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JP6239651B2 - Tapping screw - Google Patents

Tapping screw Download PDF

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JP6239651B2
JP6239651B2 JP2015554875A JP2015554875A JP6239651B2 JP 6239651 B2 JP6239651 B2 JP 6239651B2 JP 2015554875 A JP2015554875 A JP 2015554875A JP 2015554875 A JP2015554875 A JP 2015554875A JP 6239651 B2 JP6239651 B2 JP 6239651B2
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thread
screw
tapping screw
outer diameter
tapping
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JPWO2015098823A1 (en
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茂人 森
茂人 森
俊二 戸澤
俊二 戸澤
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Topura Co Ltd
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16BDEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B25/00Screws that cut thread in the body into which they are screwed, e.g. wood screws
    • F16B25/0036Screws that cut thread in the body into which they are screwed, e.g. wood screws characterised by geometric details of the screw
    • F16B25/0042Screws that cut thread in the body into which they are screwed, e.g. wood screws characterised by geometric details of the screw characterised by the geometry of the thread, the thread being a ridge wrapped around the shaft of the screw
    • F16B25/0052Screws that cut thread in the body into which they are screwed, e.g. wood screws characterised by geometric details of the screw characterised by the geometry of the thread, the thread being a ridge wrapped around the shaft of the screw the ridge having indentations, notches or the like in order to improve the cutting behaviour

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

Description

本発明は、相手材にめねじを成形しながら締結を行うタッピンねじに関し、特に、樹脂材から金属材まで、幅広い相手材に対して優れたねじ込み特性を有するタッピンねじに関する。   The present invention relates to a tapping screw that is fastened while forming a female thread on a mating material, and more particularly to a tapping screw that has excellent screwing characteristics for a wide range of mating materials from resin materials to metal materials.

従来から機械部品の組立てにはタッピンねじが用いられているが、近年、軽量化を目的として一部樹脂部品化された機械部品が増大しており、これらの組立作業においては、樹脂材用タッピンねじと金属材用タッピンねじを使い分ける必要があった。そのため、作業が煩雑なものとなり、樹脂材と鋼材の両方に共用できるような汎用性の高いタッピンねじの開発が要請されている。
樹脂材用タッピンねじと金属材用タッピンねじの間には種々の相違があるが、最も大きな相違は、樹脂材用タッピンねじは、空転トルクを高くできず、また、樹脂材特有のクリープ現象が発生して弛みやすいために、ねじ山に弛み止め用の凹部が設けられている点にある。
In the past, tapping screws have been used for assembling machine parts, but in recent years, machine parts that have been partially made into resin parts for the purpose of weight reduction have increased. In these assembling operations, tapping pins for resin materials have been used. It was necessary to use different screws and metal tapping screws. For this reason, the work becomes complicated, and there is a demand for the development of a highly versatile tapping screw that can be shared by both resin and steel.
There are various differences between the tapping screw for resin materials and the tapping screw for metal materials, but the biggest difference is that the tapping screw for resin materials cannot increase the idling torque, and the creep phenomenon peculiar to resin materials does not occur. In order to generate and loosen easily, the thread is provided with a recess for preventing loosening.

従来の弛み止め用の凹部としては、たとえば、特許文献1に記載のように、ねじ山の頂部に、凹部となる溝をつる巻き方向に複数設け、締め付け力が低下しても、溝に樹脂材が引っ掛かるようにして、弛み止めが図られていた。
しかし、このような樹脂用タッピンねじを、鋼板等の締め付けに用いようとすると、凹部が大きな抵抗となって、ねじ込みトルクが大きくなってしまう。また、ねじ山の受圧面積が小さくなるために、高い締め付け力に耐えられず、低いトルクでねじ山破壊が発生してしまうといった問題も生じる。
As a conventional recess for preventing slack, for example, as described in Patent Document 1, a plurality of grooves serving as recesses are provided at the top of a thread in the winding direction, and even if the tightening force is reduced, a resin is provided in the groove. The material was hooked to prevent loosening.
However, when such a resin tapping screw is used for fastening a steel plate or the like, the concave portion becomes a large resistance, and the screwing torque increases. In addition, since the pressure receiving area of the screw thread becomes small, there is a problem that the screw thread cannot be broken with a low torque because it cannot withstand a high tightening force.

特開平7−139536号公報JP-A-7-139536

本発明は、上記した従来技術の問題点を解決するためになされたもので、その目的とするところは、樹脂材から金属材まで幅広い相手材に対して十分な締結強度をとることができ、しかもゆるみ止めを図り得るタッピンねじを提供することにある。   The present invention was made in order to solve the above-described problems of the prior art, and the object of the present invention is to take sufficient fastening strength for a wide range of counterpart materials from resin materials to metal materials, Furthermore, it is to provide a tapping screw that can prevent loosening.

上記目的を達成するために、本発明は、相手材に塑性変形によりめねじを成形しながら締結を行うタッピンねじにおいて、
少なくとも相手材との嵌合部におけるねじ山の圧力側フランク面に、ねじ山の山頂部の外径は円筒螺旋形状を連続して保った状態で、ねじ径の円周方向に対して局部的に凹部を複数設け、
前記凹部は、前記ねじ軸の中心軸線方向から見ると扇形に切り欠かれた形状で、山頂部側からねじ山付け根側に向かって徐々に深くなるような断面形状を有し、
前記扇形の凹部の外径端は、前記山頂部よりも谷部側にずらした状態でねじ山の外径に沿っており、前記扇形の凹部の内径は、前記山頂部部とねじ山付け根との中途部に位置し、
前記ねじ山の圧力側フランク角が遊び側フランク角より小さいことを特徴とする。
In order to achieve the above object, the present invention provides a tapping screw that performs fastening while forming a female screw by plastic deformation in a counterpart material.
At least on the pressure side flank surface of the thread in the mating part with the mating member, the outer diameter of the thread crest is kept in a cylindrical spiral shape and is localized in the circumferential direction of the thread diameter. Provided with a plurality of recesses,
The concave portion has a cross-sectional shape that gradually becomes deeper from the peak top side toward the screw root side, in a shape cut out in a fan shape when viewed from the central axis direction of the screw shaft,
The outer diameter end of the fan-shaped recess is along the outer diameter of the screw thread in a state shifted from the peak to the valley side, and the inner diameter of the fan-shaped recess is the sum of the peak and the screw root. Located in the middle of
The pressure side flank angle of the thread is smaller than the play side flank angle .

