JP2011179682A - Fastening member and fastening method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fastening member prevented from being damaged due to metal fatigue even when a large impact or vibration is repeatedly applied to a fastening part using the fastening member of a nut and a bolt, hardly becoming loose attaining extremely stable fastening and fixing, and furthermore simple in constitution and easily used and manufactured. <P>SOLUTION: The fastening member 1 includes the bolt 10 and the nut 20 and fastens fastened bodies 30, 31. The bolt 10 is provided, on at least one side, with a taper part 12 enlarged in diameter toward the end, integrally with or separately from the bolt 10. The nut 20 is slidably brought into pressure contact with and locked to the taper part 12. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a fastening member and a fastening method using the fastening member.

  As a fastening member used for fastening and fixing parts and members, nuts and bolts for fastening a body to be fastened by a screw action have been widely used in various fields. These nuts and bolts are for fastening and fixing parts and members, but there is a problem that the nuts and bolts loosen when vibrations and impacts repeatedly act on these fastening parts. For the purpose, a flat washer or a spring washer has been conventionally used. In addition, parts in which an adhesive or the like is applied to the threads of these fastening members are also used.

  A nut with a washer (see Patent Literature 1 and Patent Literature 2) for the purpose of preventing the nut and bolt from loosening, a nut with a partially tapered inner surface (see Patent Literature 3), or a washer The thing of the structure attached to the nut integrally (refer patent document 4) etc. is proposed. In addition, a method of tightening and fixing by a double nut method, for example, a configuration in which two nuts are fitted with a tapered surface, and one tapered surface is eccentric with respect to the shaft core and tightened firmly by a wedge action (Patent Document) 5) has been proposed.

JP 2002-122120 A JP-A-9-72325 JP-A-3-26817 Japanese Patent Laid-Open No. 9-53628 Japanese Patent Laid-Open No. 9-42259

  However, conventional nuts with washers and double nuts have a certain loosening-preventing action, but when large vibrations or impacts are repeatedly applied to the tightening part of the nut or bolt, the tightening part tends to loosen. There was a problem. In addition, when the nut is processed to prevent loosening, there is a problem that the processing becomes complicated. In addition, there were many phenomena that metal fatigue accumulated on the bolts due to excessive tightening or repeated tightening, resulting in breakage.

  Therefore, the present invention has been made to solve these problems, and the purpose of the present invention is that even when a large impact or vibration is repeatedly applied to a tightening portion using a nut or bolt fastening member. Another object of the present invention is to provide a fastening member that can prevent breakage due to metal fatigue, that is very stable and that can be fastened and fixed, and that is simple in structure and easy to use and manufacture.

  The present invention solves the above-described problems by the solving means described below.

  The fastening member is a fastening member that includes a bolt and a nut and fastens the body to be fastened, and the bolt has at least one end side, and a tapered portion that expands toward the end portion is integral with or separate from the bolt. The nut is provided on the body, and the nut is required to be slidably pressed and locked to the tapered portion.

  According to the present invention, a member can be securely fastened without requiring strong tightening, and can be suitably used as a fastening member having an action of preventing loosening, dropping, and fatigue destruction. Further, since the fastening member according to the present invention is provided as an extremely simple structure, it has remarkable effects such as ease of use and easy manufacture.

It is the schematic which shows the example of the fastening member which concerns on 1st embodiment of this invention. It is the schematic which shows the example of the volt | bolt of the fastening member of FIG. It is the schematic which shows the example of the nut of the fastening member of FIG. It is the schematic which shows the modification of the nut of the fastening member of FIG. It is the schematic which shows the example of the nut of the fastening member which concerns on 2nd embodiment of this invention. It is the schematic which shows the example of the fastening member which concerns on 3rd embodiment of this invention. It is the schematic which shows the example of the fastening member which concerns on 4th embodiment of this invention. It is the schematic which shows the example of the volt | bolt of the fastening member which concerns on 5th embodiment of this invention. It is the schematic which shows the example of the nut of the fastening member which concerns on 5th embodiment of this invention. It is the schematic which shows the example of the fastening member which concerns on 6th embodiment of this invention. It is the schematic which shows the example of the taper member of the fastening member of FIG. It is the schematic which shows the example of the nut of the fastening member of FIG. It is the schematic which shows the example of the fastening member which concerns on 7th embodiment of this invention. It is the schematic which shows the example of the taper member of the fastening member of FIG.

DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, preferred embodiments of the invention will be described in detail with reference to the accompanying drawings.
The schematic explaining the example of the fastening member 1 which concerns on 1st embodiment of this invention is shown in FIG. FIG. 1 is a cross-sectional view showing a state in which a fastened body 30 and a fastened body 31 are fastened using the fastening member 1. Here, the fastening member 1 includes a bolt 10 and a nut 20. Furthermore, the schematic of the volt | bolt 10 which concerns on this embodiment is shown to Fig.2 (a) (front view (upper half sectional view)) and FIG.2 (b) (side view). The bolt 10 has a circular cross section and is not provided with a thread. Moreover, the schematic of the nut 20 which concerns on this embodiment is shown to Fig.3 (a) (front sectional drawing) and FIG.3 (b) (side view). The nut 20 is not provided with a thread. The bolt 10 and the nut 20 are formed using a metal material or a resin material.

The fastening member 1 in this embodiment is provided with retaining mechanisms 2 and 3 on both ends of the bolt 10. The retaining mechanism 2 provided on one end side (the right end side in FIG. 1) of the bolt 10 includes a nut mounting portion 11 provided on the bolt 10 and a nut 20 locked to the nut mounting portion 11. Composed. Furthermore, the nut mounting portion 11 is a taper in which the cross-sectional area of the cross section perpendicular to the axial direction of the bolt 10 gradually increases toward the end portion 10a (that is, the direction from the end portion 10b to the end portion 10a in FIG. 1). Part 12. The nut 20 is provided with a pressing force generation means described later and is slidably locked to the tapered portion 12.
Here, the nut 20 is formed in a shape having an outer dimension (here, the outer diameter) larger than the inner dimension (here, the inner diameter) of the through hole 31a of the joined body (here, the coupled body 31) that abuts. ing. As a result, as shown in FIG. 1, it is possible to prevent the fastened body 31 from coming off.
In addition, from the above, the length of the bolt 10 is such that when all the fastened bodies are in a predetermined fastening state, the nut mounting portion 11 is the end of the fastened body (here, the fastened body 31 at the right end). It is necessary to set so as to be arranged outward from the portion 31b (to the right from the end face 31b in FIG. 1).
It is preferable to set the dimensions and positions of each member in consideration of tolerances so that the nut 20 and the tapered portion 12 are in surface contact.

  On the other hand, the retaining mechanism 3 provided on the other end side (left end side in FIG. 1) of the bolt 10 is a bolt head portion 13 of the bolt 10. The bolt head portion 13 of the present embodiment is substantially disk-shaped and has an outer dimension (here, outer diameter) larger than the inner dimension (here, inner diameter) of the through hole 30a of the fastened body 30. According to this, the bolt head part 13 has the function of preventing the fastened body 30 from coming off. The bolt head portion 13 is not limited to a substantially disc shape, and various shapes such as a square shape and a hexagon shape can be adopted.

In this manner, the bolt 10 is inserted into the through hole 30a provided in the fastened body 30 and the through hole 31a provided in the fastened body 31, and the retaining mechanism 2 (here, the nut mounting portion 11 and the nut mounting portion 11 is connected to the nut mounting portion 11). A plurality of fastened bodies 30 and 31 (the fastened bodies are not limited to two) are sandwiched from both sides by the nut 20 to be locked and the retaining mechanism 3 (here, the bolt head portion 13). The action of tightening occurs.
Therefore, in the present embodiment, the maximum outer dimension of the nut mounting portion 11 (here, the maximum outer diameter of the tapered portion 12) is the inner dimension of the through holes 30a and 31a (here, so that the bolt 10 can be inserted). Smaller than the inner diameter).

