JPH0689768B2 - High-strength bolt / nut / washer set - Google Patents
High-strength bolt / nut / washer setInfo
- Publication number
- JPH0689768B2 JPH0689768B2 JP31369590A JP31369590A JPH0689768B2 JP H0689768 B2 JPH0689768 B2 JP H0689768B2 JP 31369590 A JP31369590 A JP 31369590A JP 31369590 A JP31369590 A JP 31369590A JP H0689768 B2 JPH0689768 B2 JP H0689768B2
- Authority
- JP
- Japan
- Prior art keywords
- bolt
- steel
- strength
- arc
- head
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
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- Bolts, Nuts, And Washers (AREA)
Description
【発明の詳細な説明】 ［産業上の利用分野］ 本発明は、各種産業分野において利用される高力ボルト
・ナットおよび座金のセットに関し、特に土木、建築、
海洋構造物構築に用いられるれる耐遅れ破壊特性の優れ
た高力ボルト・ナット・座金のセットに係る。TECHNICAL FIELD The present invention relates to a set of high-strength bolts / nuts and washers used in various industrial fields, particularly civil engineering, construction,
It relates to a set of high-strength bolts, nuts, and washers with excellent delayed fracture resistance used in the construction of offshore structures.
［従来の技術］ 各産業分野において利用される鋼材の接合に際しては、
周知のとおり各種の溶接手段のほかボルト接合手段が一
般に用いられている。[Prior Art] When joining steel materials used in various industrial fields,
As is well known, various welding means as well as bolt joining means are generally used.
さて、近時経済性の追及と技術の進歩から鋼材の高張力
化が促進され、その接合に適した手段として、高力ボル
トが採用されるようになった。Nowadays, due to the pursuit of economic efficiency and technological progress, high tensile strength of steel materials has been promoted, and high-strength bolts have been adopted as a suitable means for joining them.
特に、土木、建築分野では接合の信頼性が高く、かつ作
業性も優れていることから摩擦接合手段が多用されるよ
うになり、それに用いるボルトとして、日本工業規格の
JIS−Ｂ−1186に規定される摩擦接合用高力六角ボル
ト、六角ナット、平座金のセットおよび日本鋼構造協会
規格JSSII−09構造用トルシア形高力ボルト・六角ナッ
ト・平座金のセットが広く採用されている。In particular, in the civil engineering and construction fields, since the joining is highly reliable and the workability is excellent, friction joining means are often used.
A wide range of sets of high-strength hexagon bolts, hexagon nuts, and flat washers for friction welding specified in JIS-B-1186 and Japan Steel Structural Association standard JSSII-09 structural torcia type high-strength bolts, hexagon nuts, and flat washers. Has been adopted.
本発明は主として前記摩擦接合用高力六角ボルト・ナッ
ト・中点平座金および構造用トルシア形高力ボルト・ナ
ット・平座金の改良に関するもので、以下本発明では説
明の都合上単に高力ボルト・ナット・平座金のセットと
総称する。The present invention mainly relates to improvements in the high-strength hexagon bolts / nuts / midpoint plain washers for friction welding and the structural torcia-type high-strength bolts / nuts / plain washers. In the present invention, the high-strength bolts are simply described for convenience of description. -Generally referred to as a set of nuts and flat washers.
さて、前記高力ボルトは、遅れ破壊現象のため現在のと
ころF11T（S11T）以上のものは使用が避けられている
が、一方鋼板の製造技術はますます進歩し、経済的な価
格で高強度のものが市販されるようになり、それにとも
なって強度の高い鋼構造物を製作するため耐遅れ破壊特
性の優れた高力ボルト（特にF15T級）の開発が強く望ま
れるようになった。As for the high-strength bolt, the use of F11T (S11T) or higher is currently avoided due to the delayed fracture phenomenon, but on the other hand, the steel plate manufacturing technology has advanced more and more, and the high strength at an economical price. Since these products are now on the market, the development of high-strength bolts (especially F15T class) with excellent delayed fracture resistance has been strongly desired in order to manufacture steel structures with high strength.
さて、前記遅れ破壊の防止には、材料に耐遅れ破壊特性
の優れたニッケルクロム鋼、ニッケルクロムモリブデン
鋼、クロム鋼、クロムモリブデン鋼、機械構造用マンガ
ン鋼、マンガンクロム鋼、アルミニウムクロムモリブデ
ン鋼のうち１種または高温用合金鋼ボルト材または特殊
用途合金鋼ボルト用棒鋼や熱処理可能な低・中炭素鋼な
どを使用するほか、さらに高力ボルト各部に生ずる応力
集中を出来るだけ小さくする必要のあることが一般に知
られており、加えて該高力ボルトにおいて、遅れ破壊を
起こす部位は、主としてボルト頭の首下部、ねじ切り上
がり部およびナットの負荷座面に近いねじ部であり、こ
れらの部位は応力の集中が大きく、また高軸力での締め
付けに対しては塑性歪も大きくなるため、それらの部位
を起点として遅れ破壊が発生することは、多くの研究に
よって知られている。By the way, in order to prevent the delayed fracture, nickel chrome steel, nickel chrome molybdenum steel, chrome steel, chrome molybdenum steel, mechanical structure manganese steel, manganese chrome steel, and aluminum chrome molybdenum steel, which have excellent delayed fracture resistance, are used as materials. One of them, high temperature alloy steel bolt material, steel bar for special purpose alloy steel bolt, heat-treatable low / medium carbon steel, etc. must be used, and it is necessary to minimize stress concentration generated in each part of high strength bolt. It is generally known that, in addition, in the high-strength bolt, the parts that cause delayed fracture are mainly the lower neck of the bolt head, the threaded up part, and the threaded part near the load bearing surface of the nut. Since the stress concentration is large and the plastic strain becomes large when tightening with a high axial force, there is a delay starting from those parts. That corrupted occurs, it is known by a number of research.
前記応力集中の低減は耐疲労に対しても非常に有効なこ
とが多くの文献にて報告されており、この観点からねじ
部に関してはねじ山形状を改善しねじ谷底の応力集中を
小さくすることで耐疲労強度の増大を図った耐疲労ねじ
（以下Ａ発明と云う）が特公昭53−29780号公報に提案
されているが、前記Ａ発明は耐遅れ破壊にもかなりの効
果を備えていると考えられる。It has been reported in many literatures that the reduction of the stress concentration is also very effective for fatigue resistance. From this point of view, it is necessary to improve the screw thread shape and reduce the stress concentration at the screw root for the screw portion. In Japanese Patent Publication No. 53-29780, a fatigue resistant screw (hereinafter, referred to as A invention) whose fatigue strength is increased is proposed, but the A invention has a considerable effect on delayed fracture resistance. it is conceivable that.
前記Ａ発明は、最も遅れ破壊が発生する頻度の高いねじ
山について、その形状の改善を工夫したものであり、フ
ランク角度を（70±２）°もしくは（106±５）°と
し、それぞれのねじ谷底を半径が（0.15±0.02）ｐ（ピ
ッチ）もしくは（0.30±0.01）ｐの円弧によって形成し
たものである。The invention A is a device in which the shape of the thread with the highest frequency of delayed fracture is devised, and the flank angle is (70 ± 2) ° or (106 ± 5) °, and The valley bottom is formed by an arc having a radius of (0.15 ± 0.02) p (pitch) or (0.30 ± 0.01) p.
本発明では、前記Ａ発明については実用的な観点から後
述するようにフランク角度（70±２）°のボルトについ
て検討した。In the present invention, with respect to the invention A, a bolt having a flank angle of (70 ± 2) ° was examined from a practical viewpoint as described later.
さて、このほか市販されている高力ボルトには、前記ボ
ルト頭の首下部、ねじ切り上がり部およびナットの負荷
座面に近いねじ部などにおける応力の集中を避ける目的
で、前記ボルト頭の首下部に複合Ｒを採用し、ねじ部で
は谷底のＲを正確に刻設すると共にねじ切り上がり部の
谷底に丸みをつけたボルトが存在する。By the way, in addition to this, commercially available high-strength bolts have a lower neck portion of the bolt head for the purpose of avoiding concentration of stress in the lower neck portion of the bolt head, the thread cutting up portion, and the thread portion near the load bearing surface of the nut. There is a bolt with a rounded bottom R at the threaded portion and a rounded bottom R at the threaded portion.
しかしながら、前記市販のボルトについては、ねじ谷底
の弧状曲線がどのような理論により形成されているか明
らかにされておらず、さらにその作用効果の裏付けとな
る試験データも発表されていない。However, regarding the commercially available bolt, it has not been clarified by what theory the arc-shaped curve of the thread root is formed, and further, no test data has been published to support the action and effect.
本出願人の知る限りにおいて、特に土木、建築分野にお
ける高力ボルトにおいて、前記Ａ発明は、実用されてお
らず、また、F11T以上のもの、さらには特にF15T級のも
ので、応力の集中の少ない新規な形状を有する高力ボル
トであって、市中に広く提供されている例はない。As far as the applicant is aware, the invention A has not been put into practical use, especially in high-strength bolts in the field of civil engineering and construction, and is of F11T or higher, and more particularly of F15T class, which causes stress concentration. There are no examples of high-strength bolts having a few new shapes and widely provided in the market.
そこで、本発明者らは、まずねじ部の改善について研究
の結果、ねじ山のフランク角度が60°で、かつ等間隔ピ
ッチに刻設され、ついで、谷底が下記条件および算式に
規定される３円弧合成法によって構成される弧状曲線に
形成されている高力ボルトを開発し、従来の高力ボルト
に比し、応力集中度、塑性歪量が非常に少なく、耐遅れ
破壊特性に優れた高力ボルト（以下Ｂ発明と云う）を提
供することに成功し、先に特許出願した。Therefore, as a result of research on improvement of the threaded portion, the present inventors firstly found that the flank angles of the threads are 60 ° and are engraved at equal intervals, and then the valley bottom is defined by the following condition and formula: We have developed a high-strength bolt that is formed into an arc-shaped curve that is constructed by the arc synthesis method, and has a much smaller stress concentration and plastic strain amount than the conventional high-strength bolt, and is superior in delayed fracture resistance. We have succeeded in providing a power bolt (hereinafter referred to as B invention) and filed a patent application earlier.
しかして、前記３円弧合成法とは、とがり山の高さをＨ
とし、相対するねじ山のフランク面と谷底との移行点を
とがり山底辺から（９±１）H/20に設定し、前記それぞ
れの移行点においてフランク面に当設する半径ｒがH/6
の当接小円を描き、さらに前記相対するフランク面の延
長線がなす鋭角の２等分線上に中心を有する半径Ｒが2/
3・Ｈ以上の前記当接小円の外接円を描き、前記当接小
円と前記外接円の谷底側円弧を重畳せしめ弧状曲線を形
成する方法である。Then, with the above-mentioned three-arc synthesis method, the height of the sharp point is
Then, the transition point between the flank surface and the valley bottom of the opposite thread is set to (9 ± 1) H / 20 from the point of the sharp crest, and the radius r attached to the flank surface at each transition point is H / 6.
And a radius R having a center on the bisector of an acute angle formed by the extension lines of the opposite flanks is 2 /
A method of forming an arc-shaped curve by drawing a circumscribed circle of the contact small circle of 3 · H or more and overlapping the contact small circle with the arc of the valley bottom of the circumscribed circle.
さて、前記Ｂ発明の高力ボルトについては、そのねじ部
を日本工業規格のJIS−Ｂ−1186摩擦接合用高力六角ボ
ルトおよび日本鋼構造協会規格のJSSII−09構造用トル
シア形高力ボルトのねじ部に適用し、応力集中度、塑性
歪量について所望の効果を上げることが可能になった。Now, with regard to the high-strength bolt of the invention B, the thread portion thereof is a JIS-B-1186 high-strength hexagon bolt for friction welding of Japanese Industrial Standards and a JSSII-09 structural torcia-type high-strength bolt of Japan Steel Structural Association Standards. By applying it to the threaded portion, it became possible to obtain desired effects on the degree of stress concentration and the amount of plastic strain.
ところで、前述の改善によりねじ部の信頼性の向上に対
し、相対的に首下丸み部の改善が課題になった・すなわ
ちねじ部と首下丸み部との両者の改善ができれば、高力
ボルトの性能の飛躍的な向上が図れ、高力ボルトの市場
性は著しく拡大し、その経済的な貢献は極めて大きい。By the way, compared to the improvement of the reliability of the threaded portion due to the above-mentioned improvement, the improvement of the rounded portion under the neck became a problem. That is, if both the threaded portion and the rounded portion under the neck can be improved, the high strength bolt can be improved. The performance of the high-strength bolt has dramatically increased, the marketability of the high-strength bolt has expanded significantly, and its economic contribution is extremely large.
