JP2005090530A - Locking fastening structure for piling member - Google Patents

Locking fastening structure for piling member Download PDF

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JP2005090530A
JP2005090530A JP2003320782A JP2003320782A JP2005090530A JP 2005090530 A JP2005090530 A JP 2005090530A JP 2003320782 A JP2003320782 A JP 2003320782A JP 2003320782 A JP2003320782 A JP 2003320782A JP 2005090530 A JP2005090530 A JP 2005090530A
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bush
bolt
fastening structure
hole
slit
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Fusao Yamada
房夫 山田
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Abstract

<P>PROBLEM TO BE SOLVED: To realize a locking fastening structure for a plurality of piling members. <P>SOLUTION: A bush 8 vertically provided with a slit 10 is attached in a thin part in the form of an overturned cone having an eccentric through-hole 9 that is a little larger than a nominal diameter of a bolt 2. In a bolt through-hole 6 above a surface of a member to be fastened 4 on the side where a bolt head 2a is applied, a hole part 11 in the form of an overturned cone is bored having a taper surface of the same inclination angle to the inclination angle of the overturned cone of the bush 8. The bush 8 is inserted before fastening. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、複数重積材を締結ボルトを介して締結一体化する場合に、当該締結ボルトの螺結基盤を端側の一の被締結材にとるとする締結法における緩み止め締結構造に関するものである。   The present invention relates to a loosening prevention fastening structure in a fastening method in which when a plurality of stacked members are fastened and integrated through fastening bolts, the fastening base of the fastening bolt is taken as one fastened material on the end side. It is.

例えば２枚若しくは３枚の複数の重積材の締結法として、図６ａ，ｂに示す如く、端側の一の被締結材１に、締結ボルト２の螺結基盤としてタップ３を切り、他の被締結材４若しくは４，５にはボルト透孔６を穿がって締結する方法が従来より行われている。突き出しを少なくまとめられること、ボルト２の頭２ａとは反対側にナットを当てがわなくて済む（被締結材１がナットの役を果たしている）ので、作業条件に応じて採用される手段である。
作業条件が許せば、図示省略するも上記ボルト２の先端を被締結材１より突き出させてナットを当てがって螺結基盤の補強をすることもある。なお、図中７はボルト２頭２ａが当接する被締結材４に当てがわれる座金を示す。 For example, as a method of fastening a plurality of stacked materials of two or three, as shown in FIGS. 6a and 6b, a tap 3 as a screwing base of a fastening bolt 2 is cut on one fastening material 1 on the end side, and the like. Conventionally, a fastening method is performed by drilling a bolt through hole 6 in the material to be fastened 4 or 4 and 5. Since the protrusions can be gathered together and the nut 2 does not have to be applied to the opposite side of the head 2a of the bolt 2 (the material 1 to be fastened serves as a nut), the means adopted according to the working conditions is there.
If working conditions permit, although not shown in the drawings, the screw base may be reinforced by protruding the tip of the bolt 2 from the material to be fastened 1 and applying a nut. In the figure, reference numeral 7 denotes a washer applied to the fastened material 4 with which the two bolts 2a abut.

ところで、上記の如く、おねじ部品とめねじ部品が被締結部材を締め付けている構造を「ねじ締結体」というが、締め付けによって発生するおねじ部品の中の引っ張り力（軸力）と被締結部材の中の圧縮力（締め付け力）で一体化している。二つの力は、ねじ締結体に外力が作用していないときにつり合う。この状態における軸力と締め付け力を総称して「予張力」と呼ぶ。
ところが何等かの理由で、ねじ締結体の予張力は低下することがある。これが「ねじ緩み」である。
ねじ緩みの原因は、接触部の不具合と繰り返し外力の作用に求められる。図７で、接触部はねじ面（イ）、被締結部材両側の座面（ロとニ）、被締結部材の接合面（ハ）の四つ。一方、繰り返し外力は軸方向外力（Ｗa）、軸直角方向外力（Ｗi）、軸回りモーメント（Ｍa）曲げモーメント（Ｍb）の四つになる。予張力と繰り返し外力がそれぞれ単独あるいは相乗的に接触部のどこかに過大な力を与えたり応力を生じさせたりすることにより、マクロ的な塑性変形や滑り、ミクロ的な局部塑性変形やフレッティング（微動摩耗）を招く。この結果、予張力が失われてねじが緩む。
ねじ緩みを大別すると、ねじが戻り回転せずに生じるタイプと戻り回転して発生するタイプがある（表１）。 By the way, as described above, the structure in which the male threaded part and the female threaded part fasten the member to be fastened is referred to as “screw fastening body”, but the tensile force (axial force) in the male threaded part generated by fastening and the fastened member It is integrated with the compression force (tightening force) inside. The two forces are balanced when no external force is acting on the screw fastening body. The axial force and tightening force in this state are collectively referred to as “pretension”.
However, for some reason, the pretension of the screw fastening body may decrease. This is “screw loosening”.
The cause of the loosening of the screw is required for the failure of the contact portion and the action of repeated external forces. In FIG. 7, there are four contact portions: a threaded surface (A), seating surfaces (B and D) on both sides of the fastened member, and joint surfaces (C) of the fastened member. On the other hand, the repeated external forces are four in the axial direction external force (Wa), the axial perpendicular direction external force (Wi), the axial moment (Ma) and the bending moment (Mb). Pre-tension and repeated external force either individually or synergistically apply excessive force or generate stress somewhere in the contact area, thereby causing macro plastic deformation or slip, micro local plastic deformation or fretting. (Fine wear). As a result, the pretension is lost and the screw is loosened.
There are two types of screw loosening: a type that occurs when the screw does not rotate back and a type that occurs when the screw rotates back (Table 1).