Moreover, in this embodiment, as shown in FIG. 1, the taper part 12 is inside (end surface in FIG. 1) inside end surface 31b of the to-be-fastened body (here to-be-fastened body 31) of the said taper part 12 side. The starting end of the tapered shape is located on the left side of 31b, and is tapered outward (to the right of end surface 31b in FIG. 1) outside end surface 31b of the fastened body (fastened body 31 in this case). It is formed in a shape where the end is located.
According to this, even when deformation that extends in the axial direction occurs in the bolt 10 or when deformation that contracts in the axial direction occurs in the fastened bodies 30 and 31, the effect of the configuration of the tapered portion 12 and the nut 20 is achieved. The effect (details will be described later) can be maintained.

  Next, as shown in FIG. 1, the nut 20 according to the present embodiment is pressed and locked to the tapered portion 12 of the nut mounting portion 11. At this time, the inner surface 20d of the nut 20 and the tapered portion 12 are in contact (pressure contact) with each other so as to be slidable. In addition, in the nut 20 according to the present embodiment, the contact portion (here, the inner surface 20d) with the tapered portion 12 is formed in a tapered shape having the same inclination angle as the tapered shape of the tapered portion 12 ( (Refer FIG.1, FIG.3 (a) and FIG.3 (b)). Note that the inner surface 20d is not limited to a tapered shape, and for example, a surface shape such as a curved shape, a straight line shape parallel to the axis line, or the like is employed when viewed in the cross-sectional view of FIG. It is also possible.

As a characteristic configuration of the nut 20 according to this embodiment, the nut 20 is formed of two or more members (here, two members 20a and 20b) made of a metal material or a resin material, and is slidable on the tapered portion 12. Pressure contact force generating means for press-contacting and locking is provided. In this embodiment, the urging member 22 is provided as the pressure contact force generating means. As an example, the urging member 22 is configured using a torsion coil spring.
Further, the member 20a and the member 20b are fixed to each other by a pin 23 so as to be freely rotatable, and each of the members 20a and 20b is configured to be rotatable in the direction of an arrow in FIG. At that time, the member 20a and the member 20b are urged by the urging member 22 in a direction in which the substantially circular space 20c formed at the center is reduced (that is, a direction in which the inner diameter is reduced). This urging force causes the nut 20 to sandwich the tapered portion 12 like a clip (to sandwich the taper in a direction orthogonal to the axial direction), that is, an operation to be pressed and locked to the tapered portion 12.

  As a modification, as shown in FIG. 4A (front sectional view) and FIG. 4B (side view), a member 20a and a member 20b are connected to a plurality of biasing members 22 (here, two pulling members). A configuration in which the coil springs 22a and 22b) are connected is also conceivable.

  As described above, according to the fastening member 1 in the present embodiment, the nut 20 sandwiches the tapered portion 12 like a clip by the pressure contact force generated by the pressure contact force generation unit, that is, the biasing force generated by the biasing member 22, that is, The action of being pressed and locked to the taper portion 12 occurs. The pressure contact force, that is, the urging force, causes the inner diameter 20d of the nut 20 to move on the tapered surface of the tapered portion 12 from the larger diameter portion to the smaller diameter portion in order to reduce the diameter of the substantially circular space portion 20c of the nut 20. An action of sliding in a direction (a direction from the right side to the left side in FIG. 1) is generated. That is, the nut 20 has an action of moving in the direction from the large diameter portion to the small diameter portion (the direction from the right side in FIG. 1 toward the left side) while being pressed against the taper portion 12. As a result, the nut 20 pushes the fastened body 31 toward the fastened body 30 (in the direction from the right side to the left side in FIG. 1), so that the above-described retaining mechanism 3 (bolt head 13) The to-be-fastened body 30 and the to-be-fastened body 31 are fastened by pinching.

  On the other hand, since the action of expanding the diameter of the substantially circular space 20c of the nut 20 is suppressed by the pressing force, that is, the urging force that always presses the nut 20 against the tapered portion 12, the inner surface 20d of the nut 20 The action of sliding on the tapered surface in the direction from the small diameter portion to the large diameter portion (the direction from the left side to the right side in FIG. 1) is suppressed. That is, the action of the nut 20 moving in the direction from the small diameter portion to the large diameter portion of the taper portion 12 (the direction from the left side to the right side in FIG. 1) is suppressed, and thus the fastened body 30 and the fastened body 31 The effect of preventing loosening in fastening is achieved.

