JP2562733Y2 - Disc spring-shaped tightening member for axial braking device - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an axial braking device for preventing relative movement between two inner and outer members which are fitted so as to be movable relative to each other in the axial direction. The present invention relates to an improvement in a conical spring-shaped tightening member.

[0002]

2. Description of the Related Art As a braking device for stopping a shaft member moving in an axial direction at a predetermined position or stopping an object moving along the shaft member at a predetermined position on the shaft member, a) a shaft member having a circular outer peripheral surface; and (b) a substantially cylindrical shape, which is disposed concentrically and axially relative to the outer peripheral side of the shaft member and has a slit in the axial direction. (C) a braking member formed so as to be reduced in diameter;
An outer cylinder member disposed on the outer peripheral side of the braking member so as to be relatively immovable in the axial direction with respect to the braking member, wherein the braking member is pressed against the outer peripheral surface of the shaft member. 2. Description of the Related Art An axial braking device that prevents relative movement between a shaft member and the outer cylindrical member is known. In addition, such an axial braking device is generally (d) disposed on the outer peripheral side of the braking member in the form of a disc spring, and elastically deformed by receiving the axial thrust to be flat. Accordingly, the inner peripheral portion is configured to include a disc spring-shaped tightening member for reducing the diameter and pressing the braking member against the shaft member. 60-11
The axial braking device disclosed in Japanese Patent No. 6433 and Japanese Utility Model Application Laid-Open No. 55705/1987 is an example of such an example, and the output rod can be stopped at an arbitrary position with respect to the cylinder body.

FIG. 7 is a front view showing an example of the above-mentioned disc spring-shaped tightening member, which has a disc spring shape and has radial cutouts 130 alternately from its inner and outer peripheral edges.
And 132 are formed at equal angular intervals. And
When such a disc spring-shaped tightening member is elastically deformed to be flat by receiving a thrust in the axial direction, its inner diameter d is reduced to d 'as shown in FIG. ′. In the conventional devices described in the above publications, the disc spring-shaped tightening member is pressed flat by the piston, but at the same time, the outer peripheral side of the disc spring-shaped tightening member is restrained by a counterbore formed in the piston. By backing up, the diameter reduction to the inner peripheral side necessary for tightening the braking member while preventing the outer diameter from expanding is sufficiently obtained.

[0004]

However, in order to back up the outer peripheral side of the disc spring-like tightening member, the counterbore hole provided in the piston or the like is made to correspond to the outer diameter of the disc spring-like tightening member. It is necessary to process with high precision the dimensional accuracy of the outer diameter and inner diameter of the disc spring-shaped tightening member itself, the concentricity between the shaft member and the counterbore, etc. so that the tightening is not uneven. Need to secure. In addition, the disc spring-shaped tightening member is disposed in the annular space between the counterbore hole and the shaft member, but since it is processed with high dimensional accuracy as described above, play is reduced. Less, and the assembly is troublesome and time-consuming.

In the above example, by pressing a braking member, which is disposed on the outer cylinder member so as to be unable to move in the axial direction relative to the axis member, against the axial member, the axial movement preventing the relative movement between the shaft member and the outer cylinder member is prevented. Although the braking device has been described, the braking member is disposed on the shaft member so as not to be relatively movable in the axial direction, and the braking member is removed via a disc spring-like tightening member disposed on the inner peripheral side of the braking member. By pressing the cylindrical member, the relative movement between the shaft member and the outer cylindrical member can be prevented. Even in this case, the same problem as described above occurs when backing up the inner peripheral portion so as to prevent the inner peripheral portion from decreasing in diameter in order to sufficiently secure the effect of expanding the diameter on the outer peripheral side of the disc spring-shaped tightening member.

The present invention has been made in view of the above circumstances, and has as its object to eliminate the need to back up the side opposite to the tightening side, and to obtain an effective tightening action as in the past. The object of the present invention is to provide a conical spring-shaped tightening member.

