JP6510110B1 - Male thread member - Google Patents
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- JP6510110B1 JP6510110B1 JP2018077308A JP2018077308A JP6510110B1 JP 6510110 B1 JP6510110 B1 JP 6510110B1 JP 2018077308 A JP2018077308 A JP 2018077308A JP 2018077308 A JP2018077308 A JP 2018077308A JP 6510110 B1 JP6510110 B1 JP 6510110B1
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- 230000000630 rising effect Effects 0.000 claims abstract description 36
- 238000003780 insertion Methods 0.000 claims abstract description 11
- 230000037431 insertion Effects 0.000 claims abstract description 11
- 239000011295 pitch Substances 0.000 claims description 30
- 230000002093 peripheral effect Effects 0.000 claims description 17
- 230000007423 decrease Effects 0.000 claims description 11
- 230000007704 transition Effects 0.000 claims description 9
- 230000013011 mating Effects 0.000 claims description 4
- 230000003247 decreasing effect Effects 0.000 claims 1
- 230000004323 axial length Effects 0.000 description 18
- 230000004048 modification Effects 0.000 description 16
- 238000012986 modification Methods 0.000 description 16
- 238000003825 pressing Methods 0.000 description 3
- 239000013585 weight reducing agent Substances 0.000 description 3
- 238000012937 correction Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Abstract
【課題】短いねじ先形状によって斜め入りを防止し得るおねじ部材を提供する。【解決手段】完全ねじ山２１の軸部２０の先端側の端部２１ａにはねじの立ち上がり部２２が連続して設けられ、ねじの立ち上がり部２２は完全ねじ山２１の谷径ｄ１から完全ねじ山２１に向けて徐々に立ち上がる構成となっており、ねじ先形状部３０は、外側に凸の円弧状に膨らんだ環状凸部４０を備え、環状凸部４０の最大径ｄ２がめねじの内径Ｄ１の寸法公差の下限値以下に設定されていることを特徴とする。【選択図】図２The present invention provides a male screw member capable of preventing oblique insertion by a short screw tip shape. SOLUTION: A rising portion 22 of a screw is continuously provided at an end 21a of a tip side of a shaft portion 20 of a complete screw thread 21, and the rising portion 22 of the screw is a complete screw from a valley diameter d1 of the complete screw thread 21. The screw tip shape portion 30 includes an annular convex portion 40 that bulges outward in a circular arc shape, and the maximum diameter d2 of the annular convex portion 40 is an inner diameter D1 of a female screw. It is characterized by being set below the lower limit value of the dimensional tolerance of. [Selected figure] Figure 2
Description
本発明は、めねじへの斜め入りを防止するねじ先形状を備えたおねじ部材に関する。ここで、斜め入りとは、おねじがめねじに対して相対的に斜めに入って噛み込み、焼き付きやかじりを生じる状態をいうものとする。 The present invention relates to a male screw member having a screw tip shape that prevents oblique insertion into a female screw. Here, the term "inclination" refers to a state in which the male screw engages with the female screw at an angle to cause biting and sticking.
従来から、自動車の組立等の量産加工において、ねじの締結を行う際に、締付け機器として、作業性向上のために締め付けを高速回転で行える締付け機器が用いられている。締め付け部位によっては、作業体勢が不安定で、おねじを相手めねじに対して同一線上で行えない場合がある。締め付けが高速でかつ斜めに締め付ける場合がある悪条件下での作業のために、おねじとめねじ間でかじりや焼き付けが生じる場合がある。 2. Description of the Related Art Conventionally, in mass production processing such as automobile assembly, when fastening a screw, as a fastening device, a fastening device capable of performing fastening at high speed to improve workability has been used. Depending on the tightening position, the working posture may be unstable and the male screw may not be able to be aligned with the mating female screw. For work under adverse conditions where tightening may be fast and may be oblique, galling or baking may occur between male and female threads.
これらの対策として、たとえば、特許文献１に記載のようなパイロット付きボルトが提案されている。このパイロット付きボルトは、軸部の先端のねじ先形状を、完全ねじ山が形成された軸部の先端側に完全ねじ山よりも小径の案内ねじ山を設けるとともに、案内ねじ山よりもさらに先端側に円筒状ガイドを備えた構成となっていた。案内ねじ山は、めねじの内径と等しいか、それよりも小さい外径を有し、円筒状ガイド（外周面が円筒状のガイド）は、案内ねじ山の谷径よりも大きく、かつ、案内ねじ山の外径と等しいか、それよりも小さい径を有する構成となっていた。
めねじに螺合して締め付ける際には、先端の円筒状ガイドによって傾きが矯正されながら挿入されていき、続いて案内ねじ山が挿入され、案内ねじ山がめねじ部材のめねじ山と係合し、ピッチを整えながら完全ねじ山と螺合されるように案内されていく。
As measures against these, for example, a bolt with a pilot as described in Patent Document 1 has been proposed. This piloted bolt has a tip shape of the tip of the shaft, and a guide thread having a diameter smaller than that of the complete thread on the tip side of the fully threaded shaft, and a tip further than the guide thread. It had a configuration provided with a cylindrical guide on the side. The guide thread has an outer diameter equal to or smaller than the inner diameter of the female screw, and the cylindrical guide (a guide with a cylindrical outer peripheral surface) is larger than the valley diameter of the guide thread and It was configured to have a diameter equal to or smaller than the outer diameter of the thread.
When screwing and tightening the female screw, it is inserted while correcting the inclination by the cylindrical guide at the tip, and then the guide thread is inserted, and the guide thread is engaged with the internal thread of the female thread member. It is guided to be screwed with a complete thread while adjusting the pitch.
しかしながら、上記特許文献１のパイロット付きボルトは、完全ねじ山が形成された軸部の先端に案内ねじ山及び円筒状ガイドが延びており、ねじ自体の長さが長くなると共に、重量も増大する。また、めねじの長さが短いと円筒状ガイドでは傾き矯正が十分できず、焼き付きやかじりを防止することができない。 However, in the piloted bolt of Patent Document 1 described above, the guide thread and the cylindrical guide extend at the tip of the fully threaded shaft, and the length of the screw itself is increased and the weight is also increased. . In addition, when the length of the female screw is short, the cylindrical guide can not correct the tilt sufficiently, and the seizing and sticking can not be prevented.
本発明の目的は、短いねじ先形状によって斜め入りを防止し得るおねじ部材を提供することにある。 An object of the present invention is to provide an externally threaded member capable of preventing oblique insertion by means of a short threaded end shape.
上記目的を達成するために、本発明は、軸部に、相手部材のめねじに螺合される完全ねじ山を形成し、前記軸部の先端側に斜め入りを防止するねじ先形状を備えたおねじ部材において、
前記完全ねじ山の前記軸部の先端側の端部にはねじの立ち上がり部が連続して設けられ、該ねじの立ち上がり部は前記完全ねじ山の谷径以上の円筒面から前記完全ねじ山に向けて徐々に立ち上がる構成となっており、
前記ねじ先形状は、外側に凸の円弧状に膨らんだ環状凸部を備え、
前記環状凸部の最大径が前記めねじの内径の寸法公差の下限値以下に設定され、
前記完全ねじ山の前記軸部の先端側の端部から前記環状凸部の先端側端部までの前記軸部の中心軸線方向の長さは、前記完全ねじ山の２ピッチ以内に設定されていることを特徴とする。
ねじ穴への締付作業は、まず、環状凸部が開口端のめねじ部材のねじ穴内に所定量進入する。おねじ部材の軸部がねじ穴の中心軸線に対して傾いて進入した場合、ねじ穴の開口端に対向するおねじ部材のねじの立ち上がりから完全ねじ山を含むねじ山のどこかの位置で、ねじ穴の開口端に係合する。おねじ部材をねじ穴に挿入する力と、この係合位置においてねじ穴の開口端から作用する反力が偶力となって、軸部の傾きを修正する方向のモーメントが作用する。環状凸部の外周面の最大径は、めねじの内径以下に設定されているので、ねじ穴内において環状凸部の回転は許容され、初期の係合位置と１８０°反対側の部分がねじ穴の開口端に係合する。この状態で、軸部をねじ込み方向に回転することにより、ねじの立ち上がりの先端から一巻き目の完全ねじ山が、連続的にめねじの２巻き目のねじ山に安定して螺合し、ねじのかじりや焼き付きを防止することができる。
このように、ねじ先にねじ山の無い環状凸部を設けることによって、軸部が斜めに進入したとしたしても、めねじに噛み込むことなく空転するので、ねじのかじりや焼き付きを防止でき、さらに、軸の傾きを修正するモーメントが作用するので、従来のような円筒状ガイドが不要となり、ねじ先の長さを可及的に短くすることができる。
ＪＩＳ Ｂ １００３「締結用部品−メートルねじをもつおねじ部品のねじ先」には、ねじ先の不完全ねじ部長さｕは、２ピッチ以下（ｕ≦２Ｐ）と規定されている。本発明者らは、この不完全ねじ部長さの範囲で斜め入りを防止することを検討し、本発明にいたった。本発明のねじ先形状によれば、上記ＪＩＳ規格の不完全ねじ部長さの範囲で、かじり防止機能を実現することができる。斜め入りを防止することができる。
前記環状凸部の最大径は、前記完全ねじ山の谷径以上に構成とすることができる。
すなわち、環状凸部は、おねじの谷底すきまの範囲に収まり、ねじ穴に進入した環状凸部とめねじとのガタツキが小さく抑えられ、斜め入りをスムースに矯正できる。
In order to achieve the above object, the present invention forms a complete screw thread screwed to the female screw of the mating member in the shaft portion, and has a screw tip shape that prevents oblique insertion at the tip end side of the shaft portion. In the male screw member,
A rising portion of a screw is continuously provided at an end of the tip end side of the shaft portion of the full thread, and a rising portion of the screw is a cylindrical surface having a diameter equal to or larger than a valley diameter of the full thread. It is configured to gradually rise toward the
The screw tip shape includes an annular convex portion that bulges in a circular arc shape that is convex outward.