Figure 2005090530
Figure 2005090530

上記の「戻り回転“なし”は正しい締め付けをして予張力が失われない配慮で回避出来るが、「戻り回転“あり”」は、正しい締め付けでも、過酷な振動性の外力が作用すると軸力が低下して“緩み”を生じるもので、この“緩み”を止める数多くの提案がなされている。 The above "No return rotation" can be avoided with the correct tightening and pre-tension is not lost, but "With return rotation" is an axial force when severe vibrational external force is applied even with correct tightening. As a result of the decrease, “slack” occurs, and many proposals have been made to stop this “slack”.

緩み止め効果についての実験結果の報告も、試験片に様々な緩み止めを施したねじ締結体（ねじの呼び径はＭ１０−Ｐ１．５）を用い、振動性の力を軸直角方向に加えて軸力の低下具合いを比較している。フランジ付き六角ナット、ナイロンリング入りナットが実用的なものと評価されている。   As for the report of the experimental results on the locking effect, a screw fastening body (screw nominal diameter: M10-P1.5) with various lockings applied to the test piece was used, and a vibrating force was applied in the direction perpendicular to the axis. The degree of decrease in axial force is compared. Hexagon nut with flange and nut with nylon ring are evaluated as practical.

叙上の結果は、以下の如く解析される。すなわち、ボルト・ナットを締め付けるときに与えるトルクの４０％はねじ接合面の摩擦で４０％は座面接合面の摩擦で失う。締め付けトルクの最大でも２０％がねじのリード角で拡大されて締め付け力に変換されるに過ぎない。ねじ締結においては摩擦の制御が最も重要な課題で、これをクリアしなければ信頼性の高いねじ締結は得られない。半面、締め付けられたねじが緩み方向に回転しないのは、この摩擦の効果である。ねじ締結体に大きな軸直角外力が作用すると、ボルトあるいはナットの座面で滑り始める。ねじ接合面はねじ山半角で傾いたリード角の勾配を持つ斜面であるねじ面も滑る。このようにねじ接合面で滑り始めると、ねじ面の摩擦係数は小さくなる方向で変化する。ねじが軸直角方向の外力で戻り回転を連続的に生じる条件を満たすと、ボルト・ナットがたちまち脱落するほど急激に緩む。 The above results are analyzed as follows. That is, 40% of the torque applied when tightening the bolts and nuts is lost by friction on the screw joint surface and 40% is lost by friction on the seat joint surface. At most, 20% of the tightening torque is enlarged by the lead angle of the screw and converted into a tightening force. In screw fastening, friction control is the most important issue, and unless this is cleared, highly reliable screw fastening cannot be obtained. On the other hand, it is the effect of this friction that the tightened screw does not rotate in the loosening direction. When a large axial perpendicular force acts on the screw fastening body, it starts to slide on the seat surface of the bolt or nut. The screw joint surface also slides on the screw surface, which is a slope with a slope of the lead angle inclined by the half angle of the thread. Thus, when it begins to slide on a screw joint surface, the friction coefficient of a screw surface changes in the direction which becomes small. If the condition that the screw returns and rotates continuously with an external force perpendicular to the axis is satisfied, the bolts and nuts will loosen so rapidly that they will fall off.

既述のフランジ付き六角ナットの好成績は既述した図７中の「接触部ロ」の摩擦に因があり、ナイロンリング入りナットの好成績は、「接触部イ」の摩擦に因がある。   The above-mentioned good results of the flanged hexagon nuts are due to the friction of the “contact part b” in FIG. 7 described above, and the good results of the nuts with nylon rings are due to the friction of the “contact part a”.