[0007]

In order to achieve the above object, a first means of the present invention comprises (a) a shaft member having a circular outer peripheral surface, and (b) a substantially cylindrical shape. A braking member disposed concentrically on the outer peripheral side of the shaft member so as to be relatively movable in the axial direction and having a slit formed in the axial direction to be reduced in diameter; and (c) an outer periphery of the braking member An outer cylindrical member disposed on the side of the shaft member so as to be relatively immovable in the axial direction with respect to the braking member, wherein the braking member is pressed against the outer peripheral surface of the shaft member so that the shaft member and the outer In an axial braking device that prevents relative movement with a cylindrical member, the axial braking device is formed on the outer peripheral side of the braking member in the form of a disc spring, and is elastically deformed to be flat by receiving the axial thrust. As a result, the inner peripheral portion is reduced in diameter, and the braking member is pressed against the shaft member. A disc spring shaped fastening member that,
(D) an annular outer circumferential portion having a predetermined width in the radial direction continuously in the circumferential direction; and (e) radially inward from a plurality of circumferential circumferential portions of the annular outer circumferential portion so as to form a disc spring shape. And a plurality of operating claws extending integrally with each other.

[0008]

[Operation and effect of the first means] In such a conical disk spring-shaped tightening member, when it is elastically deformed so as to be flat by receiving the thrust in the axial direction, it becomes continuously radially continuous in the circumferential direction. Since the diameter dimension hardly changes at the annular outer peripheral portion having the predetermined width, the inner peripheral portion formed by the tips of the plurality of working claws extending radially inward from the annular outer peripheral portion is formed. The diameter is reduced exclusively, whereby the braking member is pressed against the shaft member and the relative movement between the outer cylinder member and the shaft member is prevented. In this case, since the disc spring-shaped tightening member of the present invention can obtain a sufficient diameter reducing action on the inner peripheral side without back-up on the outer diameter side, high machining accuracy for restraining the outer diameter can be obtained. Necessary counterbore holes and the like are not required, and the required accuracy of the outer diameter of the disc spring-shaped tightening member and the concentricity between the inner diameter and the outer diameter are reduced. Also, since there is no need to restrain the outer diameter, when flattened, a radial pressing action occurs only on the tightening side, and the disc spring-shaped tightening member is automatically concentric with the braking member and the shaft member, Since the tightening force can be applied uniformly in the circumferential direction, and when the disc spring-shaped tightening member is assembled, it is only necessary to fit the outer peripheral side of the braking member. There is an advantage that it becomes easy.

[0009]

A second means for achieving the above object comprises (f) an outer cylindrical member having a circular inner peripheral surface, and (g) a substantially cylindrical shape. A braking member disposed concentrically on the inner peripheral side of the outer cylinder member so as to be relatively movable in the axial direction and having a slit formed in the axial direction so that the diameter can be increased; A shaft member provided on the inner peripheral side so as to be relatively immovable in the axial direction with respect to the braking member, wherein the braking member is pressed against the inner peripheral surface of the outer cylinder member so that the outer cylinder In an axial braking device for preventing relative movement between a member and the shaft member, the axial braking device is formed on the inner peripheral side of the braking member in the form of a disc spring, and becomes flat by receiving the thrust in the axial direction. By being elastically deformed, the outer peripheral portion expands in diameter and presses the braking member against the outer cylinder member. A member with the disc spring-like fastening, (i)
An annular inner peripheral portion having a predetermined width in the radial direction continuously in the circumferential direction; and (j) radially outward from a plurality of circumferential locations of the annular inner peripheral portion so as to form a disc spring shape. And a plurality of operating claws extending integrally.

[0010]

