WO2004015285A1

WO2004015285A1 - Fastening member

Info

Publication number: WO2004015285A1
Application number: PCT/JP2003/009962
Authority: WO
Inventors: Yasuhisa Kurihara
Original assignee: Yasuhisa Kurihara
Priority date: 2002-08-08
Filing date: 2003-08-05
Publication date: 2004-02-19
Also published as: JPWO2004015285A1; JP3860200B2; AU2003252408A1

Abstract

A fastening member, which is provided as a nut or bolt having a locking action, is characterized by comprising a head for turning the fastening member around its axis, and a taper section which is in the form of a cylinder whose end extending integrally and coaxially with the head from the base of the head gradually increases in diameter to exceed the diameter of the head, and whose extension end surface is formed as a seat surface abutting against body to be fastened.

Description

Description .Technical field of fastening members

The present invention relates to a fastening member such as a nut and a port that fastens and fixes a member using a screw action, and more particularly to a fastening member having a suitable loosening prevention action. Background art

Nuts and ports have been widely used in various fields as fastening members used for fastening and fixing parts and members. These nuts and ports are used to tighten and fix parts and members. However, if vibrations repeatedly act on these fastening parts, the nuts and bolts may loosen. For this purpose, flat plate springs and spring washers have been used.

Also, for the purpose of preventing nuts and ports from loosening, nuts with washers

Japanese Patent Application Laid-Open No. 2002-122, Japanese Patent Application Laid-Open No. Hei 9-72325) and a method in which the inner peripheral surface of a nut is partially formed on a taper surface (Japanese Patent Application Laid-Open No. — Japanese Patent Publication No. 2681617) and a configuration in which a washer is integrally attached to a nut (Japanese Patent Application Laid-Open No. Hei 9-53628) have been proposed. In addition, a method of tightening and fixing by the double nut method, for example, a configuration in which two nuts are fitted by a taper surface, one taper surface is eccentric with respect to the axis, and tightened firmly by wedge action (Japanese Unexamined Patent Application Publication No. Heisei 9-142259) has been considered. However, conventional nuts with washers and double nuts have a certain degree of loosening action, but when extremely large vibrations or impacts are repeatedly applied to the tightened part of the nut or bolt, the tightened part becomes loose. There was a problem of getting out. In addition, there is a problem that when a nut or the like is processed to prevent loosening, the processing becomes complicated. Therefore, the present invention has been made to solve these problems, and its purpose is to solve the problem even when a large impact or vibration repeatedly acts on a fastening portion using a nut and bolt fastening member. An object of the present invention is to provide a fastening member such as a nut or a port which can be extremely easily tightened and fixed, is easy to use, and has a simple structure because the fastening member does not loosen. Disclosure of the invention

The present invention has the following configuration to achieve the above object.

That is, a fastening member for fastening an object to be fastened by a screw action, a head portion for rotating the fastening member around an axis, and a base portion of the head portion integrally with the head portion. The extension end side is formed in a cylindrical shape whose diameter gradually increases so as to be concentric with the head part and larger in diameter than the head part, and the extension end surface comes into contact with the object to be fastened. And a taper portion formed on the tape. By providing the taper part in a shape that gradually expands the diameter from the head part integrally with the head part, it is possible to tighten and fix the object to be fastened extremely strongly. As a result, vibration and shock are absorbed to provide a fastening member having a suitable loosening prevention function. The fastening member according to the present invention has a simple configuration, is easy to use, and is easy to manufacture.

Further, the inner surface of the taper portion is formed as a conical curved surface.

Further, since the outer surface of the tapered portion is formed as a concave curved surface, the loosening preventing action by the fastening member can be further effective.

Further, even when the outer surface of the taper portion is formed in a conical curved surface, it can have a certain loosening preventing action.

