JP4936144B2 - bolt - Google Patents

bolt Download PDF

Info

Publication number
JP4936144B2
JP4936144B2 JP2008178425A JP2008178425A JP4936144B2 JP 4936144 B2 JP4936144 B2 JP 4936144B2 JP 2008178425 A JP2008178425 A JP 2008178425A JP 2008178425 A JP2008178425 A JP 2008178425A JP 4936144 B2 JP4936144 B2 JP 4936144B2
Authority
JP
Japan
Prior art keywords
bolt
thread
range
slope
torque coefficient
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP2008178425A
Other languages
Japanese (ja)
Other versions
JP2009299884A (en
JP2009299884A5 (en
Inventor
儀高 渡辺
友範 五反田
博道 草深
和文 影山
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
OSG Corp
Original Assignee
OSG Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by OSG Corp filed Critical OSG Corp
Priority to JP2008178425A priority Critical patent/JP4936144B2/en
Publication of JP2009299884A publication Critical patent/JP2009299884A/en
Publication of JP2009299884A5 publication Critical patent/JP2009299884A5/ja
Application granted granted Critical
Publication of JP4936144B2 publication Critical patent/JP4936144B2/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Landscapes

  • Dowels (AREA)

Description

本発明は、ボルト、主としてトルシア形高力ボルト（摩擦接合ボルト）に関するものである。  The present invention relates to a bolt, mainly a torcia-type high-strength bolt (friction joint bolt).

従来、この種のトルシア形高力ボルトは、例えば図８〜１０に示すように頭部７１と、軸部７２と、軸部７２の先端に破断溝７３を介して連設されたピンテール部７４とを有し、軸部７２外周におねじ７２ａが、またピンテール部７４外周にセレーション７４ａが形成された構成となっている。  Conventionally, this type of torcia-type high-strength bolt includes a head portion 71, a shaft portion 72, and a pin tail portion 74 that is connected to the tip of the shaft portion 72 via a break groove 73 as shown in FIGS. The screw 72a is formed on the outer periphery of the shaft portion 72, and the serration 74a is formed on the outer periphery of the pin tail portion 74.

そして、使用に際しては、図１０に示すように被締付け体２Ａと被締付け体３Ａの両貫通孔２ａ，３ａにボルト７を貫通状に差し込む一方、ボルト７のおねじ７２ａ側に座金４Ａを介してナット５Ａを螺装し仮止めする。その後、専用電動レンチ６Ａを用い、そのインナースリーブ６１をピンテール７４に嵌め込み、レンチ６Ａを押しながらアウタースリーブ６２をナット５Ａに嵌め込む。然る後、電動レンチ６Ａのスイッチを入れると、アウタースリーブ６２が回り、ナット５Ａを回転させて締め付けが行われる。その後、所定トルクに達するとピンテール部７４で締付トルクの反力を受け破断溝７３が破断し、ボルト７の締め付けが完了するようになっている。  In use, as shown in FIG. 10, the bolt 7 is inserted into the through holes 2a and 3a of the clamped body 2A and the clamped body 3A in a penetrating manner, while the screw 7a side of the bolt 7 is interposed with a washer 4A. Then, the nut 5A is screwed and temporarily fixed. Thereafter, using the dedicated electric wrench 6A, the inner sleeve 61 is fitted into the pin tail 74, and the outer sleeve 62 is fitted into the nut 5A while pushing the wrench 6A. After that, when the electric wrench 6A is switched on, the outer sleeve 62 rotates, and the nut 5A is rotated to perform tightening. After that, when the predetermined torque is reached, the pin tail portion 74 receives the reaction force of the tightening torque, and the fracture groove 73 is broken to complete the tightening of the bolt 7.