Operation and effect of the second means In such a disc spring-shaped tightening member, when it is elastically deformed to be flat by receiving the thrust in the axial direction, it is continuously radially continuous in the radial direction. Since there is almost no change in radial dimension in the annular inner peripheral portion having a predetermined width, the outer peripheral portion formed by the tips of a plurality of working claws extending radially outward from the annular inner peripheral portion. Is exclusively increased in diameter, whereby the braking member is pressed against the outer cylinder member and the relative movement between the shaft member and the outer cylinder member is prevented. In this case, since the disc spring-shaped tightening member of the present invention can obtain a sufficient diameter-expanding action on the outer peripheral side even without a backup on the inner diameter side, the shaft portion requiring high machining accuracy for restraining the inner diameter. Processing and the like are not required, and the required accuracy of the inner diameter of the disc spring-shaped tightening member and the degree of concentricity between the outer diameter and the inner diameter are reduced. Also, since there is no need to restrain the inner diameter, when flattened, a radial pressing action occurs only on the tightening side, so that the disc spring-shaped tightening member is automatically concentric with the braking member and the outer cylinder member, This makes it possible to uniformly apply the tightening force in the circumferential direction. Further, when assembling such a disc spring-shaped tightening member, it is only necessary to fit the inner circumferential side of the braking member. There is an advantage that work becomes easy.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below in detail with reference to the drawings. FIG. 1 is a cross-sectional view of an axial braking device (hereinafter simply referred to as a braking device) 10 provided with a disc spring-shaped tightening member 52 according to an embodiment of the first means of the present invention.
Numeral 12 in the figure denotes a piston rod of the air cylinder which extends to the right side of the figure and is provided at a fixed position, and corresponds to a shaft member having a circular outer peripheral surface. And the braking device 1
Numeral 0 is attached to the air cylinder to stop the piston rod 12 at an arbitrary position. The cylinder block 14, which forms the main body of the braking device 10,
A body housing 20 detachably attached to the rod cover 16 of the air cylinder, having a rectangular outer shape, and a pair of circular cylinder bores 18 formed on both sides concentrically with the piston rod 12 from both sides; And a pair of cover members 22 for covering the cover from both sides in the axial direction. A rod cover 24 is fitted on the distal end side of the cylinder block 14,
The braking device 10 is integrally fixed to the distal end side of the air cylinder by a plurality of bolts 26 and nuts 28 penetrating therethrough. The cylinder block 14 corresponds to an outer cylinder member.

In the cylinder block 14, a pair of annular pistons 30 are disposed on the outer peripheral side of the piston rod 12 so as to face each other in the axial direction. It is kept airtight and slidable in the axial direction inside the cylinder bore 18. A plurality of compression coil springs 34 are disposed between the pair of pistons 30 and extend in parallel with the axis through the inward flange 32 of the main body housing 20.
Are biased by a predetermined biasing force so as to be separated from each other. In addition, the main body housing 20, a pair of lid members 22,
The airtight state between the members of the rod covers 16, 24 and the piston rod 12 is determined by various O
Held by a ring. Further, as is apparent from FIG. 1, inside the cylinder block 14, the components are disposed symmetrically with respect to the center in the axial direction, that is, the flange portion 32. Description will be made without distinction.

On the outer peripheral side of the piston rod 12 at a position on the inner peripheral side of the pair of lid members 22, a pair of brake shoes 36 as a substantially cylindrical braking member is provided in the axial direction with respect to the lid member 22. Are displaceable relative to each other and slidable with respect to the piston rod 12.
As shown in FIG. 2, the brake shoe 36 has a slit 38 formed in the axial direction so that the diameter of the brake shoe 36 can be reduced by its own elasticity, and has a flange 40 at one end. ing. By arranging the flange 40 in the state of FIG. 1 sandwiched between the lid member 22 and the rod covers 16 and 24, the cylinder block 1
4 cannot be moved relative to the axis. The outer surface 42 of the brake shoe 36 is normally in close contact with the inner surface 44 of the lid member 22, and its own inner surface 46
And a small gap between the outer peripheral surface 48 of the piston rod 12.