The fastening member may be provided as a nut having a screw hole formed in a head portion. The fastening member may include a screw shaft formed coaxially with the head portion and the tapered portion. It can be provided as a bolt integrally formed with the head portion and the tapered portion on the base side of the portion. Further, the head portion and the tapered portion are formed of an iron-based material and are quenched. BRIEF DESCRIPTION OF THE FIGURES

1A, 1B, 1C, and 1D are a front view, a cross-sectional view, a plan view, and a bottom view showing the configuration of a first embodiment of a nut as a fastening member according to the present invention. 3C and 3D are a front view, a sectional view, a plan view, and a bottom view, respectively, showing the configuration of a second embodiment of a nut as a fastening member according to the present invention. FIGS. 4A and 4B are explanatory diagrams showing the arrangement of a test nut in a slack tester; FIG. — E is an explanatory view showing another arrangement of the test nuts in the slack tester, and FIG. 6 is an explanatory view showing a state in which the workpiece is tightened using a nut. C is a front view, a left side view, and a right side view showing a configuration of a port as a fastening member according to the present invention. FIG. Is an explanatory view showing a state in which with fit. BEST MODE FOR CARRYING OUT THE INVENTION

1A to 1D are a front view, a sectional view, a plan view, and a bottom view showing the configuration of a nut as a first embodiment of a fastening member according to the present invention. The nut 10 of the present embodiment is formed by integrally forming a head portion 12 having a hexagonal planar shape and a cylindrical tapered portion 14 whose tip end gradually increases in diameter. Things. The head portion 12 is provided with a screw hole 16 like a normal nut. 1

6a is the thread.

The most characteristic configuration of the nut 10 of the present embodiment is the configuration of the taper portion 14 formed integrally with the head portion 12 concentrically with the head portion 12. As shown in FIG. 1B, the tapered portion 14 has an outer surface formed into a concave curved surface, and an inner surface formed into a conical curved surface (the cross section of the surface is linearly inclined). That is, the tapered portion 14 is formed in a trumpet shape, and is formed in a cylindrical shape in which the extension end side is warped outward. When using this nut 10, the end surface of the tapered portion 14 faces the object to be fastened, and the seating surface 14 a contacts the object to be fastened. Can be tightened. The seat surface 14a is formed in a flat surface so as to come into contact with the object to be fastened when the nut 10 is tightened and fixed to the object to be fastened. In this embodiment, as shown in FIG. 1D, a non-slip groove 14b is provided concentrically on the seat surface 14a.

FIG. 2 shows the configuration of a nut 11 as a second embodiment of the fastening member according to the present invention. The difference between the configuration of the nut 11 shown in FIG. 2 and the configuration of the nut 10 shown in FIG. 1 is the configuration of the tapered portion 14 formed integrally with the head portion 12.

FIG. 3 shows a comparison of the difference between the configuration of the nut 10 and the configuration of the nut 11. 3A shows the cross-sectional shape of the nut 10 shown in FIG. 1, and FIG. 3B shows the cross-sectional shape of the nut 11 shown in FIG. The difference between the shape of the nut 10 and the shape of the nut 11 is that, in the nut 10, the outer surface A of the tapered portion 14 is formed as a concave curved surface, whereas in the nut 11, the shape is different. The outer surface A of the taper section 14 is simply a conical curved surface. In FIG. 3B, the outline of the cross section of the tapered portion 14 is a straight line, but the outline of the cross section of the tapered portion 14 in FIG. The part 14 has a shape in which the part C (shaded part) is removed from the outer peripheral surface of the nut 11.

The inner surface of the tapered portion 14 has a conical curved surface in any of the nuts 10 and 11. Therefore, in the case of the nut 11, the thickness of the tapered portion 14 is substantially constant between the head portion 12 side and the extending end side, whereas in the case of the nut 10, the tapered portion 1 is thickened. Reference numeral 4 denotes a thin portion between the head portion 12 and an intermediate portion on the extension end side.

The nut 10 and the nut 11 shown in FIGS. 1 and 2 are provided with a head portion 12 and a tapered portion 14 extending from the head portion 12 in a cylindrical shape, so that a taper portion is provided. 14 has a function of absorbing an impact, and can be used as a fastening member having an excellent loosening prevention function. In particular, in the case of the nut 10 shown in Fig. 1, the thickness of the middle part of the tapered part 14 is reduced to reduce the nut. Elasticity is imparted to the tapered portion 14 compared to 11 to maintain sufficient tightening force when the nut 10 is tightened, and to further absorb the shock and vibration applied to the nut 10 This makes it possible to maintain the tightened state firmly. In addition, by reducing the thickness of the intermediate portion of the tapered portion 14 and slightly tapering the tapered portion 14 outward, the seating surface 14 a of the tapered portion 14 is smaller than the nut 11. And the tapered portion 14 has a hem shape on the outside to secure a large area in contact with the object to be fastened when the nut 10 is tightened. 4a is easily brought into flat contact with the object to be fastened, and has an effect of easily absorbing vibration and impact.

