JP6275825B2 - Tapping screw and its fastening structure - Google Patents

Tapping screw and its fastening structure Download PDF

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JP6275825B2
JP6275825B2 JP2016508843A JP2016508843A JP6275825B2 JP 6275825 B2 JP6275825 B2 JP 6275825B2 JP 2016508843 A JP2016508843 A JP 2016508843A JP 2016508843 A JP2016508843 A JP 2016508843A JP 6275825 B2 JP6275825 B2 JP 6275825B2
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screw
head
seating surface
tapping screw
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JPWO2015141854A1 (en
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直樹 堀内
直樹 堀内
茂人 森
茂人 森
誠也 星野
誠也 星野
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Topura Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B35/00—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws
    • F16B35/04—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws with specially-shaped head or shaft in order to fix the bolt on or in an object
    • F16B35/06—Specially-shaped heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B2/00—Friction-grip releasable fastenings
    • F16B2/005—Means to increase the friction-coefficient
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B25/00—Screws that cut thread in the body into which they are screwed, e.g. wood screws
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B39/00—Locking of screws, bolts or nuts
    • F16B39/22—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening
    • F16B39/28—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening by special members on, or shape of, the nut or bolt
    • F16B39/282—Locking by means of special shape of work-engaging surfaces, e.g. notched or toothed nuts

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Connection Of Plates (AREA)

Description

相手材に自らめねじを塑性変形により成形しながら締結を行うタッピンねじに関し、特に相手材の板厚が薄板の場合に適したタッピンねじ及びその締結構造に関する。   More particularly, the present invention relates to a tapping screw suitable for a case where the plate thickness of the mating material is a thin plate and a fastening structure thereof.

従来からこの種のタッピンねじは、空転トルクとねじ込みトルクの差が大きくなるように設定し、締め付けトルクがばらついても、確実に締め付けられるようになっている。
しかし、近年の部材の省スペース化の要請で、頭部寸法に制約があり、座面の面積を大きくできない場合もある。座面積が小さいと、締め付け時に、座面接触が小さくなってしまうため、空転トルクが低くなってしまう。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.

一方、タッピンねじが係合するねじ山数が多ければ空転トルクを高く維持できるが、近年のめねじ材の薄板化により、締め付け時に引っ掛かるねじ山数が少なくなり、空転トルクの低下を招くことになる。ねじ山形状を変更して接触面積を増大させることも考えられるが、ねじ形状の変更のみでは対応の限界がある。
ねじ山の引っ掛かり数を多くする点では、首下にアンダーカットを設け、頭部付近までおねじを延長することが有効であるが、アンダーカットを設けた分だけ座面積が小さくなってしまい、それだけでは空転トルクを高くすることができない。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.

特許第３０１７３３１号公報Japanese Patent No. 3017331

本発明者等は鋭意研究した結果、頭部座面の摩擦係数を調整することで、空転トルクを高くすることができるという着想を得た。
頭部座面に凹凸を設ける技術としては、たとえば、特許文献１に記載のようなものが知られているが、この特許文献は弛み止めのために設けられたもので、空転トルクに着眼したものではない。
本発明の目的は、座面積、ねじ山のひっかかり数を十分にとれなくても、空転トルクを向上させる得るタッピンねじを提供することにある。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.