ところで、前記首下丸み部については、前述のように応
力集中が生じ易く、応力腐食による損傷の原因になるこ
とが早くから知られており、特に荷重の高い場合には、
ねじ部の破断と共に首下丸み部の破損が大きな課題にな
る。By the way, as for the rounded portion under the neck, it is known from early on that stress concentration is likely to occur as described above and causes damage due to stress corrosion, and particularly when the load is high,
A major problem is breakage of the threaded portion and damage to the rounded portion under the neck.
そこで、解決手段の１例として、特開昭62-141303号公
報には、首下丸み部の曲率半径と対応する曲率半径の受
圧面を備えた座金を用いて引張応力の集中を緩和するボ
ルト（以下Ｃ発明と云う）が提案されている。In view of this, as one example of means for solving the problem, Japanese Patent Laid-Open No. 62-141303 discloses a bolt that uses a washer having a pressure-receiving surface having a radius of curvature corresponding to the radius of curvature of the under-neck rounded portion to reduce the concentration of tensile stress. (Hereinafter referred to as C invention) has been proposed.
［発明が解決しようとする課題］ さて、ボルトの如く構造物を接合する最重要な構成部材
は、機械的な強度はもとより、その品質の信頼性の高さ
や、経年変化に対する抵抗力の高いことに加えて、作業
性に優れ、生産性が良く価格が安いことが市場において
広く採用される条件になることは云うまでもなく、前記
Ａ発明がその優れた特質に関らず、市場において実用化
されないのは前記条件のうちの幾つかを満足しないため
であると推定される。[Problems to be solved by the invention] Now, the most important constituent members for joining structures such as bolts are not only mechanical strength but also have high reliability in quality and high resistance to aging. In addition, it is needless to say that excellent workability, high productivity and low price are the conditions to be widely adopted in the market, and the invention A is practically used in the market regardless of its excellent characteristics. It is presumed that it is not converted because it does not satisfy some of the above conditions.
本願発明者らは、土木、建築分野における高力ボルト特
にF11T以上のものについて前記応力集中の少ない新規な
形状について研究を行なった結果、前述のように新しい
フランク角度やねじ山を不等間隔ピッチに螺刻するよう
なボルトは信頼性を確認し、生産性を確かめるには膨大
な実験が必要で、経済的に著しく困難であり、市場に供
給するには長期間を要することを知り、破断に対する抵
抗力が高く、さらに作業性および生産性が良く価格が安
い前記Ｂ発明を開発したがしたが、さらに、高力ボルト
の性能を高め市場性を拡大するためには前記ねじ部の性
能向上に止まらず同時に首下丸み部についても応力集中
が少なく、耐遅れ破壊特性の優れた新規な形状のものを
開発する必要性があることを知った。The inventors of the present application have conducted research on a new shape with less stress concentration for high-strength bolts in the civil engineering and construction fields, particularly those of F11T or more, and as a result, as described above, new flank angles and threads have unequal pitches. We found out that bolts that are screwed into a machine require a great deal of experimentation to confirm reliability and productivity, are economically extremely difficult, and that it takes a long time to be supplied to the market. Although the invention B has been developed, which has high resistance to the, high workability, high productivity, and low price, in addition, in order to improve the performance of the high-strength bolt and expand the marketability, the performance of the threaded portion is improved. It was found that there is a need to develop a new shape with excellent delayed fracture resistance, in which the stress concentration is small in the rounded portion under the neck.
本発明の目的は、ねじ部に加えて首下丸み部が改善され
た高力ボルトとそれらと協同するナット・座金をセット
として提供することにあり、さらに他の目的は機械的な
強度、および品質の信頼性が高く、経年変化に対する抵
抗力の高いことに加えて、作業性と共に、生産性に優
れ、かつ価格が安い耐遅れ破壊特性の優れた高力ボルト
・ナット・座金のセットを提供することに有る。An object of the present invention is to provide a high-strength bolt having an improved roundness under the neck in addition to a screw portion and a nut / washer cooperating with the bolt as a set, and yet another object is to provide mechanical strength and In addition to high quality reliability and high resistance to aging, we also offer a set of high-strength bolts, nuts, and washers with excellent workability, low productivity, and delayed fracture resistance that are both highly productive and inexpensive. There is to do.
［課題を解決するための手段］ 本発明は、前記課題を解決し、目的を達成するもので、
下記１〜４項をその要旨とする。[Means for Solving the Problems] The present invention solves the above problems and achieves the object,
The following items 1 to 4 are the gist.
１ 頭部座面がボルト軸心に対し90°以上150°以下の
載頭円錐面を構成し、かつ首下丸み部が該頭部座面と円
筒部外面と接する曲率半径2.0mm以上5.5mm以下の円弧曲
面に形成され、さらにボルト軸心と直交する平面への前
記頭部座面の投影押圧面積Ｓが下記（１）式に示す領域
に設定され、 T/δ≦Ｓ ・・・・・・（１） T:設定締付力 kgf δ：被締付材の限界面圧 kgf/cm2 S:頭部座面の投影押圧面積 cm2 さらに、ねじ山のフランク角度が60°で、かつ等間隔ピ
ッチに刻設され、ついで、谷底が下記条件および算式に
規定される３円弧合成法（ａ）によって構成される弧状
曲線に形成されている高力ボルトと、ねじ山のフランク
角度が60°で、かつ等間隔ピッチに刻設され谷底が３円
弧合成法によって構成される弧状曲線に形成されている
ボルト雄ねじのフランク面と谷底の移行点を結ぶ直線を
基準として、ねじ先端が螺合許容域に形成された雌ねじ
を備えたナットと、内径側受圧座面が前記ボルト頭部座
面と同一載頭円錐面で、かつ略等面積に形成され、さら
に外径がボルト頭部の外径以上に構成された座金からな
る高力ボルト・ナット・座金のセット。1 The head seat surface constitutes a head conical surface of 90 ° or more and 150 ° or less with respect to the bolt axis, and the rounded portion under the neck contacts the head seat surface and the outer surface of the cylindrical portion. Radius of curvature 2.0 mm or more 5.5 mm The projected pressing area S of the head seat surface on the plane orthogonal to the bolt axis is set to the area shown by the following formula (1), and T / δ ≦ S.・ ・ (1) T: Set tightening force kgf δ: Limit surface pressure of material to be tightened kgf / cm 2 S: Projected pressing area of head seat surface cm 2 Furthermore, the flank angle of the screw thread is 60 °, And the high-strength bolts, which are engraved at equal pitches, and whose valley bottoms are formed into an arc-shaped curve constituted by the three-arc synthesis method (a) defined by the following conditions and formulas, and the flank angle of the thread Flange of male thread of bolt, which is engraved at 60 ° and equidistant pitch, and whose valley bottom is formed into an arc-shaped curve formed by the three-arc synthesis method. A nut with a female thread whose screw tip is formed in the threading permissible area, with the straight line connecting the transition point between the groove surface and the valley bottom as a reference, and the inner diameter side pressure bearing surface is the same head conical surface as the bolt head bearing surface. A set of high-strength bolts, nuts, and washers that consist of washers that have a substantially equal area and an outer diameter that is equal to or greater than the outer diameter of the bolt head.
（ａ）前記３円弧合成法は、とがり山の高さをＨとし、
相対するねじ山のフランク面と谷底との移行点をとがり
山底辺から（９±１）H/20に設定し、前記それぞれの移
行点においてフランク面に当接する半径ｒがH/6の当接
小円を描き、さらに前記相対するフランク面の延長線が
なす鋭角の２等分線上に中心を有する半径Ｒが2/3・Ｈ
以上の前記当接小円の外接円を描き、前記当接小円と前
記外接円の谷底側円弧を重畳せしめ弧状曲線を形成する
方法。(A) In the three-arc synthesis method, the height of the sharp point is H,
The transition point between the flank surface and the valley bottom of the opposite thread is set to (9 ± 1) H / 20 from the edge of the sharp point, and the radius r that abuts the flank surface at each transition point is H / 6. A small circle is drawn, and the radius R centered on the acute angle bisector formed by the extension lines of the opposite flanks is 2/3 · H
A method of drawing an circumscribed circle of the abutting small circle and forming an arc-shaped curve by superimposing the abutting small circle and the arc on the valley bottom side of the circumscribing circle.
２ 成分がニッケルクロム鋼、ニッケルクロムモリブデ
ン鋼、クロム鋼、クロムモリブデン鋼、機械構造用マン
ガン鋼、マンガンクロム鋼、アルミニウムクロムモリブ
デン鋼のうちの１種からなる前記１項記載の高力ボルト
・ナット・座金のセット。The high-strength bolt / nut according to claim 1, wherein the two components are one of nickel chromium steel, nickel chromium molybdenum steel, chromium steel, chromium molybdenum steel, mechanical structure manganese steel, manganese chromium steel, and aluminum chromium molybdenum steel.・ Set of washers.
３ 高温用合金鋼ボルト材または特殊用途合金鋼ボルト
用棒鋼から形成された前記１項記載の高力ボルト・ナッ
ト・座金のセット。3. A set of high-strength bolts, nuts, and washers according to the above item 1, which is formed from a high temperature alloy steel bolt material or a bar steel for a special purpose alloy steel bolt.
４ 熱処理可能な低・中炭素鋼から形成された前記１項
記載の高力ボルト・ナット・座金のセット。4. A set of high-strength bolts, nuts, and washers according to the above item 1, which is formed from heat-processable low / medium carbon steel.
［作用］ 本発明にかかる高力ボルト・ナット・座金のセットにお
いて、まず、高力ボルトは、頭部座面がボルト軸心に対
し90°以上150°以下の載頭円錐面を構成し、かつ首下
丸み部が該頭部座面と円筒部外面と接する曲率半径2.0m
m以上5.5mm以下の円弧曲面に形成され、さらにボルト軸
心と直交する平面への前記頭部座面の投影押圧面積Ｓが
下記（１）式に示す領域に設定されているので、 T/δ≦Ｓ ・・・・・・（１） T:設定締付力 kgf δ：被締付材の限界面圧 kgf/cm2 S:頭部座面の投影押圧面積 cm2 ボルト頭部の応力集中度合いが緩和され、ボルト締め付
け時に首下部に生ずる最大塑性歪量の低減が可能にな
り、耐遅れ破壊特性や耐疲労特性が高い。[Operation] In the set of high-strength bolts, nuts, and washers according to the present invention, first, the high-strength bolt has a head seat surface that forms a conical head surface that is 90 ° or more and 150 ° or less with respect to the bolt axis. Also, the radius of curvature where the rounded portion under the neck contacts the seat surface of the head and the outer surface of the cylindrical portion is 2.0 m
Since the projected pressing area S of the head seat surface on the plane orthogonal to the bolt axis is set in the region shown by the following formula (1), T / δ ≦ S ・ ・ ・ ・ ・ ・ (1) T: Set tightening force kgf δ: Limit surface pressure of the material to be tightened kgf / cm 2 S: Projected pressing area of head seat surface cm 2 Bolt head stress The degree of concentration is relaxed, the maximum amount of plastic strain that occurs in the lower part of the neck when tightening bolts can be reduced, and delayed fracture resistance and fatigue resistance are high.
また、内径側受圧座面が前記ボルト頭部座面と同一載頭
円錐面で、かつ略等面積に形成され、さらに外径がボル
ト頭部の外径以上に構成された座金と協同して用いるこ
とにより、後述するようにボルト頭部座面および座金の
内径側受圧座面の応力集中および塑性歪を非常に少なく
することが可能になるので、損傷に関する懸念を激減で
きる。Further, the inner diameter side pressure receiving seat surface is the same conical surface as the head surface of the bolt head, and is formed to have substantially the same area, and further, in cooperation with a washer whose outer diameter is equal to or larger than the outer diameter of the bolt head. By using it, it becomes possible to significantly reduce stress concentration and plastic strain on the bolt head bearing surface and the inner diameter side pressure bearing surface of the washer, as will be described later, so that the concern about damage can be drastically reduced.
さらに、ねじ山のフランク角度が60°で、かつ等間隔ピ
ッチに刻設され、ついで、谷底が下記条件および算式に
規定される３円弧合成法によって構成される弧状曲線に
形成されており、前記ねじ山は、JIS規格やISOおよびJS
S規格に規定された一般的なボルトのフランク角度およ
びピッチと同一なため、従来のそれらのボルトに関する
多くの特性研究や実験および実施についてのデータ採用
が可能で、研究経費を低減し、信頼性に富む高力ボルト
を経済的な価格で市場に供給することを可能とする。さ
らに、谷底が下記条件および算式に規定される３円弧合
成法によって構成される弧状曲線に形成されているた
め、従来最も問題視されていたねじ谷底における応力集
中が著しく軽減され、F11T以上の用途に対し遅れ破壊の
無い高力ボルトを実現することを可能とする。Further, the flank angle of the screw thread is 60 ° and is engraved at equal pitches, and then the valley bottom is formed into an arc-shaped curve constituted by the three-arc synthesis method defined by the following conditions and formulas. The threads are JIS standard and ISO and JS
Since it is the same as the flank angle and pitch of general bolts specified in the S standard, it is possible to adopt data for many characteristic studies and experiments and implementations of those conventional bolts, reducing the research cost and reliability. It is possible to supply the high-strength bolts rich in water to the market at an economical price. Furthermore, since the valley bottom is formed into an arc-shaped curve constructed by the three-circle arc composition method defined by the following conditions and formulas, stress concentration at the screw valley bottom, which has been regarded as the most problematic in the past, is significantly reduced, and applications above F11T On the other hand, it is possible to realize a high-strength bolt without delayed fracture.