このナイロンリング入りナットと同機構をもって緩み止めに優れるのが図８に示すスレッドフォーミングタイプのタッピンねじで、これは、単にめねじ加工費用を節約できるだけでない。おねじとめねじのはめ合い隙間がないことから、普通のねじのはめ合いで懸念されるねじ面の滑りを防ぐ効果がある。上記のフランジ付き六角ナットにあっては、図７中の「接触部ロ」（被締め付け物の表面）の状態に左右されて不確実であり、戻り回転を伴うねじ緩みを防ぐためには、ねじはめ合い部の摩擦抵抗の確保しか対策はない。   The thread-forming type tapping screw shown in FIG. 8 has the same mechanism as this nylon ring-containing nut and is excellent in preventing loosening, and this can not only save female thread processing costs. Since there is no fitting clearance between the male screw and the female screw, there is an effect of preventing the slippage of the screw surface, which is a concern when fitting ordinary screws. The above-mentioned flanged hexagon nut is uncertain because it depends on the state of “contact part b” (surface of the object to be tightened) in FIG. 7, and in order to prevent screw loosening with return rotation, The only countermeasure is to ensure the frictional resistance of the mating part.

おねじとめねじのはめ合い隙間を有しているにもかかわらず、ここに高摩擦抵抗を形成してねじ緩み止めとするのが所謂「ピッチロス」である。その機構を図９〜１１にて以下、説明する。   In spite of having a fitting clearance between the male screw and the female screw, a so-called “pitch loss” is to form a high frictional resistance to prevent screw loosening. The mechanism will be described below with reference to FIGS.

図中Ａはボルトのおねじ、Ｂはナットのめねじを夫々示す。
図９はナット緩め付け時で、めねじＢのねじ山半角の上方斜面Ｂ−１は、ボルトのおねじのねじ山半角の下方斜面Ａ−１に接圧し、反対側にはめ合い隙間に基づく間隙Ｃを形成する。相隣りのピッチＰ１、Ｐ２はＰ１＝Ｐ２である。図１０は、ナット緩み時で、めねじＢのねじ山半角の下方斜面Ｂ−２は、ボルトのおねじのねじ山半角の上方斜面Ａ−２に接圧し、反対側にはめ合い隙間に基づく間隙Ｃを形成する。相隣りのピッチＰ１、Ｐ２はＰ１＝Ｐ２である。 In the drawing, A indicates a male screw and B indicates a female screw of a nut.
FIG. 9 shows the case where the nut is loosened, and the upper slope B-1 of the thread half-angle of the female screw B comes into contact with the lower slope A-1 of the thread half-angle of the male thread of the bolt, and the opposite side is based on the fitting gap. A gap C is formed. The adjacent pitches P 1 and P 2 are P 1 = P 2 . FIG. 10 shows that when the nut is loosened, the lower slope B-2 of the thread half angle of the female screw B is in contact with the upper slope A-2 of the thread half angle of the male thread of the bolt, and the opposite side is based on the fitting clearance. A gap C is formed. The adjacent pitches P 1 and P 2 are P 1 = P 2 .

上記の図９、１０は、いずれもＰ１＝Ｐ２ピッチロス無しの場合であるが、故意にピッチを違えさせる（Ｐ１＞Ｐ２）工夫を加えた場合のナット緩み時を図１１に示すと、３点接圧が不整となり、ナットの緩みは、最上位のＢ−１とＡ−１との接圧で阻害される。これが所謂ピッチロスで、ダブルナットもこの原理での緩み止めである。その他、ナット若しくはボルトに強引な曲げ姿勢を加えること等で、ピッチロスを形成することが出来る。 FIGS. 9 and 10 show the case where P 1 = P 2 without any pitch loss, but FIG. 11 shows the time when the nut is loosened when a device is intentionally made to change the pitch (P 1 > P 2 ). And the three-point contact pressure becomes irregular, and the loosening of the nut is hindered by the contact pressure between the uppermost B-1 and A-1. This is the so-called pitch loss, and the double nut is also a locking mechanism based on this principle. In addition, pitch loss can be formed by adding a forcible bending posture to the nut or bolt.

以上の観点から図６に示される「ねじ締結体」を検討するに、ほとんど“緩み止め”効果を期待出来ないことは明らかである。   From the above point of view, when examining the “screw fastening body” shown in FIG. 6, it is clear that almost no “loosening prevention” effect can be expected.

解決しようとする問題点は、既述した複数重積材を締結ボルトを介して締結一体化する場合における緩み止め能の低さを、改善することである。   The problem to be solved is to improve the low anti-loosening capability in the case where the plurality of stacked materials described above are fastened and integrated through fastening bolts.

本発明の複数重積材の緩み止め締結構造は、ボルトの呼び径よりもやや大きい偏心貫通孔を有した逆円錐体の薄肉部に欠円用スリットを縦設したブッシュを付帯させると共に、ボルト頭の当接する側の被締結材面よりボルト透孔上部に対して、該ブッシュの逆円錐傾斜角度と同一傾斜角度のテーパ面を有する逆円錐状孔部を穿孔し、該ブッシュを介挿した状態で締結するとしたことを特徴とする。   The multi-layered material loosening-fastening fastening structure of the present invention includes a bush having a slit formed vertically in a thin portion of an inverted cone having an eccentric through hole slightly larger than the nominal diameter of the bolt, and a bolt An inverted conical hole portion having a tapered surface having the same inclination angle as the reverse cone inclination angle of the bush is drilled from the surface of the material to be fastened on the side in contact with the head to the upper part of the bolt through hole, and the bush is inserted. It is characterized in that it is fastened in a state.

