WO2015141854A1

WO2015141854A1 - Self-tapping screw and fastening structure

Info

Publication number: WO2015141854A1
Application number: PCT/JP2015/058606
Authority: WO
Inventors: 直樹堀内; 茂人森; 誠也星野
Original assignee: 株式会社トープラ
Priority date: 2014-03-20
Filing date: 2015-03-20
Publication date: 2015-09-24
Also published as: JP6275825B2; CN106133345B; JPWO2015141854A1; CN106133345A

Abstract

A self-tapping screw which can increase drag torque even when not enough seat surface area and not enough of the screw thread can engage, and a fastening structure, are provided. This self-tapping screw has a head part (10) and a screw shaft part (20), and is characterized in that, by making the seat surface (16) of the head part (10) a rough surface having minute irregularities, the frictional coefficient is increased, and the drag torque is increased without changing the driving torque during formation of internal threading.

Description

Tapping screw and its fastening structure

The present invention relates to a tapping screw that performs fastening while forming a female screw on the mating material by plastic deformation, and particularly relates to a tapping screw suitable for a case where the thickness of the mating material is a thin plate and its fastening structure.

Conventionally, this type of tapping screw has been set so that the difference between the idling torque and the screwing torque is large, and even if the tightening torque varies, it can be securely tightened.
However, due to recent demands for space saving of members, there are cases where the head dimensions are limited and the area of the seating surface cannot be increased. If the seating area is small, the seating surface contact becomes small at the time of tightening, so that the idling torque becomes low.

On the other hand, if the number of threads that the tapping screw engages is large, the idling torque can be maintained high. However, due to the recent thinning of the female thread material, the number of threads that are caught during tightening decreases, and the idling torque decreases. Become. Although it is conceivable to increase the contact area by changing the thread shape, there is a limit to the correspondence only by changing the screw shape.
In order to increase the number of thread catches, it is effective to provide an undercut under the neck and extend the male screw to the vicinity of the head, but the seat area will be reduced by the amount of the undercut, That alone cannot increase the idling torque.

Japanese Patent No. 3017331

As a result of intensive studies, the present inventors have come up with the idea that the idling torque can be increased by adjusting the friction coefficient of the head seating surface.
As a technique for providing unevenness on the head seating surface, for example, a technique as described in Patent Document 1 is known, but this patent document is provided to prevent loosening and focuses on idling torque. It is not a thing.
An object of the present invention is to provide a tapping screw that can improve the idling torque even if the seating area and the number of screw threads are not sufficient.

In order to achieve the above object, the present invention provides a tapping screw having a head portion and a screw shaft portion, wherein the seating surface of the head portion is a rough surface having fine irregularities, thereby increasing the friction coefficient and the idling torque. It is characterized by having a configuration that enhances.
Another invention has a screw fastening structure of a tapping screw that has a head and a screw shaft portion having a screw thread, and is fastened while forming a female screw in a lower hole of a mating member by the screw shaft portion. Because
The seating surface of the head is a rough surface having fine irregularities, whereby the friction coefficient is increased and the idling torque is increased.

An undercut portion is provided at the neck base of the head, the seat surface is provided in an annular shape so as to surround the undercut portion, and the surface roughness of the seat surface is set to be rougher than the undercut portion. ing.
The outer diameter of the seating surface is smaller than the maximum diameter of the head outer periphery.
In the outer periphery of the head, the head forming sag occurs to improve the tool life, the outer diameter of the seating surface is smaller than the maximum diameter of the outer periphery of the head, and the head seating area becomes smaller. By making the surface rough, the idling torque can be improved without impairing the tool life.
If the unevenness of the seating surface is provided while maintaining the seating surface flatness, the seating surface can be uniformly contacted over the entire circumference.
The surface roughness of the seating surface is preferably 15 μm to 50 μm in terms of the maximum height roughness Rz.

According to the present invention, by increasing the friction coefficient with the head seating surface as a rough surface, the idling torque can be improved even if the seating area and the number of screw threads are not sufficient, and reliable tightening can be achieved. It becomes possible.

(A) is an overall view showing a tapping screw according to an embodiment of the present invention, (B) is a sectional view taken along line BB of (A), and (C) is a partially enlarged view of (A). It is a graph which shows the surface roughness of the head seat surface of FIG. 1 compared with a conventional product. It is a graph which shows the relationship between a bearing surface roughness and idling torque. Schematic which shows the state which fastened the tapping screw of FIG.