ところで、上記したトルシア形高力ボルト７は建築、土木分野等において多量に使用されている。この建築、土木分野等では特に安全性が重視されるため、締付軸力範囲の上限・下限を、締付軸力のばらつきを考慮して設計軸力を上回り、捻じ切れを生じない値に設定されている。その際、締付軸力と比例関係にあるトルク係数を制御することにより締付軸力の確保を行うようにしている。ここでトルク係数はボルト７とナット５Ａのねじ接触部で５０％、ナット５Ａと座金４Ａの間で５０％が決定される。  By the way, the above-described Torcia-type high-strength bolt 7 is used in a large amount in the fields of construction, civil engineering, and the like. In this construction, civil engineering field, etc., safety is particularly important, so the upper and lower limits of the tightening axial force range exceed the designed axial force in consideration of variations in the tightening axial force, and do not cause twisting. Is set. At that time, the tightening axial force is ensured by controlling a torque coefficient proportional to the tightening axial force. Here, the torque coefficient is determined to be 50% at the screw contact portion between the bolt 7 and the nut 5A, and 50% between the nut 5A and the washer 4A.

しかし、通常、図９に示すようにボルト７とナット５Ａの各ねじ山斜面は共に平面であることから、図９仮想線で示すように締結時におけるボルト７のおねじ７２ａとナット５Ａのめねじ５ａとの接触位置が常に一定化されにくくトルク係数にばらつきが発生し易い問題があった。つまり、ボルト７の中心から接触位置までの距離の一定化が得られにくいと共に接触面積も一定化が困難であり、そのためトルク係数にばらつきが発生する。トルク係数がばらつきを有すると締付軸力もばらつくといった問題を有していた。  However, since the screw thread slopes of the bolt 7 and the nut 5A are usually flat as shown in FIG. 9, the male screw 72a and the nut 5A of the bolt 7 at the time of fastening are shown in FIG. There is a problem that the position of contact with the screw 5a is not always constant, and the torque coefficient tends to vary. That is, it is difficult to make the distance from the center of the bolt 7 to the contact position constant, and it is difficult to make the contact area constant, so that the torque coefficient varies. When the torque coefficient varies, there is a problem that the tightening axial force varies.

そのため、締付軸力範囲の下限はトルク係数のばらつきを考慮して設計軸力を満足するように規定している。なお、試験ロットは５本の平均値と変動係数（σ／ｘ×１００（％） σ：標準偏差 ｘ：平均値）で規定されている。  Therefore, the lower limit of the tightening axial force range is defined so as to satisfy the designed axial force in consideration of variations in the torque coefficient. The test lot is defined by an average value of five and a coefficient of variation (σ / x × 100 (%) σ: standard deviation x: average value).

また、上記した問題に対して従来では、ナット５Ａに潤滑処理を施すことにより、トルク係数を一定の範囲内に制御しようとすることも行われているが、ナット５Ａの潤滑処理だけではトルク係数のばらつきを多少は制御できるものの、締付軸力の変動係数が建築物では７％と広い範囲の規定になっている。  Further, conventionally, in order to control the torque coefficient within a certain range by applying lubrication to the nut 5A, the torque coefficient can be controlled only by the lubrication of the nut 5A. The variation coefficient of tightening axial force is regulated in a wide range of 7% for buildings.

そこで、本発明は、ボルトのナットへのねじ接触部を改良してトルク係数のばらつきを積極的に抑え、締付軸力を効果的に安定させることができるボルトの提供を課題とする。  Accordingly, an object of the present invention is to provide a bolt that can improve the screw contact portion of the bolt to the nut to actively suppress variation in torque coefficient and effectively stabilize the tightening axial force.

上記問題を解決するため願の請求項１の発明は、頭部と軸部とを有し、軸部外周におねじが形成されたボルトにおいて、軸部のおねじにおけるねじ山斜面の少なくともナットへの荷重の伝わる側に、外膨らみに膨出するトルク係数安定部が設けられている一方、トルク係数安定部における有効径部分に膨出頂部となり、かつめねじ側のねじ山斜面と平行状となる係合突面が形成されていることを特徴とする。
なお、ここでねじとは並目ねじだけではなく、細目ねじをも含む概念である。In order to solve the above problem, the invention of claim 1 of the present application is a bolt having a head portion and a shaft portion, and a screw formed on the outer periphery of the shaft portion, and at least a nut on a thread slope of the male screw of the shaft portion. On the side where the load is transmitted, there is a torque coefficient stabilizing part that bulges to the outer bulge, while the effective diameter part of the torque coefficient stabilizing part becomes the bulging top and is parallel to the thread slope on the female screw side An engagement protrusion surface is formed .
Here, the screw is a concept including not only coarse screws but also fine screws.