本発明の締結構造は、被締結物を締め付けていくと、ボルト頭若しくは介装座金を介してブッシュ上端に作用するボルトの締め付け力が、欠円用スリットに加わっていき、欠円用スリットの隙間が小さくなって、ブッシュの逆円錐状筒片は縮径し、ボルト透孔上部の逆円錐状孔部とボルトとの間にブッシュがあたかも目詰材の如く充填され、ボルトとの間にブッシュを噛み挟んだ状態となり、ボルト頭の当接する側の被締結材とボルトはブッシュを介して強固に一体化する。この時、ボルトのおねじはブッシュに喰い込むが、これは、正に図８に紹介したタッピンねじと同効果を奏する。さらには、縮径したブッシュが逆円錐状孔部に嵌合していく際に、偏心で形成のブッシュの肉厚部が、局部的に強圧し、ブッシュの目詰め効果が高まりボルトとボルト頭の当接する側の被締結材の双方に働く摩擦力が増大する。この際、ピッチロス効果をも発生させている。また、偏向的にボルト２上部に加えられる側圧はボルト２を曲げさせ被締結材１のタップ３との間のピッチを狂わせ、ピッチロスを発生させる。しかして、上部ではタッピンねじ効果とピッチロス効果、下部でピッチロス効果を奏し、緩み止めの効能が向上する。   In the fastening structure of the present invention, when the object to be fastened is tightened, the bolt tightening force acting on the upper end of the bush via the bolt head or the interposed washer is applied to the missing circle slit. As the gap becomes smaller, the reverse conical cylindrical piece of the bush is reduced in diameter, and the bush is filled as if it is a clogging material between the reverse conical hole at the top of the bolt hole and the bolt. The bush is in a state of being pinched, and the material to be fastened and the bolt on the side where the bolt head abuts are firmly integrated via the bush. At this time, the male screw of the bolt bites into the bush, which has the same effect as the tapping screw introduced in FIG. Furthermore, when the reduced-diameter bush is fitted into the inverted conical hole, the thick part of the eccentrically formed bush is locally pressurized, increasing the clogging effect of the bush and increasing the bolt and bolt head. The frictional force acting on both of the materials to be fastened on the abutting side increases. At this time, a pitch loss effect is also generated. Further, the side pressure applied to the upper portion of the bolt 2 in a deflected manner causes the bolt 2 to bend and deviates the pitch with the tap 3 of the material 1 to be fastened, thereby generating pitch loss. Thus, the tapping screw effect and the pitch loss effect are produced at the upper part, and the pitch loss effect is produced at the lower part, thereby improving the effectiveness of the loosening prevention.

シンプルで汎用性ある緩み止めの締結構造を実現した。 A simple and versatile locking structure with a locking mechanism has been realized.

図１は、本発明の締結構造の展開図であって、８はブッシュで、図示例にあっては、ボルト２の呼び径よりもやや大きい偏心貫通孔９を有した逆円錐体のリングの薄肉部に欠円用スリット１０を縦設したもので構成している。   FIG. 1 is a development view of the fastening structure of the present invention, in which 8 is a bush, and in the illustrated example, an inverted conical ring having an eccentric through hole 9 slightly larger than the nominal diameter of the bolt 2. The thin-walled portion is formed by vertically arranging a slit 10 for a missing circle.

ボルト２の頭２ａが当接する側の被締結材４の表面よりボルト透孔６上部に対しては、予め該ブッシュ８の逆円錐傾斜角度と同一傾斜角度のテーパ面を有する逆円錐状孔部１１を穿孔してある。   From the surface of the material to be fastened 4 on the side where the head 2a of the bolt 2 abuts to the upper part of the bolt through hole 6, an inverted conical hole portion having a tapered surface having the same inclination angle as the inverse cone inclination angle of the bush 8 in advance. 11 is perforated.

しかして、ブッシュ８を逆円錐状孔部１１に上半が突き出た態様の下半係止の姿勢で嵌着して、ボルト２の締結をとり行なう。 Thus, the bush 8 is fitted into the inverted conical hole 11 in the lower half locking posture with the upper half protruding, and the bolt 2 is fastened.