凹部の外径端は、ねじ山の山頂部よりも、ねじ山高さの0.1倍程度谷部側にずらしていることが好適である。
凹部の底面のねじ軸の中心軸線Nを通る面で切断した断面形状は、締め付け方向に回転させた場合に、回転方向後方に当る端縁がねじ山の圧力側フランク面と一致しており、締め付け方向前方に向かって、付け根側が徐々に深く切り込まれるように傾斜させてもよい。
凹部を遊び側フランク面にも設けることができる。
また、ねじ外径は、ねじの呼び寸法に対して小さい方向に公差範囲があることが好適である。
また、ねじ山の山角度は40°〜45°で、圧力側フランク角が遊び側フランク角より小さいことが好適である。
また、ねじピッチが、呼び径の0.27〜0.33倍とすることが好適である。
さらに、ねじ山高さを呼び径の、0.14〜0.16倍としてもよい。
It is preferable that the outer diameter end of the recess is shifted to the valley side by about 0.1 times the thread height from the top of the thread.
The cross-sectional shape cut by the plane passing through the central axis N of the screw shaft on the bottom surface of the recess has an edge that hits the rear in the rotational direction when rotated in the tightening direction, and matches the pressure side flank surface of the thread. You may make it incline so that the base side may be cut deeply gradually toward the front of a fastening direction.
A recess can also be provided on the play-side flank surface.
Further, it is preferable that the screw outer diameter has a tolerance range in a direction smaller than the nominal size of the screw.
Further, it is preferable that the thread angle is 40 ° to 45 ° and the pressure side flank angle is smaller than the play side flank angle.
The screw pitch is preferably 0.27 to 0.33 times the nominal diameter.
Furthermore, the thread height may be 0.14 to 0.16 times the nominal diameter.

本発明は、ねじ山の山頂部が溝等によって不連続となることなく、同一径で連続して螺旋状に形成されているので、ねじ山は相手材に連続的に食い込んで、ねじ込み時の抵抗が軽減され、ねじ込みトルクを低くできる。
また、ねじ山の山頂部に溝等の切欠きが無いので、高い締め付け力を必要とする鋼板等の金属材に対して、強く締め付けることが可能となり、空転トルクを大きくできる。一方、圧力側フランク面に凹部があるので、樹脂材に対する耐ゆるみ性についても確保することができる。
したがって、空転トルクの小さい樹脂材から大きい金属材まで、ねじ込みトルクと耐ゆるみ性において、従来製品よりも優れた特性をもつ。
In the present invention, since the crest of the screw thread is formed continuously and spirally with the same diameter without being discontinuous by a groove or the like, the screw thread continuously bites into the counterpart material, Resistance is reduced and screwing torque can be reduced.
Further, since there is no notch such as a groove at the top of the thread, it is possible to strongly tighten against a metal material such as a steel plate that requires a high tightening force, and the idling torque can be increased. On the other hand, since there is a recess in the pressure side flank surface, it is possible to ensure the loosening resistance against the resin material.
Therefore, from resin materials with low idling torque to large metal materials, it has better characteristics than conventional products in screwing torque and loosening resistance.

また、凹部が、山頂部側からねじ山付け根に向かって徐々に深くなるような断面形状を有していれば、山頂部側の受圧面積を大きくとることができ、耐ゆるみ性についても確保することができる。
凹部の底面を、回転方向後方に当る端縁がねじ山の圧力側フランク面と一致させておけば、締め付け方向前方に向かって抵抗は小さくなり、ねじ込みトルクは小さい。一方、弛み側の回転については、弛み方向の回転方向に対して後方部分が深くなっているので、抵抗が大きくなり、弛み止めを図ることができる。
凹部を圧力側フランク面と遊び側フランク面の両方に設ければ、めねじ成形時のねじ込みトルクをより小さくすることができる。
また、ねじ外径が、ねじの呼び寸法に対して小さい方向に公差範囲を持っているので、鋼板等の金属材に使用する場合、谷部との干渉を回避でき、小径孔でも締め付けが可能となって、下穴の孔径の許容範囲を広くできる。一方、従来の樹脂材用タッピンねじと比較すると、呼び径に対して小さい方向の公差を有するので、ねじ込みトルクが小さく、作業性に優れる。
In addition, if the recess has a cross-sectional shape that gradually deepens from the peak side toward the screw root, the pressure receiving area on the peak side can be increased, and the looseness resistance is also ensured. be able to.
If the bottom edge of the concave portion is matched with the pressure side flank surface of the screw thread at the edge that contacts the rear side in the rotation direction, the resistance decreases toward the front in the tightening direction and the screwing torque is small. On the other hand, with respect to the rotation on the slack side, since the rear portion is deeper than the rotation direction in the slack direction, the resistance is increased and the slack can be prevented.
If the concave portions are provided on both the pressure side flank surface and the play side flank surface, the screwing torque at the time of female screw molding can be further reduced.
In addition, since the outer diameter of the screw has a tolerance range in a direction smaller than the nominal size of the screw, when used for metal materials such as steel plates, interference with valleys can be avoided, and tightening with small diameter holes is also possible. Thus, the allowable range of the hole diameter of the pilot hole can be widened. On the other hand, since it has a tolerance in a small direction with respect to the nominal diameter as compared with the conventional resin material tapping screw, the screwing torque is small and the workability is excellent.