The size of the nut 10 can be appropriately designed according to the size of the screw hole 16 and the like. The design values of the nuts 10 and 11 shown in FIG. 3 are as follows. Outer diameter of head 1 2 T = 21.5 mm, screw hole diameter S = 12 mm, outer diameter of taper 14 4 R = 32 mm, seat width W = 3 mm, head 1 The height dimension between H2 and the tapered section H4 is H = 9 mm. In order to impart elasticity to the tapered portion 14, the shape of the tapered portion 14 should be a shape with a larger diameter on the distal end side, the height dimension of the tapered portion 14 should be at least a certain level, It is advantageous to reduce the thickness of the metal. The ratio of the height H of the head portion 12 to the height H of the tapered portion 14 can be set as appropriate, but usually, the ratio may be about 1: 1. The thickness of the taper portion 14 may be approximately the same as the thickness of the head portion 12 excluding the screw holes.

In the following, the results of the slack test performed on the nut 10 shown in FIG. 1 and the nut 11 shown in FIG. 2 using a high-speed slack tester will be described.

Figures 4 and 5 show the layout of the nuts tested with the high-speed slack tester during testing. Figure 4A shows an arrangement tested with nuts tightened from one side, and Figure 4B shows an arrangement tested with nuts tightened from both sides. In FIG. 4, reference numeral 30 denotes a test nut, and reference numeral 32 denotes a port. The test nut 30 is fastened and fixed by a port 32 via a vibrating barrel 34 and a jig 36. In the test, the nut was fixed using a washer 38. 40 is a vibration table. Fig. 5 shows a modification of the fastening method using nuts. Fig. 5A shows an example in which two test nuts 30 are arranged face-to-face (facing) and tightened. Fig. 5B is a test example. Nut 30 is tightened from both sides, and the inside nut 31 is inserted inside the test nut 30 and the middle nut 31 is also tightened. Fig. 5C shows the middle nut 31 as the test nut 30 on both sides. Fig. 5D shows an example where two test nuts 30 are tightened in the same direction.Fig. 5E shows an example where two test nuts 30 are This is an example in which a lock holder 33 is mounted between two test nuts 30.

For the screw loosening test, use a high-speed screw loosening tester with a frequency of 178 Orpm, and perform a loosening test with a vibration table stroke of 11 mm, impact stroke of 19 mm, and a vibration direction perpendicular to the screw axis. Was. The looseness was judged to be loose when the jig washer 36 was able to be turned by hand.

Table 1 shows the test results for the nut 10 shown in FIG. Two types of nuts with a seat width of 3.0 mm and 2.0 mm were used as test nuts. The tightening torque of the nut 10 in the loosening test was 51.2 (N-m).

table 1

(Tightening torque 51.2 Nm) The arrangement in Table 1 indicates the test arrangement of the test nut. In the test of the arrangement shown in FIG. 5E using a test nut having a seat surface width of 2.0 mm, the lock holder was broken after 13 minutes and 20 seconds.

From the test results in Table 1, the examples using the medium nut 31 loosened in a short time in each case. This result indicates that the method of tightening using the middle nut 31 is not effective.

In addition, the test nut with a seat width of 3.0 mm and the arrangement of Figs. 4A, 5D and 5E, and the test nut with a seat width of 2.0 mm, It is characteristic that the arrangement shown in FIG. 5E is maintained in a state in which it does not loosen even after 15 minutes.

This high-speed slack tester is a device for testing by repeatedly applying vibration and impact at a high speed, and in a normal nut, it loosens within a few seconds to several tens of seconds. Even the most commercially available nuts (such as the double nut structure) that are said to have the highest tightening holding force can hold for only a few minutes, and the tightening force can be maintained for 15 minutes using this test method. The nut that can hold the nut is equivalent to the highest level of the nut currently on the market and is rare for a nut structure. The test results shown in Table 1 show that the nut 10 shown in FIG. 1 has extremely high tightening holding performance and slack prevention performance.