締結態様は図４に示される。すなわち、ボルト２の螺進でブッシュ８を逆円錐状孔部１１に押し込んでいくと、欠円用スリット１０の隙間が小さくなって、ブッシュ８は縮径し、逆円錐状孔部１１とボルト２との間にブッシュ８があたかも目詰材の如く介装され、ブッシュ８を噛み挟んだ状態となり、被締結材４とボルト２はブッシュ８を介して強固に一体化して、タッピンねじ効果を奏する。 The fastening manner is shown in FIG. That is, when the bush 8 is pushed into the inverted conical hole 11 by the screwing of the bolt 2, the gap of the cutout slit 10 is reduced, the bush 8 is reduced in diameter, and the reverse conical hole 11 and the bolt are reduced. The bush 8 is inserted as if it is a clogging material between the bush 2 and the bush 8 and the bolt 8 is sandwiched between them. The material to be fastened 4 and the bolt 2 are firmly integrated with each other through the bush 8 to achieve the tapping screw effect. Play.

この際、ボルト２の螺合に伴って、縮径したブッシュ８が逆円錐状孔部１１に嵌合していく際に、偏心で形成のブッシュ８の肉厚部８ａが、径方向からボルト２を強圧し、円周上の局部的なくさび効果によって、ブッシュ８とボルト２の双方に働く摩擦力が増大する。この際ボルト２に加わる曲げは、ピッチロス効果をもたらす。他方、ボルト２下部にあっては、ボルト２が曲げられることによって、タップロス効果が発生し、上、下に発生する強力な摩擦部が緩み止めを達成する。 At this time, when the bush 8 having a reduced diameter is fitted into the inverted conical hole portion 11 as the bolt 2 is screwed, the thick portion 8a of the bush 8 formed eccentrically becomes a bolt from the radial direction. The frictional force acting on both the bush 8 and the bolt 2 increases due to the local wedge effect on the circumference. At this time, the bending applied to the bolt 2 brings about a pitch loss effect. On the other hand, at the lower part of the bolt 2, when the bolt 2 is bent, a tap loss effect is generated, and the strong friction portions generated at the upper and lower sides achieve locking prevention.

図示例では、座金７を介装したが、ボルト頭２ａに代わってブッシュ８の押し込みをしなければならず、その内径寸法は、必ずブッシュ８上面に載るものであらねばならない。上記の欠円用スリット１０は縦設（ストレート）以外のバリエーションを有している。   In the illustrated example, the washer 7 is interposed, but the bush 8 must be pushed in place of the bolt head 2a, and its inner diameter must be on the upper surface of the bush 8. The cutout slit 10 has variations other than vertical (straight).

例えば、ブッシュ８の欠円用スリット１０をボルト２のネジ部２ｂの螺旋方向と反対方向に傾斜して形成する。ブッシュ８の欠円用スリット１０がボルト２の螺旋と逆方向に傾斜していると、「戻し回転」力の作用の際にスリット１０のエッジがほぼ直交してブレーキ作用を生じ、緩み止め効果を高める。   For example, the slit 10 for the missing circle of the bush 8 is formed so as to be inclined in the direction opposite to the spiral direction of the screw portion 2b of the bolt 2. When the slit 10 for the cutout circle of the bush 8 is inclined in the direction opposite to the spiral of the bolt 2, the edge of the slit 10 is almost orthogonal to the brake action when the "returning rotation" force is applied, thereby preventing the loosening effect. To increase.

また、ブッシュ８の欠円用スリット１０を、ボルト２の螺旋方向と同一方向に傾斜して形成するとしても良い。
ボルト２の螺合の進行に伴う、螺旋状の締め付けトルクが、ブッシュ８の傾斜した欠円用スリット１０にガイドされて、すみやかにブッシュ８が均等に縮径していくため、ブッシュ８の縮径と「締め付け軸力」とが容易化される。 Further, the cutout slit 10 of the bush 8 may be formed to be inclined in the same direction as the spiral direction of the bolt 2.
The helical tightening torque accompanying the progress of the screwing of the bolt 2 is guided by the inclined slit 10 of the bush 8 and the bush 8 is immediately reduced in diameter uniformly. Diameter and “tightening axial force” are facilitated.

図３に示す如く、ブッシュ８の欠円用スリット１０の傾斜角度θを、ボルト軸に対して、略２０°から２５°に設定すると良い。これにより、欠円用スリット１０の端縁が、ボルト２のネジ部２ｂと一定の位相差を有して均等に当ることになり、螺旋状に加わる締め付けトルクにより、スムーズにブッシュ８を縮径することができる。   As shown in FIG. 3, the inclination angle θ of the cutout slit 10 of the bush 8 is preferably set to about 20 ° to 25 ° with respect to the bolt shaft. As a result, the end edge of the slit 10 for the cutout circle is evenly contacted with the screw portion 2b of the bolt 2 with a certain phase difference, and the bushing 8 is smoothly reduced in diameter by the tightening torque applied in a spiral shape. can do.