また、ねじ山の山角度を40°〜45°とし、圧力側フランク角を遊び側フランク角より小さい非対称形状としておけば、鋼板に対する特性として、ねじ山の強度を確保でき、樹脂材に対する特性として、樹脂の白化、割れを防止できる。
また、ねじピッチを、呼び径(d)の0.27〜0.33倍としておけば、従来の鋼板用ねじとの対比では、空転トルク、保持力大を大きくでき、一方、従来の樹脂用ねじとの対比では、ピッチが小さいので、空転トルクを大きくできる。
さらに、ねじ山高さを呼び径の、0.14〜0.16倍としておけば、ピッチと相俟って、空転トルク、保持力をさらに大きくできる。
Also, if the thread angle is 40 ° to 45 ° and the pressure side flank angle is an asymmetrical shape smaller than the play side flank angle, the strength of the thread can be secured as a characteristic for the steel sheet, and the characteristic for the resin material Resin whitening and cracking can be prevented.
In addition, if the screw pitch is set to 0.27 to 0.33 times the nominal diameter (d), the idling torque and the holding force can be increased in comparison with the conventional steel plate screw, while the conventional resin is used. In contrast to the screw, since the pitch is small, the idling torque can be increased.
Furthermore, if the thread height is set to 0.14 to 0.16 times the nominal diameter, the idling torque and the holding force can be further increased in combination with the pitch.

図1は本発明の実施の形態に係るタッピンねじを示すもので、(A)は斜視図、(B)は凹部を軸方向から見た図である。1A and 1B show a tapping screw according to an embodiment of the present invention, in which FIG. 1A is a perspective view and FIG. 1B is a view of a recess viewed from an axial direction. 図2(A)は図1のタッピンねじのねじ部の部分拡大側面図、(B)はねじ山の拡大図である。2A is a partially enlarged side view of the thread portion of the tapping screw of FIG. 1, and FIG. 2B is an enlarged view of the thread. 図3は本発明の他の実施の形態に係るタッピンねじを示す部分斜視図である。FIG. 3 is a partial perspective view showing a tapping screw according to another embodiment of the present invention. 図4は本発明のさらに他の実施の形態に係るタッピンねじを示すもので、(A)は斜視図、(B)は凹部の部分拡大図である。4A and 4B show a tapping screw according to still another embodiment of the present invention, in which FIG. 4A is a perspective view and FIG. 4B is a partially enlarged view of a recess.

以下に、本発明を実施するための形態を、図面を参照して詳細に説明する。
図1は本発明の実施の形態に係るタッピンねじを示している。図において、1はタッピンねじ全体を示すもので、ねじ山3が形成されたねじ軸5と、ねじ頭部7とを備えている。ねじ山3は、ねじ軸5の先端側の軸方向所定長さの領域である先端ねじ部5Aにおいて、先端側からねじ頭部7に向けて徐々にねじ山高さが高くなり、一定のねじ山高さの平行ねじ部5Bに連続的に移行している。ねじ込んだ際には、平行ねじ部5Bが、相手材に形成される めねじと嵌合する。
この平行ねじ部5Bにおけるねじ山3の圧力側フランク面31に、ねじ山の山頂部33の外径が連続するつる巻き形状である円筒螺旋形状を保った状態で、ねじ径の円周方向に対して局部的に凹部9が複数設けられている。この凹部9は、この実施の形態では、平行ねじ部5Bの全体に設けられているが、少なくとも相手材との嵌合部に設けられていればよい。
EMBODIMENT OF THE INVENTION Below, the form for implementing this invention is demonstrated in detail with reference to drawings.
FIG. 1 shows a tapping screw according to an embodiment of the present invention. In the figure, reference numeral 1 denotes the entire tapping screw, which includes a screw shaft 5 on which a thread 3 is formed and a screw head 7. The thread 3 gradually increases in height from the distal end side toward the screw head 7 in the distal end thread portion 5A, which is a region of a predetermined axial length on the distal end side of the screw shaft 5, and the constant thread height is increased. It has shifted continuously to the parallel thread portion 5B. When screwed, the parallel thread portion 5B is fitted with a female screw formed on the mating member.
The pressure side flank surface 31 of the screw thread 3 in the parallel screw part 5B maintains a cylindrical spiral shape, which is a spiral shape in which the outer diameter of the screw peak part 33 is continuous, in the circumferential direction of the screw diameter. On the other hand, a plurality of recesses 9 are provided locally. In this embodiment, the concave portion 9 is provided in the entire parallel screw portion 5B, but it is sufficient that the concave portion 9 is provided at least in the fitting portion with the counterpart material.