また、本願の請求項２記載の発明は、請求項１記載の構成において、軸部のおねじにおけるねじ山斜面の両側に係合突面が形成されており、かつ各係合突面の長さが１ｍｍ以内になっていると共に、隣り合う係合突面がＶ字状に対向し、その開放角度が６０°±２０´の範囲に設定されている一方、隣り合う係合突面から谷径に至る下側ねじ山斜面がＶ字状に対向し、その開放角度が４５°〜５８°の範囲に設定されていると 共に、隣り合う係合突面から外径側に至る上側ねじ山斜面がＶ字状に対向し、その開放角度が６２°〜７５°の範囲に設定されていることを特徴とする。The invention according to claim 2 of the present application is the configuration according to claim 1 , wherein the engaging protrusions are formed on both sides of the thread slope of the male screw of the shaft portion, and the length of each engaging protrusion is long. The adjacent engaging protrusions face each other in a V shape, and the opening angle is set in a range of 60 ° ± 20 ′. facing the lower thread slope in a V-shape extending radially, that the opening angle is set in a range of 45 ° to 58 ° both the upper thread extending radially outward from the adjacent engagement protruding surface mountain The slopes face each other in a V shape, and the opening angle is set in a range of 62 ° to 75 ° .

本発明によれば、ボルト軸部のおねじにおけるねじ山斜面のたとえば両側に、外膨らみに膨出するトルク係数安定部が設けられているから、ボルトのナットへの締め込み時に、トルク係数安定部がナットにおけるめねじのねじ山斜面と接触することになる。これにより、ボルトにおけるおねじのナットにおけるめねじとの接触位置を積極的に特定することができ、トルク係数を安定させることができる。つまり、積極的にボルト中心から接触位置までの距離を一定化させると共に接触面積も一定化させることによってトルク係数をばらつきを狭い範囲に抑えることができる。その結果、トルク係数を安定させることによって安定した締付軸力を確保することができ、安全性も向上する。その上、締付軸力の変動係数が下ることにより、より高い軸力でかつ狭い範囲での締付管理が可能となるため、使用するボルトの削減、省資源につながる。  According to the present invention, since the torque coefficient stabilizing portion that bulges to the outer bulge is provided on, for example, both sides of the thread slope of the male screw of the bolt shaft portion, the torque coefficient is stabilized when the bolt is tightened to the nut. The part comes into contact with the thread slope of the female thread in the nut. Thereby, the contact position with the internal thread in the nut of the external thread in the bolt can be positively specified, and the torque coefficient can be stabilized. In other words, the torque coefficient can be kept within a narrow range by positively fixing the distance from the center of the bolt to the contact position and making the contact area constant. As a result, a stable tightening axial force can be secured by stabilizing the torque coefficient, and safety is also improved. In addition, since the coefficient of variation of the tightening axial force is lowered, tightening management can be performed in a narrow range with a higher axial force, leading to reduction of bolts used and resource saving.

しかも、トルク係数安定部における有効径部分にその膨出頂部となり、かつめねじ側のねじ山斜面と平行となる係合突面を形成しているので、積極的に有効径部分、つまり最適な位置において接触させることができると共に、その接触もめねじ側のねじ山斜面に沿った一定の面積で安定よく接触させることができる。これによりトルク係数のばらつきを一層狭い範囲に抑えることができる。 Moreover, the effective diameter portion of the torque coefficient stabilizing portion is the bulging top portion, and the engagement protrusion surface that is parallel to the thread slope on the female screw side is formed. In addition to being able to make contact at a position, the contact can also be stably made in a certain area along the thread slope on the female screw side. Thereby, the variation of the torque coefficient can be suppressed to a narrower range.