The maximum diameter of the annular convex portion is set to be equal to or less than the lower limit value of the dimensional tolerance of the inner diameter of the female screw ,
The length in the central axis direction of the shaft from the end on the tip side of the shaft of the full thread to the end on the tip side of the annular convex portion is set within 2 pitches of the full thread It is characterized by
In the tightening operation to the screw hole, first, the annular convex portion enters a predetermined amount into the screw hole of the female screw member at the open end. When the shaft of the male thread member enters at an angle to the central axis of the screw hole, from the rise of the thread of the male thread member opposite to the open end of the screw hole, at any position of the thread including a complete thread , Engage with the open end of the screw hole. The force for inserting the male screw member into the screw hole and the reaction force acting from the open end of the screw hole in this engaged position form a couple of forces, and a moment in the direction for correcting the inclination of the shaft acts. Since the maximum diameter of the outer peripheral surface of the annular convex portion is set equal to or less than the inner diameter of the female screw, rotation of the annular convex portion is permitted in the screw hole, and the portion opposite to the initial engagement position is 180 ° Engage the open end of the. In this state, by rotating the shaft portion in the screwing direction, the complete thread of the first turn from the leading end of the screw continuously and stably engages with the thread of the second turn of the female screw, Screws can be prevented from sticking and sticking.
In this way, by providing an annular convex portion without threads at the screw tip, even if the shaft portion enters diagonally, it does not bite into the female screw and therefore it will spin, thus preventing screw galling and seizure. In addition, since the moment for correcting the inclination of the shaft acts, the conventional cylindrical guide becomes unnecessary, and the length of the screw tip can be shortened as much as possible.
According to JIS B 1003 "part for fastening-screw tip of male screw part with metric screw", the incomplete thread length u of the screw tip is specified as 2 pitch or less (u ≦ 2P). The present inventors examined preventing the diagonal entry in the range of the incomplete thread length and came to the present invention. According to the screw tip shape of the present invention, a galling prevention function can be realized in the range of the incomplete screw portion length of the above-mentioned JIS standard. Ru it is possible to prevent the diagonal filled.
The maximum diameter of the annular convex portion can be configured to be equal to or larger than the valley diameter of the complete thread.
That is, the annular convex portion falls within the range of the valley clearance of the male screw, and rattling between the annular convex portion entering the screw hole and the female screw is suppressed to be small, and the diagonal entry can be smoothly corrected.
環状凸部の外周面は、最大径となる頂部からねじの立ち上がり側に向けて徐々に小径となる反先端側円弧面を備えている構成とすることができる。
また、前記環状凸部の外周面は、最大径となる軸部の先端に向けて徐々に小径となる先端側傾斜面を備えた構成とすることができる。
このようにすれば、先端側円弧面が穴探りとして機能し、軸部とめねじの中心軸線との心ずれを解消することができる。
また、穴探り性の他に、斜め入り挿入時におねじ先端面をめねじ内部に当てることで、おねじの深沈みを防止し、めねじとの理想的な接触状態を再現できる。
前記環状凸部の前記軸部の中心軸線方向の長さは、完全ねじ山のピッチをＰとすると、（１Ｐ±０．２Ｐ）の範囲とすることができる。
このようにすれば、めねじのねじ山間に、環状凸部が入り込むことを防止することができる。
また、前記ねじの立ち上がりの先端から完全ねじ山への移行範囲は、前記軸部の１／２周以内とすることが望ましい。
移行範囲が極端に短いと、斜め入りの修正が十分に行われないうちに完全ねじ山が嵌まり合ってかじりが発生しやすく、移行長さが長すぎると、軸方向長さが長くなり、軽量化の観点から見て重量増につながるため不利となる。１／２周程度あれば、斜め入りを防止しつつ、軽量化を図ることができる。
特に、前記ねじの立ち上がり部の先端から完全ねじ山への移行範囲は、前記軸部の１／４周以上とすることができる。
また、前記環状凸部と前記円筒面の先端側との間に環状凹部を備えた構成とすることができる。
このようにすれば、斜め入りの際のめねじとの干渉を回避することができ、斜め入りの許容角度を大きくできる。
また、前記ねじの立ち上がり部が形成される円筒面の端縁が前記環状凸部の反先端側の端部に位置する構成とすることができる。
このようにすれば、環状凹部を設ける場合に比べて、軸方向の長さをより一層短くすることができる。
また、前記環状凸部の先端に向かって徐々に小径となるガイドを備えた構成とすることができる。
このようにガイドを設ければ、さらに穴探り性を高めることができる。
The outer peripheral surface of the annular convex portion can be configured to have a non-tip end side arc surface whose diameter decreases gradually from the top portion having the largest diameter toward the rising side of the screw.
Further, the outer peripheral surface of the annular convex portion can be configured to have a tip side inclined surface whose diameter is gradually reduced toward the tip of the shaft portion having the maximum diameter.
In this case, the tip side arc surface functions as a hole search, and the misalignment between the shaft and the center axis of the female screw can be eliminated.
Further, in addition to the hole profilability, by placing the end face of the external thread on the inside of the internal thread at the time of oblique insertion, it is possible to prevent the sinking of the external thread and reproduce an ideal contact state with the internal thread.
The length in the central axis direction of the shaft portion of the annular convex portion can be in the range of (1P ± 0.2P), where P is a pitch of a perfect thread.
In this way, it is possible to prevent the annular projection from entering between the threads of the female screw.
In addition, it is desirable that the transition range from the leading end of the rising of the screw to the complete screw thread be within 1⁄2 turn of the shaft portion.
If the transition range is extremely short, complete threading is likely to occur and galling may occur before the oblique correction is sufficiently performed, and if the transition length is too long, the axial length becomes long, It is disadvantageous because it leads to an increase in weight from the viewpoint of weight reduction. If it is about 1/2 turn, weight reduction can be achieved while preventing diagonal entry.
In particular, the transition region from the front end of the rising portion of the screw to complete screw threads, Ru can be 1/4 laps over the shaft portion.
Also, it can be configured to include an annular recess between the front end side of the cylindrical surface and the annular protrusion.
In this way, interference with the female screw at the time of oblique insertion can be avoided, and the allowable angle of oblique insertion can be increased.
Further, the end of the cylindrical surface on which the rising portion of the screw is formed may be positioned at the end opposite to the tip end of the annular convex portion.
In this way, the axial length can be further shortened as compared to the case where the annular recess is provided.
Moreover, it can be set as the structure provided with the guide which becomes small diameter gradually toward the front-end | tip of the said cyclic | annular convex part.
By providing the guide in this manner, the hole searchability can be further enhanced.
本発明によれば、ねじ先形状部が短くても、軸部の斜め入りを効果的に防止することができ、ねじ山のかじりや焼き付きを防止することができる。 According to the present invention, even if the screw tip shape portion is short, it is possible to effectively prevent oblique entry of the shaft portion and to prevent scuffing and seizing of the screw thread.
以下に、本発明を、図示の実施形態に基づいて詳細に説明する。
図１は、本発明の実施形態に係るおねじ部材を示している。
図において、１はおねじ部材全体を示すもので、このおねじ部材１は、頭部１０と軸部２０とを備え、軸部２０に相手部材のめねじに螺合される完全ねじ山２１を形成し、軸部２０の先端側に斜め入りを防止するねじ先形状部３０を備えている。頭部１０の形状については、図では鍔付きの六角形状を例示しているが、特に限定されるものはではなく、種々の形状の頭部形状が適用可能である。なお、図示例では有効径ボルトを例示している、呼び径ボルトにも適用可能である。
完全ねじ山２１の軸部２０の先端側の端部２２ａには、ねじの立ち上がり２２が連続して設けられ、ねじの立ち上がり部２２は完全ねじ山２１の谷径から完全ねじ山２１に向けて徐々に立ち上がる構成となっており、ねじ先形状部は、環状凸部４０を有し、環状凸部４０とねじの立ち上がり部２２の先端２２ａとの間に環状凹部５０が形成されている。
Below, the present invention will be described in detail based on the illustrated embodiments.