凹部9は、ねじ軸5の中心軸線を中心として、ねじ山3のつる巻き方向に、所定の間隔で複数設けられている。この例では、凹部9は、図1(B)に示すように、90°の周期で形成され、ねじ山一巻き毎に4個形成されている。
この凹部9は、圧力側フランク面31を山頂部33側から根元側(谷部側)に向かって徐々に深くなるように切り欠いた形状で、ねじ軸5の中心軸線方向から見ると扇形に切り欠かれている。扇形の外径はねじ山の外径に沿っており、内径がねじ山の中途部に、ねじ山の山頂部と同心円上の円弧形状であり、扇形の両端縁91,93は、ねじ軸5の中心軸線から放射状に直線的に延びている。
凹部9の外径端は、図示例では、ねじ山の山頂部33であるが、山頂部33よりも0.1H(Hはねじ山高さ)程度谷部側に存在するようにずらしておくことが好ましい。
A plurality of recesses 9 are provided at predetermined intervals in the direction in which the screw thread 3 is wound around the central axis of the screw shaft 5. In this example, as shown in FIG. 1B, the recesses 9 are formed at a period of 90 °, and four recesses 9 are formed for each turn of the thread.
The concave portion 9 has a shape in which the pressure-side flank surface 31 is cut away so as to gradually become deeper from the peak portion 33 side toward the root side (valley portion side). It is cut out. The outer diameter of the sector is along the outer diameter of the screw thread, the inner diameter is a circular arc shape concentrically with the peak of the screw thread in the middle of the screw thread, and both end edges 91 and 93 of the fan shape are screw shafts 5. Extends linearly from the central axis of the.
In the illustrated example, the outer diameter end of the concave portion 9 is the crest portion 33 of the screw thread, but it is shifted so as to be present on the trough side by about 0.1 H (H is the height of the screw thread) from the crest portion 33. Is preferred.

また、凹部9の底面92については、中心軸線Nを通る面で切断した断面形状が、中心軸線N回りのどの位相角でも同一形状、同一深さに形成されている。この例では、ねじ軸5の中心軸線を通る面で切断した断面形状は、図2に示すように、断面三角形状に切り欠いた形状で、この断面形状は、らせん方向の両端縁91,93、及び根元側の内側縁94は、圧力側フランク面31との間に段差部が形成されている。   Further, regarding the bottom surface 92 of the recess 9, the cross-sectional shape cut along the plane passing through the central axis N is formed in the same shape and the same depth at any phase angle around the central axis N. In this example, the cross-sectional shape cut by a plane passing through the central axis of the screw shaft 5 is a shape cut out in a triangular shape as shown in FIG. 2, and this cross-sectional shape has both end edges 91 and 93 in the spiral direction. A step portion is formed between the inner edge 94 on the root side and the pressure side flank surface 31.

ねじ山3は、図2(B)に示すように、ねじ軸5の中心軸線Nと直交し山頂部33の中央を通る山中心線Gに対して、圧力側フランク角αが遊び側フランク角βより小さくなるような非対称山角となっている。圧力側フランク角αと遊び側フランク角βの比率(α:β)は、2:8〜3:7とすることが好適である。   As shown in FIG. 2 (B), the screw thread 3 has a pressure-side flank angle α that is perpendicular to the center axis N of the screw shaft 5 and passes through the center of the peak portion 33. The asymmetrical angle is smaller than β. The ratio (α: β) between the pressure side flank angle α and the play side flank angle β is preferably set to 2: 8 to 3: 7.

ねじ山3の山角度は40〜45°、遊び側フランク角βは30°程度に設定し、圧力側フランク角αを8°〜18°程度に設定することが好ましい。
ピッチpは、呼び径dの0.25〜0.29倍とすることが好適である。
さらに、ねじ山高さHは、呼び径dの、0.14〜0.16倍とすることが好適である。
また、ねじの外径については、呼び寸法に対して小さい方向に公差範囲δが設定されている。
The thread angle of the screw thread 3 is preferably set to 40 to 45 °, the play side flank angle β is set to about 30 °, and the pressure side flank angle α is preferably set to about 8 ° to 18 °.
The pitch p is preferably 0.25 to 0.29 times the nominal diameter d.
Furthermore, the thread height H is preferably 0.14 to 0.16 times the nominal diameter d.
Further, regarding the outer diameter of the screw, a tolerance range δ is set in a direction smaller than the nominal dimension.

本発明のタッピンねじは、相手材にめねじを成形しながら締結を行うものである。本実施の形態では、ねじ山3の山頂部33の外径が溝等によって不連続となることなく、同一径で連続して螺旋状に形成されているので、ねじ山3は相手材に連続的に食い込んで、ねじ込み時の抵抗が軽減され、ねじ込みトルクを低くできる。
また、ねじ山3の山頂部33に溝等の切欠きが無いので、高い締め付け力を必要とする鋼板等の金属材に対して、強く締め付けることが可能となり、空転トルクを大きくできる。一方、圧力側フランク面31に凹部9があるので、締め付け力を弱くしても、圧力側フランク面に設けられた凹部9に樹脂材が食い込んでおり、クリープなどによって軸力が低下しても、凹部9で引っ掛かり、弛みを防止することができる。
したがって、空転トルクの小さい樹脂材から大きい金属材まで、ねじ込みトルクと耐ゆるみ性において、従来製品よりも優れた特性を有する。
The tapping screw of the present invention is to be fastened while forming a female screw on the mating member. In the present embodiment, the outer diameter of the crest portion 33 of the screw thread 3 is formed continuously and spirally with the same diameter without being discontinuous by a groove or the like. The resistance during screwing is reduced and the screwing torque can be lowered.
Further, since there is no notch such as a groove in the crest portion 33 of the screw thread 3, it is possible to strongly tighten against a metal material such as a steel plate that requires a high tightening force, and the idling torque can be increased. On the other hand, since the pressure side flank surface 31 has the concave portion 9, even if the tightening force is weakened, the resin material bites into the concave portion 9 provided on the pressure side flank surface, and the axial force is reduced due to creep or the like. It is possible to prevent the slack from being caught by the recess 9.
Therefore, from resin materials having low idling torque to large metal materials, the screwing torque and loosening resistance are superior to those of conventional products.

