surface slide 42 is seen from the front, the direction of extension of the groove 46 can be inclined relative to the direction of the thickness of the exhaust mobile 26. In addition, the depth and width of the groove 46 may not be constant along the direction of extension.

According to the technique disclosed in the context of the present invention, the method of manufacturing the exhaust mobile 26 is not limited, and the exhaust mobile 26 can be manufactured using, for example, a method of electroforming. In this case, a conductive film is formed on a surface of a silicon wafer to form a base plate, and a photoresistor layer is formed on the base plate. By forming a tapered portion corresponding to the inclination of the sliding surface 42 on the photoresistor layer, the exhaust mobile 26 having a sliding surface inclined with respect to the central axis of rotation CL-1 is obtained when the mobile exhaust 26 is manufactured by an electroforming process.

In the above description, the escapement mobile 26 is described and illustrated by way of example as a timepiece component, but such a timepiece component is not limited to such a configuration, and could consist, for example, of various gears or cams present inside the timepiece. Further, the movement is not limited to a structure including the escape mobile 26 and the anchor 28. For example, the technique of the present disclosure could be applied to a mechanism or the like for the transmission of a force of force. rotational drive meshing with a plurality of gear wheels.

Claims (7)

1. Timepiece component (22), comprising: a rotating body which rotates around a rotating shaft; a sliding surface (42) which is provided on the rotating body, is inclined with respect to a contact surface (44) of an associated member, faces said contact surface (44) and slides thereon further to the rotation of the rotating body; and one or a plurality of grooves (46) which extend on the sliding surface (42) in a direction intersecting with a sliding direction and are capable of retaining the lubricating oil (48). 2. Timepiece component (22) according to claim 1, wherein the sliding surface (42) is inclined relative to the central axis of rotation (CL1) of the rotating body. 3. Timepiece component (22) according to claim 2, wherein the angle of inclination of the sliding surface (42) in a plane (PL) including the central axis of rotation (CL1) with respect to said central axis of rotation (CL1) is between 1 degree and 5 degrees. 4. Timepiece component (22) according to one of claims 1 to 3, wherein the depth of the groove (46) vis-à-vis the sliding surface (42) is between 0.1 µm and 3.0 µm. 5. Timepiece component (22) according to one of claims 1 to 4, wherein the width of the groove (46) in a direction orthogonal to the direction in which the sliding surface (42) extends is between 1 μm and 20 μm. 6. Movement (24), comprising: the timepiece component (22) according to one of claims 1 to 5; and the associated element including the contact surface (44), in which a portion of the sliding surface (42) slides on the contact surface (44) in line contact or point contact with the contact surface (44) during rotation of the rotating body. 7. Timepiece (22), comprising: the movement (24) according to claim 6.