FIG. 1 shows a male screw member according to an embodiment of the present invention.
In the figure, reference numeral 1 denotes the entire male screw member. The male screw member 1 includes a head 10 and a shaft 20, and the shaft 20 has a full thread 21 screwed to a female screw of a mating member. A screw tip shape portion 30 is formed and formed on the tip end side of the shaft portion 20 to prevent oblique insertion. The shape of the head 10 is illustrated in the figure as a barbed hexagonal shape, but is not particularly limited, and various shapes of head shapes are applicable. In addition, it is applicable also to the nominal diameter bolt which has illustrated the effective diameter bolt in the example of illustration.
At the end 22 a of the tip end side of the shaft portion 20 of the complete thread 21, the rising 22 of the screw is provided continuously, and the rising 22 of the thread is directed from the valley diameter of the complete thread 21 to the complete thread 21 The screw tip shape has an annular projection 40, and an annular recess 50 is formed between the annular projection 40 and the tip 22a of the rising portion 22 of the screw.
以下、各部の構成について、図２を参照して詳細に説明する。
［ねじの立ち上がり部２２］
ねじの立ち上り部２２は、完全ねじ山２１の端部２１ａから先端２２ａに向けて徐々に高さが低くなり、先端２２ａ位置において、完全ねじ山２１の谷径ｄ１以上の外径を有する円筒面２５からの高さがゼロとなる。逆に、先端２２ａ側から見ると、円筒面２５から
完全ねじ山２１の端部２１ａに向けて、徐々に立ち上がり、完全ねじ山２１の高さに移行する。ねじの立ち上がり部２２の先端２２ａは、円筒面２５の軸部先端側の端縁２５ａに位置する。
本発明では、ねじの立ち上がり部２２の先端２２ａ位置から完全ねじ山２１の端部２１ａまでの移行範囲が、１／２周（半周）の範囲内で、軸部２０の中心軸線Ｎ１方向に換算すると、１ピッチの半分程度となっている。たとえば、ＪＩＳ規格のＭ１０×１．２５のねじの場合には、０．６２５［ｍｍ］となる。
移行範囲が極端に短いと、斜め矯正が十分に行われないうちに完全ねじ山２１が嵌まり合ってかじりが発生しやすく、移行長さが長すぎると、軸方向長さが長くなり、軽量化の観点から見て重量増につながるため不利となる。１／２周程度あれば、斜め入りを防止しつつ、軽量化を図ることができる。
Hereinafter, the configuration of each part will be described in detail with reference to FIG.
[Rise 22 of screw]
The rising portion 22 of the screw gradually decreases in height from the end 21a of the complete screw thread 21 to the tip 22a, and at the position of the tip 22a a cylindrical surface having an outer diameter equal to or more than the valley diameter d1 of the complete screw thread 21. The height from 25 is zero. Conversely, when viewed from the tip 22 a side, it gradually rises from the cylindrical surface 25 toward the end 21 a of the complete thread 21 and shifts to the height of the complete thread 21. The tip 22 a of the rising portion 22 of the screw is located at the end 25 a of the cylindrical surface 25 on the tip side of the shaft.
In the present invention, the transition range from the tip 22a position of the rising portion 22 of the screw to the end 21a of the complete screw thread 21 is converted in the direction of the central axis N1 of the shaft portion 20 within the range of 1/2 turn (half turn). Then, it is about half of one pitch. For example, in the case of a screw of M10 × 1.25 according to the JIS standard, it is 0.625 [mm].
If the transition range is extremely short, the complete thread 21 is easily fitted and galling occurs easily before the oblique correction is sufficiently performed, and if the transition length is too long, the axial length becomes long and light weight It is disadvantageous because it leads to an increase in weight from the viewpoint of If it is about 1/2 turn, weight reduction can be achieved while preventing diagonal entry.
［環状凸部４０］
環状凸部４０については、その外周面４１の軸部２０の中心軸線Ｎ１を通る縦断面形状は、外側に凸の円弧状に膨らんだ断面円弧状となっており、全周に亘って円弧状に膨らんだ形状となっている。
外周面４１の最大径となる頂部４１ａは、外周面４１の軸方向中途位置にあり、外周面４１は、頂部４１ａから、軸方向軸先端側に向けて徐々に小径となる先端側円弧面４１ｂと、頂部４１ａからねじの立ち上がり部２２側に向けて徐々に小径となる反先端側円弧面４１ｃとを備えている。先端側円弧面４１ｂと反先端側円弧面４１ｃは、頂部４１ａにおいて滑らかに連続する一つの円弧面となっている。
外周面４１の頂部４１ａの最大径である外径ｄ２は、対応するめねじ部材１００の内径Ｄ１以下（ｄ２≦Ｄ１）に設定されている。この環状凸部４０の頂部４１ａの外径ｄ２の寸法公差範囲の最大値は、内径Ｄ１の公差範囲の最小値以下に設定される。この実施例では、環状凸部４０の外径ｄ２は、内径Ｄ１よりも所定寸法だけ小さく設定されている。なお、図中ｄは、完全ねじ山２１の外径である。
また、反先端側円弧面４１ｃのねじの立ち上がり部２２側の端縁に位置する谷部５１の直径ｄ３は、頂部４１ａの外径ｄ２以下（ｄ３≦ｄ２）となっている。この谷部５１の直径ｄ３は、ねじの立ち上がり部２２が形成される円筒面２５の端縁２５ａの直径ｄ５より小径となっているので、谷部５１と円筒面２５の端縁２５ａとの間に、谷部５１から円筒面２５の端縁２５ａに向けて徐々に大径となるテーパー面５２が設けられている。また、環状凸部４０とねじの立ち上がり部２２の先端２２ａとの間に形成される環状凹部５０は、環状凸部４０の反先端側円弧面４１ｃとテーパー面５２とによって構成される。
ねじ山がＭ１０×１．２５の場合には、めねじ部材１００の内径Ｄ１が８．６４７ｍｍに対して、環状凸部４０の頂部４１ａの外径ｄ２は、８．６５±０／−０．４［ｍｍ］程度に設定することが好ましい。すなわち、公差範囲を、めねじ部材１００の内径下限値からマイナス５〜８％以内に設定している。また、環状凹部５０の谷部５１の直径ｄ３は、ねじの呼び径×８０％〜８５％（環状凸部以下）程度に設定することが好ましい。
[Annular convex portion 40]
About the annular convex part 40, the longitudinal cross-sectional shape which passes along the central axis N1 of the axial part 20 of the outer peripheral surface 41 has become a circular arc shape which bulges in the shape of a convex arc and has an arc shape over the entire circumference It has a bulging shape.
The top 41a, which is the largest diameter of the outer peripheral surface 41, is at the middle of the outer peripheral surface 41 in the axial direction, and the outer peripheral surface 41 has a tip side arc surface 41b that gradually decreases in diameter toward the axial tip end side from the top 41a. And a non-tip end side arc surface 41c whose diameter gradually decreases from the top 41a toward the rising portion 22 of the screw. The tip side arc surface 41b and the non-tip side arc surface 41c form one arc surface that is smoothly continuous at the top 41a.
The outer diameter d2, which is the maximum diameter of the top 41a of the outer circumferential surface 41, is set to be equal to or less than the inner diameter D1 of the corresponding female screw member 100 (d2 ≦ D1). The maximum value of the dimensional tolerance range of the outer diameter d2 of the top 41a of the annular convex portion 40 is set to be equal to or less than the minimum value of the tolerance range of the inner diameter D1. In this embodiment, the outer diameter d2 of the annular convex portion 40 is set smaller than the inner diameter D1 by a predetermined size. In the drawing, d is the outer diameter of the complete thread 21.
Further, the diameter d3 of the valley portion 51 located at the end edge on the rising portion 22 side of the screw on the opposite end side arc surface 41c is equal to or less than the outer diameter d2 of the top portion 41a (d3 ≦ d2). The diameter d3 of the valley portion 51 is smaller than the diameter d5 of the end 25a of the cylindrical surface 25 on which the rising portion 22 of the screw is formed. Therefore, between the valley 51 and the end 25a of the cylindrical surface 25 A tapered surface 52 is provided which gradually increases in diameter from the valley portion 51 toward the edge 25 a of the cylindrical surface 25. Further, an annular concave portion 50 formed between the annular convex portion 40 and the tip end 22 a of the rising portion 22 of the screw is constituted by the non-tip end side arc surface 41 c of the annular convex portion 40 and the tapered surface 52.
When the thread is M10 × 1.25, the inside diameter D1 of the internal thread member 100 is 8.647 mm, and the outside diameter d2 of the top portion 41a of the annular convex portion 40 is 8.65 ± 0 / −0. It is preferable to set about 4 [mm]. That is, the tolerance range is set to within -5 to 8% of the lower limit value of the inner diameter of the female screw member 100. The diameter d3 of the valley portion 51 of the annular recess 50 is preferably set to about 80% to 85% of the nominal diameter of a screw (equal to or less than the annular projection).