The piston 30 has a counterbore 50 on the side of the lid member 22. A disc spring shape is formed in an annular space formed by the counterbore 50, the lid member 22 and the brake shoe 36. The disc spring-shaped fastening members 52 to be formed are disposed two by two in a state of being stacked in the plate thickness direction.
FIG. 3 is a front view of the disc spring-shaped tightening member 52 viewed from the axial direction, and FIG. 4 is a sectional view parallel to the axial center at the center.
As shown in FIG. 2, an annular outer peripheral portion 54 having a predetermined width a in the radial direction continuously in the circumferential direction while forming a disk spring shape having a linear conical slope as a whole, and the annular outer peripheral portion A plurality of (12 in this embodiment) working claws 56 extend integrally and inward in the radial direction so as to form a disc spring shape from a plurality of locations in the circumferential direction of 54. The disc spring-shaped tightening member 52 is made of a metal elastic material such as carbon steel for a spring, and may buckle the working claw 56 in a tightened state in which a radial compressive stress is generated. It is provided with a predetermined strength so as not to be affected. The inner diameter d ₁ of the inner peripheral portion of the disc spring-shaped tightening member 52, that is, the inner diameter d ₁ of the distal end portion of the action claw portion 56 is substantially the same as the outer diameter of the brake shoe 36. The dimensional tolerance is determined in advance so as to obtain a fit in the state, while the outer diameter D ₁ of the annular outer peripheral portion 52 is determined to be smaller by a predetermined amount than the inner diameter of the counterbore 50 of the piston 30. I have. Then, in a state where the disc spring shaped fastening member 52 is brought into flat elastically deformed is挾圧axially, changes annular outer peripheral portion almost outside diameter D ₁ in 54 does not occur exclusively plurality of Working claw 52
Is uniformly bent to reduce the inner diameter d ₁ of the inner peripheral end portion.

The cylinder block 14 has a pair of pressure chambers 60 formed between a pair of pistons 30 and a pair of pressure chambers 6 formed between the piston 30 and the lid member 22.
2 is provided with a connection port (not shown) for guiding the compressed air to the air source 64.
Or 70 via pressure chambers 60 or 6 respectively.
Alternatively, the pressure air is supplied to the second air supply.
The switching valve 66 normally keeps the pipe 68 in communication with the air source 64 and keeps the pipe 70 open to the atmosphere. And the air source 64 and the pipe 68 is released to the atmosphere. Note that, as the air source 64, an air source for operating the air cylinder to which the braking device 10 is attached may be used.

In the normal state shown in FIG. 1, since air pressure acts on the pressure chamber 60 and the pressure chamber 62 is kept at the atmospheric pressure, the piston 30 generates a thrust in the axial direction on the pressure chamber 62 side. The disc spring-like fastening member 52 is pressed between the cover member 22 and the spring. In this state, the disc spring-shaped tightening member 52
Is elastically deformed flat and its inner peripheral portion (the action claw portion 56
Of the brake shoe 36).
Is pressed against the outer peripheral surface 48 of the piston rod 12. As a result, the movement of the piston rod 12 in the axial direction is prevented, so that the braking device 10 is maintained in the braking state in the normal operation state of the compressed air. On the other hand, when the switching valve 66 is switched, the air pressure acts on the pressure chamber 62 and the pressure chamber 60 is brought to the atmospheric pressure. 32, and the clamped state of the disc spring-shaped tightening member 52 with the lid member 22 is released. In this state, the disc spring-shaped tightening member 52 is returned to its original shape by its own elasticity, and its inner peripheral portion is expanded until the inner diameter d ₁ is reached.
The pressing of the piston rod 12 against the outer peripheral surface 48 of the piston rod 12 is released, and the axial movement of the piston rod 12 is allowed. When the switching valve 66 is switched in this way, the braking device 10 is kept in a non-braking state.

Here, in a situation where the brake device 10 is in the braking state as described above and the conical spring-like tightening member 52 is elastically deformed flat and the inner peripheral portion is reduced in diameter, the circumferential outer peripheral portion is reduced. In the case of No. 54, there is almost no change in the diameter and the size of the working claw 5
6 is reduced in diameter at the inner peripheral portion, compared with the case of using the disc spring-shaped tightening member shown in FIG. On the side, a sufficient diameter reducing action is obtained. Therefore, it is sufficient to the seat Guriana 50 somewhat larger than the outer diameter D ₁ of the disc spring-like fastening member, that a high machining accuracy for restraining an outer diameter D ₁ during its machining is required And the outer diameter D ₁ itself and the inner diameter d ₁
Required accuracy is reduced also such concentricity between the outer diameter D ₁ and. In addition, since the outer peripheral side is not restrained and a radial pressing action occurs only on the inner peripheral side, the disc spring-shaped tightening member 52 automatically becomes concentric with the brake shoe 36 and the piston rod 12 when the flat plate is flat. The centering action is obtained, and the tightening force can be uniformly applied in the circumferential direction.
Further, since the mating relationship is required only with the outer diameter of the brake shoe 36, when the disc spring-shaped tightening member 52 is assembled, only the fitting to the brake shoe 36 is required. It becomes easy.

