JP2009222218A - Fastener with flange - Google Patents
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- JP2009222218A JP2009222218A JP2008070757A JP2008070757A JP2009222218A JP 2009222218 A JP2009222218 A JP 2009222218A JP 2008070757 A JP2008070757 A JP 2008070757A JP 2008070757 A JP2008070757 A JP 2008070757A JP 2009222218 A JP2009222218 A JP 2009222218A
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Abstract
Description
本発明は、フランジ付きボルトやフランジ付きナット等のフランジ付きファスナーに関する。 The present invention relates to a flanged fastener such as a flanged bolt or a flanged nut.
従来から、フランジ付きボルトやフランジ付きナット等のフランジ付きファスナーは知られている（例えば、特許文献１参照）。このようなフランジ付きファスナーにおいて、例えば標準的なフランジ付き六角ボルトの場合、フランジ部に外力が負荷されたときには、そのフランジ部が反り上がるように変形し、座面面圧が頭部の外周面の各稜線直下に集中してしまう（不均一に内当たりしてしまう）ことで、結合剛性の低下を招いていた。
そこで、本発明は、上記事情に鑑み、締結時等において、フランジ部の座面面圧をほぼ均一にできるフランジ付きファスナーを得ることを目的とする。 Then, an object of this invention is to obtain the fastener with a flange which can make the bearing surface pressure of a flange part substantially uniform at the time of fastening etc. in view of the said situation.
上記の目的を達成するために、本発明に係る請求項１に記載のフランジ付きファスナーは、角柱状に形成された頭部と、前記頭部に一体に設けられるとともに、雄ネジ部が形成された本体部と、前記頭部と前記本体部との間に一体に設けられ、該頭部側表面が、該頭部の外周面の稜線部分を谷部とし、該稜線間部分を山部とする側面視略波型形状とされたフランジ部と、を有することを特徴としている。 In order to achieve the above object, a flanged fastener according to claim 1 according to the present invention is provided with a head portion formed in a prismatic shape, and is provided integrally with the head portion, and a male screw portion is formed. And the head-side surface has a ridge line portion of the outer peripheral surface of the head as a trough portion, and a portion between the ridge lines as a crest portion. And a flange portion having a substantially wave shape in a side view.
請求項１に記載の発明によれば、フランジ部の頭部側表面が、その頭部の外周面の稜線部分を谷部とし、稜線間部分を山部とする側面視略波型形状とされているので、フランジ部の各稜線間部分の曲げ剛性を各稜線部分の曲げ剛性に近づけることができる。したがって、フランジ部に締結時の締付力や外力が負荷されても、フランジ部の座面面圧をほぼ均一にできる。 According to the first aspect of the present invention, the head-side surface of the flange portion has a substantially wave shape in side view with the ridge line portion of the outer peripheral surface of the head portion as a valley portion and the portion between the ridge lines as a mountain portion. Therefore, the bending rigidity of the portion between the ridge lines of the flange portion can be brought close to the bending rigidity of each ridge line portion. Therefore, even if a fastening force or an external force at the time of fastening is applied to the flange portion, the bearing surface pressure of the flange portion can be made substantially uniform.
また、本発明に係る請求項２に記載のフランジ付きファスナーは、角筒状に形成され、内周面に雌ネジ部が形成された本体部と、前記本体部の一端側に一体に設けられ、該本体部の他端側を向く表面が、該本体部の外周面の稜線部分を谷部とし、該稜線間部分を山部とする側面視略波型形状とされたフランジ部と、を有することを特徴としている。 In addition, the flanged fastener according to claim 2 of the present invention is formed integrally with a main body portion formed in a rectangular tube shape and having an internal thread portion formed on an inner peripheral surface, and one end side of the main body portion. A flange portion having a surface facing the other end of the main body, the ridge line portion of the outer peripheral surface of the main body portion being a trough portion, and the portion between the ridge lines being substantially wave-shaped in a side view, It is characterized by having.