また、凹部9については、山頂部33側からねじ山付け根側に向かって徐々に深くなるような断面形状を有しているので、山頂部33側の受圧面積を確保することができる。
また、ねじ外径が、ねじの呼び寸法に対して小さい方向に公差範囲δを持っているので、鋼板等の金属材に使用する場合、谷部との干渉を回避でき、小径孔でも締め付けが可能となって、下穴の孔径の許容範囲を広くできる。一方、従来の樹脂材用タッピンねじと比較すると、呼び径に対して小さい方向の公差を有するので、ねじ込みトルクが小さく、作業性に優れる。
Moreover, since the concave portion 9 has a cross-sectional shape that gradually becomes deeper from the peak portion 33 side toward the screw root side, the pressure receiving area on the peak portion 33 side can be ensured.
In addition, since the outer diameter of the screw has a tolerance range δ in a direction smaller than the nominal size of the screw, when used for metal materials such as steel plates, interference with valleys can be avoided, and tightening is possible even with small diameter holes. It becomes possible, and the tolerance | permissible_range of the hole diameter of a pilot hole can be widened. On the other hand, since it has a tolerance in a small direction with respect to the nominal diameter as compared with the conventional resin material tapping screw, the screwing torque is small and the workability is excellent.

すなわち、高い締め付け力を必要とする鋼板等の金属材に対して、強く締め付けることが可能となり、空転トルクを大きくできる。一方で、樹脂材に対しては、凹部9の存在によって、弛み止めを図ることができ、ねじ込みトルクと耐ゆるみ性において、従来製品よりも優れた特性をもつ。   That is, it is possible to strongly tighten a metal material such as a steel plate that requires a high tightening force, and the idling torque can be increased. On the other hand, the resin material can be prevented from loosening due to the presence of the recess 9, and has superior characteristics to conventional products in terms of screwing torque and loosening resistance.

さらに、本実施の形態にあっては、ねじ山角度(ねじ山の山角度)θ、ねじ山高さH,ピッチpについて、鋼板用と樹脂材の両方に共用できるように、好適な範囲を選択している。
鋼板用のタッピンねじは、ねじ山角度は60°のものが多く、ねじ山高さも外径比で0.11〜0.15の範囲にある。ねじピッチは、メートルねじと同様のピッチを持つJIS規格の2種とそれ以外では、外径比で0.35〜0.42の範囲となっている。
また、ねじ山高さとピッチの比率では、メートルねじと同等ピッチのJIS規格の3種で、0.65〜0.66、それ以外では、0.31〜0.43となるようなねじ部形状を持ち、幅広く板厚や穴形状等を使い分けられている。
Furthermore, in this embodiment, a suitable range is selected so that the thread angle (thread angle) θ, the thread height H, and the pitch p can be shared by both the steel plate and the resin material. doing.
Many tapping pins for steel plates have a thread angle of 60 °, and the thread height is in the range of 0.11 to 0.15 in terms of the outer diameter ratio. The screw pitch is in the range of 0.35 to 0.42 in terms of the outer diameter ratio in two types of JIS standards having the same pitch as the metric screw and in other cases.
In addition, in the ratio of the thread height to the pitch, there are three types of JIS standards with the same pitch as the metric thread, and the thread shape is 0.65 to 0.66, otherwise 0.31 to 0.43. It has a wide range of thicknesses and hole shapes.

一方、樹脂専用のタッピンねじは、ねじ山角度θが45°以下のものが多く、ねじ山高さも外径比で0.16〜0.21の範囲となるものが多く、ねじピッチは、外径比で0.35〜0.45の範囲となっている。ねじ山高さとピッチの比率では、0.390〜0.50となるようなねじ部形状を持ち、ねじ部にはゆるみ止め機能を持たせるために、ねじ山の外径を切り欠くようにねじ山頂部に溝等の凹み部を持ったものが多い。
また、樹脂専用のタッピンねじの特徴として、ねじの呼び径に対する外径公差範囲が呼び径を基準寸法としてプラス側に位置している。さらに、ねじ山高さが鋼板用タッピンねじよりも高いため、同じ呼び径で比較すると、谷部の径が小さい値となっている。
On the other hand, many tapping screws dedicated to resin have a thread angle θ of 45 ° or less, and many thread heights are in the range of 0.16 to 0.21 in terms of the outer diameter ratio. The ratio is in the range of 0.35 to 0.45. The thread height is such that the thread height is 0.390 to 0.50 in terms of the ratio between the thread height and the pitch, and in order to provide the screw with a function to prevent loosening, the outer diameter of the thread is notched. Many of them have grooves or other indentations.
Further, as a feature of the resin-dedicated tapping screw, the outer diameter tolerance range with respect to the nominal diameter of the screw is located on the plus side with the nominal diameter as a reference dimension. Furthermore, since the thread height is higher than that of the steel plate tapping screw, the diameter of the trough is small when compared with the same nominal diameter.

上記した従来の鋼板用タッピンねじを樹脂部材に適用すると、以下のような問題があるため、樹脂部材への締め付けには使用されていない。
i)ねじ込み時、ねじ山成形時に樹脂材を大きく変形させるため、樹脂の割れや白化といった現象が多発する。
ii)鋼材に比べて樹脂材の強度は低く、めねじ破壊トルク(空転トルク)が低くなるため、めねじのボス形状として、嵌合長さを増加させ、めねじ強度を確保する必要がある。
この樹脂ボスの内径部は、射出成型時に金型から樹脂部材が分離しやすいようテーパーが付いており、このテーパーが影響してねじ込み時にねじ先端部の内径が非常に小さくなるため、ねじ谷底部と干渉してねじ込みトルクが非常に高くなってしまい、極端な場合着座しない現象も発生する。
iii)高温時における樹脂材特有のクリープ現象によりゆるみが発生する。高温にならなくても、鋼材に比べると戻しトルク比が低く、弛みやすい。
When the above-mentioned conventional steel plate tapping screw is applied to a resin member, it has the following problems and is not used for fastening to the resin member.
i) Since the resin material is greatly deformed at the time of screwing and thread forming, phenomena such as resin cracking and whitening frequently occur.
ii) Since the strength of the resin material is lower than that of the steel material and the internal thread breaking torque (idling torque) is low, it is necessary to increase the fitting length and ensure the internal thread strength as the boss shape of the internal thread. .
The inner diameter part of this resin boss is tapered so that the resin member can be easily separated from the mold during injection molding, and this taper affects the inner diameter of the screw tip when screwing. And the screwing torque becomes very high, and in the extreme case, the phenomenon of not sitting occurs.
iii) Looseness occurs due to a creep phenomenon peculiar to a resin material at a high temperature. Even if the temperature is not high, the return torque ratio is low compared to steel, and it is easy to loosen.