Next, an embodiment according to the second means of the present invention will be described. An axial braking device (hereinafter simply referred to as a braking device) 80 whose partial cross section is shown in FIG. 5 stops an outer cylinder member 82 at an arbitrary position with respect to a shaft member 84. In the drawing, the shaft member 84 fixed to the position is fitted on the outer peripheral side of the shaft member 84 from both sides of the large diameter portion 86 and the shaft member 8 is fitted.
First intermediate member 8 that is not movable in the axial direction with respect to
8, the second intermediate member 90, and the third intermediate member 91 are integrally provided. An annular piston 94 is slidably provided between the first intermediate member 88 and the second intermediate member 90 in a circular cylinder bore 92 formed in the first intermediate member 88 and the large diameter portion 86. Has been established,
A brake shoe 98 as a braking member is fixed to the outer peripheral side of the second intermediate member 90 so as to be slidable with respect to the circular inner peripheral surface 96 of the outer cylinder member 82. In the annular space between the two, two disc spring-shaped fastening members 100 are arranged so as to overlap in the plate thickness direction. Also,
Outer cylinder member 82, first intermediate member 88, second intermediate member 90,
The airtight state between the third intermediate member 91, the shaft member 84, and the piston 94 is determined by various O
Held by a ring.

The brake shoe 98 has a substantially cylindrical shape, and has a slit (not shown) formed in the axial direction similarly to the brake shoe 36. The slit can be expanded by being pressed from the inside. , One end is provided with an inward flange 102. The flange 102 is disposed between the step portion 104 of the second intermediate member 90 and the third intermediate member 91 in the state shown in FIG. It is considered impossible. Normally, the inner peripheral surface 106 of the brake shoe 98 is in close contact with the outer peripheral surface 108 of the second intermediate member 90, and a minute space is formed between the outer peripheral surface 110 of the brake shoe 98 and the inner peripheral surface 96 of the outer cylinder member 82. It has a gap.

The disk spring-shaped tightening member 100 has a disk spring shape having a linear conical slope as a whole, and as shown in FIG.
An annular inner circumferential portion 112 having a predetermined width b in the radial direction continuously in the circumferential direction, and radially outward from a plurality of circumferential locations of the annular inner circumferential portion 112 so as to form a disc spring shape. It has a plurality of (18 in this embodiment) working claws 114 extending integrally. The disc spring-shaped fastening member 100 is also made of the same metal elastic material as the disc spring-shaped fastening member 52, and has a predetermined strength so that the working claw portion 114 does not buckle in the tightened state. Provided.
Outer peripheral portion of the disc spring-shaped tightening member 100, that is, the action claw portion 1
Outer diameter D ₂ at the distal portion of the 14, wherein has substantially been the same size as the inner diameter of the brake shoe 98, in advance dimensional tolerances as for example fitting a negligible clearance fit state is obtained are determined On the other hand, the annular inner peripheral portion 1
The inner diameter dimension d ₂ of the piston 12 is determined to be larger than the outer diameter of the small diameter portion 115 of the piston 94 by a predetermined amount. In the state where the disc spring-shaped fastening member 100 is pressed in the axial direction and is elastically deformed flat, the inner diameter dimension d ₂ hardly changes in the annular inner peripheral portion 112, and only a plurality of inner diameter portions d ₂ are formed. The working claw 114 is bent, and the outer diameter D due to the tip of the outer peripheral portion thereof
₂ is expanded.