In addition, as described above, in the case of the conventional fastening member, there is a problem that when the impact or vibration is repeatedly applied to the tightening portion of the nut or bolt, there is a problem that the tightening portion is easily loosened, and the tightening is further strengthened. If it became, the subject of the metal fatigue and destruction resulting from the impact and the vibration had arisen.
However, according to the fastening member 1 in the present embodiment, the inner surface 20d of the nut 20 moves from the large diameter portion on the tapered surface of the tapered portion 12 as the impact / vibration assumed in a normal use environment is applied. The action of sliding in the direction toward the small diameter portion is promoted. This is an operational effect obtained by a configuration in which the nut 20 is always pressed against the tapered portion 12 having a tapered shape. Although this effect is apparent from experience, as a phenomenon, the impact force / vibration force is a static state where the contact state between the inner surface 20d of the nut 20 and the tapered surface of the tapered portion 12 is governed by the static friction coefficient. Therefore, it is considered that the sliding action controlled by the dynamic friction coefficient causes the sliding action on the taper surface due to the component force in the taper surface direction of the pressure contact force of the nut 20. As a result of such an action, the action of the nut 20 moving in the direction from the large diameter part to the small diameter part of the taper part 12 is promoted, so that the fastening force generated in the axial direction of the bolt 10 (by the retaining mechanisms 2 and 3). The force between the fastened body 30 and the fastened body 31 can be increased, and the fastened state between the fastened body 30 and the fastened body 31 is more stable (they are securely fastened and have no looseness). State).
Thus, it can be said that the effect of stabilizing the fastening by the external force such as impact / vibration, which has been an adverse element of the prior art, is a remarkable effect peculiar to the fastening member in the present invention.
In addition, in order to reduce the friction coefficient at the time of sliding, you may lubricate the contact location between the inner surface 20d of the nut 20, and the taper surface of the taper part 12. FIG.

Then, the fastening method which fastens using the fastening member 1 in this embodiment is demonstrated using FIG.
As a procedure, first, the fastened body 30 and the fastened body 31 are arranged at a predetermined fastening position, and the through hole 30a and the through hole 31a are matched. Next, the bolt 10 is inserted into the through hole 30a and the through hole 31a from the end 13a.

Next, the nut 20 is pressed and locked to the taper portion 12 of the nut mounting portion 11 so that the retaining mechanism 2 is in a predetermined assembled state (see FIG. 1).
Even in this state, the drop-off preventing mechanisms 2 and 3 can prevent the fastened body 30 and the fastened body 31 from falling off, so that the fastening method may be terminated in this step.

As the next step, the bolt 10 is impacted by, for example, hitting the bolt head portion 13 with a tool such as a hammer lightly. As a result, as described above, the action of the nut 20 moving in the direction from the large diameter portion of the taper portion 12 toward the small diameter portion is promoted. Therefore, the fastening force generated in the axial direction of the bolt 10 (with the retaining mechanisms 2 and 3). The force between the fastened body 30 and the fastened body 31 can be increased, and the fastened state between the fastened body 30 and the fastened body 31 is more stable (they are securely fastened and have no looseness). State).
As another method, vibration may be applied to the bolt 10 by connecting or abutting vibration generating means (not shown) to the bolt head portion 13. A method of giving an impact or vibration to the nut 20 instead of (or together with) the bolt 10 is also conceivable.
Alternatively, instead of a method of artificially applying an impact or vibration to the bolt 10 or the nut 20, a method of directly using an external force received from the external environment at the time of use can be considered.

Then, the fastening member 1 which concerns on 2nd embodiment of this invention is demonstrated (refer FIG. 5).
The fastening member 1 according to this embodiment has the same basic configuration as that of the first embodiment described above, and is different in the structure of the nut 20. Therefore, the difference will be mainly described.