上記目的を達成するために、本発明は、頭部とねじ軸部とを有するタッピンねじにおいて、前記頭部の座面を微細な凹凸を有する粗面とすることにより、摩擦係数を高めて空転トルクを高める構成としたもので、
前記頭部の首下付け根部にはアンダーカット部が設けられており、前記座面はアンダーカット部を取り囲むように円環状に設けられ、座面の表面粗さはアンダーカット部よりも粗く設定されていることを特徴とする。
また、他の発明は、頭部とねじ軸部とを有するタッピンねじにおいて、
前記頭部の座面を微細な凹凸を有する粗面とすることにより、摩擦係数を高めて空転トルクを高める構成としたもので、
前記座面の微細な凹凸は座面平面度を維持して設けられることを特徴とする。
さらに、他の発明は、頭部と、ねじ山を備えたねじ軸部とを有し、前記ねじ軸部のねじ山によって相手材の下孔にめねじを成形しながら締結されるタッピンねじのねじ締結構造であって、
前記頭部の座面を微細な凹凸を有する粗面とすることにより、摩擦係数を高めて空転トルクを高める構成としたもので、
前記頭部の首下付け根部にはアンダーカット部が設けられており、前記座面はアンダーカット部を取り囲むように円環状に設けられ、座面の表面粗さはアンダーカット部よりも粗く設定されていることを特徴とする。
さらに、他の発明は、頭部と、ねじ山を備えたねじ軸部とを有し、前記ねじ軸部のねじ山によって相手材の下孔にめねじを成形しながら締結されるタッピンねじのねじ締結構造であって、
前記頭部の座面を微細な凹凸を有する粗面とすることにより、摩擦係数を高めて空転トルクを高める構成としたもので、
前記座面の微細な凹凸は座面平面度を維持して設けられることを特徴とする。 In order to achieve the above object, according to the present invention, in a tapping screw having a head and a screw shaft portion, the seating surface of the head is a rough surface having fine irregularities, thereby increasing the friction coefficient and causing the idling. It is configured to increase 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. It is characterized by being.
Another invention is a tapping screw having a head portion and a screw shaft portion.
By making the seating surface of the head a rough surface having fine irregularities, the friction coefficient is increased and the idling torque is increased.
The minute unevenness of the seating surface is provided while maintaining the seating surface flatness.
Furthermore, another invention has a head and a screw shaft portion provided with a screw thread, and is a tapping screw that is fastened while forming a female screw in a pilot hole of a mating member by the screw thread of the screw shaft portion. A screw fastening structure,
By making the seating surface of the head a rough surface having fine irregularities, 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. It is characterized by being.
Furthermore, another invention has a head and a screw shaft portion provided with a screw thread, and is a tapping screw that is fastened while forming a female screw in a pilot hole of a mating member by the screw thread of the screw shaft portion. A screw fastening structure,
By making the seating surface of the head a rough surface having fine irregularities, the friction coefficient is increased and the idling torque is increased.
The minute unevenness of the seating surface is provided while maintaining the seating surface flatness.

前記座面の外径は、頭部外周の最大径よりも小さい。
頭部の外周には、工具寿命を向上させる為に頭部成形ダレが発生し、頭部外周の最大径より座面の外径が小さく、頭部座面積は小さくなってしまうが、座面を粗面とすることで、工具寿命を損なうことなく、空転トルクを向上させることができる。
座面の微細な凹凸は座面平面度を維持して設けておけば、座面を全周にわたって均等に接触させることができる。
座面の表面粗さは、最大高さ粗さＲｚで、１５μｍ〜５０μｍが好適である。 The outer diameter of the bearing surface is smaller than the maximum diameter of the head circumference.
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.

本発明によれば、頭部座面を粗面として摩擦係数を高めることにより、座面積、ねじ山のひっかかり数を十分にとれなくても、空転トルクを向上させることができ、確実な締め付けが可能となる。   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）は本発明の実施の形態に係るタッピンねじを示す全体図、（Ｂ）は（Ａ）のＢ−Ｂ線断面図、（Ｃ）は（Ａ）の部分拡大図である。(A) is the whole figure which shows the tapping screw which concerns on embodiment of this invention, (B) is the BB sectional drawing of (A), (C) is the elements on larger scale of (A). 図１の頭部座面の表面粗さを従来品と比較して示すグラフである。It is a graph which shows the surface roughness of the head seat surface of FIG. 1 compared with a conventional product. 座面粗さと空転トルクの関係を示すグラフである。It is a graph which shows the relationship between a bearing surface roughness and idling torque. 図１のタッピンねじの締め付けた状態を示す概略図。Schematic which shows the state which fastened the tapping screw of FIG.