ブッシュ８の欠円用スリット１０の幅Ｓを、ボルト２を締め切った状態で、隙間を有する幅とすると良い。
締め切った状態で、ブッシュ８の欠円用スリット１０の端面が隙間を有する幅となるように、欠円用スリット１０の幅を設定しているため、締め切った状態にあっても、逆円錐状孔部１１とボルト８との間に噛み挟まれた状態のブッシュ８の強力なバネ力を維持して、強力な一体化を図ることができる。 The width S of the cutout slit 10 of the bush 8 may be a width having a gap in a state where the bolt 2 is tightened.
Since the width of the cut-out slit 10 is set so that the end face of the cut-out slit 10 of the bush 8 has a gap in the closed state, an inverted conical shape is obtained even in the closed state. It is possible to maintain a strong spring force of the bush 8 in a state of being sandwiched between the hole 11 and the bolt 8 and achieve a strong integration.

ブッシュ８を合成樹脂で形成しても良い。腐食が激しい場所に用いる場合等、使用目的や使用状況に応じて、弾力性に富んで強固な緩み止め効果を発揮する合成樹脂の長所を用いることができる。   The bush 8 may be formed of a synthetic resin. In the case of using in a place where corrosion is severe, the advantage of the synthetic resin which is rich in elasticity and exhibits a strong loosening prevention effect can be used depending on the purpose of use and the situation of use.

図２に示された如く、ブッシュ８の押し込みは、被締結材４の表面保護の面からも座金７を介する施工が多い。
そこで、ブッシュ８を単純リングで構成することなく、座金７付きで構成すると施工もやり易くなる。 As shown in FIG. 2, the pushing of the bush 8 is often performed through the washer 7 in terms of the surface protection of the material to be fastened 4.
Therefore, if the bush 8 is configured with a washer 7 without being configured with a simple ring, the construction is also facilitated.

図４ａ、ｂに示す組み付け手順は、ブッシュ８上面内径寄りに座金７嵌挿用の脚部１２を突設し、これを拡張付勢力を利用して座金７を透孔７ａに嵌挿圧着して一体化させて、座金７付きブッシュ８としたものである。
締め付け時、ブッシュ８は縮径化によって自動的に座金７から分離する。
部品管理上のメリットを享受できる。 The assembly procedure shown in FIGS. 4A and 4B is such that a leg 12 for inserting the washer 7 is provided close to the inner diameter of the upper surface of the bush 8, and the washer 7 is inserted into and crimped into the through-hole 7a using an extended urging force. The bush 8 with the washer 7 is integrated.
When tightening, the bush 8 is automatically separated from the washer 7 by reducing the diameter.
Benefit from parts management.

図４における座金７付きは、分離構成であるが、一体構成とすることもできる。
拡張付勢力が増加する分、逆円錐状孔部１１との間の一体化効果が大きくなる。 4 with a washer 7 is a separated configuration, but can also be integrated.
As the expanded biasing force increases, the effect of integration with the inverted conical hole 11 increases.

すなわち、図５に示すブッシュ８″は、座金部７′に、ボルトの呼び径よりもやや大きい偏心貫通孔を有し、該貫通孔９′の周囲に、ボルト軸方向下方にしたがって縮径する逆円錐状筒片１３を垂設し、座金部７′と逆円錐状筒片１３に連続した欠円用スリット１０′を形成して成る。
座金部７′は逆円錐状筒片１３と一体に縮径するので、ブッシュ８″としては大幅に拡張する付勢力を増し対逆円錐状孔部１１への接圧力を高める。 That is, the bush 8 ″ shown in FIG. 5 has an eccentric through hole slightly larger than the nominal diameter of the bolt in the washer portion 7 ′, and the diameter is reduced around the through hole 9 ′ in the lower direction of the bolt axis. An inverted conical cylindrical piece 13 is suspended, and a washer part 7 ′ and an inverted conical cylindrical piece 13 are formed to form a cutout slit 10 ′ continuous.
Since the diameter of the washer portion 7 ′ is integrally reduced with the inverted conical cylindrical piece 13, the urging force that greatly expands as the bush 8 ″ is increased and the contact pressure to the opposite conical hole portion 11 is increased.

複数重積材を締結ボルトを介して締結一体化する場合に、当該締結ボルトの螺結基盤を端側の一の被締結材にとるとする締結法における緩み止め不全が解消され、メンテ上の煩わしさが無くなることが考えられる。   When multiple stacking materials are fastened and integrated through fastening bolts, the loosening prevention failure in the fastening method in which the fastening base of the fastening bolt is taken as one fastening material on the end side is eliminated, It is conceivable that the troublesomeness is eliminated.