一方、従来の樹脂用タッピンねじを鋼板に適用すると、以下のような問題があるため、鋼板部材への締め付けには使用されていない。
i)ピッチが大きいため、薄板鋼板への締め付けに関して、十分なめねじ強度が確保できず、めねじ破壊トルク(空転トルク)が低く、保持力も低い値となる。
ii)樹脂ボス対応のためにねじ長さが長くなり、鋼板に適用した場合、ねじ先端側の周辺部材との干渉が生じる。
iii)ねじ部に切欠き部のあるものが多く、ねじ山高さも小さいため、鋼板の高い締め付け力に耐えられず、低いトルクでねじ山破壊が発生する。
iv)谷径が小さいため、厚板ねじ込み時にねじり破断が発生する。
v)鋼板用のねじと比較すると、外径が大きいため、同じ下穴条件では、ねじ込みトルクが高くなる。
以上のことから、鋼材と樹脂材をねじ込み材としたタッピンねじはそれぞれの材質毎で異なるねじ部形状をもったタッピンねじを使用する必要があった。
On the other hand, when the conventional resin tapping screw is applied to a steel plate, it has the following problems and is not used for fastening to a steel plate member.
i) Since the pitch is large, sufficient internal thread strength cannot be ensured for tightening to a thin steel plate, the internal thread breaking torque (idling torque) is low, and the holding force is also low.
ii) The length of the screw becomes long to cope with the resin boss, and when applied to a steel plate, interference with peripheral members on the screw tip side occurs.
iii) Many of the threaded portions have notches and the thread height is small, so that the steel sheet cannot withstand the high tightening force of the steel sheet, and the thread breakage occurs with a low torque.
iv) Since the valley diameter is small, torsional breakage occurs when a thick plate is screwed.
v) Since the outer diameter is large compared to the steel plate screw, the screwing torque is increased under the same pilot hole conditions.
From the above, it has been necessary to use a tapping screw having a screw part shape that is different for each material as a tapping screw using a steel material and a resin material as a screwing material.

これに対して、本発明のタッピンねじにおいて、ねじ山角度θ、ねじ山高さH、ピッチpについて、上記のような範囲に設定すれば、従来の鋼材用のタッピンねじ(JIS規格)及び樹脂用のタッピンねじと比較して次のような効果がある。
ねじ山角度θについて
ねじ山角度θは40〜45°で、樹脂用のタッピンねじと同程度に設定しているので、樹脂に対する食い込み量は従来と同様であり、樹脂材に対して白化、割れ等を防止できる。
一方、ねじ山3は、圧力側フランク角αが遊び側フランク角βより小さく非対称となっており、特に遊び側のフランク角は30°程度となるので、従来の鋼板用のタッピンねじと同程度の角度があるので、鋼材用として利用した場合でも、遊び側フランク面側の強度は高く、ねじ山が潰れることなく、鋼材を塑性変形させることができる。
On the other hand, in the tapping screw of the present invention, if the thread angle θ, the thread height H, and the pitch p are set in the above ranges, the conventional tapping screw for steel (JIS standard) and resin Compared with the tapping screw, there are the following effects.
About the thread angle θ The thread angle θ is 40 to 45 °, which is set to the same level as the tapping screw for resin. The amount of biting into the resin is the same as before, and the resin material is whitened and cracked. Etc. can be prevented.
On the other hand, the screw thread 3 has a pressure side flank angle α smaller than the play side flank angle β and is asymmetric, and in particular, the play side flank angle is about 30 °, which is about the same as a conventional steel plate tapping screw. Therefore, even when it is used for a steel material, the play side flank surface side has a high strength, and the steel material can be plastically deformed without crushing the threads.

ねじ山高さHについて
本実施の形態では、ねじ山高さHを呼び径dの、0.14〜0.16倍としており、JIS規格タッピンねじの0.11〜0.15と樹脂用のタッピンねじの0.16〜0.21の中間程度に設定されている。
JIS規格タッピンねじよりねじ山高さHが高いので、谷部に干渉して焼きつきが発生するレベルの小さい穴径に対しても、ねじ込みが可能であり、適用できる穴径の許容範囲が大きい。特に、ねじ外径を、呼び寸法に対して小さい方向に公差範囲を設定しているので、より干渉しにくい構造となっている。
Thread height H In this embodiment, the thread height H is 0.14 to 0.16 times the nominal diameter d, and JIS standard tapping screws 0.11 to 0.15 and a tapping screw for resin Of 0.16 to 0.21.
Since the screw thread height H is higher than that of the JIS standard tapping screw, it can be screwed in even with a small hole diameter that interferes with the valley and generates seizure, and the allowable range of the applicable hole diameter is large. In particular, since the tolerance range is set in a direction in which the outer diameter of the screw is smaller than the nominal dimension, the structure is less likely to interfere.