さらに、環状凸部４０の軸方向長さＬ２は、環状凸部４０がねじ穴１２０内において、めねじのねじ山１２１の間に嵌り込むことがないように、１ピッチ（１Ｐ）程度、好ましくは、（１±０．２）Ｐ程度とすることが好ましい。
また、完全ねじ山２１の端部２１ａの山頂から軸部２０の先端、すなわち軸端面２６まで軸方向長さＬ１としては、２ピッチ程度以上に設定することが好ましい。初期嵌合時に、軸部２０とねじ穴１２０の開口部との嵌合代が、この程度あれば、締付作業を安定して行うことができる。
この実施形態では、Ｌ１は２ピッチ（２Ｐ）に設定されており、テーパー面５２の軸方向長さＬ３は、０．５ピッチ（０．５Ｐ）程度に設定されている。また、このテーパー面５２のテーパー角度θは、谷部５１の直径ｄ３とテーパー面５２の軸方向長さＬ３の関係によって定まるが、図示例では４０°程度に設定される。
ＪＩＳ Ｂ １００３「締結用部品−メートルねじをもつおねじ部品のねじ先」に、ねじ先の不完全ねじ部長さｕは、２ピッチ以下（ｕ≦２Ｐ）と規定されており、本実施形態は、このＪＩＳ規格の範囲内でかじり防止機能を実現するものである。
Further, the axial length L2 of the annular convex portion 40 is preferably about 1 pitch (1 P), preferably, so that the annular convex portion 40 is not fitted into the thread 121 of the female screw in the screw hole 120. Is preferably about (1 ± 0.2) P.
The axial length L1 from the peak of the end 21a of the complete thread 21 to the tip of the shaft portion 20, that is, the axial end surface 26, is preferably set to about 2 pitches or more. If the fitting allowance between the shaft portion 20 and the opening of the screw hole 120 is about this extent at the time of initial fitting, the tightening operation can be stably performed.
In this embodiment, L1 is set to 2 pitches (2P), and the axial length L3 of the tapered surface 52 is set to about 0.5 pitches (0.5P). The taper angle θ of the tapered surface 52 is determined by the relationship between the diameter d3 of the valley 51 and the axial length L3 of the tapered surface 52, but is set to about 40 ° in the illustrated example.
The incomplete thread length u of the screw tip is specified as 2 pitches or less (u ≦ 2P) in JIS B 1003 “Fastening parts – screw tip of male screw part with metric screw”, and this embodiment The anti-glare function is realized within the scope of this JIS standard.
上記環状凸部４０と環状凹部５０は、次のように設定されている。
すなわち、中心軸線Ｎ１を通る断面上で、軸部２０の軸端面２６の中心Ｏをとり、螺合するめねじの内径Ｄ１を直径とする仮想円Ｃを描いた場合に、環状凸部４０の外周面４１が、仮想円Ｃの内側に位置するように設定されている。外周面４１の断面円弧の曲率半径Ｒは、仮想円Ｃの半径（Ｄ１／２）以下に設定される。
これは、軸部２０のねじ先形状部３０がめねじ部材１００のねじ穴１２０に挿入された状態で、軸部２０が軸端面２６の中心Ｏを中心として傾いた場合に、環状凸部４０の外周面４１がねじ穴１２０のめねじのねじ山１２１に引っ掛からない形状としたものである。
環状凸部４０の外周面４１の頂部４１ａは、軸端面２６を通る仮想円Ｃの直径線Ｃ１から、軸方向にｆだけ軸方向反先端側にオフセットされており、反先端側円弧面４１ｃは仮想円Ｃに近接しているが、先端側円弧面４１ｂは、頂部４１ａから軸部の先端に向けて徐々に小径となる方向に湾曲するのに対して、仮想円Ｃは、環状凸部４０の頂部４１ａの位置から直径線Ｃ１に向けて大径に拡がるので、先端側円弧面４１ｂは頂部４１ａ側から軸方向先端側に向けて徐々に仮想円Ｃとの隙間が広がるように構成される。
本実施形態のように、小径となる先端側円弧面４１ｂを設けておけば、軸部２０とねじ穴１２０の中心ずれがあった場合でも、ねじ穴１２０の開口端に係合することができ、穴探り性を有する利点がある。軸端面２６の先端径は、図示例では谷部５１の径と同程度に記載しているが、特に限定されるものではなく、仮想円Ｃの範囲内で設定される。
次に、図６を参照し、環状凸部４０の外周面４１の変形例について説明する。
図６（Ａ）は、変形例１を示している。
この変形例１では、環状凸部４０の外周面１４１は、軸方向先端側の先端側円筒面１４１ｂと、この先端側円筒面１４１ｂから軸方向反先端側に向けて徐々に小径となる円弧状の反先端側円弧面１４１ｃとによって構成されている。先端側円筒面１４１ｂと反先端側円弧面１４１ｃとは、接続部１４１ａにおいて滑らかに接続されている。接続部１４１ａは、図中、一転鎖線で示すように、軸方向中央位置（上記実施形態では頂部４１ａの位置）に位置しているが、中央位置には限定されない。この変形例１では、最大径部は、先端側円筒面１４１ｂである。また、先端側円筒面１４１ｂの軸端面２６との角部は圧造によりアールが付けられたアール部１４１ｄとなっている。
図６（Ｂ）は、変形例２を示している。
この変形例２では、環状凸部４０の外周面２４１は、頂部２４１ａを隔てて、軸方向先端側に向かって円錐状に徐々に小径となる先端側テーパー面２４１ｂと、軸方向反先端側に向けて円弧状に小径となる反先端側円弧面２４１ｃとによって構成されている。先端側テーパー面２４１ｂと反先端側テーパー面２４１ｃとは、頂部２４１ａにおいて滑らかに接続されており、頂部２４１ａが最大径部となる。また、先端側テーパー面２４１ｂの軸端面２６との角部は、圧造によりアールが付けられたアール部２４１ｄとなっている。
この変形例２の先端側テーパー面２４１ｂについては、上記実施形態の先端側円弧面と同様に、穴探りとして機能する。
図６（Ｃ）は、変形例３を示している。
この変形例３では、環状凸部４０の外周面３４１の軸方向断面形状は、頂部３４１ａが軸方向先端近傍に位置し、谷部５１から仮想円Ｃに沿って、円弧状に徐々に大径となるように湾曲する円弧面３４１ｃによって構成され、最大径が、変形例１、変形例２よりも大きくなっている。また、この変形例も、円弧面３４１ｃと軸端面２６との角部は、圧造によりアールが付けられたアール部３４１ｄとなっている。
The annular convex portion 40 and the annular concave portion 50 are set as follows.
That is, the outer periphery of the annular convex portion 40 in the case of drawing the imaginary circle C having the center O of the axial end surface 26 of the shaft portion 20 on the cross section passing through the central axis N1 and having the inner diameter D1 of the female screw as a diameter. The surface 41 is set to be located inside the virtual circle C. The curvature radius R of the cross-sectional arc of the outer circumferential surface 41 is set to the radius (D1 / 2) or less of the imaginary circle C.
This is because, when the shaft portion 20 is inclined about the center O of the shaft end face 26 in a state where the screw tip shape portion 30 of the shaft portion 20 is inserted into the screw hole 120 of the female screw member 100, The outer peripheral surface 41 is shaped so as not to be caught by the thread 121 of the female screw of the screw hole 120.
The top 41a of the outer peripheral surface 41 of the annular convex portion 40 is axially offset by f from the diameter line C1 of the imaginary circle C passing through the axial end surface 26 by f in the axial direction. Although it is close to the virtual circle C, the tip side arc surface 41b is curved in a direction in which the diameter gradually decreases from the top 41a toward the tip of the shaft, while the virtual circle C is an annular convex 40 The tip side arc surface 41b is configured such that a gap with the virtual circle C gradually widens from the top 41a side toward the tip end side in the axial direction from the position of the top 41a toward the diameter line C1. .
As in the present embodiment, if the tip side arc surface 41b having a small diameter is provided, even when there is a center deviation between the shaft portion 20 and the screw hole 120, the open end of the screw hole 120 can be engaged. , There is an advantage of having a hole detectability. The tip diameter of the axial end surface 26 is described to be approximately the same as the diameter of the valley portion 51 in the illustrated example, but is not particularly limited, and is set within the range of the imaginary circle C.
Next, a modification of the outer peripheral surface 41 of the annular convex portion 40 will be described with reference to FIG.
FIG. 6A shows a first modification.