しかして前記３円弧合成法とは、とがり山の高さをＨと
し、相対するねじ山のフランク面と谷底との移行点をと
がり山底辺から（９±１）H/20に設定し、前記それぞれ
の移行点においてフランク面に当接する半径ｒがH/6の
当接小円を描き、さらに前記相対するフランク面の延長
線がなす鋭角の２等分線上に中心を有する半径Ｒが2/3
・Ｈ以上の前記当接小円の外接円を描き、前記当接小円
と前記外接円の谷底側円弧を重畳せしめ弧状曲線を形成
する方法を云う。The three-circle synthesizing method means that the height of the sharp point is H, and the transition point between the flank surface and the valley bottom of the opposite thread is set to (9 ± 1) H / 20 from the sharp peak bottom side, At each transition point, a radius r abutting on the flank surface draws an abutting small circle of H / 6, and a radius R having a center on the bisector of the acute angle formed by the extension lines of the opposing flank surfaces is 2 / 3
A method of drawing an circumscribed circle of the abutting small circles of H or more and forming arc-shaped curves by superimposing the abutting small circles and the arcs on the valley bottom of the circumscribing circle.
さらに、ねじ山のフランク角度が60°で、かつ等間隔ピ
ッチに刻設され谷底が３円弧合成法によって構成される
弧状曲線に形成されているボルト雄ねじのフランク面と
谷底の移行点を結ぶ直線を基準として、ねじ先端が螺合
許容域に形成された雌ねじを備えたナットを前記高力ボ
ルトと協同して用いる場合は、ナットに強い引張力が作
用しても破壊に対する恐れが無く、実用上ナットと高力
ボルトの螺合部分に対する心配は全く無い。Further, a straight line connecting the flank surface of the male thread of the bolt and the transition point of the valley bottom, in which the flank angle of the screw thread is 60 °, and the valley bottom is formed as an arc-shaped curve formed by the three-arc composition method at equal intervals. When using a nut equipped with a female screw with the screw tip formed in the screwing allowable range in cooperation with the high-strength bolt, there is no risk of damage even if a strong tensile force acts on the nut, There is no need to worry about the screwing part of the upper nut and high-strength bolt.
さて以上述べた前記高力ボルトおよびナットと座金のセ
ットはメートル並目ねじが螺刻された周知の高力ボルト
に比し著しく改良されているので、より高い強度を要求
される用途に対し適合性があり、F11T以上の要求に破損
の懸念無く応ずることができる。Since the set of high-strength bolts and nuts and washers described above is a significant improvement over the known high-strength bolts with metric coarse threads, it is suitable for applications requiring higher strength. It is possible to meet the requirements of F11T and above without fear of damage.
つぎに、本発明にかかる高力ボルトおよびナットと座金
のセットは、低・中炭素鋼で製造しても従来の高力ボル
トおよびナットと座金のセットに比し品質的に優れたも
のが得られるが、さらに成分がニッケルクロム鋼、ニッ
ケルクロムモリブデン鋼、クロム鋼、クロムモリブデン
鋼、機械構造用マンガン鋼、マンガンクロム鋼、アルミ
ニウムクロムモリブデン鋼のうちの１種から製造すると
それらの鋼材の焼入、焼戻性の優れた特性からより信頼
性の優れた製品を作ることができる。Next, the set of high-strength bolts and nuts and washers according to the present invention is superior in quality to conventional sets of high-strength bolts and nuts and washers even when manufactured from low / medium carbon steel. However, if the component is manufactured from one of nickel chromium steel, nickel chromium molybdenum steel, chromium steel, chromium molybdenum steel, mechanical structure manganese steel, manganese chromium steel, aluminum chromium molybdenum steel, quenching of those steel materials It is possible to make more reliable products from the characteristics of excellent temperability.
さらにそのことは、高温用合金鋼ボルト材または特殊用
途合金鋼ボルト用棒鋼から形成する場合も同様である。Further, the same applies to the case of forming from a high temperature alloy steel bolt material or a bar steel for a special purpose alloy steel bolt.
ところで、ナットや座金については、力学的な観点から
高力ボルトに対するような品質的に厳しい要求は無いの
で、熱処理可能な低・中炭素鋼から選択される適宜な成
分鋼を用いることは許容でき、そのような選択は経済性
から見た場合有利なことが多い。By the way, regarding nuts and washers, there is no strict quality requirement from the viewpoint of high strength bolts from a mechanical point of view, so it is acceptable to use an appropriate component steel selected from heat treatable low / medium carbon steel. However, such an option is often advantageous from the economical point of view.
この意味において本発明の高力ボルト・ナット・座金の
セットは成分的に品質選択の広い自由度を有する。In this sense, the set of high-strength bolts, nuts and washers of the present invention has a wide degree of freedom in quality selection as a component.
さて、以上述べた本発明の高力ボルト・ナット・座金の
セットは機械的強度が高く、耐遅れ破壊特性が優れてい
ることに加えて、さらに加工や熱処理に適しているの
で、生産性が良く、大量生産が可能であり適正な価格で
市場に供給することができる。By the way, the set of high-strength bolts, nuts, and washers according to the present invention described above has high mechanical strength and excellent delayed fracture resistance, and in addition, it is suitable for processing and heat treatment. Good, mass production is possible, and it can be supplied to the market at a reasonable price.
［実施例］ 以下、本発明につき、図面に従って詳細に説明する。[Examples] Hereinafter, the present invention will be described in detail with reference to the drawings.
第１図（ａ）は本発明にかかる高力ボルト１の頭部２の
頂部平面図で、第１図（ｂ）は高力ボルト１の概略正面
図であり、胴部座面３はボルト軸心４に対し角度θ１が
90°以上150°以下の載頭円錐面を形成し、該胴部座面
３に接する首下丸み部５は曲率半径が2.0mm以上5.5mm以
下の円弧曲面に構成されている。1 (a) is a top plan view of a head 2 of a high-strength bolt 1 according to the present invention, FIG. 1 (b) is a schematic front view of the high-strength bolt 1, and a body seat surface 3 is a bolt. Angle θ 1 with respect to axis 4
A rounded conical surface 5 that forms a frusto-conical surface of 90 ° or more and 150 ° or less and is in contact with the body seat surface 3 is formed into an arcuate curved surface with a radius of curvature of 2.0 mm or more and 5.5 mm or less.
ねじ部は本発明にかかる３円弧合成法により刻設された
ねじ山を備えている。The threaded portion is provided with a screw thread engraved by the three-arc synthesis method according to the present invention.
円筒部７は前記JIS規格、JSSII−09に準拠した定めら
れ、また頭部２は本実施例では一般に座と称される段部
８を有するものが示されているが、該段部８は無くても
差し支えない。The cylindrical portion 7 is defined in accordance with the JIS standard, JSSII-09, and the head portion 2 is shown to have a step portion 8 generally called a seat in this embodiment. It doesn't matter if you don't have it.
さて、第２図（ａ）、（ｂ）は本発明の実施例にかかる
平座金９の平面図および概略縦断面図で、内径側受圧座
面10は前記頭部座面３と同一載頭円錐面即ち平座金９の
軸心11に対し角度θ２が90°以上150°以下の円錐面に
形成されているが、その面積Ｓは頭部座面３と略等面積
に設定される。さらに、平座面９の孔12の直径は前記円
筒部７と適宜な間隙を有するようにJIS規格に準拠して
定めるが、通常は0.5mm〜1.5mmの範囲に設定する。2 (a) and 2 (b) are a plan view and a schematic vertical sectional view of the flat washer 9 according to the embodiment of the present invention, in which the inner diameter side pressure bearing surface 10 is the same as the head bearing surface 3. The conical surface, that is, a conical surface having an angle θ 2 with respect to the axis 11 of the flat washer 9 of 90 ° or more and 150 ° or less is formed, and the area S thereof is set to be substantially equal to the head seat surface 3. Further, the diameter of the hole 12 of the flat seat surface 9 is determined in accordance with the JIS standard so as to have an appropriate gap with the cylindrical portion 7, but it is usually set in the range of 0.5 mm to 1.5 mm.
つぎに、首下丸み部の曲率半径を2.0mm以上5.5mm以下に
限定する理由について説明する。Next, the reason why the radius of curvature of the rounded portion under the neck is limited to 2.0 mm or more and 5.5 mm or less will be described.
ボルト軸部に生じた引張応力をボルト頭部下に伝達する
際に該首下丸み部で応力の方向が変わるので、該首下丸
み部にはねじ底と同様に応力の集中が生ずる。When the tensile stress generated in the bolt shaft portion is transmitted under the head portion of the bolt, the stress direction changes in the under-neck rounded portion, so that the stress concentrates in the under-neck rounded portion similarly to the screw bottom.
そこで、首下丸み部の曲率半径を大きくすることによ
り、応力集中を軽減する案が考えられるが、従来の規格
および作業性からボルト頭部の大きさをなるべく変えな
いとすると頭部座面と座金の内径側受圧座面面積が小さ
くなり、両座面間の圧縮力がボルト、座金とも許容値を
越えることになり、ボルト頭部を大きくすると曲げモー
メントが増大し、首下丸み部の応力が大きくなり、耐遅
れ破壊特性が低下すると云う問題が生ずる。Therefore, it is possible to reduce stress concentration by increasing the radius of curvature of the rounded portion under the neck, but if the size of the bolt head should not be changed as much as possible from the conventional standards and workability, the head seat surface The inner diameter side pressure bearing surface area of the washer becomes smaller, the compressive force between both bearing surfaces exceeds the allowable value for both the bolt and washer, and increasing the bolt head increases the bending moment and stresses the rounded neck. Becomes larger and the delayed fracture resistance deteriorates.
そこで、首下丸み部に連設する座面に勾配を設けること
により、大きな曲率半径を採用しても頭部を大きくする
ことなく必要な座面面積が確保できることになると考え
その研究に着手し、まず、曲率半径の改善を検討した。Therefore, by grading the seating surface that is connected to the rounded portion under the neck, it is possible to secure the necessary seating surface area without enlarging the head even if a large radius of curvature is adopted, and started research on that. , First, we examined the improvement of the radius of curvature.
さて、下記第１表はM22 F15Tの高力ボルトについてJIS
規格に規定された形状において曲率半径ｒを2.0mm〜8.5
mmの範囲に設定した際の最大応力集中係数κと最大塑性
歪量εｐを解析した値を示すものであり、解析は首下丸
み部の曲率半径ｒをパラメーターとし有限要素法を用い
た弾性および弾塑性解析により実施したものである。By the way, the following Table 1 shows the high strength bolts of M22 F15T JIS
The radius of curvature r is 2.0 mm to 8.5 in the shape specified in the standard.
The values show the analyzed values of the maximum stress concentration factor κ and the maximum plastic strain amount εp when set in the range of mm, and the analysis is based on the elasticity radius using the finite element method with the curvature radius r of the rounded portion under the neck as a parameter. It was carried out by elasto-plastic analysis.
さらに、第３図、第４図のグラフは、それぞれ縦軸に最
大応力集中係数κおよび最大塑性歪量εｐをとり横軸に
首下丸み部の曲率半径ｒを取って、解析結果をプロット
したものである。 Further, in the graphs of FIGS. 3 and 4, the vertical axis represents the maximum stress concentration factor κ and the maximum plastic strain amount εp, and the horizontal axis represents the radius of curvature r of the rounded portion under the neck, and the analysis results are plotted. It is a thing.
前記第１表および第３図、第４図のグラフから曲率半径
ｒは5.5mmを越えると最大応力集中係数κの低下が非常
に緩やかになり、最大塑性歪量εｐも小さくなるので、
過大な曲率半径ｒを採用する必要のないことが明らかで
ある。From the graphs of Table 1 and FIGS. 3 and 4, when the radius of curvature r exceeds 5.5 mm, the maximum stress concentration coefficient κ decreases very gradually, and the maximum plastic strain amount εp also decreases.
It is clear that it is not necessary to adopt an excessive radius of curvature r.
さらに、曲率半径ｒは2.0mm以下では最大応力集中係数
κおよび最大塑性歪量εｐが大きくなり、高軸力を要求
される高力ボルトでは問題が生ずる。Further, when the radius of curvature r is 2.0 mm or less, the maximum stress concentration coefficient κ and the maximum plastic strain amount εp become large, which causes a problem in a high strength bolt that requires a high axial force.