以下に、本発明を、図示の実施形態に基づいて詳細に説明する。
図１は本発明の実施の形態に係るタッピンねじを示している。図において、１はタッピンねじを示すもので、このタッピンねじ１は、頭部１０と、頭部１０から延びるねじ軸２０とを備え、ねじ軸２０には、完全ねじ山形状のねじ山２１が形成された平行ねじ部２２と、平行ねじ部２２の先端側に先端に向けて徐々に小径となるテーパねじ部２４とを備えている。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.

頭部１０は鍋形形状で、頂部にビット穴１８が設けられ、頭部１０の裏面側に、締め付け時に被締結材に着座する座面１６が設けられている。この実施の形態では、頭部裏面には、ねじ軸２０の首下が頭部と接続される付け根部の周囲にアンダーカット部１２が設けられ、座面１６は、アンダーカット部１２を取り囲むように全周に亘って円環状に形成されている。
また、頭部１０の外周側面は高さ方向中央部から頭部裏面に向かって徐々に小径となるように縮径された頭部成形ダレ１４となっている。この頭部成形ダレ１４の縮径分だけ、頭部１０外周の最大径よりも座面１６の外径は小さくなっている。
本発明は、座面１６を微細な凹凸を有する粗面とすることにより摩擦係数を高め、空転トルクを高めたものである。座面１６の表面粗さは、アンダーカット部１２よりも粗く設定される。アンダーカット部１２の表面粗さは頭部１０の表面粗さとほぼ同じであり、座面１６の表面粗さは頭部１０の表面粗さよりも粗い。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.

図２は、本発明の実施品と従来品とを比較して示す粗さ線図である。（Ａ）は本発明の実施品の拡大斜視、（Ｂ）はその粗さ線図、（Ｃ）は従来品の拡大写真、（Ｄ）はその粗さ線図である。
本発明の実施品の場合、図２（Ｂ）に示すように、０．２５ｍｍ間における最大山高さ及び最大谷高さのピークが５本未満となっている。５本以上の細かいピークとなると、摩擦力に与える影響はあまり大きくなく、０．２５ｍｍ間における最大山高さ及び最大谷高さのピークを５本未満とすることが好ましい。
従来品の場合、図２（Ｄ）に示すように、座面の表面粗さは、Ｒｚ（最大高さ粗さ、日本工業規格ＪＩＳ Ｂ０６０１，２００１改正）で１０μｍより小さいレベルである（基準長さは０．２５ｍｍ）。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).

図４は、本実施の形態のタッピンねじを、薄板の被締結材１１０とめねじ材１２０を重ねて締結した締結構造を示している。特に図示していないが、被締結材１１０及びめねじ材には下孔が設けられており、締結初期には、ねじ軸部２０のねじ山２１によって下孔にめねじが成形され、さらに締め付けることにより、頭部の座面１６が被締結材１１０に着座し、さらに、空転トルク以下の所定のトルクに達するまで締め付けることにより、締め付け作業が終了する。
着座した後の締め付けによって、締め付けられていくが、本実施の形態では座面１６に微細な凹凸が設けられているので、摩擦係数が高く、座面１６と被締結材１１０間の摩擦トルクが高くなり、その分、空転トルクも高くなっている。すなわち、座面１６を粗面にするだけで、ねじ込みトルクと空転トルクの差を大きくでき、適正な締め付けトルクを設定することで、ねじが破損することなく、確実に締め付けることができる。
特に、この実施の形態では、アンダーカット部１２を設けて、可及的にねじ軸２０のねじ山２１を頭部に近づけて形成し、係合するねじ山数を多くしており、空転トルクをより大きくできる。図示例では、アンダーカット部１２によって、２山のひっかかり数が一山多くなって３山程度となっている。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.