In the first modification, the outer circumferential surface 141 of the annular convex portion 40 has a tip end side cylindrical surface 141b on the tip side in the axial direction, and an arc shape whose diameter gradually decreases from the tip side cylindrical surface 141b toward the tip opposite to the axial direction. And an arc surface 141c opposite to the front end side. The tip end side cylindrical surface 141 b and the non-tip end side arc surface 141 c are smoothly connected at the connection portion 141 a. The connection portion 141a is located at the axial center position (the position of the top 41a in the above embodiment) as indicated by a one-dotted chain line in the figure, but is not limited to the center position. In the first modification, the largest diameter portion is the tip side cylindrical surface 141 b. Further, a corner portion of the tip end side cylindrical surface 141b with the axial end surface 26 is a rounded portion 141d which is rounded by pressing.
FIG. 6B shows a second modification.
In the second modification, the outer peripheral surface 241 of the annular convex portion 40 has a tip side taper surface 241b which gradually decreases in diameter in a conical shape toward the tip end side in the axial direction with the top portion 241a separated; It is comprised by the opposite end side circular arc surface 241c which becomes small diameter toward a circular arc shape. The tip side taper surface 241b and the non-tip side taper surface 241c are smoothly connected at the top portion 241a, and the top portion 241a is the maximum diameter portion. In addition, a corner portion of the tip side tapered surface 241b with the axial end surface 26 is a rounded portion 241d that is rounded by pressing.
The distal end side tapered surface 241b of the second modification functions as a hole search similar to the distal end side arc surface of the above embodiment.
FIG. 6C illustrates a third modification.
In the third modification, the axial cross-sectional shape of the outer peripheral surface 341 of the annular convex portion 40 is such that the apex 341a is located in the vicinity of the tip in the axial direction, and the diameter gradually increases in a circular arc from the valley 51 to the virtual circle C. The maximum diameter is larger than that of the first modification and the second modification. Further, also in this modification, the corner between the arc surface 341c and the axial end surface 26 is a rounded portion 341d having a radius by pressing.
次に、図３を参照して、本実施形態のおねじ部材の締め付け作業について説明する。
ねじ穴１２０への締付作業は、まず、環状凸部４０がめねじ部材１００のねじ穴１２０
内に所定量進入する。
図３（Ａ）に示すように、おねじ部材１の軸部２０の中心軸線Ｎ１が、ねじ穴１２０の中心軸線Ｎ２に対して傾いている場合、ねじ穴１２０の開口端に対向するおねじ部材１のねじの立ち上がり部２２と完全ねじ山２１を含むねじ山のどこかの位置で、ねじ穴１２０の開口端に係合する。図示例では、初期の係合位置ａ１は、完全ねじ山２１の端部２１ａがめねじ部材１００のねじ山が谷部で切断された位置（図中、右端）で、めねじのねじ山１２１のフランク面に係合している。
この状態で、おねじ部材１をねじ穴１２０に押し込むと、押し込み力と、係合位置ａ１においてねじ穴１２０の開口端から作用する反力が偶力となって、軸部２０の傾きを修正する方向、図中反時計回り方向のモーメントＭｃｃが作用する。環状凸部４０の外周面４１は断面円弧状であり、その頂部４１ａの外径ｄ２は、めねじ部材１００のねじ穴１２０の内径Ｄ１以下に設定されているので、ねじ穴１２０内で環状凸部４０の回転は許容され、図３（Ｂ）に示すように、軸部２０は初期の係合位置ａ１を支点として、反時計回り方向に回転する。
そして、図３（Ｃ）に示すように、初期の係合位置ａ１と１８０°反対側の部分がねじ穴１２０の開口端に係合する（係合位置ａ２）。この状態で、軸部を回転することで、ねじの立ち上がり部２２の先端２２ａからねじの立ち上がり部２２及び一巻き目の完全ねじ山２１が、連続してめねじ部材１００の２巻き目のねじ山１２１に安定して螺合していき、ねじのかじりや焼き付きを防止することができる。
Next, with reference to FIG. 3, the tightening operation of the externally threaded member of the present embodiment will be described.
In the tightening operation to the screw hole 120, first, the annular convex portion 40 is a screw hole 120 of the female screw member 100.
Enter a predetermined amount inside.
As shown in FIG. 3 (A), when the central axis N1 of the shaft portion 20 of the male screw member 1 is inclined with respect to the central axis N2 of the screw hole 120, a male screw facing the open end of the screw hole 120 The open end of the threaded hole 120 is engaged at some location on the thread including the screw up 22 and full thread 21 of the member 1. In the illustrated example, the initial engagement position a1 is a position where the end 21a of the complete thread 21 is cut at the bottom of the thread of the internal thread member 100 (right end in the figure). Engaged with flanks.
In this state, when the male screw member 1 is pushed into the screw hole 120, the pushing force and the reaction force acting from the open end of the screw hole 120 at the engagement position a1 become a couple force, and the inclination of the shaft portion 20 is corrected. The moment Mcc in the counterclockwise direction in the drawing acts. The outer peripheral surface 41 of the annular convex portion 40 has an arc shape in cross section, and the outer diameter d2 of the top 41a thereof is set to be equal to or smaller than the inner diameter D1 of the screw hole 120 of the female screw member 100. The rotation of the portion 40 is permitted, and as shown in FIG. 3B, the shaft portion 20 rotates counterclockwise with the initial engagement position a1 as a fulcrum.
Then, as shown in FIG. 3C, the portion on the opposite side to the initial engagement position a1 by 180 ° engages with the open end of the screw hole 120 (engagement position a2). In this state, by rotating the shaft portion, the rising portion 22 of the screw and the complete thread 21 of the first winding are continuously from the tip 22a of the rising portion 22 of the screw, and the screw of the second turn of the female screw member 100 is continued. It is possible to stably screw on the mountain 121 and to prevent galling and seizing of the screw.
図３（Ａ）〜（Ｃ）では、初期の係合位置ａ１が、完全ねじ山２１の端部２１ａのフランク面が、めねじ部材１００の開口端の谷部で切断したねじ山のフランク面に当接する位置としたが、反対に傾いた場合には、図４（Ａ）に示すように、ねじの立ち上がり部２２の先端２２ａから３６０°回転した位置の完全ねじ山２１が、ねじの無いおねじ部材１の開口端に係合する（係合位置ａ３）。この状態でおねじ部材１を押し込むと、図中、時計回り方向のモーメントＭｃが作用し、初期の係合位置ａ３を支点として、時計回り方向に回転して傾きが修正される。
また、図４（Ｂ）に示すように、軸部２０が、図中反時計回りに大きく傾いた場合には、テーパー面５２が開口端に初期係合する場合もあり（破線で囲んだ係合位置ａ４）、この場合にも、係合位置ａ４を支点として、時計回り方向のモーメントＭｃが作用して傾きが修正される。また、図４（Ｃ）に示すように、軸部２０が、図中時計回りに大きく傾いた場合には、完全ねじ山２１の端部２１ａがめねじのねじ山１２１に係合せずに、テーパー面５２が係合する場合がある（破線で囲んだ係合位置ａ５）。この場合には、係合位置ａ５を支点として、反時計回り方向のモーメントＭｃｃが作用して傾きが修正される。図４（Ｂ），（Ｃ）の場合には、最終的に、図３（Ｃ）に示すように、係合位置ａ１と、１８０°反対側の係合位置ａ２で係合することになる。
In FIGS. 3 (A) to 3 (C), the flank surface of the thread where the flank surface of the end 21a of the complete thread 21 is cut at the valley of the open end of the internal thread member 100 at the initial engagement position a1. However, if it inclines in the opposite direction, as shown in FIG. 4A, the complete thread 21 at a position rotated 360 ° from the tip 22a of the rising portion 22 of the screw is not screwed. It engages with the open end of the male screw member 1 (engagement position a3). In this state, when the male screw member 1 is pushed in, a moment Mc in the clockwise direction acts in the figure, and the inclination is corrected by rotating clockwise with the initial engagement position a3 as a fulcrum.
Further, as shown in FIG. 4B, when the shaft portion 20 is largely inclined counterclockwise in the drawing, the tapered surface 52 may be initially engaged with the open end (the relationship surrounded by the broken line is shown in FIG. In the combined position a4), also in this case, the moment Mc in the clockwise direction acts on the engaging position a4 as a fulcrum to correct the inclination. Further, as shown in FIG. 4C, when the shaft portion 20 is largely inclined clockwise in the figure, the end portion 21a of the complete thread 21 does not engage with the thread 121 of the female screw, and is tapered. The surface 52 may be engaged (engagement position a5 surrounded by a broken line). In this case, a moment Mcc in the counterclockwise direction acts on the engaging position a5 as a fulcrum to correct the inclination. In the case of FIGS. 4B and 4C, finally, as shown in FIG. 3C, the engagement position a1 is engaged with the engagement position a2 opposite to the 180 °. .