ピッチpについての特性
また、呼び径(d)に対するねじピッチ(p)の比率(p/d)を、0.27〜0.33倍とし、JIS規格の1種、2種、4種のピッチの比率(0.31〜0.43)より小さく設定しているので、空転トルク、保持力が高く、特に薄板に対して係合するねじ山の数が多くなり、従来に比べて薄板に対して有利である。
また、JIS規格の3種のタッピンねじよりもピッチの比率が大きいため、ねじ込みトルクが3種よりも低く、3種よりも適用下穴の範囲が広く汎用性がある。
なお、ねじ山角度θ、ねじ山高さH,ピッチpについては、これらの範囲に限定されるものではなく、相手材に応じて適切な範囲を選択することができることはもちろんである。
Characteristics of Pitch p Also, the ratio (p / d) of the screw pitch (p) to the nominal diameter (d) is 0.27 to 0.33 times, and the pitch of 1 type, 2 types or 4 types of JIS standards. The ratio is set to be smaller than the ratio (0.31 to 0.43), so that the idling torque and holding force are high, especially the number of threads that engage with the thin plate increases, and compared with the conventional thin plate It is advantageous.
Further, since the pitch ratio is larger than the three types of JIS standard tapping screws, the screwing torque is lower than the third type, and the range of the prepared pilot holes is wider than the third type and is versatile.
Note that the thread angle θ, the thread height H, and the pitch p are not limited to these ranges, and it is a matter of course that an appropriate range can be selected according to the mating material.

他の実施の形態
図3には、本発明の他の実施の形態が示されている。
上記実施の形態では、凹部9が圧力側フランク面31のみに設けられているが、この実施の形態では、圧力側フランク面31のみでなく、圧力側フランク面31と遊び側フランク面32の両方に設けられている。このように、凹部9を遊び側フランク面32にも設ければ、めねじ成形時のねじ込みトルクをより小さくすることができる。
Other Embodiments FIG. 3 shows another embodiment of the present invention.
In the above embodiment, the concave portion 9 is provided only on the pressure side flank surface 31, but in this embodiment, not only the pressure side flank surface 31 but also both the pressure side flank surface 31 and the play side flank surface 32. Is provided. Thus, if the recessed part 9 is provided also in the play side flank surface 32, the screwing torque at the time of internal thread shaping | molding can be made smaller.

また、図4には、本発明のさらに他の実施の形態が示されている。
上記実施の形態では、凹部9の扇形の底面92をねじ軸の中心軸線Nを通る面で切断した断面形状が、中心軸線Nまわりのどの位相角でも同一深さで同一形状となっているが、この実施の形態では、扇形の凹部29の底面292のねじ軸の中心軸線Nを通る面で切断した断面形状が、締め付け方向、すなわち、図中、ねじ軸5の先端に向かって、ねじ軸の中心軸線N周りに時計回り方向に回転させた場合に、回転方向後方に当る第2端縁293がねじ山の圧力側フランク面31と一致している。そして、締め付け方向前方に向かって、付け根側が徐々に深く切り込まれるように傾斜し、前端に当たる第1端縁291では、根元側が深い三角形状の段差が形成されている。また、根元側の円弧状の内側縁294は、圧力側フランク面31に対して、第2端縁293から第1端縁291に向かって徐々に深くなる段差が形成されている。
ねじ込む際には、図1に示した実施の形態では後方の端縁93が相手材に引っ掛かって抵抗になりやすいが、この実施の形態の場合には、後方の第2端縁293が圧力側フランク面31と同一面となっているので、抵抗は小さくねじ込みトルクは小さい。一方、弛み側の回転については、弛み方向の回転方向に対して後方になる第1端縁291が段差となっているので、抵抗が大きくなり、弛み止めを図ることができる。
FIG. 4 shows still another embodiment of the present invention.
In the above embodiment, the cross-sectional shape obtained by cutting the fan-shaped bottom surface 92 of the recess 9 with a plane passing through the central axis N of the screw shaft is the same shape at the same depth at any phase angle around the central axis N. In this embodiment, the cross-sectional shape of the bottom surface 292 of the fan-shaped recess 29 cut along the plane passing through the central axis N of the screw shaft is the screw shaft in the tightening direction, that is, toward the tip of the screw shaft 5 in the figure. When rotating clockwise around the central axis N, the second end edge 293 hitting the rear in the rotational direction coincides with the pressure side flank surface 31 of the thread. And it inclines so that the base side may be gradually cut deeply toward the front in the tightening direction, and a first step edge 291 that hits the front end has a triangular step on the base side. Further, the arcuate inner edge 294 on the root side is formed with a step which gradually deepens from the second end edge 293 toward the first end edge 291 with respect to the pressure side flank surface 31.
When screwing, in the embodiment shown in FIG. 1, the rear edge 93 is easily caught by the mating member and becomes resistant. In this embodiment, the rear second edge 293 is on the pressure side. Since it is the same surface as the flank surface 31, the resistance is small and the screwing torque is small. On the other hand, with respect to the rotation on the slack side, the first end edge 291 that is rearward with respect to the rotation direction of the slack direction is a step, so that the resistance increases and the slack can be prevented.

なお、上記実施の形態では、樹脂材と鋼板の両方に共用できるタッピンねじとして説明したが、樹脂材と鋼板に限定されるものではなく、鋼板とアルミ材、アルミ材と樹脂材の共用品としても適用可能である。
また、樹脂材と鋼板の両方に共用できるものではなく、要するに、ねじ山の圧力側フランク面に、ねじ山の山頂部の外径は円形状態を連続して保った状態で、ねじ径の円周方向に対して局部的に凹部が複数設けられていることが特徴であり、ねじ山角度θ、ねじ山高さH,ピッチpを選択することで、樹脂材専用のタッピンねじとして利用することもできるし、鋼板専用のタッピンねじとしても利用可能である。要するに、樹脂材から金属材まで幅広い相手材に対して適用可能である。
In addition, in the said embodiment, although demonstrated as a tapping screw which can be shared with both a resin material and a steel plate, it is not limited to a resin material and a steel plate, As a common product of a steel plate and an aluminum material, an aluminum material and a resin material Is also applicable.
In addition, it cannot be used for both resin and steel plates. In short, the outer diameter of the crest of the screw thread on the pressure flank surface of the screw thread is kept circular, and the thread diameter circle It is characterized in that a plurality of recesses are provided locally in the circumferential direction. By selecting the thread angle θ, thread height H, and pitch p, it can also be used as a tapping screw dedicated to resin materials. It can also be used as a tapping screw dedicated to steel plates. In short, the present invention can be applied to a wide range of counterpart materials from resin materials to metal materials.