Hereinafter, the present invention will be described in detail based on illustrated embodiments.
FIG. 1 shows a tapping screw according to an embodiment of the present invention. In the figure, reference numeral 1 denotes a tapping screw. The tapping screw 1 includes a head 10 and a screw shaft 20 extending from the head 10, and a screw thread 21 having a complete thread shape is formed on the screw shaft 20. The formed parallel screw portion 22 and a taper screw portion 24 that gradually decreases in diameter toward the tip end are provided on the tip end side of the parallel screw portion 22.

The head portion 10 has a pan shape, a bit hole 18 is provided at the top portion, and a seat surface 16 that is seated on the material to be fastened when tightened is provided on the back surface side of the head portion 10. In this embodiment, an undercut portion 12 is provided on the back surface of the head portion around the base portion where the neck of the screw shaft 20 is connected to the head portion, and the seat surface 16 surrounds the undercut portion 12. Are formed in an annular shape over the entire circumference.
Moreover, the outer peripheral side surface of the head 10 is a head forming sag 14 that is reduced in diameter so that the diameter gradually decreases from the center in the height direction toward the back of the head. The outer diameter of the seating surface 16 is smaller than the maximum diameter of the outer periphery of the head 10 by the reduced diameter of the head shaping sag 14.
In the present invention, the seating surface 16 is a rough surface having fine irregularities, thereby increasing the coefficient of friction and increasing the idling torque. The surface roughness of the seating surface 16 is set to be rougher than that of the undercut portion 12. The surface roughness of the undercut portion 12 is substantially the same as the surface roughness of the head 10, and the surface roughness of the seating surface 16 is rougher than the surface roughness of the head 10.

FIG. 2 is a roughness diagram showing a comparison between the product of the present invention and the conventional product. (A) is an enlarged perspective view of an embodiment of the present invention, (B) is its roughness diagram, (C) is an enlarged photograph of a conventional product, and (D) is its roughness diagram.
In the case of the product of the present invention, as shown in FIG. 2B, the peak of the maximum peak height and the maximum valley height between 0.25 mm is less than five. When five or more fine peaks are obtained, the influence on the frictional force is not so great, and it is preferable that the peak of the maximum peak height and the maximum valley height between 0.25 mm be less than five.
In the case of the conventional product, as shown in FIG. 2D, the surface roughness of the bearing surface is Rz (maximum height roughness, Japanese Industrial Standard JIS B0601, 2001 revision) and is a level smaller than 10 μm (reference length). Is 0.25 mm).

FIG. 4 shows a fastening structure in which the tapping screw of the present embodiment is fastened by overlapping a thin fastening material 110 and a female screw material 120. Although not shown in particular, the to-be-fastened material 110 and the female screw material are provided with a pilot hole, and in the initial stage of fastening, a female screw is formed in the pilot hole by the screw thread 21 of the screw shaft portion 20 and further tightened. As a result, the seating surface 16 of the head is seated on the material to be fastened 110 and further tightened until a predetermined torque equal to or less than the idling torque is reached, thereby completing the tightening operation.
Although tightening is performed by tightening after seating, in this embodiment, since the seat surface 16 is provided with fine irregularities, the friction coefficient is high, and the friction torque between the seat surface 16 and the material to be fastened 110 is high. The idling torque is increased accordingly. That is, the difference between the screwing torque and the idling torque can be increased only by making the seating surface 16 rough, and by setting an appropriate tightening torque, the screw can be securely tightened without being damaged.
In particular, in this embodiment, the undercut portion 12 is provided, the thread 21 of the screw shaft 20 is formed as close to the head as possible, and the number of threads to be engaged is increased. Can be made larger. In the illustrated example, the number of hooks of two peaks is increased by one by the undercut portion 12 to about three peaks.

In addition, although the seat area is narrowed by providing the undercut portion 12, the seat surface 16 is compared with the conventional example in which the undercut portion 12 is not actually provided and the seat surface 16 is not roughened. Even if the area was small, the idling torque increased with the rough surface.
Moreover, since the idling torque can be increased even if the head forming sag 14 is left, there is an advantage that the tool life can be increased.