The piston 94 is urged by a compression coil spring 116 provided in the first intermediate member 88 toward the second intermediate member 90 with a predetermined urging force. In the first pressure chamber 118 and the second pressure chamber 120 formed between the first intermediate member 88 and the second intermediate member 90, respectively, pressure air is supplied through passages 122 and 124 formed inside the shaft member 84. It is supplied as an alternative. In the state shown in FIG. 5, air pressure is applied to the pressure chamber 118, and the piston 94 presses the disc spring-shaped tightening member 100 with the second intermediate member 90 to apply a thrust in the axial direction. Let me. In this state, the disc spring-shaped tightening member 100 is elastically deformed flat and its outer peripheral portion (the tip side of the action claw portion 114) is enlarged in diameter, so that the brake shoe 98 is attached to the inner peripheral surface 96 of the outer cylinder member 82. Pressed to. This allows
The braking device 80 is held in a braking state that prevents the outer cylinder member 82 from moving in the axial direction. On the other hand, when the supply state of the compressed air is switched and the air pressure is applied to the pressure chamber 120, the piston 94 is moved toward the first intermediate member 88 against the urging force of the compression coil spring 116, and the disc spring The clamping state of the clamp member 100 is released. In this state, the disc spring-shaped tightening member 100 is returned to its original shape and its outer peripheral portion is reduced in diameter until the outer diameter D ₂ is reached. 9
6 is released, and the outer cylinder member 82 is brought into a non-braking state in which movement in the axial direction is permitted.

Here, when the braking device 80 is in the above-described braking state and the conical spring-shaped tightening member 100 is elastically deformed flat and its outer peripheral portion expands in diameter, the annular inner peripheral portion 112 In this case, the diameter dimension hardly changes, and the outer peripheral portion of the action claw portion 114 is exclusively enlarged, so that the diameter is larger than that in the case of using the disc spring-shaped tightening member shown in FIG. Thus, a sufficient diameter-expanding effect can be obtained on the outer peripheral side even if there is no backup on the inner peripheral side. Thus, for example, with high processing accuracy is not required to restrain the inner diameter d ₂ of the disc spring shaped fastening member during processing of the small-diameter portion 115, an inner diameter d ₂ itself and the inner diameter d
Required accuracy is reduced also such concentricity between ₂ and outer diameter D _2. Further, the inner diameter d ₂ since there is no need to constrain, flattened upon disc spring shaped fastening member 100 is a brake shoe 98 further is automatically concentric with the outer cylindrical member 82, the clamping force in the circumferential direction In addition, when the disc spring-shaped tightening member 100 is assembled, it only has to be fitted on the inner peripheral side of the brake shoe 98, so that the assembling work is facilitated. It is.

Although the embodiment of the present invention has been described in detail with reference to the drawings, the present invention can be implemented in other modes.

For example, in each of the above-described embodiments, a predetermined width a in the radial direction of the annular outer peripheral portion 54 of the disc spring-shaped tightening member 52 and a diameter of the annular inner peripheral portion 112 of the disc spring-shaped tightening member 100 are determined. The predetermined width b in the direction can be arbitrarily determined, and the number and shape of the working claws 56 and 114 can be appropriately changed.

In addition, the disc spring-shaped tightening members 52 and 100 in each of the above-described embodiments have a disc spring shape having a straight conical slope, but the conical slope has a positive or negative curvature. It may have a given disc spring shape.

In each of the above-described embodiments, the braking devices 10 and 80 are both fixedly disposed. However, the piston rod 12 and the outer cylinder member 82 are fixedly disposed. In addition, a configuration may be adopted in which the braking devices 10, 80, and the like are provided so as to be movable with respect to them, and the movements thereof are prevented and allowed.

Also, in each of the above-described embodiments, the disc spring-shaped tightening member 52 is provided with a predetermined gap in the counterbore 50 of the piston 30 and the piston 9
4, the disc spring-shaped tightening member 100 is provided with a predetermined gap in the outer peripheral space of the small diameter portion 115.
The gap in each of the above cases is not necessarily required, and the counterbore 50 and the small diameter portion 115 can be omitted.

In the embodiment of FIG. 1 described above,
The driving of the pair of pistons 30 causes the piston rod 12
Is braked, but it is also possible to brake the piston rod 12 with only one of the pistons 30.