In Table 1, the test results for the test nut with a seat width of 3.0 mm and the arrangement of Figs. 4B and 5A, and for the test nut with a seat width of 2.0 mm and Fig. However, it is held without loosening for about several minutes, and the highest degree of loosening prevention effect is not obtained, but it is recognized that it has a considerable degree of loosening prevention performance as compared with a normal nut. In other words, a considerable degree of anti-slack performance is confirmed even for arrangements other than the arrangement in which no slack is observed for 15 minutes. In the case of these arrangements, better results can be obtained by means such as increasing the tightening torque of the test nut, and depending on the application, it can be sufficiently used. Next, Tables 2 and 3 show that, for the nut 11 shown in Fig. 2, using the high-speed screw loosening tester with a frequency of 178 Orpm described above, the loosening of the screw was performed under the same conditions as the above-mentioned test. The result of the test is shown. Table 2 shows the case where the tightening torque is 35.8 (Nm). The test nuts were tested for the layout of Figs. 4A and 4B. Table 2

(Tightening torque: 35 · 8 N-m) Table 3 shows the results of a test in which the tightening torque was set to 51.2 (N · m), as in Table 1. In Table 3, for those with a bearing surface width of 3.Omm, the tightening torque was made even larger than 51.2 (N, m), and the test was performed again at 75.8 (Nm). went. The nuts were tested in the configuration shown in Figure 4A. Table 3

(Tightening torque 51.2 Nm) According to the test results shown in Tables 2 and 3, the nut 11 is inferior in the loosening preventing effect as compared with the nut 10 shown in FIG. The test results for nut 10 described above Comparing the results with the test results of the nut 11, the nut 10 is superior in the tightening action and the anti-loosening action. The test results show that making the outer surface of the tapered portion 14 a concave curved surface is effective in absorbing shock and vibration acting on the nut, and acting on the nut by the tapered portion 14. It is thought that vibration and impact are absorbed, and that the anti-slack function works well.

In addition, even in the case of the nut 11 shown in FIG. 2, as shown in Table 3, when the tightening force on the nut 11 is increased, it is possible to exert a considerable degree of loosening prevention effect by using a certain time. Therefore, depending on the material of the nut, the nut 11 shown in FIG. 2 can be sufficiently used depending on the intended use.

FIG. 6 shows a use example in which the nut 10 of the above embodiment is used for fastening a member to be fastened. 22 a and 22 b are the objects to be fastened, pass the port 24 through the through holes provided in the objects 22 a and 22 b, and screw the nut 10 into the port 24 to tighten it. It is fixed. 26 a and 26 b are flat washers. As shown in the figure, the nut 10 is screwed into the port 24 with the seat surface 14a of the tapered portion 14 facing the object to be fastened, and the head portion 12 is tightened with a spanner or the like. This allows the objects 22a and 22b to be tightened and fixed by exactly the same operation as a general nut.

The nuts 10 and 11 of the present embodiment are the same as ordinary nuts except that the taper section 14 is provided so as to extend from the head section 12. There is an advantage that it can be used by the same operation as the nuts used in the above. Further, by tightening with a predetermined torque, the object to be fastened can be securely tightened and fixed. The nuts 10 and 11 of the present embodiment do not easily loosen due to the action of the tapered portion 14, and thus are preferably used as nuts for preventing loosening, particularly for an object to which vibration or impact repeatedly acts. can do.

By providing the anti-slip groove 14b in the seat surface 14a, the nuts 10 and 11 can be prevented from slipping, and a more favorable tightening action can be obtained. W 200

10

In addition, resin or soft metal is filled in the space D inside the tapered portion 14 of the nuts 10 and 11, and the resin or soft metal is compressed when the nuts 10 and 11 are tightened. Then, the nuts 10 and 11 can be tightened together with the resin or the soft metal.

In the above embodiment, a nut has been described as an embodiment of the fastening member. However, a porto as another embodiment of the fastening member will be described below.

7A, 7B, and 7C are a front side, a left side view, and a right side view of Porto 40 as a fastening member according to the present invention. The port 40 of the present embodiment is characterized in that the taper portion 14 is formed integrally with the head portion 12 to extend from the head portion 12 to the screw shaft 42 side. The configuration of the tapered portion 14 is exactly the same as that of the tapered portion 14 in the nut 10 described above. ing.