本発明締結構造の施工手順説明図である。（実施例１）It is construction procedure explanatory drawing of this invention fastening structure. (Example 1) 本発明締結構造説明図である。（実施例１）It is this invention fastening structure explanatory drawing. (Example 1) 本発明におけるブッシュの説明図である。（実施例１）It is explanatory drawing of the bush in this invention. (Example 1) ａ、ｂは、本発明におけるブッシュの組み付け手順図である。（実施例２）a and b are assembly procedure diagrams of the bush in the present invention. (Example 2) 本発明におけるブッシュの説明図である。（実施例３）It is explanatory drawing of the bush in this invention. Example 3 ａ、ｂは、従来の締結構造の説明図である。a and b are explanatory drawings of a conventional fastening structure. ねじ締結体の簡略モデルである。It is a simplified model of a screw fastening body. タッピンねじ説明図である。It is a tapping screw explanatory drawing. ピッチロス説明図である。It is pitch loss explanatory drawing. ピッチロス説明図である。It is pitch loss explanatory drawing. ピッチロス説明図である。It is pitch loss explanatory drawing.

符号の説明Explanation of symbols

１ 締結材
２ 締結ボルト
２ａ ボルト頭
２ｂ ネジ部
３ タップ
４ 被締結材
６ ボルト透孔
７ 座金
７ａ 透孔
８ ブッシュ
８′ ブッシュ
８″ ブッシュ
８ａ 肉厚部
９′ 貫通孔
１０ 欠円用スリット
１０′ 欠円用スリット
１１ 逆円錐状孔部
１２ 脚部
１３ 逆円錐状筒片 DESCRIPTION OF SYMBOLS 1 Fastening material 2 Fastening bolt 2a Bolt head 2b Screw part 3 Tap 4 Fastened material 6 Bolt through-hole 7 Washer 7a Through-hole 8 Bush 8 'Bush 8 "Bush 8a Thick part 9' Through-hole 10 Notch-circle slit 10 ' Slit for cutout 11 Reverse conical hole 12 Leg 13 Reverse conical cylindrical piece

Claims (8)

ボルトの呼び径よりもやや大きい偏心貫通孔を有した逆円錐体の薄肉部に欠円用スリットを縦設したブッシュを付帯させると共に、ボルト頭の当接する側の被締結材面よりボルト透孔上部に対して、該ブッシュの逆円錐傾斜角度と同一傾斜角度のテーパ面を有する逆円錐状孔部を穿孔し、該ブッシュを介挿した状態で締結するとしたことを特徴とする複数重積材の緩み止め締結構造。 A bush with vertical slits attached to the thin part of the inverted conical body with an eccentric through hole slightly larger than the nominal diameter of the bolt is attached, and the bolt through-hole from the surface of the material to be fastened on the side where the bolt head abuts A multi-stacked material characterized in that an inverted conical hole portion having a tapered surface having the same inclination angle as the reverse cone inclination angle of the bush is drilled in the upper portion and fastened with the bush interposed therebetween The anti-loosening fastening structure. ブッシュの欠円用スリットをボルトのネジ部の螺旋方向と反対方向に傾斜して形成した請求項１記載の複数重積材の緩み止め締結構造。 The multi-layered material loosening-fastening structure according to claim 1, wherein the slit for the cutout circle of the bush is formed so as to be inclined in a direction opposite to the spiral direction of the screw portion of the bolt. ブッシュの欠円用スリットを、ボルトのネジ部の螺旋方向と同一方向に傾斜して形成した請求項１記載の複数重積材の緩み止め締結構造。 The multi-layered material loosening-fastening structure according to claim 1, wherein the slit for the cutout circle of the bush is formed so as to be inclined in the same direction as the spiral direction of the screw portion of the bolt. ブッシュの欠円用スリットの傾斜角度を、ボルト軸に対して、略２０°から２５°に設定するとした請求項１記載の複数重積材の緩み止め締結構造。 The multi-layered material loosening-stop fastening structure according to claim 1, wherein an inclination angle of the slit for the cutout circle of the bush is set to approximately 20 ° to 25 ° with respect to the bolt shaft. ブッシュの欠円用スリットの幅を、ボルトとナットを締め切った状態で、隙間を有する幅とした請求項１記載の複数重積材の緩み止め締結構造。 The multi-layer material loosening-fastening structure according to claim 1, wherein a width of the slit for the cutout circle of the bush is a width having a gap in a state where the bolt and the nut are tightened. ブッシュ若しくはナットを合成樹脂で形成した請求項１記載の複数重積材の緩み止め締結構造。 The multi-layered material loosening-fastening structure according to claim 1, wherein the bush or nut is formed of a synthetic resin. ブッシュ上面内径寄りに対座金７嵌挿用の脚部を突設し、これを拡張付勢力を利用して座金透孔に嵌挿圧着して一体化させて、座金付きブッシュとしたものを用いることを特徴とする請求項１〜６記載の複数重積材の緩み止め締結構造。 A bushing with a washer is used by projecting a leg portion for inserting the washer 7 near the inner surface of the bush and integrating it by inserting and pressing it into the through hole of the washer using an extended biasing force. The multi-layered material loosening-fastening structure according to claim 1, wherein: 座金部に、ボルトの呼び径よりもやや大きい偏心貫通孔を有し、該貫通孔の周囲に、ボルト軸方向下方にしたがって縮径する逆円錐状筒片を垂設し、座金部と逆円錐状筒片に連続した欠円用スリットを形成して成るブッシュを用いることを特徴とする請求項１〜６記載の複数重積材の緩み止め締結構造。 The washer part has an eccentric through hole that is slightly larger than the nominal diameter of the bolt, and an inverted conical cylindrical piece that is reduced in diameter in the bolt axial direction downward is suspended around the through hole, and the washer part and the reverse cone 7. A multi-layered material loosening-fastening structure according to claim 1, wherein a bush formed by forming a slit for a continuous circle in a cylindrical piece is used.
JP2003320782A 2003-09-12 2003-09-12 Locking fastening structure for piling member Pending JP2005090530A (en)