さらに、係合突面の長さをそれぞれ１ｍｍ以内にすると共に、隣り合う係合突面をＶ字状に対向させ、その開放角度を６０°±２０′の範囲に設定する一方、隣り合う係合突面から谷径に至る下側ねじ山斜面をＶ字状に対向させ、その開放角度が４５°〜５８°の範囲に設定すると共に、隣り合う係合突面から外径側に至る上側ねじ山斜面をＶ字状に対向させ、その開放角度を６２°〜７５°の範囲に設定するようにすれば、トルク係数安定部の有効径部分に位置する係合突面のみを確実かつ正確にめねじ側のねじ山斜面に一定の面積で安定よく接触させることができ、トルク係数をばらつきをより効果的に狭い範囲に抑えることができるのでこのましい。  Further, the length of the engaging protrusions is set within 1 mm, the adjacent engaging protrusions are opposed in a V shape, and the opening angle is set in the range of 60 ° ± 20 ′, while the adjacent engaging protrusions are The lower thread slope from the mating face to the valley diameter is opposed in a V shape, the opening angle is set in the range of 45 ° to 58 °, and the upper side from the adjacent engaging face to the outer diameter side If the thread slopes are opposed in a V shape and the opening angle is set in the range of 62 ° to 75 °, only the engagement protrusion located at the effective diameter portion of the torque coefficient stabilizing portion can be reliably and accurately set. This is preferable because it allows stable contact with the thread slope on the female thread side with a constant area, and the variation in torque coefficient can be more effectively suppressed within a narrow range.

以下、本発明の実施の形態を図に基づいて説明する。  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

図１〜３は、本発明に係るトルシア形高力ボルト（以下単にボルトという）を示すもので、このボルト１は、図３に示すように大径の頭部１１と、軸部１２と、軸部１２の先端に破断溝１３を介して連設される小径のピンテール部１４とを有し、軸部１２外周におねじ１５が、またピンテール部１４外周にセレーション１６が形成されている。  1 to 3 show a torcia-type high-strength bolt (hereinafter simply referred to as a bolt) according to the present invention. The bolt 1 includes a large-diameter head 11, a shaft 12, and a shaft 12 as shown in FIG. 3. The shaft portion 12 has a small-diameter pin tail portion 14 connected to the front end of the shaft portion 12 via a breaking groove 13. A screw 15 is formed on the outer periphery of the shaft portion 12, and a serration 16 is formed on the outer periphery of the pin tail portion 14.

そして、図１及び図２に示すようにボルト１における軸部１２のおねじ１５におけるねじ山斜面の両側に、外膨らみに膨出するトルク係数安定部１５ａ，１５ａが設けられている。トルク係数安定部１５ａ，１５ａにおける有効径ｄ２部分には、その膨出頂部となりかつ後記するナットのめねじにおけるねじ山斜面と平行となる係合突面１５ｂ，１５ｂが形成されている。このとき各係合突面１５ｂ，１５ｂの長さが１ｍｍ以内になっていると共に、隣り合う係合突面１５ｂ，１５ｂがＶ字状に対向し、その開放角度が６０°±２０′の範囲に設定されている一方、隣り合う係合突面１５ｂ，１５ｂから谷径ｄ１に至る下側ねじ山斜面がＶ字状に対向し、その開放角度が４５°〜５８°の範囲に設定されていると共に、隣り合う係合突面から外径ｄ側に至る上側ねじ山斜面がＶ字状に対向し、その開放角度が６２°〜７５°の範囲に設定されている。As shown in FIGS. 1 and 2, torque coefficient stabilizing portions 15 a and 15 a that bulge outwardly are provided on both sides of the thread slope of the male screw 15 of the shaft portion 12 in the bolt 1. Torque coefficient stable unit 15a, the effective diameter d 2 portion in 15a, engagement protruding surface 15b which is parallel to the thread slopes at the internal thread of the nut to become and below its bulging top, 15b are formed. At this time, the length of each of the engaging protrusions 15b and 15b is within 1 mm, the adjacent engaging protrusions 15b and 15b are opposed in a V shape, and the opening angle is in the range of 60 ° ± 20 ′. while it is set to, adjacent engagement protruding surface 15b, the lower thread slope leading from 15b to the root diameter d 1 is opposed to the V-shape, the opening angle is set in a range of 45 ° to 58 ° In addition, the upper thread slope extending from the adjacent engaging projection surface to the outer diameter d side is opposed in a V shape, and the opening angle is set in the range of 62 ° to 75 °.

トルク係数安定部１５ａは平ダイス等（丸型転造ダイスでも可能）でおねじ１５を転造により形成する際、同時に形成される。  The torque coefficient stabilizing portion 15a is formed at the same time when the external thread 15 is formed by rolling with a flat die or the like (also possible with a round rolling die).

