JP2573244Y2 - screw - Google Patents

screw

Info

Publication number
JP2573244Y2
JP2573244Y2 JP1994006971U JP697194U JP2573244Y2 JP 2573244 Y2 JP2573244 Y2 JP 2573244Y2 JP 1994006971 U JP1994006971 U JP 1994006971U JP 697194 U JP697194 U JP 697194U JP 2573244 Y2 JP2573244 Y2 JP 2573244Y2
Authority
JP
Japan
Prior art keywords
screw
torque
bit fitting
torque transmission
fitting groove
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 - Lifetime
Application number
JP1994006971U
Other languages
Japanese (ja)
Other versions
JPH0719611U (en
Inventor
幸三 山本
Original Assignee
オーエスジー販売 株式会社
幸三 山本
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by オーエスジー販売 株式会社, 幸三 山本 filed Critical オーエスジー販売 株式会社
Priority to JP1994006971U priority Critical patent/JP2573244Y2/en
Publication of JPH0719611U publication Critical patent/JPH0719611U/en
Application granted granted Critical
Publication of JP2573244Y2 publication Critical patent/JP2573244Y2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Description

【考案の詳細な説明】[Detailed description of the invention]

【0001】[0001]

【産業上の利用分野】本考案は、5方向又は6方向のビ
ット嵌合溝又はビット嵌合突起を有するねじに関する。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a screw having five or six-way bit fitting grooves or projections.

【0002】[0002]

【従来の技術】強力な締結力に耐え得るねじとして6方
向のビット嵌合溝又はビット嵌合突起を有するものが従
来より知られており、その従来例が図及び図にそれ
ぞれ示されている。
2. Description of the Related Art Conventionally, screws having a bit fitting groove or a bit fitting protrusion in six directions have been known as screws capable of withstanding a strong fastening force, and examples of such conventional screws are shown in FIGS. 8 and 9 , respectively. ing.

【0003】図にはねじの平面図が示されている。図
において、ねじの頭部2にはビット嵌合溝3が形成さ
れ、このビット嵌合溝3は第1補助円20で囲まれる如
く締結具のトルクが伝達されない非トルク伝達部Aと
この非トルク伝達部Aの外側位置で等間隔に配置されて
いる6個のトルク伝達係止部Bとから成る。この各トル
ク伝達係止部Bは第2補助円21上とこれより大径の
第3補助円22上とを中心に交互に、且つ、互いに接す
るように第4及び第5補助円23,24を描き、この第
4及び第5補助円23,24に沿って輪郭が形成されて
いる。
FIG. 8 shows a plan view of a screw. Figure
8 , a bit fitting groove 3 is formed in the screw head 2, the bit fitting groove 3 is a non-torque transmitting portion A to which the torque of the fastener is not transmitted as surrounded by the first auxiliary circle 20 .
And six torque transmission locking portions B which are arranged at equal intervals outside the non-torque transmitting portion A. Each torque transmitting engaging portion B are alternately around the upper second auxiliary circle 21 above and which from the large-diameter third auxiliary circle 22, and the fourth and fifth auxiliary circle 23 in contact with each other, 24, and a contour is formed along the fourth and fifth auxiliary circles 23, 24.

【0004】図には他のねじの平面図が示されてい
る。図において、このねじも前記と同様に頭部2のビ
ット嵌合溝3が非トルク伝達部Aとトルク伝達係止部B
とから形成されている。そして、このトルク伝達係止部
Bは第6補助円(外周円)25上を中心として等間隔に
第7補助円26を描き、この第6及び第7補助円25,
26に沿って輪郭が形成されている。
FIG. 9 shows a plan view of another screw. In FIG. 9 , the bit fitting groove 3 of the head 2 has the non-torque transmitting portion A and the torque transmitting
And is formed from The torque transmission locking portion B draws seventh auxiliary circles 26 at equal intervals around the sixth auxiliary circle (outer peripheral circle) 25, and the sixth and seventh auxiliary circles 25, 25.
An outline is formed along 26.