次に、本発明の他の実施形態について説明する。
以下の説明では、主として上記実施形態と異なる点について説明し、同一の構成部分については、同一の符号を付して説明を省略する。
図７は、本発明の実施形態に係るおねじ部材の要部を示すもので、（Ａ）は要部正面図、（Ｂ）は（Ａ）の１８０°反対側を示す要部裏面図である。
本実施形態は、上記実施形態に対して、テーパ面５２を無くした例であり、ねじの立ち上がり部２２が形成される円筒面２５の先端側の端縁２５ａが、環状凸部４０と反先端側の端縁に位置する。
円筒面２５の軸方向先端側の端縁２５ａは、ねじの中心軸線Ｎ１と直交する面上の円であるが、反先端側の端縁２５ｂは、完全ねじ山２１の端部から一巻き分の完全ねじ山２１の付け根との螺旋状の境界線である。したがって、立ち上がり部が２２が完全に立ち上がった完全ねじ山２１の端部２１ａ位置を起点とすると、図７（Ａ）の完全ねじ山２１の端部２１ａ位置では（図７（Ａ）の右端、図７（Ｂ）の左端）、先端側の端縁２５ａと反先
端側の端縁２５ｂの隙間はほぼゼロであり、図７（Ｂ）に示すように、裏側に回ると、図中左端から右端に向かって、反先端側の端縁２５ｂが完全ねじ山２１のリード角方向に傾斜して延び、先端側の端縁２５ａに対して軸方向の間隔が徐々に拡がっていき、さらに、図７（Ａ）に示すように、完全ねじ山２１の端部２１ａに向かって、さらに軸方向の間隔が拡大していき、元の基点位置に対して１ピッチ離れた位置に達する。
したがって、円筒面２５は、起点においては、軸方向の長さはほぼゼロで、一周して完全ねじ山２１の１ピッチ分の軸方向長さとなる螺旋状の円筒面である。立ち上がり部２２は、この円筒面２５から徐々に立ち上がって完全ねじ山の端部２１ａに至る。
本実施形態では、上記実施形態のテーパー面５２の０．５ピッチ分が無いために、最小で、１．５ピッチまで短縮可能である（Ｌ１＝Ｌ２（１ピッチ）＋Ｌ４（完全ねじ山２１の半分（１／２ピッチ（０．５ピッチ））。
その際、谷部５１が無く、おねじの立ち上がり部２２は、環状凸部４０の反先端側円弧面４１ｃの反先端側端部付近に位置する先端２２ａから立ち上がりが始まる。円筒面２５の径ｄ５については、完全ねじ山２１の谷径ｄ１以上、環状凸部４０の外径ｄ２以下に設定される（ｄ２≧ｄ５≧ｄ１）。図示例は、円筒面１５の径ｄ５が完全ねじ山２１の谷径ｄ１と同一の例である。
谷径ｄ１と環状凸部４０の外径ｄ２は、めねじ部材１００のねじ穴の内径Ｄ１の下限値以下であり、円筒面２５の径ｄ５は完全ねじ山２１の谷径ｄ１以上となるように公差範囲が設定され、締付に影響がない程度の僅かな隙間とすることでガタツキが小さく抑えられ、斜め入りをスムースに矯正することができる。
なお、形状の相違はあるものの、上記実施形態と同様に、ねじ山がＭ１０×１．２５の場合には、めねじ部材１００の内径Ｄ１は８．６４７ｍｍに対して、環状凸部４０の頂部４１ａの外径ｄ２は、８．６５±０／−０．４［ｍｍ］程度に設定することが好ましい。すなわち、公差範囲を、めねじ部材１００の内径下限値からマイナス５〜８％以内に設定している。
Next, another embodiment of the present invention will be described.
In the following description, points different from the above embodiment will be mainly described, and the same components will be assigned the same reference numerals and descriptions thereof will be omitted.
FIG. 7 shows the main part of the external thread member according to the embodiment of the present invention, (A) is a front view of the main part, (B) is a rear view of the main part showing the 180 ° opposite side of (A). is there.
The present embodiment is an example in which the tapered surface 52 is eliminated from the above embodiment, and the end edge 25a of the tip side of the cylindrical surface 25 on which the rising portion 22 of the screw is formed is the annular convex portion 40 and the opposite tip. Located on the side edge.
The end 25a on the axial tip side of the cylindrical surface 25 is a circle on a plane orthogonal to the central axis N1 of the screw, while the end 25b on the non-tip side is one turn from the end of the full thread 21 The spiral boundary with the root of the complete thread 21 of the. Therefore, assuming the end 21a of the complete thread 21 where the rising portion 22 has completely risen as a starting point, at the end 21a of the complete thread 21 of FIG. 7 (A) (right end of FIG. The gap between the end 25a on the tip end side and the end 25b on the non-tip end side is almost zero, and as shown in FIG. 7 (B), from the left end in FIG. Toward the right end, the edge 25b on the non-tip side inclines and extends in the lead angle direction of the complete screw thread 21, and the axial distance gradually increases with respect to the edge 25a on the tip side. As shown in FIG. 7 (A), the axial distance further increases toward the end 21a of the complete thread 21 and reaches a position one pitch away from the original base position.
Therefore, at the starting point, the cylindrical surface 25 is a helical cylindrical surface having an axial length of substantially zero and having a length corresponding to one pitch of the complete screw thread 21 in a round. The rising portion 22 gradually rises from the cylindrical surface 25 to the end 21a of the complete thread.
In the present embodiment, since there is no 0.5 pitch portion of the tapered surface 52 in the above embodiment, it can be shortened to 1.5 pitch at the minimum (L1 = L2 (one pitch) + L4 (full thread 21 Half (1/2 pitch (0.5 pitch)).
At that time, there is no valley portion 51, and the rising portion 22 of the male screw starts rising from the tip 22a located in the vicinity of the non-tip end of the non-tip side arc surface 41c of the annular convex portion 40. The diameter d5 of the cylindrical surface 25 is set to be equal to or greater than the valley diameter d1 of the complete screw thread 21 and equal to or less than the outer diameter d2 of the annular convex portion 40 (d2 ≧ d5 ≧ d1). In the illustrated example, the diameter d5 of the cylindrical surface 15 is the same as the valley diameter d1 of the complete screw thread 21.
The valley diameter d1 and the outer diameter d2 of the annular convex portion 40 are equal to or less than the lower limit value of the inner diameter D1 of the screw hole of the female screw member 100, and the diameter d5 of the cylindrical surface 25 is equal to or more than the valley diameter d1 of the complete screw thread 21 By setting the tolerance range to be a slight gap that does not affect the tightening, rattling can be suppressed to be small, and it is possible to smoothly correct the diagonal entry.
Although there is a difference in shape, as in the above embodiment, when the screw thread is M10 × 1.25, the inner diameter D1 of the female screw member 100 is 8.647 mm and the top of the annular convex portion 40 The outer diameter d2 of 41a is preferably set to about 8.65 ± 0 / −0.4 [mm]. That is, the tolerance range is set to within -5 to 8% of the lower limit value of the inner diameter of the female screw member 100.