図４〜６は、ボルト１の施工状態を示す説明図で、各図中において符号２，３は被締付け体、４は座金、５は段付きナット、６はインナースリーブ６１とアウタースリーブ６２を有する専用電動レンチ６である。なお、専用電動レンチ６は既存のものであるのでその詳細については省略する。  4-6 is explanatory drawing which shows the construction state of the volt | bolt 1. In each figure, the code | symbols 2 and 3 are to-be-tightened bodies, 4 is a washer, 5 is a stepped nut, 6 is the inner sleeve 61 and the outer sleeve 62. It is a dedicated electric wrench 6 having. Since the dedicated electric wrench 6 is an existing one, details thereof are omitted.

次に、上記したボルトの作用について説明する。  Next, the operation of the bolt described above will be described.

まず、図４に示すように、ボルト１の施工前の使用状態を示す説明図で、被締付け体２と被締付け体３の取付孔２ａ，２ｂにボルト１を差し込む一方、ボルト１のおねじ１５側に座金４を介してナット５を螺装し仮止めする。  First, as shown in FIG. 4, the bolt 1 is inserted into the mounting holes 2 a and 2 b of the clamped body 2 and the clamped body 3, while the bolt 1 is threaded. A nut 5 is screwed to the 15 side via a washer 4 and temporarily fixed.

次に、図５に示すように、専用電動レンチ６を用い、そのインナースリーブ６１をピンテール部１４に嵌め込み、電動レンチ６を押しながらアウタースリーブ６２をナット５に嵌め込む。その後、電動レンチ６のスイッチを入れると、アウタースリーブ６２が回り、ナット５を回転させて締め付けが行われる。所定トルクに達するとピンテール部１４で締付トルクの反力を受け破断溝１３が破断し、ボルト１の締め付けが完了する。破断溝１３が破断したら、電動レンチ６のスイッチを離し、レンチ６を手前に引いてアウタースリーブ６２をナット５から外して作業を終える。  Next, as shown in FIG. 5, using the dedicated electric wrench 6, the inner sleeve 61 is fitted into the pin tail portion 14, and the outer sleeve 62 is fitted into the nut 5 while pushing the electric wrench 6. Thereafter, when the electric wrench 6 is switched on, the outer sleeve 62 rotates and the nut 5 is rotated to perform tightening. When the predetermined torque is reached, the pin tail portion 14 receives the reaction force of the tightening torque and the fracture groove 13 is broken, and the bolt 1 is completely tightened. When the breaking groove 13 is broken, the switch of the electric wrench 6 is released, the wrench 6 is pulled forward, the outer sleeve 62 is removed from the nut 5, and the operation is finished.

この際、軸部１２のおねじ１５におけるねじ山斜面の有効径ｄ２部分が膨出頂部となるように、外膨らみに膨出するトルク係数安定部１５ａが設けられているから、ボルト１のナット５への締め込み時に、図７に示すようにトルク係数安定部１５ａがナット５におけるめねじ５ａのねじ山斜面と接触することになる。これにより、ボルト１におけるおねじ１５のナット５におけるめねじ５ａとの接触位置を積極的に特定することができ、トルク係数を安定させることができる。つまり、積極的にボルト１の中心から接触位置までの距離を一定化させると共に接触面積も一定化させることができ、これによってトルク係数のばらつきを狭い範囲に抑えることができる。その結果、トルク係数を安定させることで安定した締付軸力を確保することができ、安全性も向上する。その上、締付軸力の変動係数が下がることにより、より高い軸力でかつ狭い範囲での締付管理が可能となるため、使用するボルトの削減、省資源につながる顕著な効果が得られる。At this time, as the effective diameter d 2 portion of the thread slopes at the external thread 15 of the shaft portion 12 is bulged top, because the torque coefficient stable unit 15a that bulges to the outer bulge is provided, the bolt 1 When tightening to the nut 5, the torque coefficient stabilizing portion 15 a comes into contact with the thread slope of the female screw 5 a in the nut 5 as shown in FIG. 7. Thus, the contact position between the female thread 5a of the nut 5 of the male screw 15 positively able to identify the bolt 1, the torque coefficient can be stabilized. In other words, the distance from the center of the bolt 1 to the contact position can be positively constant and the contact area can be constant, thereby suppressing the variation in torque coefficient within a narrow range. As a result, a stable tightening axial force can be secured by stabilizing the torque coefficient, and safety is also improved. Moreover, the lower the coefficient of variation of the fastening shaft force is Rukoto, since it becomes possible tightening management in higher axial forces in and narrow range, reduction of the bolts to be used, the remarkable effect that leads to resource savings can get.