【0005】[0005]

【考案が解決しようとする課題】前者にあっては、締結
具をビット嵌合溝3に嵌合して回転トルクを作用させる
と、この回転トルクがトルク伝達係止部Bの内壁面に直
角な方向に作用する力(以下、「面直角力」という。)
Wとしてねじに与えられる。この面直角力Wはねじの円
周接線方向の力Fと半径方向の力Rに分けられ、この力
Fが回転駆動力としてねじに作用する。回転駆動力Fは
着力点におけるトルク伝達係止部Bの内壁面の接線l
と着力点を通る半径線lとの間の角度(以下、「駆動
角」という。)をαとすると、F=Wcosαとなる。
従って、駆動角αが小さくなればなるほど締結具の回転
トルクがロスなくねじの回転駆動力Fに変換されるが、
この従来例ではα=25゜程度であるため回転トルクの
伝達ロスが大きいという欠点があった。
In the former, when a fastener is fitted into the bit fitting groove 3 and a rotational torque is applied, the rotational torque is perpendicular to the inner wall surface of the torque transmission locking portion B. Force acting in various directions (hereinafter referred to as “plane normal force”)
Given to the screw as W. The surface normal force W is divided into a force F in the circumferential tangential direction of the screw and a force R in the radial direction, and this force F acts on the screw as a rotational driving force. The rotational driving force F is equal to the tangent line l 1 of the inner wall surface of the torque transmission locking portion B at the point of application.
And the angle between the radial line l 2 passing through the force applied points (hereinafter, referred to as "drive angle".) When the alpha, the F = Wcosα.
Therefore, as the drive angle α becomes smaller, the rotational torque of the fastener is converted to the rotational drive force F of the screw without loss,
In this conventional example, since α = approximately 25 °, there is a disadvantage that the transmission loss of the rotational torque is large.

【0006】後者にあっては、着力点が図に示す如く
最外周であれば駆動角αがゼロであるため回転トルクの
伝達ロスが全くないが、締結具の嵌合部はビット嵌合溝
3より若干小さく形成されるため着力点はむしろ最外周
より内周側になる。そのため、回転トルクの伝達ロスが
全くないという状態はまれであり、むしろ着力点の位置
の変動によって伝達効率が変化するため安定した高い伝
達効率が得られないという欠点があった。また、トルク
伝達係止部Bの先端がほぼ90゜の角度を有するため、
このビット嵌合溝3を圧造成形する際にこの付近が破損
しやすいという欠点があった。
In the latter case, if the point of application is the outermost periphery as shown in FIG. 9 , the driving angle α is zero, so that there is no transmission loss of the rotational torque. Since it is formed slightly smaller than the groove 3, the point of application is rather on the inner peripheral side than the outermost peripheral. Therefore, there is rarely a state in which there is no transmission loss of the rotational torque. Rather, there is a disadvantage that the transmission efficiency changes due to a change in the position of the point of application, so that stable high transmission efficiency cannot be obtained. Further, since the tip of the torque transmission locking portion B has an angle of approximately 90 °,
When the bit fitting groove 3 is formed by forging, there is a disadvantage that the vicinity thereof is easily damaged.

【0007】そこで、本考案は、安定した高い伝達効率
の回転トルクが得られ、且つ、ビット嵌合溝の圧造成形
時に破損のおそれがないねじを提供することを目的とす
る。
SUMMARY OF THE INVENTION It is an object of the present invention to provide a screw capable of obtaining a stable rotational torque with high transmission efficiency and having no risk of breakage during forging of a bit fitting groove.