請求項２に記載の発明によれば、フランジ部の本体部側表面が、その本体部の外周面の稜線部分を谷部とし、稜線間部分を山部とする側面視略波型形状とされているので、フランジ部の各稜線間部分の曲げ剛性を各稜線部分の曲げ剛性に近づけることができる。したがって、フランジ部に締結時の締付力や外力が負荷されても、フランジ部の座面面圧をほぼ均一にできる。 According to the second aspect of the invention, the main body side surface of the flange portion has a substantially wave shape in a side view in which the ridge line portion of the outer peripheral surface of the main body portion is a valley portion and the portion between the ridge lines is a mountain portion. Therefore, the bending rigidity of the portion between the ridge lines of the flange portion can be brought close to the bending rigidity of each ridge line portion. Therefore, even if a fastening force or an external force at the time of fastening is applied to the flange portion, the bearing surface pressure of the flange portion can be made substantially uniform.
以上のように、本発明によれば、締結時等において、フランジ部の座面面圧をほぼ均一にできるフランジ付きファスナーを提供することができる。 As described above, according to the present invention, it is possible to provide a flanged fastener capable of making the bearing surface pressure of the flange portion substantially uniform during fastening or the like.
以下、本発明の最良な実施の形態について、図面に示す実施例を基に詳細に説明する。まず最初に、本実施形態に係るフランジ付きファスナーの一例としてのフランジ付き六角ボルト１０について説明する。図１はフランジ付き六角ボルト１０の概略斜視図であり、図２（Ａ）はフランジ付き六角ボルト１０の概略平面図、図２（Ｂ）は同じく概略正面図である。そして、図３は図２（Ｂ）とは９０°異なる方向から見たときのフランジ付き六角ボルト１０の概略正面図である。なお、説明の便宜上、各図において矢印ＵＰで示す方向を上方向とする。 DESCRIPTION OF THE PREFERRED EMBODIMENTS The best mode for carrying out the present invention will be described below in detail based on the embodiments shown in the drawings. First, the flanged hexagon bolt 10 as an example of the flanged fastener according to the present embodiment will be described. 1 is a schematic perspective view of a hexagon bolt 10 with a flange, FIG. 2A is a schematic plan view of the hexagon bolt 10 with a flange, and FIG. 2B is a schematic front view of the same. FIG. 3 is a schematic front view of the flanged hexagon bolt 10 when viewed from a direction 90 ° different from that in FIG. For convenience of explanation, the direction indicated by the arrow UP in each figure is the upward direction.
図１〜図３で示すように、このフランジ付き六角ボルト１０は、六角柱状に形成された頭部１２と、頭部１２の下面中央に一体かつ同心軸に設けられた円柱状の本体部１４と、頭部１２と本体部１４との間に一体かつ同心軸に設けられた円板状のフランジ部１６と、を有している。なお、このフランジ部１６は、その外周縁部１９が、頭部１２の外周面１２Ｂに形成された各稜線１２Ａ部分よりも径方向外側へ所定長さ（後述する距離Ｓ２）張り出すような直径Ｒを有している。 As shown in FIGS. 1 to 3, the hexagonal bolt 10 with flange includes a head 12 formed in a hexagonal column shape, and a columnar main body 14 provided on a concentric shaft integrally with the center of the lower surface of the head 12. And a disc-shaped flange portion 16 provided integrally and concentrically between the head portion 12 and the main body portion 14. The flange portion 16 has a diameter such that the outer peripheral edge portion 19 projects a predetermined length (distance S2 described later) radially outward from each ridgeline 12A portion formed on the outer peripheral surface 12B of the head 12. R is included.