以上が本発明において、首下丸み部を頭部座面と円筒部
外面と接する曲率半径2mm以上5.5mm以下の円弧曲面に形
成する理由である。In the present invention, the above is the reason why the rounded portion under the neck is formed as an arcuate curved surface having a radius of curvature of 2 mm or more and 5.5 mm or less that contacts the head seat surface and the outer surface of the cylindrical portion.
つぎに、頭部座面３について説明する。Next, the head seat surface 3 will be described.
第５図は本発明の一実施例にかかる六角ボルト頭部２の
切欠部分図で、説明の便宜上平座金９はハッチングを省
略している。FIG. 5 is a cutaway partial view of the hexagonal bolt head 2 according to the embodiment of the present invention. For convenience of explanation, the flat washer 9 is not hatched.
さて、頭部座面３を設計するには、まず頭部座面３の投
影押圧面積Ｓを下記（１）式で求める。In order to design the head seat surface 3, first, the projected pressing area S of the head seat surface 3 is obtained by the following equation (1).
T/δ≦Ｓ ・・・・・・（１） T:設定締付力 kgf δ：被締付材の限界面圧 kgf/cm2 S:頭部座面の投影押圧面積 cm2 第５図で説明すると、ボルトに要求される設定締付力Ｔ
を付与すべき強度設計からボルト頭部の直径Ｂおよび頭
の高さＨ、段差８の高さh1、該h1を除く高さh0、円筒部
７の直径l3等は決定される。T / δ ≦ S ・ ・ ・ ・ ・ ・ (1) T: Set tightening force kgf δ: Limit surface pressure of the material to be tightened kgf / cm 2 S: Projected pressing area of head seat surface cm 2 Fig. 5 To explain, set tightening force T required for the bolt
Diameter B and the head height H of the bolt head from strength design should impart, height h 1 of the step 8, the h 1 height h 0, except for the diameter l 3 etc. of the cylindrical portion 7 is determined .
本発明では、それらの諸元については前述にように寸法
に関与する諸要因たとえば生産性、作業性、経済性を考
慮してJIS規格の範囲で利用できる寸法諸元を一義的に
採用するが、本発明の理論に従って新しく定めることを
否定するものではない。In the present invention, with respect to those specifications, dimension factors that can be used within the range of JIS standard are unambiguously adopted in consideration of various factors related to dimensions, such as productivity, workability, and economic efficiency, as described above. It does not deny that a new definition is made according to the theory of the present invention.
さて、本発明では、頭部座面がボルト軸心に対し90°以
上150°以下の載頭円錐面を構成するように角度θ１を
選定するが、この理由については後述する。Now, in the present invention, although the head seat surface is selected angle theta 1 to constitute a frusto conical surface of more than 90 ° 150 ° or less with respect to the bolt shaft center, for this reason will be described later.
さて、第５図の例では角度θ１を120°とし、段差８の
端部13を通り、ボルト軸心４と交又する線分14を描き、
該線分14上に設定される頭部座面３の投影押圧面積Ｓか
ら求められる交点Ｐと円筒部７の側面15と接する半径ｒ
の内接円弧を首下丸み部の円弧曲面とした。Now, in the example of FIG. 5, the angle θ 1 is 120 °, and a line segment 14 passing through the end 13 of the step 8 and intersecting with the bolt axis 4 is drawn,
The radius r at which the intersection point P determined from the projected pressing area S of the head seat surface 3 set on the line segment 14 and the side surface 15 of the cylindrical portion 7 contact
The inscribed arc of is the arc curved surface of the rounded portion under the neck.
また、前記投影押圧面積Ｓは交点Ｐ−Ｐ間長さl2を内径
とし、段差８で示す座の直径B0を外径とする被締付材上
のリング面積として仮想できる。第５図においてl0は該
リングの幅を示す。Further, the projection pressing area S of intersection P-P between the length l 2 and an inner diameter, can be a virtual diameter B 0 of the seat indicated by the step 8 as a ring area on the fastened member to the outer diameter. In FIG. 5, l 0 indicates the width of the ring.
本発明では前述の手順に限らず、半径ｒ、幅l0を定めて
から角度θ１の設計を行ってもよく、たとえば、あらか
じめ幅l0をもとめ、ついで軸心４と平行しそれぞれ交点
Ｐと段差８の端部13を通る平行線を引き、つぎに端部13
をとおる角度θ１の1/2の範囲で軸心４と交差する線分
を引き、前記平行線と線分で囲われた範囲に中心を有し
前記円筒部７の側面15と接する半径ｒの内接円弧を描
き、ついで設定角度θ１を有する頭部座面３を決定して
も良い。The present invention is not limited to the above-described procedure, but the radius r and the width l 0 may be set before the angle θ 1 is designed. For example, the width l 0 is determined in advance, and then the intersection point P is set in parallel with the axis 4. And a parallel line passing through the end 13 of the step 8 and then the end 13
A line segment intersecting the axis 4 is drawn in the range of 1/2 of the angle θ 1 passing through the radius θ 1 , and the radius r which has the center in the range surrounded by the parallel lines and the line segment and is in contact with the side surface 15 of the cylindrical portion 7 It is also possible to draw an inscribed circular arc and then determine the head seat surface 3 having the set angle θ 1 .
また、ボルト頭部の直径Ｂと座の直径B0との差を2mm〜6
mmの範囲（図において半差をl1で示す、従って該半差は
通常1mm〜3mmの範囲となる）とし、平座金９の内径と円
筒部７の外径との差は1.0mm〜3.0mmの範囲（従って図に
示す半差は通常0.5mm〜1.5mmの範囲となる）とするが該
寸法は厳密に限定するものではなく、機能を阻害しない
範囲内で自由に設計できることは云うまでもない。Also, the difference between the diameter B of the bolt head and the diameter B 0 of the seat is 2 mm to 6 mm.
mm range (half-difference is shown by l 1 in the figure, so the half-difference is usually in the range of 1 mm to 3 mm), and the difference between the inner diameter of the flat washer 9 and the outer diameter of the cylindrical portion 7 is 1.0 mm to 3.0 mm. The range is mm (hence the half difference shown in the figure is usually 0.5 mm to 1.5 mm), but the size is not strictly limited, and it goes without saying that it can be freely designed within the range that does not impair the function. Nor.
つぎに、投影押圧面積Ｓは定めるにあたり、平座金９の
厚みｔを適切な範囲とする必要性について説明する。Next, the necessity of setting the thickness t of the flat washer 9 within an appropriate range when determining the projected pressing area S will be described.
第６図、第７図はそれぞれ形状を異にする平座金9a、9b
の片側断面図で、説明の都合上ハツチングを省略してい
る。6 and 7 show plain washers 9a and 9b having different shapes.
In the cross-sectional view of one side, hatching is omitted for convenience of explanation.
第６図において内径側受圧座面10は、前述のように前記
頭部座面３と同一載頭円錐面即ち平座金9aの軸心11に対
し角度θ２が90°以上150°以下の円錐面に形成されて
いるが、図では実施例として角度θ２が120°の内径側
受圧座面10について、説明の便宜上底面17と平行な水平
面18に対する角度θ３が30°の傾きを有するものとして
作図している。In FIG. 6, the pressure receiving seat surface 10 on the inner diameter side is the same head conical surface as the head seat surface 3 as described above, that is, a cone whose angle θ 2 is 90 ° or more and 150 ° or less with respect to the axis 11 of the flat washer 9a. Although it is formed on the surface, the inner diameter side pressure bearing surface 10 having an angle θ 2 of 120 ° as an example in the drawing has an angle θ 3 of 30 ° with respect to a horizontal plane 18 parallel to the bottom surface 17 for convenience of description. Is plotted as.
さて、内径側受圧座面10は前記頭部座面３と略等しく設
計されているので、その底面17に対する投影押圧面積は
頭部座面３の投影押圧面積Ｓと略等しい。そこで前記頭
部座面３の投影押圧面のリング幅l0を平座金9aについて
も準用する。Since the inner diameter side pressure receiving surface 10 is designed to be substantially equal to the head seat surface 3, the projected pressing area of the bottom surface 17 thereof is substantially equal to the projected pressing area S of the head seat surface 3. Therefore, the ring width l 0 of the projection pressing surface of the head seat surface 3 is also applied to the flat washer 9a.
つぎに、内径側受圧座面10の下端19および上端20から底
面17に垂線21,22を描くと該垂線21,22間が幅l0となり、
垂線21と孔面23間を距離l4、垂線22と側面24間の距離l5
とすると底面17の幅l6は、l6＝l4＋l0＋l5となる。Next, when the vertical lines 21 and 22 are drawn from the lower end 19 and the upper end 20 of the inner diameter side pressure bearing surface 10 to the bottom face 17, the space between the vertical lines 21 and 22 becomes the width l 0 ,
Distance l 4 between perpendicular 21 and hole surface 23, distance l 5 between perpendicular 22 and side surface 24
Then, the width l 6 of the bottom surface 17 is l 6 = l 4 + l 0 + l 5 .
また、前記水平面18と垂線22の交点ｎと上端20間の距離
h2は内径側受圧座面10の高さとなる。Also, the distance between the intersection point n of the horizontal plane 18 and the vertical line 22 and the upper end 20.
h 2 is the height of the pressure bearing surface 10 on the inner diameter side.
さらに符号25は内径側受圧座面に動く作用力を示す。Further, reference numeral 25 indicates an acting force that moves to the inner diameter side pressure receiving surface.
つぎに、前記第６図、第７図の平座金9a、9bの各寸法諸
元の具体的数値を第２表に示し、ついでそれに基く平座
金9a、9bの内径側受圧座面応力度分布、下面部鉛直応力
度分布を第８図〜第11図に示す。Next, Table 2 shows specific numerical values of the dimensions of the flat washers 9a and 9b shown in FIGS. 6 and 7, and the pressure distribution of the pressure bearing surface of the flat washers 9a and 9b on the basis of them. The lower surface vertical stress distributions are shown in FIGS.
さて、第８図は縦軸に応力度kg/mm2、横軸にボルト軸心
からの距離mmをとり、内径側受圧座面10の応力度合分布
を測定したグラフで、破線26は平座金9aの厚みｔを6m
m、実線27はｔが8mm、一点鎖線28はｔが9mmの場合を示
し、実線29,30は比較のためにJIS規格のF15T、F10Tの測
定結果を示す。 Now, Fig. 8 is a graph in which the stress intensity distribution of the inner diameter side pressure bearing surface 10 is measured with the vertical axis representing the stress degree kg / mm 2 and the horizontal axis representing the distance mm from the bolt shaft center. The thickness t of 9a is 6m
m, the solid line 27 shows the case where t is 8 mm and the alternate long and short dash line 28 shows the case where t is 9 mm, and the solid lines 29 and 30 show the measurement results of JIS standard F15T and F10T for comparison.
通常平座金の引張り強さは130kg/mm2程度であるから、
平座金の厚みｔは少なくとも6mm以上望ましくは8mm程度
の厚みがよいことが判る。Normally, the flat washer has a tensile strength of about 130 kg / mm 2 ,
It is understood that the flat washer has a thickness t of at least 6 mm or more, preferably about 8 mm.
また、第９図は縦軸に応力度kg/mm2、横軸にボルト軸心
からの距離mmをとり、平座金の下面部鉛直応力度分布即
ち換言すると投影押圧面応力度分布を測定したグラフ
で、第８図と同様に破線31は平座金９の厚みｔを6mm、
実線32はｔが8mm、一点鎖線33はｔが9mmの場合を示し、
実線34,35は比較のためにJIS規格のF15T、F10Tの測定結
果を示す。Further, in FIG. 9, the vertical axis shows the stress degree kg / mm 2 , and the horizontal axis shows the distance mm from the bolt axis, and the vertical stress distribution of the lower surface of the flat washer, in other words, the projection pressing surface stress distribution was measured. In the graph, the broken line 31 indicates the thickness t of the flat washer 9 as 6 mm, as in FIG.
The solid line 32 shows the case where t is 8 mm, and the alternate long and short dash line 33 shows the case where t is 9 mm.
Solid lines 34 and 35 show the measurement results of JIS standard F15T and F10T for comparison.
通常被締付材がSS41級の鋼板の場合限界面圧は40kg/mm2
前後と考えてよいので、平座金９の厚みｔは少なくとも
8mm程度が望ましく6mm以下では問題が生ずることが判
る。Normally, when the tightening material is SS41 grade steel plate, the limit surface pressure is 40 kg / mm 2.
Since it can be considered as front and rear, the thickness t of the flat washer 9 is at least
It is understood that about 8 mm is desirable, and a problem occurs if it is 6 mm or less.
つぎに、第10図、第11図は、第７図に示す角度θ２が90
°の載頭円錐面を有する平座金９のそれぞれ内径側受圧
座面応力度分布、下面部鉛直応力度分布を示すグラフで
ある。Next, FIGS. 10 and 11 show that the angle θ 2 shown in FIG.
5 is a graph showing a stress distribution of pressure-bearing seat surfaces on the inner diameter side and a vertical stress distribution of lower surface portions of a flat washer 9 having a truncated cone surface of 90 degrees.