【0008】[0008]

【課題を解決するための手段】上記課題を達成するため
の本考案のねじは、ねじ部と頭部とから成り、この頭部
の上面には前記ねじ部と同芯上のビット嵌合溝又はビッ
ト嵌合突起を設け、このビット嵌合溝又はビット嵌合突
起を中心位置の非トルク伝達部と等間隔位置に配置
され前記非トルク伝達部から半径方向外側に延びる5個
又は6個のトルク伝達係止部とから構成し、隣り合う前
記トルク伝達係止部の半径方向延長部分間の中心角をθ
とし、前記各トルク伝達係止部の両側の半径方向延長部
分間の中心角をθとすると、θ:θ=1.4:1と
なるように構成し、前各トルク伝達係止部の半径方向
延長部分には半径線と平行な直線部分を構成すると共
各トルク伝達係止部の先端部分をアールに構成した
ことを特徴としている。
In order to achieve the above object, a screw according to the present invention comprises a screw portion and a head, and the upper surface of the head has a bit fitting groove coaxial with the screw portion. or bit fitting projection provided to the bit fitting groove or bit fitting projections, and a non-torque transmitting portion of the center position, five equally spaced positions extending radially outward from said non-torque transmitting portions or 6 And the center angle between the radially extending portions of the adjacent torque transmission locking portions is θ.
And then, when the the central angle and theta 1 between the radially extending portion of both sides of each torque transmission engagement section, θ: θ 1 = 1.4: 1 and configured to be, before Symbol the torque transmission engagement with the radial extension of the parts constituting the radial line parallel to the linear portion, the tip portion of each torque transmission engagement portion is characterized in <br/> by being configured to Earl.

【0009】[0009]

【作用】締結具をねじのビット嵌合溝又はビット嵌合突
起に嵌合して回転すると、双方の嵌合が多少緩くて着力
点が変動しても着力点は常にトルク伝達係止部の直線部
分となり、駆動角がほぼ一定でかつ小さい値となるため
安定した高い伝達効率の回転トルクが得られる。また、
トルク伝達係止部の先端部分がアールに形成されている
ため、圧造成形時に破損のおそれがない。
When the fastener is rotated by fitting it into the bit fitting groove or the bit fitting protrusion of the screw, the fitting point is always the torque transmitting locking portion even if the fitting is slightly loose and the fitting point fluctuates. Since the driving angle is a linear portion and the driving angle is almost constant and small, a stable and high transmission efficiency rotational torque can be obtained. Also,
Since the tip portion of the torque transmission locking portion is formed in a round shape, there is no possibility of breakage during forging.

【0010】[0010]

【実施例】以下、本考案の実施例を図面を用いて説明す
る。図1から図には本考案の実施例が示されている。
DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings. 1 to 7 show an embodiment of the present invention.

【0011】図2には5方向のビット嵌合溝のねじの縦
断面図が、図3にはそのねじの平面図がそれぞれ示され
ている。図2及び図3において、ねじは外周面に螺旋突
起が設けられたねじ部1とこのねじ部1の上端に一体成
形された頭部2とから構成されている。この頭部2には
ねじ部1と同芯上のビット嵌合溝3が形成されている
る。
FIG. 2 is a longitudinal sectional view of the screw of the bit fitting groove in five directions, and FIG. 3 is a plan view of the screw. 2 and 3, the screw is composed of a screw portion 1 provided with a spiral projection on the outer peripheral surface and a head portion 2 integrally formed on the upper end of the screw portion 1. The head 2 has a bit fitting groove 3 formed concentrically with the screw portion 1.

【0012】図1には図3の拡大平面図が示されてお
り、前記ビット嵌合溝3は第8補助円4で囲まれる如く
締結具のトルクが伝達されない非トルク伝達部Aとこの
非トルク伝達部Aの外側位置で等間隔に配置された5個
のトルク伝達係止部Bとから成る。この各トルク伝達係
止部Bは半径方向外方に延び、この半径方向延長部分に
、前記トルク伝達係止部Bを二分する半径線lと平
行な直線部分3aを構成すると共に各トルク伝達係止部
Bの先端部分3bがアールに構成されている。
FIG. 1 is an enlarged plan view of FIG. 3, wherein the bit fitting groove 3 has a non-torque transmitting portion A to which the torque of the fastener is not transmitted as surrounded by an eighth auxiliary circle 4 and a non-torque transmitting portion A. And five torque transmission locking portions B arranged at equal intervals outside the torque transmission portion A. Extends Each torque transmitting engaging portion B is radially outward, each torque with this Radially extending portion constitutes a linear portion parallel 3a the radial line l 2 which bisects the torque transmission engagement section B The distal end portion 3b of the transmission locking portion B is formed in a round shape.