1 タッピンねじ
3 ねじ山
31 圧力側フランク面、32 遊び側フランク面
33 ねじ山頂部
5 ねじ軸
7 ねじ頭部
9 凹部、91,93 端縁、92 底面、94 内側縁
29 凹部、291 第1端縁、293 第2端縁、292 底面、294 内側縁
d 呼び径
G 山中心線
N 中心軸線
p ピッチ
α 圧力側フランク角
β 遊び側フランク角
θ 山角度
DESCRIPTION OF SYMBOLS 1 Tapping screw 3 Thread 31 Pressure side flank surface, 32 Play side flank surface 33 Thread top part 5 Screw shaft 7 Screw head 9 Recessed part, 91, 93 Edge, 92 Bottom face, 94 Inner edge 29 Recessed part, 291 1st end Edge, 293 Second edge, 292 Bottom surface, 294 Inner edge d Nominal diameter G Mountain center line N Center axis p Pitch α Pressure side flank angle β Play side flank angle θ Mountain angle

Claims (8)

相手材に塑性変形によりめねじを成形しながら締結を行うタッピンねじにおいて、
少なくとも相手材との嵌合部におけるねじ山の圧力側フランク面に、ねじ山の山頂部の外径は円筒螺旋形状を連続して保った状態で、ねじ径の円周方向に対して局部的に凹部を複数設け
前記凹部は、前記ねじ軸の中心軸線方向から見ると扇形に切り欠かれた形状で、山頂部側からねじ山付け根側に向かって徐々に深くなるような断面形状を有し、
前記扇形の凹部の外径端は、前記山頂部よりも谷部側にずらした状態でねじ山の外径に沿っており、前記扇形の凹部の内径は、前記山頂部部とねじ山付け根との中途部に位置し、
前記ねじ山の圧力側フランク角が遊び側フランク角より小さいことを特徴とするタッピンねじ。
In a tapping screw that is fastened while forming a female thread by plastic deformation to the counterpart material,
At least on the pressure side flank surface of the thread in the mating part with the mating member, the outer diameter of the thread crest is kept in a cylindrical spiral shape and is localized in the circumferential direction of the thread diameter. Provided with a plurality of recesses ,
The concave portion has a cross-sectional shape that gradually becomes deeper from the peak top side toward the screw root side, in a shape cut out in a fan shape when viewed from the central axis direction of the screw shaft,
The outer diameter end of the fan-shaped recess is along the outer diameter of the screw thread in a state shifted from the peak to the valley side, and the inner diameter of the fan-shaped recess is the sum of the peak and the screw root. Located in the middle of
A tapping screw, wherein a pressure side flank angle of the thread is smaller than a play side flank angle .
前記扇形の凹部の外径端は、ねじ山の山頂部よりも、ねじ山高さの0.1倍程度谷部側にずらしている請求項1に記載のタッピンねじ。 2. The tapping screw according to claim 1, wherein an outer diameter end of the fan-shaped concave portion is shifted to a valley portion side by about 0.1 times a screw thread height from a peak portion of the screw thread. 前記凹部の底面のねじ軸の中心軸線を通る面で切断した断面形状は、締め付け方向に回転させた場合に、回転方向後方に当る端縁がねじ山の圧力側フランク面と一致しており、締め付け方向前方に向かって、付け根側が徐々に深く切り込まれるように傾斜している請求項1又は2に記載のタッピンねじ。   The cross-sectional shape cut by the plane passing through the central axis of the screw shaft on the bottom surface of the recess has an edge that hits the rear in the rotational direction when rotated in the tightening direction, and matches the pressure side flank surface of the thread. The tapping screw according to claim 1, wherein the tapping screw is inclined so that the base side is gradually cut deeper toward the front in the tightening direction. 凹部を遊び側フランク面にも設けた請求項1乃至3のいずれかの項に記載のタッピンねじ。   The tapping screw according to any one of claims 1 to 3, wherein a concave portion is also provided on the play-side flank surface. ねじ外径は、ねじの呼び寸法に対して小さい方向に公差範囲がある請求項1乃至のいずれかの項に記載のタッピンねじ。The tapping screw according to any one of claims 1 to 4 , wherein the screw outer diameter has a tolerance range in a direction smaller than a nominal size of the screw. ねじ山の山角度は40〜45°である請求項1乃至5のいずれかの項に記載のタッピンねじ。 The tapping screw according to any one of claims 1 to 5 , wherein a thread angle of the thread is 40 to 45 °. ねじピッチが、呼び径の0.27〜0.33倍とした請求項1乃至6のいずれかの項に
記載のタッピンねじ。
The tapping screw according to any one of claims 1 to 6, wherein the screw pitch is 0.27 to 0.33 times the nominal diameter.
ねじ山高さを呼び径の、0.14〜0.16倍とした請求項1乃至7のいずれかの項に記載のタッピンねじ。   The tapping screw according to any one of claims 1 to 7, wherein the thread height is 0.14 to 0.16 times the nominal diameter.
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