As shown in FIG. 5A (front sectional view) and FIG. 5B (side view), the nut 20 according to the present embodiment is formed in a C shape or a U shape using a metal material or a resin material. It is formed as an integral member. Further, the inner dimension (herein, the inner diameter of the substantially circular space portion 20c) of the contact portion with the taper portion 12 is set so that the taper portion 12 can be press-fitted and locked within the elastic deformation region of the material used. Is formed smaller than the outer dimension (here, the minimum outer diameter in the assumed use area of the tapered portion 12).
That is, in the nut 20 according to the present embodiment, the pressing force generating means for slidably pressingly locking the tapered portion 12 is deformed (expanded diameter) in the elastic deformation region when fitted to the tapered portion 12. It is a restoring force that attempts to return to its original shape.
As in the first embodiment described above, the inner surface 20d of the nut 20 is tapered.

  The effect of the fastening member 1 according to the present embodiment is basically the same as that of the first embodiment described above. In particular, since the nut 20 according to the present embodiment has a simple structure, it is easy to use and manufacture, and the manufacturing cost can be reduced.

Next, the fastening member 1 according to the third embodiment of the present invention will be described (see FIG. 6).
The fastening member 1 according to this embodiment has the same basic configuration as that of the first embodiment described above, and is different in the structure of the bolt 10. Therefore, the difference will be mainly described.

As shown in the schematic diagram of FIG. 6, the bolt 10 according to the present embodiment includes an O-ring 14 as a retaining mechanism 3 provided on the other end side (left end side in FIG. 1) of the bolt 10. is there. In the present embodiment, in the state where the O-ring 14 is mounted in the circumferential groove 15 of the bolt 10, the outer dimension (here, the outer diameter) of the O-ring 14 is the inner dimension of the through hole 30 a of the fastened body 30 ( Here, the configuration is larger than the inner diameter). As a result, as shown in FIG. 6, the fastened body 30 can be prevented from coming off. As an example, the O-ring 14 is configured using a rubber material.
As a modification, instead of the O-ring 14, a C-ring (not shown) made of a metal material or a resin material may be provided.

  The effect of the fastening member 1 according to the present embodiment is basically the same as that of the first embodiment described above. In particular, unlike the first embodiment described above, the bolt 10 according to the present embodiment does not have a bolt head portion, and thus can be inserted into the through holes 30a and 31a from the end portion 10b side. Become. Accordingly, as shown in FIG. 6, the maximum outer dimension of the nut mounting portion 11 (here, the maximum outer diameter of the tapered portion 12) is formed larger than the inner dimension (here, the inner diameter) of the through holes 30a and 31a. Therefore, effects such as improvement in the degree of freedom in designing the taper angle or improvement in the strength of the nut mounting portion 11 can be obtained.

Then, the fastening member 1 which concerns on 4th embodiment of this invention is demonstrated (refer FIG. 7).
The fastening member 1 according to this embodiment has the same basic configuration as that of the first embodiment described above, and is different in the structure of the bolt 10 and the nut 20. Therefore, the difference will be mainly described.

  As shown in the schematic diagram of FIG. 7, the bolt 10 according to the present embodiment has a shape in which the taper angle of the taper portion 12 is larger than that of the first embodiment described above. Moreover, the shape where the start end of the said taper shape is located outside the end surface 31b of the to-be-fastened body (here to-be-fastened body 31) by the side of the said taper part 12 (right side rather than the end surface 31b in FIG. 1). Have.

  Further, the nut 20 according to this embodiment can have the same basic configuration as the first embodiment or the second embodiment described above. However, as a difference, it has a structure in which not the inner surface 20d but the end surface 20e is brought into contact (pressure contact) with the bolt 10 and locked. Therefore, in the present embodiment, the shape of the end surface 20 e is formed into a tapered shape having the same inclination angle as the tapered shape of the tapered portion 12. In addition, a gap is formed between the inner surface 20 d of the nut 20 and the outer peripheral surface of the bolt 10.

  The effect of the fastening member 1 according to the present embodiment is basically the same as that of the first embodiment described above. In particular, since the taper angle (inclination angle) of the taper portion 12 and the corresponding taper angle (inclination angle) of the nut 20 can be increased, the diameter of the nut 20 can be prevented from expanding even for a larger impact. It is possible to exert a strong loosening prevention effect.