【0013】このトルク伝達係止部Bの作成は外周円上
5の等間隔位置に5個の第9補助円6を前記第8補助円
4に接するように描くと共に隣接する第9補助円6間の
位置で、第9補助円6と外周円5に接すると共に互いに
接する2個の第10補助円7を描く。
The torque transmission locking portion B is formed by drawing five ninth auxiliary circles 6 at equal intervals on the outer circumferential circle 5 so as to be in contact with the eighth auxiliary circle 4 and adjoining the ninth auxiliary circle 6. At the position between them, two tenth auxiliary circles 7 are drawn that are in contact with the ninth auxiliary circle 6 and the outer peripheral circle 5 and are in contact with each other.

【0014】次に、隣接する第9補助円6同士の中心点
Oを結ぶ第1補助線8とこの第1補助線8に平行でかつ
第10補助円7の中心点O′を通る第2補助線9とを描
く。そして、第9補助円6と第10補助円7と外周円5
に沿うと共に第1補助線8と第9補助円6との交点を通
る半径線lに平行な直線を引くことによって輪郭を形
成する。上記直線が半径線lと平行な直線部分3aを
構成し、第10補助円7に沿って形成される部分がアー
ルを構成する。
Next, a first auxiliary line 8 connecting the center points O of the adjacent ninth auxiliary circles 6 and a center point O 'of the tenth auxiliary circle 7 parallel to the first auxiliary line 8. Is drawn with the second auxiliary line 9 passing through. Then, the ninth auxiliary circle 6, the tenth auxiliary circle 7, and the outer peripheral circle 5
Forming a contour by subtracting the straight line parallel to the radial line l 2 passing through the first auxiliary line 8 to the intersection of the ninth auxiliary circle 6 with along. The straight line constitutes a linear portion parallel 3a the radial line l 2, portions formed along a tenth auxiliary circle 7 constitutes ares.

【0015】第10補助円7の半径rを可変にすること
によってアールの曲率が変化すると共に直線部分3a
の長さも変化する。図4にはr=N/8の場合が示さ
(Nはトルク伝達係止部Bの幅である。)、図5に
r=/2・(1−cosβ)の場合がそれぞれ示
されている(Gは外周円5の直径長さであり、βは軸心
から中心点Oを結ぶ直線と半径線l との中心角であ
る。)ここで、r=N/8未満の場合にはアールの
曲率が小さすぎて圧造成形時に破損する可能性があるた
め、rはN/8以上か、それ以上が好ましい。また、
/2・(1−cosβ)の場合には前記直線部分
3aがなくなってしまうため、rは/2・(1−co
sβ)未満とする必要がある。従って、第10補助円7
の半径rは、 N/8≦r</2・(1−cosβ) を満たす値に設定されている。
By changing the radius r of the tenth auxiliary circle 7, the curvature of the radius is changed, and the linear portion 3a
Also varies in length. FIG. 4 shows the case of r = N / 8
Is (N is the width of the torque transmission engagement section B.), FIG. 5, the case of r = G / 2 · (1 -cosβ) is shown, respectively (G diameter length of the outer periphery £ 5 And β is the axis
Central angle der between the straight line and the radial line l 2 connecting the center point O from
You. ) . Here, if r is less than N / 8 , the radius of curvature of the radius is so small that there is a possibility of breakage during forging, so r is preferably at least N / 8 or more. Also, r
= In the case of G / 2 · (1-cosβ ) , the order linear portion 3a becomes rather, r is G / 2 · (1-co
sβ). Therefore, the tenth auxiliary circle 7
Radius r of the Ru Tei is set to a value satisfying N / 8 ≦ r <G / 2 · (1-cosβ).