また、フランジ部１６の頭部１２側表面である上面１８は、頭部１２の各稜線１２Ａ直下が谷部１８Ａとなり、頭部１２の各稜線１２Ａ間が山部１８Ｂとなるような側面視略波型形状とされている。そして、このフランジ部１６の上面１８は、その外周縁部１９から頭部１２の外周面１２Ｂに向かって板厚が徐々に厚くなる傾斜面とされており、その外周縁部１９の板厚は全周において同一とされている。また、フランジ部１６の本体部１４側表面である下面（以下「座面」という）１７は平面とされており、本体部１４の下部側には、雄ネジ部１５が所定高さ（長さ）形成されている。 Further, the upper surface 18 that is the surface of the flange portion 16 on the head 12 side is abbreviated in a side view such that a portion directly below each ridge line 12A of the head 12 is a valley portion 18A and a space between the ridge lines 12A of the head portion 12 is a mountain portion 18B. It has a corrugated shape. And the upper surface 18 of this flange part 16 is made into the inclined surface from which the plate | board thickness becomes thick gradually toward the outer peripheral surface 12B of the head 12 from the outer periphery part 19, The plate | board thickness of the outer periphery part 19 is It is the same all around. Further, a lower surface (hereinafter referred to as “seat surface”) 17 that is a surface of the flange portion 16 on the main body portion 14 side is a flat surface, and a male screw portion 15 is formed at a predetermined height (length) on the lower side of the main body portion 14. ) Is formed.
ここで、フランジ付き六角ボルト１０における頭部１２及びフランジ部１６の寸法の一例をＭ１０サイズの場合で示す。まず、頭部１２は、平面視で対辺間の距離Ｗ１が、Ｗ１＝１４．０ｍｍ、対角間の距離Ｗ２が、Ｗ２＝１６．１６６ｍｍとされている。そして、フランジ部１６は、平面視でその直径Ｒが、Ｒ＝２１．５ｍｍとされ、外周縁部１９における最小板厚Ｄ１が、Ｄ１＝１．４ｍｍ、山部１８Ｂにおける最大板厚Ｄ２が、Ｄ２＝４．１ｍｍ、谷部１８Ａにおける最大板厚Ｄ３が、Ｄ３＝２．３７１ｍｍとされている。なお、谷部１８Ａにおけるフランジ部１６の板厚は、従来のフランジ部の板厚と同じにしてもよい。 Here, an example of the dimension of the head 12 and the flange part 16 in the hexagon bolt 10 with a flange is shown in the case of M10 size. First, the head 12 has a distance W1 between opposite sides W1 = 14.0 mm and a distance W2 between diagonals W2 = 16.666 mm in plan view. The flange portion 16 has a diameter R of R = 21.5 mm in a plan view, a minimum plate thickness D1 at the outer peripheral edge portion 19 is D1 = 1.4 mm, and a maximum plate thickness D2 at the peak portion 18B is D2 = 4.1 mm, and the maximum plate thickness D3 in the valley portion 18A is D3 = 2.371 mm. The plate thickness of the flange portion 16 in the valley portion 18A may be the same as the plate thickness of the conventional flange portion.
また、フランジ部１６の波型形状とされた上面１８の谷部１８Ａにおける底部（頭部１２との境界部分）は、側面視で曲率半径３．５ｍｍの曲面とされており、山部１８Ｂにおける頂部（頭部１２との境界部分）は、側面視で曲率半径０．９ｍｍの曲面とされている。更に、側面視で、山部１８Ｂにおける上面１８の傾斜角度θ１は、θ１＝３５．７５４°とされ、谷部１８Ａにおける上面１８の傾斜角度θ２は、θ２＝１９．９９９°とされている。なお、これらの寸法は一例であり、特に限定されるものではない。 Moreover, the bottom part (boundary part with the head part 12) in the trough part 18A of the upper surface 18 in the corrugated shape of the flange part 16 is a curved surface having a curvature radius of 3.5 mm in a side view, and in the peak part 18B. The top portion (the boundary portion with the head portion 12) is a curved surface having a curvature radius of 0.9 mm in a side view. Furthermore, when viewed from the side, the inclination angle θ1 of the upper surface 18 at the peak portion 18B is θ1 = 35.754 °, and the inclination angle θ2 of the upper surface 18 at the valley portion 18A is θ2 = 19.999 °. In addition, these dimensions are examples and are not particularly limited.