Then, the fastening member 1 which concerns on 5th embodiment of this invention is demonstrated (refer FIG. 8, FIG. 9).
The fastening member 1 according to this embodiment has the same basic configuration as that of the first embodiment described above, and is different in the structure of the bolt 10 and the nut 20. Therefore, the difference will be mainly described.

  As shown in the schematic diagram of FIG. 8, the bolt 10 according to the present embodiment has a rectangular cross-sectional shape. 8A is a front view (upper half sectional view), FIG. 8B is a side view, and FIG. 8C is a sectional view taken along the line DD in FIG. 8A. Note that, as a premise for using the bolt 10 according to the present embodiment, it is needless to say that the through holes 30a and 31a in the fastened bodies 30 and 31 need to have a rectangular shape through which the bolt 10 can be inserted.

  Further, as shown in FIG. 9A (front sectional view) and FIG. 9B (side view), the nut 20 according to the present embodiment is basically the same as the embodiment shown in FIG. The same can be done. However, the difference is that the inner surface 20d that comes into contact with the bolt 10 is linearly formed.

  The effect of the fastening member 1 according to the present embodiment is basically the same as that of the first embodiment described above. In particular, since the cross-sectional shape of the bolt 10 is rectangular, an effect that the fastened bodies 30 and 31 do not rotate with respect to the bolt 10 is obtained. Therefore, in the case of a fastening structure in which only one fastening portion using the fastening member 1 is provided, it is possible to obtain an effect that the fastened body 30 and the fastened body 31 do not rotate relative to each other.

Then, the fastening member 1 which concerns on 6th embodiment of this invention is demonstrated (refer FIG. 10).
The fastening member 1 according to the present embodiment includes a taper portion 12 whose cross-sectional area gradually increases toward the end portion on one end side (the right end side in FIG. 10) of the bolt 10 as the nut mounting portion 11 of the bolt 10. This is an example provided separately from the bolt 10. That is, the taper portion 12 is formed on the taper member 16 fixed to the bolt 10.
In addition, regarding the present embodiment, the basic technical idea is the same as that of the other embodiments, and therefore, the difference in configuration will be mainly described.

  As shown in the schematic diagram of FIG. 10, the bolt 10 according to the present embodiment is formed in a columnar shape without a thread on one end side (right end side in FIG. 10) opposite to the bolt head portion 13. A taper member 16 (see FIG. 11) is fitted and fixed to the one end side.

  Here, as shown in FIG. 11A (front sectional view) and FIG. 11B (side view), the taper member 16 has a cylindrical shape having two inner diameters, a small diameter portion 16a and a large diameter portion 16b. And the taper part 12 is formed in the end surface by the side of the small diameter part 16a (left side in Fig.11 (a)).

  A method of fixing the taper member 16 to the bolt 10 will be described with reference to FIG. First, the bolt 10 is inserted into a fastened body (here, fastened bodies 30, 31). Next, the taper member 16 is fitted into one end side of the bolt 10 (right end side in FIG. 10) from the taper portion 12 side. Next, in a state where the taper member 16 is retracted to the other end side (the left end side in FIG. 10) of the bolt 10 from the predetermined fixing position, the fixing member (here, the ring member 10c) is formed in the ring groove 10c. , C ring 17) is fitted. Next, the taper member 16 is moved to a predetermined fixing position, that is, a position where the C-ring 17 is fitted to the large-diameter portion 16b of the taper member 16, whereby the taper member 16 is fixed to the bolt 10. In this state, the nut 20 is pressed and locked to the tapered portion 12. At this time, assuming the time-dependent change such as familiarity between the nut 20 and the taper member 16, the fixing position of the taper member 16 is the other end side of the bolt 10 than the position calculated by dimensions (the left end side in FIG. 10). The surface contact between the nut 20 and the taper member 16 (taper portion 12) can be ensured by setting the position to a position that is moved by a minute amount (set as a tolerance).