【0016】また、隣り合うトルク伝達係止部Bの半径
方向延長部分間の中心角をθとし、各トルク伝達係止部
Bの両側の半径方向延長部分間の中心角をθとする
と、第9補助円6の直径dによって中心角θと中心角θ
の比が決定されθ:θ=1.4:1とすればビット
嵌合溝3と締結具の嵌合突部10のせん断面積は図6に
示すようにほぼ等しくなるため、締結具の耐久性が向上
する利点がある。すなわち、ねじの材質は、引っ張り強
さ等を考慮して一般にクロムモリブテン鋼が用いられ、
その硬度が約8.8以上のものが使用されている一方、
締結具もねじとほぼ同じ材質,硬度のものが使用されて
いる。したがって、ビット嵌合溝3と締結具の嵌合突部
10のせん断面積は、例えば締結具側が小さい場合は回
転トルクを付与した際に嵌合突部10の山が潰れてしま
うおそれがある。しかし、本考案の場合は、θ:θ
1.4:1に決定されているため、図6に示すようにビ
ト嵌合溝3側のせん断面積(右下がり斜線)と締結具
の嵌合突部10のせん断面積(左下がり斜線)がほぼ等
しくなる。このため、両者3,10の摩耗量が均一かつ
互いに少なくなり、この結果、締結具及びねじの耐久性
が向上するのである。 そして、θ:θ=1.4:1に
する場合の中心角θと中心角θ はそれぞれ以下の値と
なる。中心角θは、θ=360゜/n・1.4/2.4
(n:トルク伝達係止部の数)の式で表されるため、5
方向の場合にθ=42゜,θ =30゜、6方向の場合
には、θ=35゜,θ =25゜となる。中心角βは、
β=360゜/2nの式で表されるため、5方向の場合
にβ=36゜、6方向の場合にβ=30゜となる。
Further, the central angle between the radially extending portion of the adjacent torque transmitting engaging portion B and theta, when the central angle between the radially extending portion of both sides of each torque transmission engagement section B and theta 1, The central angle θ and the central angle θ depend on the diameter d of the ninth auxiliary circle 6.
When the ratio of 1 is determined and θ: θ 1 = 1.4: 1, the shear area of the bit fitting groove 3 and the fitting projection 10 of the fastener is shown in FIG.
As shown, they are almost equal, and thus there is an advantage that the durability of the fastener is improved. That is, the material of the screw is tensile strength
Chromium molybdenum steel is generally used in consideration of
While those whose hardness is about 8.8 or more are used,
The fasteners are made of the same material and hardness as the screws.
I have. Therefore, the bit fitting groove 3 and the fitting projection of the fastener are formed.
The shear area of 10 is, for example, when the fastener side is small,
When the rolling torque is applied, the peak of the fitting projection 10 is crushed.
There is a possibility that. However, in the case of the present invention, θ: θ 1 =
1.4: because it is determined in 1, Tsugumi <br/> Tsu shear area DOO fitting groove 3 side (right downward oblique line) as shown in FIG. 6 and the fastener
Area of the mating projection 10 is approximately equal
It becomes difficult. For this reason, the wear amount of both 3 and 10 is uniform and
Less each other, resulting in fastener and screw durability
Is improved. Then, when θ: θ 1 = 1.4: 1, the center angle θ and the center angle θ 1 have the following values, respectively. The central angle θ is θ = 360 ° / n · 1.4 / 2.4.
(N: number of torque transmission locking parts)
Theta = 42 ° in the case of direction, theta 1 = 30 °, in the case of 6 direction, theta = 35 °, the theta 1 = 25 °. The central angle β is
Since β = 360 ° / 2n, β = 36 ° in five directions and β = 30 ° in six directions.

【0017】ねじの製造に際し、ねじ用パンチをねじの
頭部2上面に押圧するとねじの頭部2にせん断破壊が生
じてねじ用パンチの形状に沿ったビット嵌合溝3が形成
される。このビット嵌合溝3の形状から最もせん断破壊
に無理があるトルク伝達係止部Bの先端部分がアールに
形成されているため、ねじ用パンチの形状に沿わない破
損が生じることがない。
In manufacturing the screw, when the screw punch is pressed against the upper surface of the screw head 2, shear fracture occurs in the screw head 2 and a bit fitting groove 3 is formed along the shape of the screw punch. Due to the shape of the bit fitting groove 3, the tip end of the torque transmission locking portion B, which is most difficult to shear breakage, is formed in a round shape, so that damage that does not conform to the shape of the screw punch does not occur.