第10図の一点鎖線で示す曲線36は平座金9bの厚みが9mm
の応力度変化を示すものであるが、図から明らかなよう
に局部的な応力集中が大きく、角度θ２が90°以下では
問題が生ずる。The curve 36 shown by the alternate long and short dash line in FIG. 10 has a flat washer 9b with a thickness of 9 mm.
As shown in the figure, the local stress concentration is large and a problem occurs when the angle θ 2 is 90 ° or less.
さらに、第11図において一点鎖線で示す曲線37は平座金
9bの厚みが9mmの下面部鉛直応力度変化を示すものであ
るが、図から明らかなように平座金9bの孔に近い内側か
ら外側側面に向けて応力度が高くなり、平座金9bを押し
拡げようとする力の作用が大きくなることを示してい
る。Furthermore, in FIG. 11, the curved line 37 shown by the alternate long and short dash line is a plain washer.
Although the thickness of 9b shows the change in vertical stress on the lower surface of 9mm, as is clear from the figure, the stress increases from the inside close to the hole of the plain washer 9b to the outer side, and the plain washer 9b is pushed. It shows that the action of the force to expand becomes greater.
以上のことから、角度θ２を90°以下とすることは望ま
しく無いことが判る。そこで本発明では角度θ２の下限
限界を90°とした。From the above, it is understood that it is not desirable to set the angle θ 2 to 90 ° or less. Therefore, in the present invention, the lower limit of the angle θ 2 is set to 90 °.
また、前記第８図〜第11図の説明から明らかなように、
平座金の孔径および前記距離l4、l5、幅l6について適宜
な寸法を設定することにより、被締付材を所定のボルト
軸力付与時に限界面圧以下の適正領域にとどめることが
出来る。Further, as is clear from the description of FIGS. 8 to 11,
By setting appropriate dimensions for the hole diameter of the flat washer, the distances l 4 , l 5 , and the width l 6 , it is possible to keep the material to be tightened in an appropriate region below the limit surface pressure when a predetermined bolt axial force is applied. .
そこで、本発明では前述のとおり改善個所の受圧座面を
除き他の寸法諸元はJIS−Ｂ−1186の規定を準用する。Therefore, in the present invention, as described above, the specifications of JIS-B-1186 apply mutatis mutandis to the dimensions other than the pressure-receiving seat surface of the improved portion.
さて、本発明では前述のとおり、頭部座面がボルト軸心
に対し90°以上150°以下の円錐面を構成し、かつ首下
丸み部が該頭部座面と円筒部外面と接する曲率半径2.0m
m以上5.5mm以下の円弧曲面に形成され、さらにボルト軸
心と直交する平面への前記頭部座面の投影押圧面積Ｓが
下記（１）式に示す領域に設定されている高力ボルトに
ついて、 T/δ≦Ｓ ・・・・・・（１） T:設定締付力 kgf δ：被締付材の限界面圧 kgf/cm2 S:頭部座面の投影押圧面積 cm2 その有用性を説明したが、そのような頭部を有するボル
トは前記JISに規定される摩擦接合用高力六角ボルトやJ
SSに規定する構造用トルシア形高力ボルトに限らず、た
とえばJIS−Ｂ−1180に規定されるような六角ボルトに
適用して破壊に対する抵抗力の優れたボルトとすること
ができる。しかし加工コスト、生産性に見合う性能の点
から本発明では摩擦接合用高力六角ボルトおよび構造用
トルシア形高力ボルト等に規定される高力ボルトに限定
した。Now, in the present invention, as described above, the head seat surface constitutes a conical surface of 90 ° or more and 150 ° or less with respect to the bolt axis center, and the under-neck rounded portion has a curvature in contact with the head seat surface and the outer surface of the cylindrical portion. Radius 2.0m
A high-strength bolt which is formed in an arc curved surface of m or more and 5.5 mm or less and in which the projected pressing area S of the head seat surface on a plane orthogonal to the bolt axis is set in the region shown in the following formula (1) , T / δ ≦ S ・ ・ ・ ・ ・ ・ (1) T: Set tightening force kgf δ: Limit surface pressure of material to be tightened kgf / cm 2 S: Projected pressing area of head seat surface cm 2 Its usefulness As described above, bolts with such a head are high-strength hexagon bolts for friction welding and J
Not only the structural torcia-type high-strength bolts specified in SS, but also hexagonal bolts specified in JIS-B-1180, for example, can be used as a bolt having excellent resistance to breakage. However, from the viewpoint of performance commensurate with processing cost and productivity, the present invention is limited to high-strength hexagon bolts for friction welding and high-strength bolts specified for structural torcia type high-strength bolts.
さて、つぎにねじ形状について詳細に説明するが、説明
の都合上、まずねじ谷底形成に関し前記３円弧合成法に
従った描図とその作用につき実施例に従って説明する。Next, the screw shape will be described in detail. For convenience of description, first, a drawing according to the above-described three-arc synthesis method for forming a screw root and its action will be described according to an embodiment.
第12図において、とがり山38の高さをＨとし、相対する
ねじ山39a、39bのフランク面40a、40bと谷底41との移行
点42a、42bをとがり山底辺43から（９＋１）H/20即ち1/
2・Ｈに設定し、前記それぞれの移行点42a、42bにおい
てフランク面40a、40bに当接する半径ｒがH/6の当接小
円44a、44bを描き、さらに前記フランク面の40a、40bの
延長線45a、45bがなす鋭角の２等分線46上に中心47を有
する半径Ｒが2/3・Ｈの外接円48を、前記当接小円44a、
44bと外接するように描き、前記当接小円44a、44bの谷
底側円弧44a1、44b1と前記該外接円48の谷底側円弧48a
を重畳せしめ弧状曲線49を形成し、該弧状曲線49をねじ
谷底とする。In FIG. 12, the height of the point 38 is set to H, and the transition points 42a and 42b between the flanks 40a and 40b of the opposite threads 39a and 39b and the valley bottom 41 are set to (9 + 1) H / 20 from the point 43 of the pointed peak. That is 1 /
2. Set to H, draw contact small circles 44a and 44b with radius r of H / 6 that contact the flank surfaces 40a and 40b at the transition points 42a and 42b, respectively. A circumscribing circle 48 having a center 47 on a bisector 46 of an acute angle formed by the extension lines 45a and 45b and a radius R of 2/3 · H is defined by the contact small circles 44a,
It is drawn so as to be circumscribed with 44b, and the valley bottom side arcs 44a 1 and 44b 1 of the contact small circles 44a and 44b and the valley bottom side arc 48a of the circumscribed circle 48.
Are overlapped with each other to form an arcuate curve 49, and the arcuate curve 49 is used as a screw root.
本発明では、前述の如く前記当接小円44a、44bと外接円
48の谷底側円弧を重ねて移行点においてフランク面の直
線部とスムーズに移行する弧状曲線49とするところを、
前記当接小円と外接円の谷底側円弧を重畳せしめ弧状曲
線を形成すると云う。In the present invention, as described above, the contact small circles 44a, 44b and the circumscribed circle
Where the valley bottom side arc of 48 is overlapped and the straight part of the flank surface and the arc-shaped curve 49 that smoothly transitions at the transition point,
It is said that an arc-shaped curve is formed by superimposing the valley-side arcs of the abutting small circle and the circumscribing circle.
さて、本発明においては前記移行点42a、42bをとがり山
底辺43から（９±１）H/20に設定するが、その理由は、
本発明の目的を満足する前記弧状曲線48を形成するにあ
たり、ねじ抜けを防止する適切なひっかかり率を保持す
るためであって、下限の8/20・Ｈ以下では本発明の目的
を満足する弧状曲線を形成することが出来ず、上限の10
/20・Ｈ以上では適切はひっかかり率を保持することが
困難なためである。Now, in the present invention, the transition points 42a, 42b are set to (9 ± 1) H / 20 from the sharp mountain bottom side 43, the reason is as follows.
In forming the arc-shaped curve 48 which satisfies the object of the present invention, the arc-shaped curve 48 which satisfies the object of the present invention is maintained at a lower limit of 8/20 · H or less in order to maintain an appropriate catching rate for preventing the screw from coming off. Unable to form a curve, upper limit of 10
This is because it is difficult to maintain a proper catching rate above / 20 · H.
また、前記それぞれの移行点42a、42bにおいて半径ｒが
H/6の当接小円44a、44bを、フランク面に当接して描く
のは、応力集中の少ないねじ谷底の弧状曲線を得るた
め、前記移行点42a、42bにつき、それぞれ異なった径を
有する種々の当接小円について、多くの位置を中心とし
て数多くの弧状曲線を設定し、応力計算を行ない、その
うちの最も応力集中の度合いが低いものを選定した結果
である。Also, at the transition points 42a and 42b, the radius r is
The contact small circles 44a and 44b of H / 6 are drawn in contact with the flank surface so that the transition points 42a and 42b have different diameters in order to obtain an arc-shaped curve of the thread root with less stress concentration. With respect to various abutting small circles, a large number of arc-shaped curves are set around many positions, stress calculation is performed, and the one with the lowest degree of stress concentration is selected.
さらに前記フランク面の40a、40bの延長線45a、45bがな
す鋭角の２等分線上に中心46を有する半径Ｒが2/3・Ｈ
以上の外接円47を、前記当接小円44a、44bと外接するよ
うに描き、前記当接小円44a、44bの谷底側円弧44a1、44
b1と前記外接円48の谷底側円弧48aを重畳せしめ弧状曲
線49を形成を形成するのは、前記当接小円44a、44bの谷
底側円弧44a1、44b1と最も円滑な弧状曲線を得ることが
できるためであり、これも多くのシュミレーションによ
って得られた経験値である。Further, the radius R having the center 46 on the bisector of the acute angle formed by the extension lines 45a and 45b of the flank surfaces 40a and 40b is 2/3 · H.
The above circumscribing circle 47 is drawn so as to circumscribe the contact small circles 44a, 44b, and the bottom arcs 44a 1 , 44 of the contact small circles 44a, 44b are drawn.
b 1 and the valley bottom side arc 48a of the circumscribed circle 48 are overlapped to form an arc-shaped curve 49, which forms the smoothest arc-shaped curve with the valley bottom side arcs 44a 1 and 44b 1 of the contact small circles 44a and 44b. This is because it can be obtained, and this is also an experience value obtained by many simulations.
さて、前述のようにして得られた前記弧状曲線49に従っ
て、形成したねじ谷底が最も応力集中の度合いが低く、
塑性歪の少ないことについて、第13図〜第21図により説
明する。Now, according to the arc-shaped curve 49 obtained as described above, the formed screw root has the lowest degree of stress concentration,
The fact that the plastic strain is small will be described with reference to FIGS. 13 to 21.
第13図〜第21図は第３表に示す成分を有する低炭素鋼を
素材として、それぞれのねじ形状に製造したM22ボルト
（日本建築学会・建築工事標準仕様書JASS6に準拠、但
しピッチＰは2.5mm）について、軸方向に一様の引っ張
り荷重をかけ、軸対称有限要素解析（８節点アイソパラ
メトリック法）を行なった例を示すグラフであって、第
13図〜第15図は弾性荷重時の応力の集中度合を計算した
ものであり、第16図〜第18図はF15Tに相当する高力ボル
トをボルト軸力（30.7Ton）で一様に引っ張ったときの
塑性歪の大きさを計算したものである。Figures 13 to 21 show M22 bolts manufactured according to the respective screw shapes using low carbon steel having the components shown in Table 3 (conforms to the Japan Society of Architects / Building Construction Standard Specification JASS6, but the pitch P is 2.5mm) is a graph showing an example of performing an axially symmetric finite element analysis (8-node isoparametric method) by applying a uniform tensile load in the axial direction.
Figures 13 to 15 are calculated stress concentrations under elastic load, and Figures 16 to 18 show that a high-strength bolt equivalent to F15T is uniformly pulled by bolt axial force (30.7Ton). This is a calculation of the magnitude of the plastic strain when applied.
また、第19図はF10TのJISメートル並目ねじを前記JASS6
に規定する標準ボルト張力（22.5Ton）で一様に引っ張
ったときの塑性歪の大きさを計算したものである。Also, Fig. 19 shows the F10T JIS metric coarse screw
This is a calculation of the magnitude of plastic strain when uniformly stretched with the standard bolt tension (22.5Ton) specified in Section 2.
第13図は本発明の高力ボルトにかかるものであり、図か
ら明らかなようにねじ谷底における応力集中係数は、最
大値で1.66であって、第14図に示す前記Ａ発明の1.98と
比較して著しく低いことが判る。FIG. 13 relates to the high-strength bolt of the present invention, and as is clear from the figure, the stress concentration factor at the thread root is 1.66 at the maximum value, which is compared with 1.98 of the A invention shown in FIG. It turns out that it is extremely low.