  This restricts the taper member 16 from moving in the direction of one end side of the bolt 10 (right end side in FIG. 10). Note that the movement of the taper member 16 to the other end side (the left end side in FIG. 10) of the bolt 10 is regulated by the nut 20 being pressed and locked to the taper portion 12.

In the present embodiment, similar to the above-described fourth embodiment, the taper portion 12 has a large taper angle, so that the same effect as that of the same embodiment can be obtained.
In addition, as compared with the fourth embodiment, the taper portion 12 is formed on the taper member 16 separate from the bolt 10, thereby providing a wide contact area between the taper portion 12 and the nut 20. Therefore, it is possible to perform reliable press-contact locking.

Moreover, the example of the nut 20 which concerns on this embodiment is shown in FIG. 12 (FIG. 12 (a) is front sectional drawing, FIG.12 (b) is a side view). The basic structure of the nut 20 is the same as that of the fourth embodiment described above, but there is a difference in the shape of the biasing member. Specifically, the urging member 24 of the present embodiment is formed in a ring shape along the outer peripheral surface of the nut 20, and is configured to be fitted and fixed in a fitting groove 20 f provided in the nut 20. Yes. Reference numeral 20g in the drawing is a hole for inserting a tool for expanding the diameter (not shown) used when fitting the nut 20 to the nut mounting portion 11 (tapered portion 12). In other words, the inner diameter of the nut 20 is increased or decreased with the pin 25 as the axis of rotation.
The nut 20 according to the present embodiment is not limited to the above configuration, and the nut 20 according to the above-described fourth embodiment may be used.

  The effect of the fastening member 1 according to the present embodiment is basically the same as that of the first embodiment described above. In particular, the taper angle (inclination angle) of the taper portion 12 and the corresponding taper angle (inclination angle) of the nut 20 can be increased, and a wide contact area between the taper portion 12 and the nut 20 can be provided. Therefore, it is possible to prevent the diameter of the nut 20 from expanding even for a larger impact, and to prevent the nut 20 from falling off, thereby exhibiting a strong loosening prevention effect.

Next, the fastening member 1 according to the seventh embodiment of the present invention will be described (see FIG. 13).
The fastening member 1 according to this embodiment has the same basic configuration as that of the above-described sixth embodiment, and is different in the structure of the bolt 10 and the taper member 16, and therefore will be described mainly with respect to the difference.

  As shown in FIG. 14A (front sectional view) and FIG. 14B (side view), the taper member 16 according to the present embodiment has the same basic configuration as the above-described sixth embodiment. can do. However, as a difference, the structure for fixing to the bolt 10 is different. Specifically, the inner diameter is substantially the same as the outer diameter of the bolt 10, and a plurality of crimping tongue pieces 16c are provided on the end face opposite to the end face on which the tapered portion 12 is formed. 16c,... Are provided.

  On the other hand, the bolt 10 according to the present embodiment is provided with a notch groove 10d into which the caulking tongue pieces 16c, 16c,... Of the taper member 16 are fitted by caulking as shown in the schematic diagram of FIG. ing. In addition, as shown in FIG. 13, the attachment position of the taper member 16 can be adjusted by providing a plurality of notch grooves 10d.

  Here, a method of fixing the taper member 16 to the bolt 10 will be described with reference to FIG. First, the bolt 10 is inserted into a fastened body (here, fastened bodies 30, 31). Next, the taper member 16 is fitted into one end side (right end side in FIG. 13) of the bolt 10 from the taper portion 12 side. Next, the taper member 16 is fixed to the bolt 10 by aligning the taper member 16 at a predetermined fixing position and by crimping the caulking tongue pieces 16c, 16c,... Into the notch groove 10d. Is completed. In this state, the nut 20 is pressed and locked to the tapered portion 12. At this time, assuming the time-dependent change such as familiarity between the nut 20 and the taper member 16, the other end side of the bolt 10 than the position where the fixing position of the taper member 16 is calculated by the dimensions (the left end side in FIG. 13). The surface contact between the nut 20 and the taper member 16 (taper portion 12) can be ensured by setting the position to a position that is moved by a minute amount (set as a tolerance).