また、トルク係数安定部１５ａにおける有効径ｄ２部分にその膨出頂部となり、かつめねじ側のねじ山斜面と平行となる係合突面１５ｂを形成しているので、積極的に有効径ｄ２部分、つまり最適な位置において接触させることができると共に、その接触もめねじ側のねじ山斜面に沿った一定の面積で安定よく接触させることができ、トルク係数のばらつきを一層狭い範囲に抑えることができる。Further, it becomes the bulging top to the effective diameter d 2 portion in the torque coefficient stable portion 15a, and therefore forms the engaging protruding surface 15b which is parallel to the thread slope of the internal thread side, actively effective diameter d It is possible to make contact in two parts, that is, in an optimal position, and the contact can be stably made in a certain area along the thread slope on the female screw side, and the variation in torque coefficient is suppressed to a narrower range. Can do.

さらに、係合突面１５ｂの長さをそれぞれ１ｍｍ以内にすると共に、隣り合う係合突面１５ｂ，１５ｂをＶ字状に対向させ、その開放角度を６０°±２０′の範囲に設定する一方、隣り合う係合突面１５ｂ，１５ｂから谷径ｄ１に至る下側ねじ山斜面をＶ字状に対向させ、その開放角度が４５°〜５８°の範囲に設定すると共に、隣り合う係合突面から外径ｄ側に至る上側ねじ山斜面をＶ字状に対向させ、その開放角度を６２°〜７５°の範囲に設定するようにしているので、トルク係数安定部１５ａの有効径ｄ２部分に位置する係合突面のみを確実かつ正確にめねじ５ａ側のねじ山斜面に一定の面積で安定よく接触させることができ、トルク係数のばらつきをより効果的に狭い範囲に抑えることができる。Further, the length of the engaging protrusion 15b is within 1 mm, and the adjacent engaging protrusions 15b and 15b are opposed to each other in a V shape, and the opening angle is set within a range of 60 ° ± 20 ′. , adjacent the engagement protruding surface 15b, the lower thread slope leading from 15b to the root diameter d 1 is opposed to the V-shape, with its opening angle is set in a range of 45 ° to 58 °, adjacent the engagement Since the upper thread slope from the projecting surface to the outer diameter d side is opposed in a V shape and the opening angle is set in the range of 62 ° to 75 °, the effective diameter d of the torque coefficient stabilizing portion 15a is set. Only the engagement protrusions located in the two parts can be reliably and accurately brought into contact with the thread slope on the female screw 5a side in a constant area, and the variation in torque coefficient can be more effectively suppressed to a narrow range. Can do.

因みに、ボルトサイズがＭ２２の本案ボルトを製造し、ボルトサイズがＭ２２の従来ボルトとの締付軸力の比較実験を行った。その実験結果は次の通りであった。  In this connection, the present bolt with a bolt size of M22 was manufactured, and a comparative experiment of the tightening axial force with a conventional bolt with a bolt size of M22 was conducted. The experimental results were as follows.

Figure 0004936144
Figure 0004936144
Figure 0004936144
Figure 0004936144

上記した表１から明らかなように、従来品では、締付軸力の変動係数が４．８３％程度だが、本案ボルト１ではおねじ１５の斜面に外膨らみに膨出するトルク係数安定部１５ａを設けることにより変動係数を２．２２％まで下げることができた。このように変動係数が下ることにより、高い軸力でかつ狭い範囲での締付管理が可能となるため、使用するボルトの削減、省資源につながる。  As apparent from Table 1 above, the conventional product has a coefficient of variation of the tightening axial force of about 4.83%, but with the proposed bolt 1, the torque coefficient stabilizing portion 15a that bulges outwardly on the slope of the external thread 15. It was possible to reduce the coefficient of variation to 2.22%. By reducing the coefficient of variation in this way, it is possible to perform tightening management in a narrow range with high axial force, leading to reduction of bolts to be used and resource saving.