ちなみに、第15図に示す如くJISメートル並目ねじの応
力集中係数は2.54であって、本発明の新規なねじとの差
はさらに著しい。By the way, as shown in FIG. 15, the JIS metric coarse screw has a stress concentration factor of 2.54, and the difference from the novel screw of the present invention is more remarkable.
さらに、塑性歪について比較すると、第16図に示すとお
り、本発明にかかる高力ボルトのねじ谷底における塑性
歪は1300μであるのに対し、第17図に示すように前記Ａ
発明の耐疲労ねじのそれは2500μであり、ISOメートル
並目ねじについては、第18図に示すとおり7300μであっ
て、比較にならぬほどその差異は大きい。Further, comparing the plastic strains, as shown in FIG. 16, the plastic strain at the thread root of the high-strength bolt according to the present invention is 1300μ, while as shown in FIG.
The fatigue resistance screw of the invention is 2500 μ, and the ISO metric coarse screw is 7300 μ as shown in FIG. 18, and the difference is so large that it cannot be compared.
さらに、本発明にかかる高力ボルト（F15T級）の塑性歪
1300μは、従来遅れ破壊の発生が極めて小さいとされて
いるF10T高力ボルトの塑性歪5300μに比べてもはるかに
小さく、本発明にかかる高力ボルトが耐遅れ破壊特性に
優れていることが判る。Furthermore, the plastic strain of the high-strength bolt (F15T class) according to the present invention
1300μ is much smaller than the plastic strain 5300μ of the F10T high strength bolt, which has been considered to be extremely small in the occurrence of delayed fracture, and it can be seen that the high strength bolt according to the present invention has excellent delayed fracture resistance. .
而して、従来遅れ破壊特性の評価は困難であったが、水
素脆化感受性で評価する手段が開発され、該評価法に基
づいて遅れ破壊特性の優れた低・中炭素鋼からなる高強
度鋼が提案されるようになり、たとえば、第４表に示す
成分を有する低・中炭素鋼が高力ボルトに適しているこ
とが知られている。 Although it has been difficult to evaluate delayed fracture characteristics in the past, a means for evaluating hydrogen embrittlement susceptibility has been developed, and high strength made of low / medium carbon steel with excellent delayed fracture characteristics has been developed based on this evaluation method. Steel has been proposed, and it is known that, for example, low-medium carbon steel having the components shown in Table 4 is suitable for high-strength bolts.
従って、本発明において、これらの周知の耐遅れ破壊特
性の優れた低・中炭素鋼からなる高強度鋼を高力ボルト
素材として利用すれば、耐遅れ破壊について相乗効果が
期待出来ることは云うまでもない。 Therefore, in the present invention, it is needless to say that a synergistic effect on delayed fracture can be expected by using a high-strength steel made of low-medium carbon steel having excellent well-known delayed fracture resistance as a high-strength bolt material. Nor.
また、本発明の高力ボルトについては、軸部からねじ部
に向け、長さがねじピッチの４倍以上の移行部を設け、
さらに移行部とねじ部の境界部はねじ底のアールより大
きな丸みを有するものとした。Further, in the high-strength bolt of the present invention, a transition portion having a length of 4 times or more of the screw pitch is provided from the shaft portion to the screw portion,
Further, the boundary portion between the transition portion and the screw portion has a roundness larger than the radius of the screw bottom.
本発明者らの知見では、これらの改良は、それらの位置
が遅れ破壊の起点になる率が著しく低下することから、
かなりの効果が有ると認められる。According to the knowledge of the present inventors, these improvements result in a significant decrease in the rate at which those positions become the starting points of delayed fracture,
It is recognized that it has a considerable effect.
つぎに、本発明における前記移行点を上下限について説
明する。Next, the upper and lower limits of the transition point in the present invention will be described.
前述の第13図、第16図は本発明において前記移行点をそ
の上限であるとがり山底辺から1/2・Ｈに設定した例で
あり、第20図、第21図は移行点をその下限である8/20・
Ｈに設定し、他の条件は第13図、第16図と同様とした例
を示す。The above-mentioned FIGS. 13 and 16 are examples in which the upper limit of the transition point is set to 1 / 2.H from the bottom of the sharp mountain in the present invention, and FIGS. 20 and 21 show the lower limit of the transition point. Is 8/20
An example in which H is set and other conditions are the same as those in FIGS. 13 and 16 is shown.
さて、第20図は応力集中係数、第21図は塑性歪を図示し
ているが、前者は最大値が1.71で、後者は1130μであり
本発明にかかる移行点の設定許容領域において良い成績
が期待できることを明白に示している。By the way, FIG. 20 shows the stress concentration factor, and FIG. 21 shows the plastic strain.The former has a maximum value of 1.71, and the latter has a value of 1130μ, which is a good result in the setting allowable range of the transition point according to the present invention. It clearly shows what to expect.
また、前記外接円の半径Ｒを2/3・Ｈ以上とする理由
は、2/3・Ｈ以下では、所望の滑らかな弧状曲線が得ら
れず応力集中係数および塑性歪が大きくなり本発明の目
的を果たすことが出来ず、一方2/3・Ｈ以上であれば、
外接円の谷底側円弧が限り無く直線に近くても目的を達
成することを本発明者らは確認したからである。Further, the reason why the radius R of the circumscribed circle is set to 2/3 · H or more is that if the radius is 2/3 · H or less, a desired smooth arc-shaped curve cannot be obtained, and the stress concentration factor and the plastic strain increase, and the present invention If you can not achieve the purpose, while 2/3 · H or more,
This is because the present inventors have confirmed that the object can be achieved even if the valley-side arc of the circumscribed circle is as close to a straight line as possible.
しかして、外接円の半径Ｒはむやみに大きくする必要は
無く2/3・Ｈ〜2H程度で充分好ましい結果を得ることが
できる。However, the radius R of the circumscribing circle does not need to be unduly increased, and a sufficiently preferable result can be obtained at about 2/3 · H to 2H.
次に、本発明にかかる高力ボルト（以下Ｂボルトと云
う）とJASS6に準拠して製造した高力ボルト（以下Ｃボ
ルトと云う）について、ナット回転法による破壊に到る
までのボルト軸力付与試験を実施して、耐破壊特性を比
較した結果について説明する。Next, regarding the high-strength bolt according to the present invention (hereinafter referred to as B-bolt) and the high-strength bolt manufactured according to JASS6 (hereinafter referred to as C-bolt), the bolt axial force until the destruction by the nut rotation method is reached. The results of comparing the fracture resistance characteristics of the applied test will be described.
試験に用いた低・中炭素鋼の成分を第５表に示す。Table 5 shows the components of the low and medium carbon steels used in the test.
ボルト本体は棒材を冷間鍛造にて頭部および軸部を形成
したあと、ねじ部を切削加工し、その後900℃で水焼入
れし、ついで430℃で焼戻す手段によって150kg/mm2の強
度に製造したが、ナットおよび座金については、説明を
省略する。ボルトの寸法はM22で首下長さが90mm、ねじ
ピッチは2.5mmである。 The bolt body has a head and shaft formed by cold forging the rod, then the thread is cut, then water-quenched at 900 ° C, and then tempered at 430 ° C to obtain a strength of 150 kg / mm 2 . However, the description of the nut and the washer is omitted. The size of the bolt is M22, the length under the neck is 90 mm, and the screw pitch is 2.5 mm.
なお、Ｂボルトに使用するナットの下孔径はＣボルトに
使用する通常のものよりも、0.8mm大きく加工した。The prepared hole diameter of the nut used for the B bolt was 0.8 mm larger than that of the normal nut used for the C bolt.
第22図は、前記ボルト軸力付与試験の結果を示すグラフ
で、横軸はナット回転角（度）で、縦軸はボルト軸力
（Ton）を示す。FIG. 22 is a graph showing the results of the bolt axial force application test, where the horizontal axis represents the nut rotation angle (degree) and the vertical axis represents the bolt axial force (Ton).
初期トルク15kgf.mを付与したのち、ナット締めを行な
ったが、Ｂボルトは略900度を越える付近で遊びねじ部
で破断が生じ、周知のねじ山形状を有するＣボルトは60
0度を越える付近で遊びねじ部で破断した。After applying an initial torque of 15 kgf.m, the nut was tightened, but the B bolt fractured at the idle thread near approximately 900 degrees, and the C bolt with the well-known thread shape had 60
Fracture occurred at the idle thread near 0 degrees.
第22図から明らかなように本発明にかかる新しいねじ部
を有する高力ボルトは従来の周知高力ボルトに比しねじ
部の耐破壊特性が著しく改善されていることが判る。As is apparent from FIG. 22, the high-strength bolt having the new thread portion according to the present invention has a significantly improved fracture resistance of the thread portion as compared with the conventionally known high-strength bolt.
さらに、第22図で明らかなようにＢボルトの最大軸力は
Ｃボルトに比し10％程度大きくなっている。これは本発
明のねじ形状は従来のJISメートル並目ねじに比べてボ
ルトの有効断面積が10％程度大きくなっていることを示
しており、見かけ上は10％程度さらに高強度のボルトを
使用したのと同じ効果が期待できる。Further, as is clear from FIG. 22, the maximum axial force of B bolt is about 10% larger than that of C bolt. This shows that the screw shape of the present invention has an effective area of the bolt that is about 10% larger than that of the conventional JIS metric coarse screw. Apparently, a bolt with a higher strength of about 10% is used. You can expect the same effect as you did.
さて、次に本発明の高力ボルト・ナットおよび座金と先
願の種別セットを下記第６表に示す。Next, Table 6 below shows the high-strength bolt / nut and washer of the present invention and the type set of the prior application.
つぎに、本発明にかかる高力ボルトの遅れ破壊試験結果
について説明する。 Next, the results of the delayed fracture test of the high-strength bolt according to the present invention will be described.
下記第７表に示す化学成分の鋼を用いてM22X90mmの本発
明にかかる六角高力ボルト（以下Ｄボルトと云う）と、
同じサイズのJIS−Ｂ−1186に規定される摩擦接合用六
角高力ボルト（以下Ｅボルトと云う）および前記Ａ発明
記載のフランク角70℃のねじ形状を有するボルト（以下
Ｆボルトと云う）の３種を冷間鍛造および転造法にて成
形し、ついで860℃の温度雰囲気で30分加熱後、油焼入
しさらに後述する種々の温度で120分焼戻す手段により
強度を変化させたボルトを製作した。A hexagonal high-strength bolt (hereinafter referred to as D bolt) of the present invention of M22 × 90 mm using steel having the chemical composition shown in Table 7 below.
A hexagonal high-strength bolt for friction welding (hereinafter referred to as E-bolt) of the same size and a bolt having a screw shape with a flank angle of 70 ° C. (hereinafter referred to as F-bolt) described in A invention above. Three types of bolts were formed by cold forging and rolling, then heated in an atmosphere of 860 ° C for 30 minutes, oil-quenched, and tempered for 120 minutes at various temperatures described below. Was produced.
ついで、前記Ｄ、Ｅ、Ｆボルトから採取した試験片（JI
S4号）による引張試験を実施した結果を第８表に示す。 Then, test pieces (JI
The results of the tensile test according to S4) are shown in Table 8.
つぎに、前記Ｄ〜Ｆボルトについて遅れ破壊試験を下記
要領により実施した。 Next, a delayed fracture test was performed on the D to F bolts according to the following procedure.
第23図（ａ）、（ｂ）は試験に用いた被締付け鋼板の上
・下鋼板50,51（上鋼板は厚さ25mm、幅100mm、長さ770m
m、860mm、下鋼板は厚さ25mm、幅100mm、長さ860mm）の
概略側面図および平面図で、符号52a、52bは図示してい
ない試験用架台に取付けるための貫通孔、符合53に代表
せしめる貫通孔は試験用ボルトの取り付け孔で、前記被
締付け鋼板の上・下鋼板50,51に前記Ｄ〜Ｆボルトの各
種別10本ずつをそれぞれのボルトの耐力点まで締め付
け、温度60℃、湿度約95％の高温高湿槽中に放置して、
ボルトの遅れ破壊の有無を６ヶ月間観察した。その結果
は第９表に示すとおりで、本発明のＤボルトは周知の
Ｅ、Ｆボルトに比し耐遅れ破壊特性が極めて優れてい
る。Figures 23 (a) and (b) show the upper and lower steel plates 50, 51 used in the test (the upper steel plate is 25 mm thick, 100 mm wide, and 770 m long).
m, 860 mm, lower steel plate is 25 mm thick, 100 mm wide, 860 mm long) in schematic side view and plan view. Reference numerals 52a and 52b are through holes for attaching to a test stand (not shown), and is represented by reference numeral 53. The through-holes to be tightened are test-bolt mounting holes, and each of the D to F bolts is tightened to the upper and lower steel plates 50 and 51 of the steel plate to be tightened to a proof point of each bolt at a temperature of 60 ° C. Leave it in a high temperature and high humidity tank with a humidity of about 95%,
The presence or absence of delayed fracture of the bolt was observed for 6 months. The results are shown in Table 9, and the D bolt of the present invention has extremely excellent delayed fracture resistance as compared with the known E and F bolts.