The screw shaft 4 2 is arranged concentrically with the head portion 1 2 and the tapered portion 14, and is connected to the head portion 1 2 at the base position of the head portion 1 2, and the head portion 1 2 And the tapered portion 14 and the screw shaft 42 are integrally formed. 4 2a is a thread. FIG. 7B shows a state in which a hexagonal hole 12 a for fitting a hexagonal wrench is formed on the top of the head portion 12. Fig. 7C shows that the tapered portion 14 is provided concentrically with the screw shaft 42, and the non-slip groove 14b is formed in the seating surface 14a of the tapered portion 14. .

FIG. 8 shows a state in which the objects to be fastened 28 a and 28 b are tightened and fixed using the bolt 40 of the present embodiment. The screw shaft 42 of Porto 40 is screwed into the screw hole 29 provided in the object 28 b, and the seating surface 14 a of the tapered portion 14 of Porto 40 is connected to the end face of the object 28 a. And affixed. In the case of the bolt 40 of the present embodiment, similarly to the nuts 10 and 11 described above, the action of the taper portion 14 integrally formed with the head portion 12 causes the porto 40 to be loosened. , And can be securely tightened and fixed.

The bolt 40 shown in Figs. 7 and 8 has a hexagonal hole 12a in the head 12 However, it is also possible to form the head portion 12 itself in a hexagonal shape in a planar shape, and to turn and tighten the porto 40 with a spanner or the like. As described above, the form of the port 40 is not limited to the shape of the present embodiment, and can be formed into various shapes.

FIG. 8 shows an example in which the bolt 40 is used alone to fasten and fasten an object to be fastened, but the member is obtained by combining the port 40 shown in FIG. 8 with the nuts 10 and 11 described above. Of course, it is also possible to use it for tightening and fixing. In this case, similarly to the structure shown in FIG. 4B, the members are tightened from both sides by the tightening members provided with the taper portions 14, so that the members can be effectively tightened and fixed. .

The material used for the fastening members such as nuts and bolts according to the present invention is not particularly limited, but it has a certain strength and durability required for the fastening members such as nuts and bolts, and has a tapered portion. It must be formed to have a certain elasticity and strength as 14. For example, it is also effective to quench using iron-based materials.

Also, the shape and dimensions of the nuts and bolts used as fastening members can be set as appropriate, and are similarly applicable from small diameter to large diameter. Since the configurations of the head portion 12 and the tapered portion 14 are simple, there is an advantage that their manufacture is easy.

Claims

The scope of the claims

1. A fastening member for fastening an object to be fastened by a screw action,

A head portion for rotating the fastening member around the axis,

An extending end surface is formed integrally with the head portion from the base portion of the head portion so as to be concentric with the head portion and gradually increase in diameter at the extending end side so as to have a larger diameter than the head portion. And a tapered portion formed on a seat surface that comes into contact with the object to be fastened.

2. The fastening member according to claim 1, wherein the inner surface of the tapered portion is formed as a conical curved surface.

3. The fastening member according to claim 1, wherein an outer surface of the tapered portion is formed as a concave curved surface.

4. The fastening member according to claim 2, wherein an outer surface of the tapered portion is formed to have a concave curved surface.

5. The fastening member according to claim 1, wherein an outer surface of the taper portion is formed in a conical curved surface.

6. The fastening member according to claim 1, wherein the fastening member is formed as a nut having a screw hole formed in a head portion.

7. The fastening member according to claim 3, wherein the fastening member is formed as a nut having a screw hole formed in a head portion.

8. The fastening member is formed as a port in which a screw shaft formed concentrically with the head portion and the tapered portion is formed integrally with the head portion and the tapered portion on the base side of the head portion. The fastening member according to claim 1, wherein

9. The fastening member, wherein a screw shaft formed concentrically with the head portion and the tapered portion is formed as a port integrally formed with the head portion and the tapered portion on the base side of the head portion. 4. The fastening member according to claim 3, wherein

10. The fastening member according to claim 1, wherein the head portion and the taper portion are formed of an iron-based material, and are quenched.