In each of the above-described embodiments, the air pressure is applied to the pressure chamber 60 or the first pressure chamber 118 to obtain the braking state.
To generate thrust in the axial direction on the pistons 30, 94. However, the compression coil springs 34, 1 generate an urging force enough to obtain a desired thrust.
By arranging 16 or the like, it is also possible to omit the supply of the pressure air for bringing into the braking state.

Although not specifically exemplified, the present invention can be implemented in various modified and improved modes based on the knowledge of those skilled in the art.

[Brief description of the drawings]

FIG. 1 is a diagram showing a cross section and a pneumatic circuit configuration of an axial braking device including a disc spring-shaped tightening member of FIG. 3;

FIG. 2 is a front view of a braking member in the axial braking device of FIG. 1;

FIG. 3 is a front view of the disc spring-shaped tightening member according to the first embodiment of the present invention, as viewed from the axial direction;

FIG. 4 is a central sectional view of the disc spring-shaped fastening member of FIG. 3;

FIG. 5 is a partial sectional view showing a main part of an axial braking device provided with the disc spring-shaped tightening member of FIG. 6;

FIG. 6 is a front view of the disc spring-shaped tightening member as one embodiment according to the second means of the present invention, as seen from the axial direction.

FIG. 7 is a diagram illustrating an example of a conventional disc spring-shaped tightening member.

FIG. 8 is a view for explaining deformation characteristics of the disc spring-shaped tightening member of FIG. 7;

[Explanation of symbols]

 10: Axial braking device 12: Piston rod (shaft member) 14: Cylinder block (outer cylinder member) 36: Brake shoe (braking member) 38: Slit 48: Outer peripheral surface 52: Belleville spring-like tightening member 54: Annular Outer peripheral portion 56: Working claw portion 80: Axial braking device 82: Outer cylinder member 84: Shaft member 96: Inner peripheral surface 98: Brake shoe (braking member) 100: Belleville spring-like tightening member 112: Annular inner peripheral portion 114: Working claw

Claims (2)

(57) [Scope of request for utility model registration] 1. A shaft member having a circular outer peripheral surface, and a substantially cylindrical shape disposed concentrically on the outer peripheral side of the shaft member so as to be relatively movable in the axial direction, and a slit in the axial direction. A braking member formed to be able to be reduced in diameter, and an outer cylinder member disposed on an outer peripheral side of the braking member so as to be incapable of relative movement in the axial direction with respect to the braking member; Is pressed against the outer peripheral surface of the shaft member to prevent relative movement between the shaft member and the outer cylindrical member. A coned disc spring-shaped fastening member that receives the thrust in the axial direction and is elastically deformed so as to be flattened so that an inner peripheral portion is reduced in diameter and presses the braking member against the shaft member. An annular outer peripheral portion having a predetermined width in the radial direction continuously in the circumferential direction; A plurality of working claws extending integrally inward in a radial direction so as to form a disc spring shape from a plurality of circumferential locations of the outer peripheral portion of the disc-shaped outer peripheral portion. Attached member. 2. An outer cylindrical member having a circular inner peripheral surface, and a substantially cylindrical shape disposed concentrically on the inner peripheral side of the outer cylindrical member so as to be relatively movable in the axial direction. A braking member having a slit formed in the center direction and capable of expanding in diameter; and a shaft member disposed on the inner peripheral side of the braking member so as to be immovable relative to the braking member in the axial direction. An axial braking device for preventing the relative movement between the outer cylinder member and the shaft member by pressing the braking member against the inner peripheral surface of the outer cylinder member; The inner peripheral side of the spring is deformed elastically so as to become flat by receiving the thrust in the axial direction, so that the outer peripheral portion expands in diameter and presses the braking member against the outer cylindrical member. A fastening member, an annular inner peripheral portion having a predetermined width in a radial direction continuously in the circumferential direction; A plurality of working claws extending integrally outward in the radial direction so as to form a disc spring shape from a plurality of circumferential locations of the annular inner peripheral portion; Spring-like fastening member.