さて、以上本発明の高力ボルトについては、六角高力ボ
ルトを例として説明したが、形状、特性等に関する要件
はトルシア形高力ボルトについても同様であり、僅かに
異なる点は第24図に示すようにトルシア形高力ボルト54
は頭部55が丸頭であり、下部に破断溝56、ピンテール57
を備えていることであって、本発明の要旨である首下丸
み部58、頭部座面59、ねじ部60に関する要件は全く同様
であり、ナット・座金についても同様である。即ち前記
頭部、破断溝、ピンテールが前記首下丸み部、頭部座
面、ねじ部に直接影響することは無いので、説明は省略
する。 Now, as for the high-strength bolt of the present invention, the hexagonal high-strength bolt has been described as an example, but the requirements regarding the shape and the characteristics are the same for the torcia-type high-strength bolt, and slightly different points are shown in FIG. 24. Torsia type high strength bolt 54 as shown
Has a round head 55, a broken groove 56 and a pin tail 57 at the bottom.
The requirements for the under-neck rounded portion 58, the head seat surface 59, and the screw portion 60, which are the features of the present invention, are exactly the same, and the same applies to the nuts and washers. That is, since the head portion, the fractured groove, and the pin tail do not directly affect the rounded portion under the neck, the head seat surface, and the screw portion, description thereof will be omitted.
但し、形状の異なる両者の頭部外径については、六角高
力ボルトの場合は二面幅で、トルシア形高力ボルトの頭
部外径については第25図に示すように頭部下面外径Ｂを
外径と云う。However, the outer diameters of the heads with different shapes are the width across flats in the case of hexagonal high-strength bolts, and the outer diameters of the heads of the Torcia type high-strength bolts are as shown in Fig. 25. B is called the outer diameter.
前記第25図に示すトルシア形高力ボルト54の頭部55の寸
法符合において前記第５図と同様のものは同一の定義の
ものであり、よって説明は省く。In the dimension matching of the head portion 55 of the torcia-type high-strength bolt 54 shown in FIG. 25, the same parts as those in FIG. 5 have the same definitions, and therefore the description thereof will be omitted.
つぎに、第26図は本発明における異なったトルシア形高
力ボルト61の頭部62の概略説明図で、第25図に示すトル
シア形高力ボルト54と異なり段部８を有していない。Next, FIG. 26 is a schematic explanatory view of a head portion 62 of a different torcia type high strength bolt 61 according to the present invention, which does not have the step portion 8 unlike the torcia type high strength bolt 54 shown in FIG.
このように、頭部座面63については本発明の目的を逸脱
しない限りにおいて、自由に設計しても良いが、本発明
者らの研究範囲では、品質管理、作業性の点で段部８を
有する前記トルシア形高力ボルト54が最も実用性がある
と認められた。As described above, the head seat surface 63 may be freely designed as long as it does not deviate from the object of the present invention, but within the scope of the present inventors' research, the step portion 8 is provided in terms of quality control and workability. The above-mentioned torcia-type high-strength bolt 54 having the above was found to be the most practical.
つぎに、高力ボルトの前記新しい雄ねじに螺合するナッ
トについて第27図の螺合状態説明図に従って説明する。Next, a nut to be screwed to the new male screw of the high strength bolt will be described with reference to the screwing state explanatory diagram of FIG.
第27図において、39a、39bは高力ボルトの雄ねじ山で、
43は底辺であり、42a、42bは移行点を示し、それらの定
義は第12図で説明した通りである。In FIG. 27, 39a and 39b are male threads of high strength bolts,
43 is the base, 42a and 42b are transition points, and their definitions are as described in FIG.
さて、図に示すように本実施例ではナットのねじ山64の
先端65は、前記移行点42a、42bを結ぶ直線66と一致して
いる。前記直線66を本発明では螺合の基準とする。Now, as shown in the drawing, in the present embodiment, the tip 65 of the thread 64 of the nut coincides with the straight line 66 connecting the transition points 42a and 42b. In the present invention, the straight line 66 is used as a reference for screwing.
本発明者等の研究によれば、前記先端65が前記直線66か
ら底辺43に近づくことは幾何学的にできない筈である
が、実際の螺合ではボルト、ナット両者の馴染み具合か
らH/20程度を限度とし前記直線66を越えて前記先端65が
底辺43に近づいても螺合は可能である。また、前記先端
65が前記底辺43から遠ざかる方向において直線66を越え
る場合は絶対距離でH/10が限度であり、それ以上ではひ
っかかり率が小さくなり、ねじ抜けを起こす恐れが大き
い。そこで本発明では前記直線66を基準として底辺43に
近づく側にH/20、反対側にH/10の範囲を螺合許容域と定
義し、前記先端65が常に螺合許容域に位置するようにナ
ットを形成する。つぎに、本発明の高力ボルト・ナット
・座金に関する材質であるが、本発明では、JISに規定
するボルト用の合金鋼を採用し、よい結果を得ることが
できる。According to the research conducted by the present inventors, it should be geometrically impossible for the tip 65 to approach the bottom side 43 from the straight line 66, but in actual screwing, H / 20 from the familiarity of both bolts and nuts. Screwing is possible even if the tip 65 approaches the bottom side 43 beyond the straight line 66 within the limit. Also, the tip
When 65 exceeds the straight line 66 in the direction away from the base 43, the absolute distance is H / 10, and if it is more than that, the catching rate becomes small and there is a high possibility that the screw will come off. Therefore, in the present invention, the range of H / 20 on the side approaching the base 43 and the range of H / 10 on the opposite side are defined as the screwing allowable range with the straight line 66 as a reference, and the tip 65 is always located in the screwing allowable range. Form nuts on. Next, regarding the materials relating to the high-strength bolts, nuts, and washers of the present invention, in the present invention, alloy steel for bolts specified in JIS can be adopted and good results can be obtained.
たとえば、JIS−Ｇ−4102ニッケルクロム鋼鋼材、JIS−
Ｇ−4103ニッケルクロムモリブデン鋼鋼材、JIS−Ｇ−4
104クロム鋼鋼材、JIS−Ｇ−4105クロムモリブデン鋼鋼
材、JIS−Ｇ−4106機械構造用マンガン鋼鋼材およびマ
ンガンクロム鋼鋼材、JIS−Ｇ−4107高温用合金鋼ボル
ト材、JIS−Ｇ−4108特殊用途合金鋼ボルト用棒鋼、JIS
−Ｇ−4202アルミニウムクロムモリブデン鋼鋼材など好
適に用いることができる。For example, JIS-G-4102 nickel chrome steel, JIS-
G-4103 Nickel chrome molybdenum steel steel, JIS-G-4
104 chrome steel steel, JIS-G-4105 chrome molybdenum steel, JIS-G-4106 Manganese steel for machine structure and manganese chrome steel, JIS-G-4107 High temperature alloy steel bolt, JIS-G-4108 Special Applications Alloy steel Steel bar for bolts, JIS
-G-4202 Aluminum chrome molybdenum steel and the like can be preferably used.
また、材質についてはナット、座金についても同様な合
金鋼が利用できるが、ナット、座金は高力ボルトに比し
て遅れ破壊に対する考慮や機械的な強度についての懸念
が少なく、従って要求特性に適する限りにおいて価格の
安い合金鋼を用いることが経済的であり、本発明ではJI
S−Ｂ−1186に規定される機械的性質を満足する限りに
おいてナット、座金を熱処理可能な低・中炭素鋼材から
製造し高い経済性を得ることが可能である。Similar alloy steels can be used for nuts and washers in terms of material, but nuts and washers are less concerned about delayed fracture and mechanical strength than high-strength bolts, and are therefore suitable for required characteristics. As far as possible, it is economical to use cheap alloy steel, and in the present invention, JI
As long as the mechanical properties specified in S-B-1186 are satisfied, it is possible to manufacture nuts and washers from heat-treatable low / medium carbon steel materials and obtain high economic efficiency.
［発明の効果］ 以上詳細に説明した通り、本発明にかかる高力ボルト・
ナット・座金のセットは応力集中度、塑性歪量が非常に
小さく、優れた耐遅れ破壊特性を備えているので、信頼
性が高く、産業上の実用効果は極めて多大である。[Effects of the Invention] As described in detail above, the high-strength bolt according to the present invention
The set of nuts and washers has a very small stress concentration and plastic strain amount and excellent delayed fracture resistance, so it is highly reliable and has a great industrial practical effect.
また、特に従来最も課題とされてきた高力ボルトについ
て首下部もしくは該首下部とねじ部が改良された結果、
従来の高力ボルトに比して応力集中度、塑性歪量を小さ
くすることに成功したので、その結果高い耐遅れ破壊特
性を与えることが可能となり、鋼板接合にあたり使用本
数の低減ができ、ために施行スピードの向上、施行コス
トの低減が可能となった。さらに接合部もコンパクトで
済むため、総合的に極めて大きな経済効果が期待出来
る。In addition, as a result of the improvement of the lower neck part or the lower neck part and the screw part of the high-strength bolt, which has been the most problematic conventionally,
Since we succeeded in reducing the stress concentration and the amount of plastic strain compared to conventional high-strength bolts, it is possible to provide high delayed fracture resistance and reduce the number of steel plates used for joining steel plates. It is possible to improve the execution speed and reduce the execution cost. In addition, the joints can be made compact, so an extremely large economic effect can be expected overall.
また、構造的にみて頭部座面や首下丸み部は形態的に加
工が容易であるため、ボルト頭部加工時の成形用金型の
寿命延長がはかれ、加えてナット・座金についても同様
な理由から生産コストの低減が可能となる。さらにねじ
部についても本発明の形状を採用することによりねじ加
工が容易になり、ねじ成形用金型の寿命が延長する等、
経済的な生産が可能となる。Also, from the structural point of view, the head seat surface and the rounded portion under the neck are morphologically easy to process, which extends the life of the molding die when machining the head of a bolt, and also for nuts and washers. For the same reason, the production cost can be reduced. Furthermore, by adopting the shape of the present invention for the threaded portion as well, threading becomes easier, and the life of the thread forming die is extended.
Economical production becomes possible.
また、フランク角度がJISメートル並目ねじと同じで、
ピッチについてもJISメートル並目ねじと同じものが採
用できるため、作業にあたって違和感が無く、作業性も
良いため作業現場に受け入れられ易いと云う利点があ
り、また信頼性についても、摩擦係数値（κ）の変化が
小さいため周知のJISメートル並目ねじに関する試験デ
ータや実績値の採用が可能で、研究費や生産計画費、設
備費などの大幅な節約が出来る。Also, the flank angle is the same as JIS metric coarse thread,
Since the same pitch as JIS metric coarse thread can be adopted, there is no discomfort in the work and it has the advantage that it is easy to be accepted at the work site because of the good workability. Also, regarding the reliability, the friction coefficient value (κ ) Is small, it is possible to use well-known JIS metric coarse screw test data and actual values, and it is possible to significantly reduce research costs, production planning costs, equipment costs, etc.
さらに、既に述べたように応力集中の低減は耐疲労特性
の向上にも非常に効果があることから、本発明にかかる
高力ボルトは耐疲労ボルトとしても優れた効果が期待で
きる。Further, as described above, the reduction of stress concentration is also very effective in improving fatigue resistance, so that the high-strength bolt according to the present invention can be expected to be excellent in fatigue resistance.