【0018】また、このようにして製造されたねじを用
いて締結するには、ねじ孔にねじ頭部2の先端を位置さ
せて締結具をねじのビット嵌合溝3に嵌合して回転す
る。すると、締結具の回転トルクがビット嵌合溝3のト
ルク伝達係止部Bの内壁に作用してねじがねじ孔に螺入
される。この回転トルクの伝達に際して、双方の嵌合が
多少緩いため着力点が変動するが着力点はトルク伝達係
止部Bの直線部分3aのいずれかのポイントになる。そ
のため、駆動角αがほぼ一定で、且つ、小さい値(α≒
12゜)となるので、安定した高い伝達効率の回転トル
クがねじに作用する。
Further, in order to fasten using the screw manufactured in this way, the tip of the screw head 2 is positioned in the screw hole, and the fastener is fitted into the bit fitting groove 3 of the screw and rotated. I do. Then, the rotation torque of the fastener acts on the inner wall of the torque transmission locking portion B of the bit fitting groove 3, and the screw is screwed into the screw hole. In transmitting the rotational torque, the point of application fluctuates due to the looseness of the engagement between the two, but the point of application is any point on the linear portion 3a of the torque transmission locking portion B. Therefore, the drive angle α is almost constant and small (α ≒
12 °), so that a rotational torque with stable and high transmission efficiency acts on the screw.

【0019】図には6方向のビット嵌合溝のねじの平
面図が示されており、このねじも前記実施例と略同様に
トルク伝達係止部Bが形成されている。従って、前記実
施例と同一構成箇所には同一符号を付してその説明を省
略する。
FIG. 7 is a plan view of a screw of a bit fitting groove in six directions, and this screw also has a torque transmission locking portion B substantially in the same manner as in the above embodiment. Therefore, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof will be omitted.

【0020】尚、上記実施例では頭部2の上面にビット
嵌合溝3を設けたが、これと同一形状のビット嵌合突起
を頭部2に設けても同様の作用・効果が得られる。
Although the bit fitting groove 3 is provided on the upper surface of the head 2 in the above embodiment, the same operation and effect can be obtained by providing a bit fitting projection having the same shape on the head 2. .

【0021】また、この明細書において、頭部2とはね
じ部1と同一径に構成され、頭部2の外周面にも螺施突
起がねじ部1から延長されて形成されている場合をも含
む概念である。
In this specification, the case where the head 2 has the same diameter as the threaded portion 1 and a threaded projection is formed on the outer peripheral surface of the head 2 so as to extend from the threaded portion 1 will be described. It is a concept that also includes

【0022】[0022]

【考案の効果】以上述べたように本考案によれば、ビッ
ト嵌合溝又はビット嵌合突起の各トルク伝達係止部に半
径線と平行な直線部分を構成すると共にその先端部分を
アールに構成したので、着力点が常に直線部分となるた
め安定した高い伝達効率の回転トルクが得られると共に
先端部分がアールのためビット嵌合溝の圧造成形時に破
損のおそれがないという効果を奏する。特に、本考案で
は、隣り合う前記トルク伝達係止部の半径方向延長部分
間の中心角をθとし、前記各トルク伝達係止部の両側の
半径方向延長部分間の中心角をθとすると、θ:θ
=1.4:1となるよう構成したので、ビット嵌合溝又
はビット嵌合突起と締結具の嵌合部分とのせん断面積が
ほぼ等しくなるため、締結具及びねじの耐久性が向上す
るという効果を奏する。
As described above, according to the present invention, a linear portion parallel to the radius line is formed at each torque transmission locking portion of the bit fitting groove or the bit fitting projection, and the tip portion is rounded. With this configuration, since the contact point is always a linear portion, a stable and high transmission efficiency rotational torque can be obtained, and since the tip portion is round, there is an effect that there is no possibility of breakage during the forging of the bit fitting groove. In particular, in the present invention, the central angle between the radial extension of the torque transmission engagement section adjacent to theta and, when the the central angle and theta 1 between the radially extending portion of both sides of each torque transmission engagement portion , Θ: θ 1
= 1.4: 1, the shear area between the bit fitting groove or the bit fitting projection and the fitting part of the fastener is substantially equal, and the durability of the fastener and the screw is improved. It works.