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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007285422A (en) * 2006-04-18 2007-11-01 Nippon Steel Corp Bearing joint part and bearing joint bolt
JP2009116066A (en) * 2007-11-07 2009-05-28 Korg Inc Damper for piano and piano with damper
WO2011048709A1 (en) 2009-10-22 2011-04-28 Ichishima Tatsuru Method for fastening subframe to motor vehicle body by means of fastening bolts and subframe rigid collar for motor vehicle
US8353659B2 (en) 2009-10-22 2013-01-15 Tatsuru Ichishima Fastening method for a fastening bolt of a sub frame to car body and a sub frame rigid collar for car used for the fastening method
JP2014055673A (en) * 2012-09-13 2014-03-27 Lisi Aerospace Fastening device
WO2015016317A1 (en) * 2013-08-01 2015-02-05 Ｎｅｘｔ Ｉｎｎｏｖａｔｉｏｎ合同会社 Structure for preventing reverse rotation of threaded body
CN107147233A (en) * 2017-06-30 2017-09-08 广东威灵电机制造有限公司 Electric motor end cap assembly and motor and electric motor mounting structure
CN108869509A (en) * 2018-09-03 2018-11-23 杨富云 A kind of fastener locking method and its vibrationproof bolt
CN109714924A (en) * 2019-02-21 2019-05-03 山西全安新技术开发有限公司 It is a kind of for fastening the method and device of electric apparatus for explosive atmospheres cavity
US10302107B2 (en) * 2016-07-01 2019-05-28 Ford Motor Company Fastening system and method using a compressible sleeve
CN111237317A (en) * 2020-03-18 2020-06-05 成都迈特航空制造有限公司 Anti-loosening high-temperature-resistant fastening assembly with adjustable pretightening force

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007285422A (en) * 2006-04-18 2007-11-01 Nippon Steel Corp Bearing joint part and bearing joint bolt
JP4724590B2 (en) * 2006-04-18 2011-07-13 新日本製鐵株式会社 Bearing joint and bearing joint bolt
JP2009116066A (en) * 2007-11-07 2009-05-28 Korg Inc Damper for piano and piano with damper
WO2011048709A1 (en) 2009-10-22 2011-04-28 Ichishima Tatsuru Method for fastening subframe to motor vehicle body by means of fastening bolts and subframe rigid collar for motor vehicle
US8353659B2 (en) 2009-10-22 2013-01-15 Tatsuru Ichishima Fastening method for a fastening bolt of a sub frame to car body and a sub frame rigid collar for car used for the fastening method
JP2014055673A (en) * 2012-09-13 2014-03-27 Lisi Aerospace Fastening device
WO2015016317A1 (en) * 2013-08-01 2015-02-05 Ｎｅｘｔ Ｉｎｎｏｖａｔｉｏｎ合同会社 Structure for preventing reverse rotation of threaded body
US9909608B2 (en) 2013-08-01 2018-03-06 NejiLaw inc. Structure for preventing reverse rotation of threaded body
US10302107B2 (en) * 2016-07-01 2019-05-28 Ford Motor Company Fastening system and method using a compressible sleeve
CN107147233A (en) * 2017-06-30 2017-09-08 广东威灵电机制造有限公司 Electric motor end cap assembly and motor and electric motor mounting structure
CN107147233B (en) * 2017-06-30 2020-01-31 广东威灵电机制造有限公司 Motor end cover assembly, motor and motor mounting structure
CN108869509A (en) * 2018-09-03 2018-11-23 杨富云 A kind of fastener locking method and its vibrationproof bolt
CN109714924A (en) * 2019-02-21 2019-05-03 山西全安新技术开发有限公司 It is a kind of for fastening the method and device of electric apparatus for explosive atmospheres cavity
CN109714924B (en) * 2019-02-21 2024-06-04 山西全安新技术开发有限公司 Method and device for fastening explosion-proof electrical equipment cavity
CN111237317A (en) * 2020-03-18 2020-06-05 成都迈特航空制造有限公司 Anti-loosening high-temperature-resistant fastening assembly with adjustable pretightening force

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