第１図（ａ）は高力ボルト頭部の頂部平面図、第１図
（ｂ）は高力ボルトの概略正面図、第２図（ａ）、
（ｂ）は平座金の平面図および概略縦断面図、第３図、
第４図は首下丸み部の最大応力集中係数および最大塑性
歪量を示すグラフ、第５図はボルト頭部の切欠部分図、
第６図、第７図は平座金の部分片側断面図、第８図は平
座金の内径側受圧座面の応力度分布を示すグラフ、第９
図は平座金の下面部鉛直応力度分布を示すグラフ、第10
図は異なった平座金の内径側受圧座面の応力度分布を示
すグラフ、第11図は下面部鉛直応力度分布を示すグラ
フ、第12図は本発明にかかるねじ山及び谷底の形状決定
要領図、第13図は本発明にかかる高力ボルトに関する応
力集中係数を示すグラフ、第14図、第15図は比較のため
の周知高力ボルトに関する応力集中係数を示すグラフ、
第16図は本発明にかかる高力ボルトに関する塑性歪を示
すグラフ、第17図、第18図は比較のための周知高力ボル
トに関する塑性歪を示すグラフ、第19図はF10TのJISメ
ートル並目ねじを前記JASS6に規定する標準ボルト張力
（22.5Ton）で一様に引っ張ったときの塑性歪の大きさ
を計算した結果を示すグラフ、第20図は本発明にかかる
移行点を変えた例に関する高力ボルトの応力集中係数を
示すグラフ、第21図は本発明にかかる移行点を変えた例
に関する高力ボルトの塑性歪を示すグラフ、第22図はボ
ルト軸力付与試験の結果を示すグラフ、第23図（ａ）、
（ｂ）は試験に用いた被締付け鋼板の上・下鋼板の概略
側面および平面図、第24図はトルシア形高力ボルトの概
略正面図、第25図、第26図はトルシア形高力ボルトの頭
部座面形状と座金の概略説明図、第27図はナットの螺合
状態説明図である。 １…高力ボルト、２…頭部 ３…頭部座面、４…ボルト軸心 ５…首下丸み部、６…ねじ部 ７…円筒部、８…段部 ９、9a、9b…平座金 10…内径側受圧座面 11…軸心、12…孔 13…端部、14…線分 15…側面、16…被締付材 17…底面、18…水平面 19…下端、20…上端 21…垂線、22…垂線 23…孔面、24…側面 25…作用力 26〜37…応力度変化曲線 38…とがり山 39a、39b…ねじ山 40a、40b…フランク面 41…谷底 42a、42b…移行点 43…底辺 44a、44b…当接小円 44a1、44b1…谷底側円弧 45a、45b…延長線 46…２等分線、47…中心 48…外接円、48a…谷底側円弧 49…弧状曲線、50…上鋼板 51…下鋼板 52a、52b…試験用架台取付用貫通孔 53…試験ボルト取付用貫通孔 54…トルシア形高力ボルト 55…頭部、56…破断溝 57…ピンテール、58…首下丸み部 59…頭部座面、60…ねじ部 61…トルシア形高力ボルト 62…頭部、63…頭部座面 64…ナットのねじ山、65…先端 66…直線（基準）1 (a) is a top plan view of the head of the high-strength bolt, FIG. 1 (b) is a schematic front view of the high-strength bolt, FIG. 2 (a),
(B) is a plan view and a schematic vertical sectional view of a plain washer, FIG.
FIG. 4 is a graph showing the maximum stress concentration factor and the maximum amount of plastic strain in the rounded portion under the neck, and FIG. 5 is a cutaway partial view of the bolt head,
6 and 7 are partial side cross-sectional views of the flat washer, FIG. 8 is a graph showing the stress distribution on the inner diameter side pressure receiving seat surface of the flat washer, 9
The figure is a graph showing the vertical stress distribution of the plain washer,
Figure is a graph showing the stress distribution of the pressure bearing surface on the inner diameter side of different plain washers, Fig. 11 is a graph showing the vertical stress distribution of the lower surface, and Fig. 12 is a procedure for determining the shape of the threads and the valley bottom according to the present invention. FIG. 13, FIG. 13 is a graph showing a stress concentration factor for a high-strength bolt according to the present invention, FIGS. 14 and 15 are graphs showing a stress concentration factor for a known high-strength bolt for comparison,
FIG. 16 is a graph showing the plastic strain related to the high-strength bolt according to the present invention, FIG. 17, FIG. 18 is a graph showing the plastic strain related to a known high-strength bolt for comparison, and FIG. 19 is a JIS metric average of F10T. FIG. 20 is a graph showing the result of calculating the magnitude of plastic strain when the eye screw is uniformly pulled by the standard bolt tension (22.5 Ton) specified in JASS6, FIG. 20 is an example in which the transition point according to the present invention is changed. 21 is a graph showing the stress concentration factor of the high-strength bolt, FIG. 21 is a graph showing the plastic strain of the high-strength bolt regarding an example in which the transition point according to the present invention is changed, and FIG. 22 is the result of the bolt axial force application test. Graph, Figure 23 (a),
(B) is a schematic side view and plan view of the upper and lower steel plates to be tightened used in the test, Fig. 24 is a schematic front view of the Torsia type high-strength bolt, and Figs. FIG. 27 is a schematic explanatory view of a head seat surface shape and a washer, and FIG. 27 is an explanatory view of a nut screwed state. 1 ... High-strength bolt, 2 ... Head 3 ... Head seat surface, 4 ... Bolt shaft center 5 ... Under neck rounded part, 6 ... Screw part 7 ... Cylindrical part, 8 ... Step part 9,9a, 9b ... Flat washer 10 ... Inner diameter side pressure bearing surface 11 ... Shaft center, 12 ... Hole 13 ... End, 14 ... Line segment 15 ... Side, 16 ... Tightened material 17 ... Bottom, 18 ... Horizontal plane 19 ... Bottom, 20 ... Top 21 ... Perpendicular line, 22 ... Perpendicular line 23 ... Hole face, 24 ... Side face 25 ... Acting force 26 ... 37 ... Stress variation curve 38 ... Point 39a, 39b ... Thread 40a, 40b ... Frank face 41 ... Valley 42a, 42b ... Transition point 43 ... Base 44a, 44b ... Abutting small circle 44a 1 , 44b 1 ... Valley bottom arc 45a, 45b ... Extension line 46 ... Bisecting line, 47 ... Center 48 ... Outer circle, 48a ... Valley bottom arc 49 ... Arc curve , 50… Upper steel plate 51… Lower steel plate 52a, 52b… Test frame mounting through hole 53… Test bolt mounting through hole 54… Torcia type high strength bolt 55… Head, 56… Break groove 57… Pintail, 58… Rounded part under neck 59… Head seat surface, 60… Screw part 61… Torsi Form high-strength bolts 62 ... head 63 ... thread of the head seat surface 64 ... nut 65 ... tip 66 ... linear (reference)
フロントページの続き (72)発明者 宮川 敏夫 福岡県行橋市西泉４―３―２ 日鐵ボルテ ン株式会社内 (72)発明者 鈴木 信一 神奈川県相模原市淵野辺５―10―１ 新日 本製鐵株式會社第２技術研究所内(72) Inventor Toshio Miyagawa 4-3-2 Nishiizumi, Yukuhashi City, Fukuoka Prefecture Nippon Steel Volten Co., Ltd. (72) Inventor Shinichi Suzuki 5-10-1, Fuchinobe, Sagamihara City, Kanagawa Iron and Steel Co., Ltd. 2nd Technical Research Center
Claims (4)
°以下の載頭円錐面を構成し、かつ、首下丸み部が該頭
部座面と円筒部外面と接する曲率半径2.0mm以上5.5mm以
下の円弧曲面に形成され、さらにボルト軸心と直交する
平面への前記頭部座面の投影押圧面積Ｓが下記（１）式
に示す領域に設定され、 T/δ≦Ｓ ・・・・・・（１） T:設定締付力 kgf δ：被締付材の限界面圧 kgf/cm2 S:頭部座面の投影押圧面積 cm2 さらに、ねじ山のフランク角度が60°で、かつ等間隔ピ
ッチに刻設され、ついで、谷底が下記条件および算式に
規定される３円弧合成法（ａ）によって構成される弧状
曲線に形成されている高力ボルトと、ねじ山のフランク
角度が60°で、かつ等間隔ピッチに刻設され谷底が３円
弧合成法によって構成される弧状曲線に形成されている
ボルト雄ねじのフランク面と谷底の移行点を結ぶ直線を
基準として、ねじ先端が螺合許容域に形成された雌ねじ
を備えたナットと、内径側受圧座面が前記ボルト頭部座
面と同一載頭円錐面で、かつ略等面積に形成され、さら
に外径がボルト頭部の外径以上に構成された座金からな
る高力ボルト・ナット・座金のセット。 （ａ）前記３円弧合成法は、とがり山の高さをＨとし、
相対するねじ山のフランク面と谷底との移行点をとがり
山底辺から（９±１）H/20に設定し、前記それぞれの移
行点においてフランク面に当接する半径ｒがH/6の当接
小円を描き、さらに前記相対するフランク面の延長線が
なす鋭角の２等分線上に中心を有する半径Ｒが2/3・Ｈ
以上の前記当接小円の外接円を描き、前記当接小円と前
記外接円の谷底側円弧を重畳せしめ弧状曲線を形成する
方法1. The head seat surface is 90 ° or more with respect to the bolt shaft center.
A circular conical surface with a radius of curvature of 2.0 mm or more and 5.5 mm or less that makes contact with the head seat surface and the outer surface of the cylindrical portion, and that is perpendicular to the bolt axis. The projected pressing area S of the head seating surface on the plane to be set is set in the region shown in the following formula (1), and T / δ ≦ S ··· (1) T: Set tightening force kgf δ: Limit surface pressure of the material to be tightened kgf / cm 2 S: Projected pressing area of head bearing surface cm 2 Furthermore, the flank angles of the threads are 60 °, and they are engraved at equal pitches. The high-strength bolts formed in the arc-shaped curve formed by the three-arc synthesis method (a) specified in the conditions and formulas, and the flank angles of the threads are 60 °, and the valley bottoms are engraved at equal pitches. 3 A straight line that connects the flank surface of the male thread of the bolt and the transition point of the valley bottom formed in an arc-shaped curve constructed by the arc synthesis method And a nut having a female screw whose screw tip is formed in the screwing permissible area, and the inner diameter side pressure bearing surface is formed on the same conical surface of the head surface of the bolt head and has a substantially equal area. A set of high-strength bolts, nuts, and washers consisting of washers whose outer diameter is greater than the outer diameter of the bolt head. (A) In the three-arc synthesis method, the height of the sharp point is H,
The transition point between the flank surface and the valley bottom of the opposite thread is set to (9 ± 1) H / 20 from the edge of the sharp point, and the radius r that abuts the flank surface at each transition point is H / 6. A small circle is drawn, and the radius R centered on the acute angle bisector formed by the extension lines of the opposite flanks is 2/3 · H
A method of drawing an circumscribed circle of the contact small circle and forming an arc-shaped curve by overlapping the contact small circle and the arc of the valley bottom of the circumscribed circle
モリブデン鋼、クロム鋼、クロムモリブデン鋼、機械構
造用マンガン鋼、マンガンクロム鋼、アルミニウムクロ
ムモリブデン鋼のうち１種からなる請求項１記載の高力
ボルト・ナット・座金のセット。2. The high strength according to claim 1, wherein the component is one of nickel chromium steel, nickel chromium molybdenum steel, chromium steel, chromium molybdenum steel, mechanical structure manganese steel, manganese chromium steel, and aluminum chromium molybdenum steel. A set of bolts, nuts and washers.
鋼ボルト用棒鋼から形成された請求項１記載の高力ボル
ト・ナット・座金のセット。3. A set of high-strength bolts, nuts, and washers according to claim 1, which is formed from high temperature alloy steel bolt material or bar steel for special purpose alloy steel bolts.
請求項１記載の高力ボルト・ナット・座金のセット。4. The set of high-strength bolts, nuts and washers according to claim 1, which is made of heat-processable low / medium carbon steel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP31369590A JPH0689768B2 (en) | 1989-11-21 | 1990-11-19 | High-strength bolt / nut / washer set |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30266389 | 1989-11-21 | ||
| JP1-302663 | 1989-11-21 | ||
| JP31369590A JPH0689768B2 (en) | 1989-11-21 | 1990-11-19 | High-strength bolt / nut / washer set |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03229009A JPH03229009A (en) | 1991-10-11 |
| JPH0689768B2 true JPH0689768B2 (en) | 1994-11-14 |
Family
ID=26563220
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP31369590A Expired - Fee Related JPH0689768B2 (en) | 1989-11-21 | 1990-11-19 | High-strength bolt / nut / washer set |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0689768B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009174563A (en) * | 2008-01-21 | 2009-08-06 | Shinichi Nishida | Bolt and fastener using the same |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4142853B2 (en) * | 2001-03-22 | 2008-09-03 | 新日本製鐵株式会社 | High strength bolt with excellent delayed fracture resistance |
| JP4954248B2 (en) * | 2009-07-16 | 2012-06-13 | 株式会社東京鋲兼 | Self tapping screw |
| CN103967906A (en) * | 2013-01-29 | 2014-08-06 | 中国航空工业集团公司西安飞机设计研究所 | Super-strength MJ-thread alloy steel bolt |
| JP2017194079A (en) * | 2016-04-18 | 2017-10-26 | 株式会社ＮｅｊｉＬａｗ | Male screw body, female screw body, screw body design method, and thread structure |
| CN105673659A (en) * | 2016-04-22 | 2016-06-15 | 贵州航天精工制造有限公司 | Front bolt for bearing pedestal |
| JP7018616B2 (en) * | 2020-11-04 | 2022-02-14 | 松本重工業株式会社 | Aluminum alloy bolt |
| CN112576594B (en) * | 2020-12-07 | 2022-01-11 | 泰尔重工股份有限公司 | Large-root fillet uniform-strength thread and machining method thereof |
-
1990
- 1990-11-19 JP JP31369590A patent/JPH0689768B2/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009174563A (en) * | 2008-01-21 | 2009-08-06 | Shinichi Nishida | Bolt and fastener using the same |
| JP4701253B2 (en) * | 2008-01-21 | 2011-06-15 | 新一 西田 | Bolt and fastener using the same |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03229009A (en) | 1991-10-11 |
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