【図面の簡単な説明】[Brief description of the drawings]

【図1】ねじの拡大平面図。FIG. 1 is an enlarged plan view of a screw.

【図2】ねじの縦断面図。FIG. 2 is a longitudinal sectional view of a screw.

【図3】ねじの平面図。FIG. 3 is a plan view of a screw.

【図4】他の例のねじの拡大平面図。FIG. 4 is an enlarged plan view of a screw of another example.

【図5】さらに他の例のねじの拡大平面図。FIG. 5 is an enlarged plan view of a screw of still another example.

【図6】ビット嵌合溝と締結具の嵌合突部とのせん断面
積を示す説明図。
FIG. 6 is a shear plane between a bit fitting groove and a fitting protrusion of a fastener.
Explanatory drawing showing a product.

【図7】6方向のビット嵌合溝のねじの拡大平面図。 FIG. 7 is an enlarged plan view of a screw in a bit fitting groove in six directions.

【図8】従来例のねじの平面図。 FIG. 8 is a plan view of a conventional screw.

【図9】FIG. 9 他の従来例のねじの平面図。FIG. 9 is a plan view of another conventional screw.

【符号の説明】[Explanation of symbols]

1…ねじ部 2…頭部 3…ビット嵌合溝 3a…直線部分 3b…先端部分(アール) A…非トルク伝達部 B…トルク伝達係止部G…外周円の直径 DESCRIPTION OF SYMBOLS 1 ... Screw part 2 ... Head part 3 ... Bit fitting groove 3a ... Linear part 3b ... Tip part (R) A ... Non-torque transmission part B ... Torque transmission locking part G ... Diameter of outer circumference circle

フロントページの続き (56)参考文献 実開 昭53−97261(JP,U) 実公 昭53−33078(JP,Y2) 米国特許2445978(US,A) 英国公開2397216(GB,A)Continuation of the front page (56) References JP-A-53-97261 (JP, U) JP-A-53-33078 (JP, Y2) US Patent 2,449,978 (US, A) British publication 2397216 (GB, A)

Claims (1)

(57)【実用新案登録請求の範囲】(57) [Scope of request for utility model registration] 【請求項1】 ねじ部と頭部とから成り、この頭部の上
面には前記ねじ部と同芯上のビット嵌合溝又はビット嵌
合突起を設け、このビット嵌合溝又はビット嵌合突起
中心位置の非トルク伝達部と等間隔位置に配置さ
れ前記非トルク伝達部から半径方向外側に延びる5個又
は6個のトルク伝達係止部とから構成し、隣り合う前記
トルク伝達係止部の半径方向延長部分間の中心角をθと
し、前記各トルク伝達係止部の両側の半径方向延長部分
間の中心角をθとすると、θ:θ=1.4:1とな
るように構成し、前各トルク伝達係止部の半径方向延
長部分には半径線と平行な直線部分を構成すると共に
各トルク伝達係止部の先端部分をアールに構成したこと
を特徴とするねじ。
The present invention comprises a screw portion and a head, and a bit fitting groove or a bit fitting projection concentric with the screw portion is provided on an upper surface of the head portion. projections, and a non-torque transmitting portion of the center position, consist of a five or six torque transmitting engagement portion are arranged at equal intervals positions extending radially outward from said non-torque transmitting portion, the adjacent torque transmitting the central angle between the radially extending portion of the locking portion and theta, when the the central angle and theta 1 between the radially extending portion of both sides of each torque transmission engagement section, θ: θ 1 = 1.4: 1 configured so that, together with the radially extending portion of the front Symbol respective torque transmission engagement portion constituting the radial line parallel to the linear portion,
A screw, wherein a tip portion of each torque transmission locking portion is formed in a radius.
JP1994006971U 1994-06-15 1994-06-15 screw Expired - Lifetime JP2573244Y2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP1994006971U JP2573244Y2 (en) 1994-06-15 1994-06-15 screw