なお、上記した実施の形態では、トルク係数安定部１５ａを軸部１２のおねじ１５におけるねじ山斜面の両側に設けたものについて説明したけれども、軸部１２のおねじ１５におけるねじ山斜面のナットへ荷重の伝わる側だけに設けるようにしてもよい。また、本発明は並目ねじだけではなく、細目ねじにも適用できること勿論である。  In the above-described embodiment, the torque coefficient stabilizing portion 15a is provided on both sides of the thread slope of the male screw 15 of the shaft portion 12. However, the nut of the thread slope of the male screw 15 of the shaft portion 12 is described. It may be provided only on the side where the load is transmitted. Of course, the present invention can be applied not only to coarse threads but also to fine threads.

本発明に係るボルトのおねじ部分の拡大縦断面図である。  It is an expansion longitudinal cross-sectional view of the external thread part of the bolt which concerns on this invention. 同おねじにおける要部の拡大縦断面図である。  It is an expanded longitudinal cross-sectional view of the principal part in the same external thread. 同ボルト全体の一部省略正面図である。  It is a partially omitted front view of the entire bolt. 同ボルトの施工前の状態を示す説明図である。  It is explanatory drawing which shows the state before construction of the bolt. 同ボルトの施工中の状態を示す説明図である。  It is explanatory drawing which shows the state under construction of the bolt. 同ボルトの施工後の状態を示す説明図である。  It is explanatory drawing which shows the state after construction of the bolt. 同施工後における要部の拡大縦断面図である。  It is an expanded longitudinal cross-sectional view of the principal part after the construction. 従来ボルトの一部省略正面図である。  It is a partially omitted front view of a conventional bolt. 従来ボルトの要部拡大縦断面図である。  It is a principal part expansion longitudinal cross-sectional view of the conventional volt | bolt. 従来ボルトの施工状態を示す説明図である。  It is explanatory drawing which shows the construction state of the conventional volt | bolt.

符号の説明Explanation of symbols

１ ボルト
１１ 頭部
１２ 軸部
１５ おねじ
１５ａ トルク係数安定部
１５ｂ 係合突面1 Bolt 11 Head 12 Shaft 15 Male thread 15a Torque coefficient stabilizing part 15b Engagement protrusion

Claims (2)

頭部と軸部とを有し、軸部外周におねじが形成されたボルトにおいて、軸部のおねじにおけるねじ山斜面の少なくともナットへの荷重の伝わる側に、外膨らみに膨出するトルク係数安定部が設けられている一方、トルク係数安定部における有効径部分に膨出頂部となり、かつめねじ側のねじ山斜面と平行状となる係合突面が形成されていることを特徴とするボルト。Torque that bulges to the outer bulge at least on the side of the thread slope of the thread on the male thread of the shaft, where the load is transmitted to the nut, in a bolt that has a head and a shaft and has a screw formed on the outer periphery of the shaft While the coefficient stabilizing portion is provided, the effective diameter portion of the torque coefficient stabilizing portion is formed as an bulging top portion, and an engagement protrusion surface is formed in parallel with the thread slope on the female screw side. Bolts to do. 軸部のおねじにおけるねじ山斜面の両側に係合突面が形成されており、かつ各係合突面の長さが１ｍｍ以内になっていると共に、隣り合う係合突面がＶ字状に対向し、その開放角度が６０°±２０´の範囲に設定されている一方、隣り合う係合突面から谷径に至る下側ねじ山斜面がＶ字状に対向し、その開放角度が４５°〜５８°の範囲に設定されてい ると共に、隣り合う係合突面から外径側に至る上側ねじ山斜面がＶ字状に対向し、その開放角度が６２°〜７５°の範囲に設定されていることを特徴とする請求項１記載のボルト。 Engagement protrusions are formed on both sides of the thread slope of the male thread of the shaft, and the length of each engagement protrusion is within 1 mm, and adjacent engagement protrusions are V-shaped. The opening angle is set in the range of 60 ° ± 20 ′, while the lower thread slope from the adjacent engagement protrusion surface to the valley diameter is V-shaped, and the opening angle is 45 ° to 58 have been set in the range of ° Rutotomoni upper thread slope leading to the outer diameter side from the adjacent engagement protruding surface faces the V-shape, the range of the opening angle is 62 ° to 75 ° bolt according to claim 1, characterized in that it is set.
JP2008178425A 2008-06-11 2008-06-11 bolt Expired - Fee Related JP4936144B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2008178425A JP4936144B2 (en) 2008-06-11 2008-06-11 bolt