図８は、図７の実施形態の変形例を示すもので、（Ａ）は要部正面図、（Ｂ）は（Ａ）の１８０°反対側を示す要部裏面図である。
図７の例は、円筒面２５の径ｄ５が完全ねじ山２１の谷径ｄ１と同一の例であったが（ｄ５＝ｄ１）、図８の変形例は、円筒面２５の径ｄ５が谷径ｄ１より大きくした例である（ｄ５＞ｄ１）。なお、この例では、円筒面２５の径ｄ５は、環状凸部４０の外径ｄ２より小さい（ｄ２＞ｄ５）。
図８でも、完全ねじ山２１の端部２１ａの頂部から、ねじ先の環状凸部４０の軸端面２６までの寸法Ｌ１は、図７と同じく１．５ピッチに設定している。
環状凸部４０の外径ｄ２は同じで、円筒面２５の外径ｄ５を、谷径ｄ１よりも大径としているので、その分だけ、図７に対して、円筒面２５の先端側の端縁２５ａの位置が、環状凸部４０の頂部４１ａ側に移動し、環状凸部４０の軸方向長さＬ２´が短くなっている。一方、完全ねじ山２１の端部２１ａの頂部から、ねじ先の環状凸部４０の軸端面２６までの寸法Ｌ１は変わらないので、完全ねじ山２１の端部２１ａの頂部から円筒面２５の先端側の端縁２５ａまでの長さＬ４´は、図７に対して長くなっている。
また、完全ねじ山２１の外径ｄは同じで、円筒面２５の外径ｄ５が大径となっているので、円筒面２５の反先端側の螺旋状の端縁２５ｂの位置は、一巻き目の完全ねじ山２１の頂部側に移動している。
したがって、円筒面２５の軸方向の長さは、周方向のどの位置においても、図７に比べて長くなっている。
すなわち、立ち上がり部が２２が完全に立ち上がった完全ねじ山２１の端部２１ａ位置を起点とすると、図８（Ａ）の完全ねじ山２１の端部２１ａ位置では（図８（Ａ）の右端、図８（Ｂ）の左端）、先端側の端縁２５ａと反先端側の端縁２５ｂは軸方向長さＬ４１´だけ離れており、図８（Ｂ）に示すように、図７と同様に、裏側に回ると、図中左端から右端に向かって、反先端側の端縁２５ｂが完全ねじ山２１のリード角方向に傾斜して延
び、先端側の端縁２５ａに対して軸方向の間隔が徐々に拡がっていき、さらに、図８（Ａ）に示すように、完全ねじ山２１の端部２１ａに向かって、さらに軸方向の間隔が拡大していき、元の起点の位相に到達するが、図７と相違して１ピッチよりも若干離れた位置となる。
起点位相に達した状態で、一巻き目の完全ねじ山と２巻き目の完全ねじ山の谷部が円筒面の径となっている軸方向の隙間が大きく、一巻き目と２巻き目の間の谷部分２７が、円筒面２５の径ｄ５から、徐々に小さくなって谷径ｄ１に移行している。
したがって、円筒面２５は、起点においては、軸方向の長さはほぼゼロで、一周して完全ねじ山２１の１ピッチ分の軸方向長さとなる螺旋状の円筒面である。立ち上がり部２２は、この円筒面２５から徐々に立ち上がって完全ねじ山の端部２１ａに至る。
また、円筒面２５の外径ｄ５が完全ねじ山の谷径ｄ１よりも大きいので、円筒面２５から完全ねじ山２１の頂部までの高さは、図７に対して低くなり、円筒面２５からの立ち上がり部２２の長さは、その分だけ短くなっている。
このように変形例のように構成すれば、図７に比べて、めねじとの間の隙間がより小さくなり、ガタツキが小さく抑えられ、斜め入りをスムースに矯正することができる。
なお、図８において、完全ねじ山２１の端部２１ａにおける円筒面２５の先端側の端縁２５ａと反先端側の端縁２５ｂとの軸方向長さＬ４１´を短くすることで、完全ねじ山２１の端部２１ａから環状凸部４０の軸端面２６までの軸方向長さＬ１をさらに短くすることが可能である。軸方向長さＬ４１´は、ゼロまで短くすることができる。
図９（Ａ）は、図７の円筒面２５の径ｄ５が谷径ｄ１と同一の場合（ｄ５＝ｄ１）、図９（Ｂ）は、図８の円筒面２５の径ｄ５が谷径ｄ１より大きい場合（ｄ５＞ｄ１）のめねじとの嵌合状態を、模式的に示している。
このように、締付に影響がない程度に、円筒面２５の径ｄ５を谷径ｄ１より大きくすれば、図９（Ｂ）に示すように、円筒面２５とめねじ１２１との隙間ｇをより小さくすることができ、ガタツキが小さく抑えられ、斜め入りをスムースに矯正することができる。
FIG. 8 shows a modification of the embodiment of FIG. 7, in which (A) is a front view of the main part, and (B) is a rear view of the main part showing the 180 ° opposite side of (A).
In the example of FIG. 7, the diameter d5 of the cylindrical surface 25 is the same as the valley diameter d1 of the complete thread 21 (d5 = d1), but in the modification of FIG. This is an example larger than the diameter d1 (d5> d1). In this example, the diameter d5 of the cylindrical surface 25 is smaller than the outer diameter d2 of the annular convex portion 40 (d2> d5).
In FIG. 8 as well, the dimension L1 from the top of the end 21a of the full thread 21 to the axial end face 26 of the annular convex portion 40 at the screw tip is set to 1.5 pitch as in FIG.
Since the outer diameter d2 of the annular convex portion 40 is the same, and the outer diameter d5 of the cylindrical surface 25 is larger than the valley diameter d1, the end on the tip side of the cylindrical surface 25 with respect to FIG. The position of the edge 25a moves toward the top 41a of the annular convex portion 40, and the axial length L2 'of the annular convex portion 40 is shortened. On the other hand, since the dimension L1 from the top of the end 21a of the complete thread 21 to the axial end face 26 of the annular convex portion 40 at the screw tip does not change, the tip of the cylindrical surface 25 from the top of the end 21a of the complete thread 21 The length L4 'to the side edge 25a is longer with respect to FIG.
Further, since the outer diameter d of the complete screw thread 21 is the same, and the outer diameter d5 of the cylindrical surface 25 is large, the position of the spiral edge 25b on the opposite tip side of the cylindrical surface 25 is one turn. It has moved to the top side of the full thread 21 of the eye.
Therefore, the axial length of the cylindrical surface 25 is longer than that in FIG. 7 at any position in the circumferential direction.
That is, starting from the end 21a position of the complete thread 21 where the rising portion 22 has completely risen, at the end 21a position of the complete thread 21 in FIG. 8 (A) (right end of FIG. 8B, the end edge 25a on the tip end side and the end edge 25b on the non-tip end side are separated by an axial length L41 ', and as shown in FIG. 8B, as in FIG. When turned to the back side, the end 25b on the non-tip end side inclines in the lead angle direction of the complete thread 21 from the left end to the right end in the drawing, and the axial distance with respect to the end end 25a Gradually expand, and further, as shown in FIG. 8A, the axial interval further expands toward the end 21 a of the complete thread 21 and reaches the original origin phase. However, unlike FIG. 7, the position is slightly away from one pitch.
When the starting phase is reached, there is a large axial gap in which the full thread of the first turn and the valley of the full thread of the second turn are the diameter of the cylindrical surface. The valley portion 27 between them gradually decreases from the diameter d5 of the cylindrical surface 25 and shifts to the valley diameter d1.
Therefore, at the starting point, the cylindrical surface 25 is a helical cylindrical surface having an axial length of substantially zero and having a length corresponding to one pitch of the complete screw thread 21 in a round. The rising portion 22 gradually rises from the cylindrical surface 25 to the end 21a of the complete thread.
Further, since the outer diameter d5 of the cylindrical surface 25 is larger than the valley diameter d1 of the complete thread, the height from the cylindrical surface 25 to the top of the complete thread 21 is lower than in FIG. The length of the rising portion 22 is shortened by that amount.
With such a configuration as in the modified example, the gap with the female screw is smaller than that in FIG. 7, the rattling can be suppressed to be small, and the diagonal entry can be smoothly corrected.
In FIG. 8, the axial length L 41 ′ of the end 25 a of the tip side of the cylindrical surface 25 and the end 25 b of the non-tip side at the end 21 a of the complete thread 21 is shortened to complete the complete thread. It is possible to further shorten the axial length L1 from the end 21a of the end 21 to the axial end face 26 of the annular convex portion 40. The axial length L41 'can be shortened to zero.
9A shows the case where the diameter d5 of the cylindrical surface 25 in FIG. 7 is the same as the valley diameter d1 (d5 = d1), FIG. 9B shows the diameter d5 of the cylindrical surface 25 in FIG. In the case of larger (d5> d1), the fitting state with the female screw is schematically shown.
Thus, if the diameter d5 of the cylindrical surface 25 is made larger than the valley diameter d1 to such an extent that tightening is not affected, as shown in FIG. 9B, the gap g between the cylindrical surface 25 and the female screw 121 is further increased. It can be made smaller, rattling can be kept small, and diagonal entry can be corrected smoothly.
図５は、本発明のさらに他の実施形態を示している。
この実施形態では、環状凸部４０の先端に、穴探り性向上を目的としたガイド６０を設けたものである。ガイド６０は、環状凸部４０の先端側円弧面４１ｂの端部から、軸方向先端側に向けて徐々に小径となるようにテーパー形状としたもので、先端面は直径ｄ４の円形の端面となっている。
図５（Ａ）乃至（Ｃ）は、ガイド６０の軸方向長さＬ５を変えたもので、（Ａ）の例は１ピッチ（１Ｐ）、（Ｂ）の例は２ピッチ（２Ｐ）、（Ｃ）の例は３ピッチ（３Ｐ）に設定されている。
また、ガイド６０の先端面のねじ先径ｄ４は、図５（Ｄ）に模式的に示すように、穴探り性を持たせるために、軸中心に対し、振り幅（２／３）ｄ（≒０．６７ｄ）程度まで許容できる範囲に設定される。振り幅（２／３）ｄの場合のｄ４は、（１／３）ｄであり、ねじ（ナット）の呼び径×３３．３％である。より好ましくは、ねじ（ナット）の呼び径×（３０％〜４５％）とする。４５％の場合の振り幅は０．５５ｄ、３０％の場合の振り幅は０．７ｄであり、３０％〜４５％では、振り幅は０．５５ｄ〜０．７ｄの範囲となる。図５（Ａ）〜（Ｃ）の例では、ｄ４は共に同一で、テーパー角度が相違している。図示例では、（Ａ）の例では１１５°、（Ｂ）の例では８０°、（Ｃ）の例では６０°に設定されている。
完全ねじ山２１の端部２１ａから谷部５１までの軸方向長さは１ピッチ（１Ｐ）、環状凸部４０の軸方向長さは１ピッチ（１Ｐ）に設定されており、完全ねじ山２１の端部２１ａから、ガイド６０の先端までの全体の長さＬ１は、（Ａ）の例では３ピッチ程度、（Ｂ）の例では４ピッチ程度、（Ｃ）の例では５ピッチ程度となる。
このようにガイド６０を設ければ、ねじ部材の中心軸線がねじ穴１２０の中心位置から多少ずれていても、ガイド６０の先端部が係合し、ねじ穴１２０に係合させることができ、挿入性を確保することができる。そして、環状凸部と環状凹部の作用によって、斜め入
りが防止され、作業性に優れたねじ部材を実現することができる。
なお、図５の例は、環状凸部と円筒面の間にテーパー面を有する構成を例示しているが、図７及び図８に示すように、テーパー面の無い構成についても適用可能である。
FIG. 5 shows still another embodiment of the present invention.