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP1994006971U JP2573244Y2 (en) 1994-06-15 1994-06-15 screw

Publications (2)

Publication Number Publication Date
JPH0719611U JPH0719611U (en) 1995-04-07
JP2573244Y2 true JP2573244Y2 (en) 1998-05-28

Family

ID=11653095

Family Applications (1)

Application Number Title Priority Date Filing Date
JP1994006971U Expired - Lifetime JP2573244Y2 (en) 1994-06-15 1994-06-15 screw

Country Status (1)

Country Link
JP (1) JP2573244Y2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012112523A (en) * 2010-11-24 2012-06-14 Lisi Aerospace Fixing member with recess at the end of its threaded shank, male element fitting into the recess, handling tool and gauge including such male element

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5238076B2 (en) * 2009-06-24 2013-07-17 オーエスジーシステムプロダクツ株式会社 Screw tightening structure, screw, and screw tightening tool
MY196632A (en) * 2011-08-25 2023-04-24 Infastech Ip Pte Ltd Tapered Lobular Driver and Fastener

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2445978A (en) 1945-05-07 1948-07-27 Domnic V Stellin Socket head screw
GB2397216A (en) 2003-01-14 2004-07-21 Derek Keith Morley A wiper blade and water supply arrangement

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2397216A (en) * 1944-06-16 1946-03-26 Domnic V Stellin Socket head screw
JPS5397261U (en) * 1977-01-10 1978-08-07
JPS5333078U (en) * 1977-08-03 1978-03-23

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2445978A (en) 1945-05-07 1948-07-27 Domnic V Stellin Socket head screw
GB2397216A (en) 2003-01-14 2004-07-21 Derek Keith Morley A wiper blade and water supply arrangement

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012112523A (en) * 2010-11-24 2012-06-14 Lisi Aerospace Fixing member with recess at the end of its threaded shank, male element fitting into the recess, handling tool and gauge including such male element
KR101753409B1 (en) 2010-11-24 2017-07-03 리지 아에로스페이스 A fixing member with a recess at the end of its threaded shank, a male element, a handling tool and a gauge comprising such a male element

Also Published As

Publication number Publication date
JPH0719611U (en) 1995-04-07

Similar Documents

Publication Publication Date Title
US6997085B2 (en) Threaded-fastener wrenching structure, threaded fastener and wrenching tool
JP2001020926A (en) Drive system
JP4801837B2 (en) A spiral drive system for threaded fasteners
US6698315B1 (en) High torque wrenching system
US6485220B2 (en) Tool joint
US7455329B2 (en) Fast make-up fatigue resistant rotary shouldered connection
US5137407A (en) Head drive for threaded fastener
KR100681082B1 (en) Flexible shaft coupling
EP1590515B1 (en) Fast make-up fatigue resistant rotary shouldered connection
US6101907A (en) Interference fit joint and method and indexable ratchet wrench utilizing same
CA1066542A (en) Lobular socket head fastener with service slot
US4259889A (en) Thread tapping form
US5408905A (en) Tiltable ball-type driver
US6361257B1 (en) Parallel wave washer
US4110051A (en) Apparatus for producing a non-releasable connection and non-releasable connection produced with such apparatus
JP2573244Y2 (en) screw
JPH03163207A (en) Screw
US20040047712A1 (en) Bolt fastener
CN111365350A (en) Nut assembly and bolt kit
WO2003100272A1 (en) Screw tightening construction, and screw and screw tightening tool
JP3026965B1 (en) Screw tightening structure, screw and screw tightening tool
US20020039523A1 (en) Fastener including a head and a shank at least partially including a threaded portion
JPH06337018A (en) Shaft coupling
US20230321799A1 (en) Anti-Slip Fastener Driver
CN212202794U (en) Nut assembly and bolt kit

Legal Events

Date Code Title Description
EXPY Cancellation because of completion of term