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2008178425A JP4936144B2 (en) 2008-06-11 2008-06-11 bolt

Publications (3)

Publication Number Publication Date
JP2009299884A JP2009299884A (en) 2009-12-24
JP2009299884A5 JP2009299884A5 (en) 2011-01-27
JP4936144B2 true JP4936144B2 (en) 2012-05-23

Family

ID=41546979

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2008178425A Expired - Fee Related JP4936144B2 (en) 2008-06-11 2008-06-11 bolt

Country Status (1)

Country Link
JP (1) JP4936144B2 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5299816B2 (en) * 2008-12-29 2013-09-25 日本ファスナー工業株式会社 nut
JP5984329B2 (en) * 2010-10-01 2016-09-06 濱中ナット株式会社 Bolt rolling method
WO2018079137A1 (en) * 2016-10-28 2018-05-03 株式会社トープラ Male thread and thread-fastening structure

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS51121651A (en) * 1975-04-18 1976-10-25 Shunji Yamamoto Screw and its manufacturing method
JPS5852690B2 (en) * 1976-01-23 1983-11-24 バブコツク日立株式会社 Fixed bed catalytic reactor
JPS57195912A (en) * 1981-05-29 1982-12-01 Mitsubishi Heavy Ind Ltd Screw joint
JPH06173925A (en) * 1992-12-07 1994-06-21 Yamashina Seikosho:Kk Screw
US5722808A (en) * 1996-09-11 1998-03-03 Conti Fasteners Ag Threaded fastener system
JPH10338824A (en) * 1996-12-27 1998-12-22 Nittetsu Boruten Kk Rust-preventive coating composition for screw fastening member, screw fastening member and apparatus for screw fastening
JP2002235717A (en) * 2001-02-08 2002-08-23 Minebea Co Ltd Deformed screw

Also Published As

Publication number Publication date
JP2009299884A (en) 2009-12-24

Similar Documents

Publication Publication Date Title
TWI622709B (en) Screw with interrupted scraping edge, production method and application thereof
EP2679835B1 (en) Threaded fastener
CA2265156C (en) Anti-cross threading fastener
CA2485500A1 (en) Pull stem fastener with pull groove for swaging collars
JP3666754B2 (en) Screws for fixing metal profiles and plastic profiles or one of them or plastic plates on the substructure
JP4936144B2 (en) bolt
WO2018120629A1 (en) Bolt and method for manufacturing same
JP5299816B2 (en) nut
JP4340103B2 (en) Screw fastening structure
TWI747010B (en) Wood screw
EP1886031B1 (en) Fastener and method for reducing stress failure in an engine component
WO2012073589A1 (en) Locking screw
JP6228203B2 (en) Screw part and method of manufacturing screw part
JP4713387B2 (en) Bolt joint structure
JP4728041B2 (en) Reinforcing threaded mechanical joints
KR101157458B1 (en) Bolt
WO1996023142B1 (en) Locking devices
JP3138712U (en) Tapping bolt
JP3109980B2 (en) Tapping screw
CA2265140A1 (en) Improved anti-cross threading fastener
JP2000314414A (en) Embedded nut for architecture
CN217421807U (en) High-strength bolt for universal shaft of rolling mill
US20190107142A1 (en) Nut
JP2009185845A (en) Fastening member
JP2019113156A (en) Locking screw

Legal Events

Date Code Title Description
A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20101112

A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20101112

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20110929

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20111011

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20111110

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20120124

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20120209

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20150302

Year of fee payment: 3

R150 Certificate of patent or registration of utility model

Ref document number: 4936144

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

Free format text: JAPANESE INTERMEDIATE CODE: R150

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

LAPS Cancellation because of no payment of annual fees