In this embodiment, a guide 60 for improving the hole searchability is provided at the tip of the annular convex portion 40. The guide 60 is tapered so that the diameter gradually decreases from the end of the tip side arc surface 41b of the annular convex portion 40 toward the tip end side in the axial direction, and the tip surface is a circular end face having a diameter d4 It has become.
5 (A) to 5 (C) are obtained by changing the axial length L5 of the guide 60. In the example of (A), one pitch (1P), and in the example of (B), two pitch (2P), The example of C) is set to 3 pitches (3P).
Further, as schematically shown in FIG. 5D, the screw tip diameter d4 of the tip end face of the guide 60 has a swing width (2/3) d (about 2/3) with respect to the axial center in order to provide hole searchability. It is set to an acceptable range up to about 0.67 d). In the case of the swing width (2/3) d, d4 is (1/3) d, and the nominal diameter of the screw (nut) × 33.3%. More preferably, the nominal diameter of the screw (nut) × (30% to 45%). The swing width in the case of 45% is 0.55 d, the swing width in the case of 30% is 0.7 d, and in the range of 30% to 45%, the swing width is in the range of 0.55 d to 0.7 d. In the example of FIGS. 5A to 5C, d4 is the same and the taper angles are different. In the illustrated example, the angle is set to 115 ° in the example of (A), 80 ° in the example of (B), and 60 ° in the example of (C).
The axial length of the complete screw thread 21 from the end 21a to the valley 51 is set to 1 pitch (1 P), and the axial length of the annular convex 40 is set to 1 pitch (1 P). The total length L1 from the end 21a of the head to the tip of the guide 60 is about 3 pitches in the example of (A), about 4 pitches in the example of (B), and about 5 pitches in the example of (C) .
By providing the guide 60 in this manner, even if the central axis of the screw member is slightly deviated from the central position of the screw hole 120, the tip of the guide 60 can be engaged and engaged with the screw hole 120. Insertability can be secured. And by the effect | action of an annular convex part and an annular recessed part, diagonal insertion is prevented and the screw member excellent in workability | operativity can be implement | achieved.
Although the example shown in FIG. 5 exemplifies a configuration having a tapered surface between the annular convex portion and the cylindrical surface, as shown in FIGS. 7 and 8, the configuration is also applicable to a configuration having no tapered surface. .
１ おねじ部材、
１０ 頭部
２０ 軸部
２１ 完全ねじ山、２１ａ 端部、２２ ねじの立ち上がり、２２ａ 先端
２５ 円筒面、２５ａ 端縁、２６ 軸端面
３０ ねじ先形状部
４０ 環状凸部、
４１ 外周面、
４１ａ 頂部、４１ｂ 先端側円弧面、４１ｃ 反先端側円弧面
５０ 環状凹部
５１ 谷部、５２ テーパー面
６０ ガイド
１００ めねじ部材
１２０ ねじ穴、１２１ ねじ山
Ｃ 仮想円、Ｃ１ 直径線、Ｏ 中心
Ｄ１ 内径（ねじ穴１２０の内径）
Ｍｃ モーメント（時計回り）、Ｍｃｃ モーメント（反時計回り）
Ｎ１ 中心軸線（軸部）、Ｎ２ 中心軸線（ねじ穴）
Ｒ 曲率半径（環状凸部）
ａ１、ａ２、ａ３、ａ５ 係合位置
ｄ 外径（完全ねじ山２１の外径）
ｄ１ 直径（完全ねじ山２１の谷径）
ｄ２ 外径（環状凸部４０の頂部４１ａの外径（最大径））
ｄ３ 直径（谷部の直径）
ｄ４ 直径（軸端面の直径）
ｄ５ 直径（円筒面２５の直径）
θ テーパー角度（テーパー面の角度）
1 Male thread member,
Reference Signs List 10 head 20 shaft portion 21 full thread, 21a end portion, 22 screw rising, 22a tip 25 cylindrical surface, 25a end edge, 26 axial end surface 30 screw tip shape portion 40 annular convex portion,
41 outer surface,
41a top, 41b tip side arc face 41c non-tip side arc face 50 annular recess 51 valley, 52 taper face 60 guide 100 female thread member 120 screw hole, 121 thread C virtual circle, C1 diameter line, O center D1 inner diameter (Inside diameter of screw hole 120)
Mc moment (clockwise), Mcc moment (counterclockwise)
N1 central axis (shaft), N2 central axis (screw hole)
R radius of curvature (annular convex)
a1, a2, a3, a5 engagement position d outside diameter (outside diameter of complete thread 21)
d1 diameter (valley diameter of full thread 21)
d2 Outer diameter (the outer diameter (maximum diameter) of the top 41a of the annular convex portion 40)
d3 diameter (diameter of valley)
d4 diameter (diameter of shaft end face)
d5 diameter (diameter of cylindrical surface 25)
θ taper angle (angle of tapered surface)
Claims (10)
前記完全ねじ山の前記軸部の先端側の端部にはねじの立ち上がり部が連続して設けられ、該ねじの立ち上がり部は前記完全ねじ山の谷径以上の円筒面から前記完全ねじ山に向けて徐々に立ち上がる構成となっており、
前記ねじ先形状は、外側に凸の円弧状に膨らんだ環状凸部を備え、
前記環状凸部の最大径が前記めねじの内径の寸法公差の下限値以下に設定され、
前記完全ねじ山の前記軸部の先端側の端部から前記環状凸部の先端側端部までの前記軸部の中心軸線方向の長さは、前記完全ねじ山の２ピッチ以内に設定されていることを特徴とするおねじ部材。 A male screw member having a screw tip shape which forms a complete screw thread screwed to a female screw of a mating member in the shaft portion and prevents oblique insertion at the tip end side of the shaft portion,
A rising portion of a screw is continuously provided at an end of the tip end side of the shaft portion of the full thread, and a rising portion of the screw is a cylindrical surface having a diameter equal to or larger than a valley diameter of the full thread. It is configured to gradually rise toward the
The screw tip shape includes an annular convex portion that bulges in a circular arc shape that is convex outward.
The maximum diameter of the annular convex portion is set to be equal to or less than the lower limit value of the dimensional tolerance of the inner diameter of the female screw,
The length in the central axis direction of the shaft from the end on the tip side of the shaft of the full thread to the end on the tip side of the annular convex portion is set within 2 pitches of the full thread externally threaded member, characterized in that there.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018077308A JP6510110B1 (en) | 2018-04-13 | 2018-04-13 | Male thread member |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018077308A JP6510110B1 (en) | 2018-04-13 | 2018-04-13 | Male thread member |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP6510110B1 true JP6510110B1 (en) | 2019-05-08 |
| JP2019183998A JP2019183998A (en) | 2019-10-24 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2018077308A Active JP6510110B1 (en) | 2018-04-13 | 2018-04-13 | Male thread member |
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Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01182613A (en) * | 1988-01-16 | 1989-07-20 | Toopura:Kk | Screw with pilot |
| JPH0547519U (en) * | 1991-11-29 | 1993-06-25 | 三菱マテリアル株式会社 | bolt |
| JP3739012B2 (en) * | 1996-04-26 | 2006-01-25 | 株式会社トープラ | Bolt with pilot |
| US6328515B1 (en) * | 1996-09-24 | 2001-12-11 | Textron Inc. | Fastener with anti-cross-threading point and method of assembly |
| US6158938A (en) * | 1998-03-11 | 2000-12-12 | Illinois Tool Works Inc | Anti-cross threading fastener |
| JP2000291616A (en) * | 1999-04-07 | 2000-10-20 | Nagoya Screw Mfg Co Ltd | Screw |
| JP2000329125A (en) * | 1999-05-17 | 2000-11-28 | Iwata Bolt Kk | Male screw |
| JP2001304221A (en) * | 2000-04-24 | 2001-10-31 | Nishio Seimitsu Kk | Automatically assembling bolt |
| JP3173041U (en) * | 2011-11-02 | 2012-01-19 | 株式会社音戸工作所 | Bolt with anti-seizure function |
| JP6382744B2 (en) * | 2015-02-23 | 2018-08-29 | 株式会社トープラ | Male thread member |
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2018
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| JP2019183998A (en) | 2019-10-24 |
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