また、アンダーカット部１２を設けることで座面積が狭くなっているものの、実際にアンダーカット部１２を設けないで座面１６を粗面にしない従来例と比較したところ、本願発明のように座面積が狭くても、粗面とした方が、空転トルクが高くなった。
また、頭部成形ダレ１４を残しても空転トルクを高くできるので、工具命数を長くできるという利点もある。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.

図３は、座面粗さと空転トルクの関係を示している。
座面粗さは、最大高さ粗さＲｚ（日本工業規格ＪＩＳ Ｂ０６０１，２００１改正、基準長さ０．２５ｍｍ）で、５μｍ〜５０μｍの範囲のデータを示している。グラフに示される通り、当初、５μｍで２．７［Ｎ・ｍ］程度であったところ、１０μｍで３．０［Ｎ・ｍ］、１５μｍで３．２［Ｎ・ｍ］、３０μｍで３．７［Ｎ／ｍ］、４０μｍ〜５０μｍで３．８〜３．９［Ｎ／ｍ］となっている。
この結果から、最大高さ粗さＲｚが、１０μmを越えていれば効果が出始めるので、１０μｍ〜５０μｍの範囲であれば、空転トルクを十分高くでき、１５μｍ以上がより効果的である。また、３０μｍを超えると５０μほぼ横ばいとなるので、１５μｍ〜３０μｍの範囲が好適である。座面１６は基本的に平面であり、微細な凹凸は座面平面度を維持して設けられる。
特に、図４に示した３山程度、たとえば２山乃至５山程度しかねじ山ひっかかり数が確保できない場合でも、最大高さ粗さＲｚの範囲を上記範囲１０μｍ〜５０μｍ、より好ましくは１５μｍ〜３０μｍに設定することにより、空転トルクを大きくでき、適正な締結トルクで締結することができる。もちろん、ねじ山の引っ掛かり数は２山乃至５山程度に限定されるものではなく、５山以上であってもよいし、場合によっては２山以下でもよい。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, if the maximum height roughness Rz exceeds 10 μm, the effect starts to appear. Therefore, if it is in the range of 10 μm to 50 μm, the idling torque can be sufficiently increased, 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 suitable. The seating surface 16 is basically a flat surface, and fine irregularities are provided while maintaining the seating surface flatness.
In particular, even in the case where 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.

なお、上記実施の形態ではアンダーカット部を設けているが、アンダーカット部を設けない構成でもよいし、頭部成形ダレが無い構成でもよい。
頭部形状としては、鍋形に限られず種々の頭部形状に適用することができる。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.

１ タッピンねじ
１０ 頭部
１２ アンダーカット部
１４ 頭部成形ダレ
１６ 座面
２０ ねじ軸、２１ ねじ山、２２ 平行ねじ部、２４ テーパねじ部
１１０ 被締結材、１２０ めねじ材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 (12)