FIG. 3 shows the relationship between the bearing surface roughness and the idling torque.
The bearing surface roughness is a maximum height roughness Rz (Japanese Industrial Standard JIS B0601,2001 revision, reference length 0.25 mm) and represents data in the range of 5 μm to 50 μm. As shown in the graph, the initial value was about 2.7 [N · m] at 5 μm, but was 3.0 [N · m] at 10 μm, 3.2 [N · m] at 15 μm, and 3.3 at 30 μm. 7 [N / m], 40 μm to 50 μm, and 3.8 to 3.9 [N / m].
From this result, the effect starts to appear when the maximum height roughness Rz exceeds 10 μm. Therefore, the idling torque can be sufficiently increased in the range of 10 μm to 50 μm, and 15 μm or more is more effective. Further, if it exceeds 30 μm, it will be almost flat by 50 μm, so the range of 15 μm to 30 μm is preferable. The seating surface 16 is basically a flat surface, and fine irregularities are provided while maintaining the seating surface flatness.
In particular, even when the number of screw threads can be secured only about 3 threads, for example, 2 to 5 threads shown in FIG. 4, the range of the maximum height roughness Rz is 10 μm to 50 μm, more preferably 15 μm to 30 μm. By setting to, idling torque can be increased and fastening can be performed with an appropriate fastening torque. Of course, the number of hooks of the thread is not limited to about 2 to 5 but may be 5 or more, or 2 or less depending on the case.

In addition, although the undercut part is provided in the said embodiment, the structure which does not provide an undercut part may be sufficient, and the structure without head shaping | molding sagging may be sufficient.
The head shape is not limited to the pan shape, and can be applied to various head shapes.

DESCRIPTION OF SYMBOLS 1 Tapping screw 10 Head 12 Undercut part 14 Head shaping | molding sagging 16 Seat surface 20 Screw shaft, 21 Thread, 22 Parallel thread part, 24 Tapered thread part 110 Fastened material, 120 Female thread material

Claims

In a tapping screw having a head and a screw shaft,
A tapping screw characterized in that the seating surface of the head is a rough surface having fine irregularities to increase the friction coefficient and increase the idling torque.
An undercut portion is provided at the neck base of the head, the seat surface is provided in an annular shape so as to surround the undercut portion, and the surface roughness of the seat surface is set to be rougher than the undercut portion. The tapping screw according to claim 1.
The tapping screw according to claim 1 or 2, wherein the outer diameter of the seating surface is smaller than the maximum diameter of the outer periphery of the head.
4. The tapping screw according to any one of claims 1 to 3, wherein the fine unevenness of the seating surface is provided while maintaining the seating surface flatness.
5. The tapping screw according to claim 1, wherein the surface roughness of the seating surface is 10 μm to 50 μm in terms of a maximum height roughness Rz.
The tapping screw according to any one of claims 1 to 5, wherein the surface roughness of the seating surface is rougher than the surface roughness of the outer periphery of the head.
A screw fastening structure of a tapping screw having a head and a screw shaft portion provided with a screw thread, and being fastened while forming a female screw in a lower hole of a counterpart material by the screw thread of the screw shaft portion;
A screw fastening structure for a tapping screw, characterized in that the seating surface of the head is a rough surface having fine irregularities to increase the friction coefficient and increase the idling torque.
The screw fastening structure for a tapping screw according to claim 7, wherein the number of hooks with the female screw is 2 to 5 and the surface roughness of the seating surface is 10 μm to 50 μm at a maximum height roughness Rz. .
An undercut portion is provided at the neck base of the head, the seat surface is provided in an annular shape so as to surround the undercut portion, and the surface roughness of the seat surface is set to be rougher than the undercut portion. The screw fastening structure for a tapping screw according to claim 7 or 8, wherein
The screw fastening structure for a tapping screw according to any one of claims 7 to 9, wherein the outer diameter of the seating surface is smaller than the maximum diameter of the outer periphery of the head.
The screw fastening structure for a tapping screw according to any one of claims 7 to 10, wherein the fine unevenness of the seating surface is provided while maintaining the seating surface flatness.
The screw fastening structure for a tapping screw according to any one of claims 7 to 11, wherein the surface roughness of the seating surface is rougher than the surface roughness of the outer periphery of the head.