  This restricts the taper member 16 from moving in the direction of one end side of the bolt 10 (right end side in FIG. 13). Note that the movement of the taper member 16 to the other end side (the left end side in FIG. 13) of the bolt 10 is restricted by the nut 20 being pressed and locked to the taper portion 12.

  The effect of the fastening member 1 according to the present embodiment is basically the same as that of the sixth embodiment described above. In addition to this, since it is not necessary to separately provide a fixing member (for example, C ring 17), a cost reduction effect can be obtained by reducing the number of parts.

As described above, in the case of fastening members such as conventional bolts and nuts (for example, hexagonal bolts and hexagonal nuts having a thread) or loosening nuts that have been subjected to secondary processing, they are subjected to impact and vibration. When used in an environment, a strong axial force must be applied to prevent loosening. As a result, familiarity, sag, depression, etc. of the metal may occur on the threads and seating surface, resulting in loosening. There was a problem to get.
However, according to the fastening member according to the present invention, it is possible to prevent loosening by fastening the fastened body without generating a strong axial force as in the prior art, so that wear between metals is prevented. At the same time, a remarkable effect is exhibited in preventing metal fatigue and breakage of the bolt.

  In addition, if the fastening member according to the present invention is used in an environment that receives impact or vibration, the fastening of the body to be fastened is further ensured by receiving the impact or vibration generated as an environmental factor. An effect is produced.

  Further, once the fastened body is securely fastened, the nut is prevented from loosening (sliding in the loosening direction), and the loosening prevention effect can be maintained.

  Further, since the fastening member according to the present invention can have a very simple structure, it has remarkable effects such as ease of use and easy manufacture.

  Needless to say, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the present invention.

DESCRIPTION OF SYMBOLS 1 Fastening member 2, 3 Retaining mechanism 10 Bolt 11 Nut mounting part 12 Taper part 13 Bolt head part 14 O ring 16 Taper member 17 C ring 20 Nut 22, 24 Energizing member 30, 31 Fastened body

Claims (7)

A fastening member that includes a bolt and a nut and fastens a fastened body,
The bolt has at least one end side, and a taper portion whose diameter increases toward the end portion is provided integrally or separately with the bolt,
The nut is slidably pressed and locked to the tapered portion. A fastening member having a retaining mechanism at both ends of the bolt, inserting the bolt into through holes provided in a plurality of fastened bodies, and clamping the plurality of fastened bodies from both sides by the retaining mechanism. Because
At least one end side retaining mechanism includes a nut mounting portion provided on the bolt, and a nut locked to the nut mounting portion,
As the nut mounting portion, a taper portion whose cross-sectional area gradually increases toward the end on the one end side is provided integrally with the bolt or separately.
The nut has pressure contact force generating means for slidably press-fitting to the tapered portion, and is formed in a shape having an outer dimension larger than the inner dimension of the through hole of the coupled body to be abutted. The fastening member characterized by the above-mentioned. The fastening member according to claim 2, wherein the nut is formed of two or more members made of a metal material or a resin material, and includes an urging member as the pressure contact force generating means. The nut is a C-shaped or U-shaped member formed using a metal material or a resin material, and the taper is configured so that it can be press-fitted to the taper portion within an elastic deformation region of the material used. The fastening member according to claim 1, wherein an inner shape dimension of a contact portion with the portion is smaller than an outer dimension of the contact portion in the tapered portion. The fastening position according to any one of claims 1 to 4, wherein the nut has a contact portion with the tapered portion formed in a tapered shape having the same inclination angle as the tapered shape of the tapered portion. Element. The taper portion is formed in a shape in which a taper-shaped start end is located inward from the end surface of the fastened body on the taper portion side, and a taper-shaped end is located outward from the end surface. The fastening member according to any one of claims 1 to 5, wherein: A fastening method for fastening a plurality of bodies to be fastened using the fastening member according to claim 1,
After the nut is pressed and locked to the tapered portion,
By applying an impact or vibration to the bolt or the nut, the nut is slid from the large-diameter side to the small-diameter side of the tapered portion, and is generated in the axial direction of the bolt that fastens the plurality of fastened bodies. A fastening method characterized by increasing a fastening force.

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