頭部とねじ軸部とを有するタッピンねじにおいて、
前記頭部の座面を微細な凹凸を有する粗面とすることにより、摩擦係数を高めて空転トルクを高める構成としたもので、
前記頭部の首下付け根部にはアンダーカット部が設けられており、前記座面はアンダーカット部を取り囲むように円環状に設けられ、座面の表面粗さはアンダーカット部よりも粗く設定されていることを特徴とするタッピンねじ。 In a tapping screw having a head and a screw shaft,
By making the seating surface of the head a rough surface having fine irregularities, 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. A tapping screw characterized by being made . 前記座面の外径は、頭部外周の最大径よりも小さい請求項１に記載のタッピンねじ。 The tapping screw according to claim 1, wherein an outer diameter of the seating surface is smaller than a maximum diameter of a head outer periphery. 前記座面の微細な凹凸は座面平面度を維持して設けられる請求項１又は２に記載のタッピンねじ。 The tapping screw according to claim 1 or 2 , wherein the fine unevenness of the seating surface is provided while maintaining the seating surface flatness. 前記座面の表面粗さは、最大高さ粗さＲｚで、１０μｍ〜５０μｍとする請求項１乃至３のいずれかの項に記載のタッピンねじ。 The tapping screw according to any one of claims 1 to 3 , wherein the seat surface has a maximum surface roughness Rz of 10 µm to 50 µm. 前記座面の表面粗さは頭部外周の表面粗さよりも粗い請求項１乃至４のいずれかの項に記載のタッピンねじ。   The tapping screw according to any one of claims 1 to 4, wherein a surface roughness of the seating surface is rougher than a surface roughness of a head outer periphery. 頭部とねじ軸部とを有するタッピンねじにおいて、
前記頭部の座面を微細な凹凸を有する粗面とすることにより、摩擦係数を高めて空転トルクを高める構成としたもので、
前記座面の微細な凹凸は座面平面度を維持して設けられることを特徴とするタッピンねじ。 In a tapping screw having a head and a screw shaft,
By making the seating surface of the head a rough surface having fine irregularities, the friction coefficient is increased and the idling torque is increased.
The tapping screw is characterized in that the fine unevenness of the seating surface is provided while maintaining the seating surface flatness. 頭部と、ねじ山を備えたねじ軸部とを有し、前記ねじ軸部のねじ山によって相手材の下孔にめねじを成形しながら締結されるタッピンねじのねじ締結構造であって、
前記頭部の座面を微細な凹凸を有する粗面とすることにより、摩擦係数を高めて空転トルクを高める構成としたもので、
前記頭部の首下付け根部にはアンダーカット部が設けられており、前記座面はアンダーカット部を取り囲むように円環状に設けられ、座面の表面粗さはアンダーカット部よりも粗く設定されていることを特徴とするタッピンねじのねじ締結構造。 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;
By making the seating surface of the head a rough surface having fine irregularities, 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. screw fastening structure tapping screw, characterized in that it is. めねじとの引っ掛かり山数が２山乃至５山であり、前記座面の表面粗さは、最大高さ粗さＲｚで、１０μｍ〜５０μｍである請求項７に記載のタッピンねじのねじ締結構造。   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. . 前記座面の外径は、頭部外周の最大径よりも小さい請求項７又は８に記載のタッピンねじのねじ締結構造。 The screw fastening structure for a tapping screw according to claim 7 or 8 , wherein an outer diameter of the seating surface is smaller than a maximum diameter of a head outer periphery. 前記座面の微細な凹凸は座面平面度を維持して設けられる請求項７乃至９のいずれかの項に記載のタッピンねじのねじ締結構造。 The screw fastening structure for a tapping screw according to any one of claims 7 to 9 , wherein the fine unevenness of the seating surface is provided while maintaining the seating surface flatness. 前記座面の表面粗さは頭部外周の表面粗さよりも粗い請求項７乃至１０のいずれかの項に記載のタッピンねじのねじ締結構造。 The screw fastening structure for a tapping screw according to any one of claims 7 to 10 , wherein the surface roughness of the seating surface is rougher than the surface roughness of the outer periphery of the head. 頭部と、ねじ山を備えたねじ軸部とを有し、前記ねじ軸部のねじ山によって相手材の下孔にめねじを成形しながら締結されるタッピンねじのねじ締結構造であって、
前記頭部の座面を微細な凹凸を有する粗面とすることにより、摩擦係数を高めて空転トルクを高める構成としたもので、
前記座面の微細な凹凸は座面平面度を維持して設けられることを特徴とするタッピンねじのねじ締結構造。 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;
By making the seating surface of the head a rough surface having fine irregularities, the friction coefficient is increased and the idling torque is increased.
The screw fastening structure of a tapping screw, wherein the unevenness of the seating surface is provided while maintaining the seating surface flatness.
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