次に、本実施形態に係るフランジ付きファスナーの一例としてのフランジ付き六角ナット２０について説明する。図４（Ａ）はフランジ付き六角ナット２０の概略斜視図であり、図４（Ｂ）は同じく概略正面図である。そして、図５（Ａ）はフランジ付き六角ナット２０の概略平面図であり、図５（Ｂ）は図４（Ｂ）とは９０°異なる方向から見たときのフランジ付き六角ナット２０の概略正面図である。なお、説明の便宜上、各図において矢印ＵＰで示す方向を上方向とする。 Next, the flanged hex nut 20 as an example of the flanged fastener according to the present embodiment will be described. 4A is a schematic perspective view of the flanged hexagon nut 20, and FIG. 4B is a schematic front view of the same. 5A is a schematic plan view of the flanged hex nut 20, and FIG. 5B is a schematic front view of the flanged hex nut 20 when viewed from a direction different from 90 ° from FIG. 4B. FIG. For convenience of explanation, the direction indicated by the arrow UP in each figure is the upward direction.
図４、図５で示すように、このフランジ付き六角ナット２０は、六角筒状に形成され、その内周面に雌ネジ部２４が形成された本体部２２と、本体部２２の一端側である下端部に一体かつ同心軸に設けられた円板状のフランジ部２６と、を有している。なお、このフランジ部２６も、その外周縁部２９が、本体部２２の外周面２２Ｂに形成された各稜線２２Ａ部分よりも径方向外側へ所定長さ（後述する距離Ｓ２）張り出すような直径Ｒを有している。 As shown in FIGS. 4 and 5, the flanged hexagon nut 20 is formed in a hexagonal cylindrical shape, and a main body portion 22 having an internal thread portion 24 formed on the inner peripheral surface thereof, and one end side of the main body portion 22. And a disk-like flange portion 26 provided on a concentric shaft at a lower end portion. The flange portion 26 also has a diameter such that the outer peripheral edge portion 29 protrudes a predetermined length (distance S2 described later) radially outward from each ridge line 22A portion formed on the outer peripheral surface 22B of the main body portion 22. R is included.
また、フランジ部２６の上面２８（本体部２２の他端側である上端部を向く表面）は、本体部２２の各稜線２２Ａ直下が谷部２８Ａとなり、本体部２２の各稜線２２Ａ間が山部２８Ｂとなるような側面視略波型形状とされている。そして、このフランジ部２６の上面２８は、その外周縁部２９から本体部２２の外周面２２Ｂに向かって板厚が徐々に厚くなる傾斜面とされており、その外周縁部２９の板厚は全周において同一とされている。また、フランジ部２６の下面（以下「座面」という）２７は平面とされている。 Further, the upper surface 28 of the flange portion 26 (the surface facing the upper end portion which is the other end side of the main body portion 22) is a valley portion 28 </ b> A directly below each ridge line 22 </ b> A of the main body portion 22, and a mountain between each ridge line 22 </ b> A of the main body portion 22. It has a substantially wave shape in a side view so as to be the portion 28B. And the upper surface 28 of this flange part 26 is made into the inclined surface from which the plate | board thickness becomes thick gradually toward the outer peripheral surface 22B of the main-body part 22 from the outer peripheral part 29, The plate | board thickness of the outer peripheral part 29 is It is the same all around. The lower surface (hereinafter referred to as “seat surface”) 27 of the flange portion 26 is a flat surface.
ここで、フランジ付き六角ナット２０における本体部２２及びフランジ部２６の寸法の一例を示すが、各部の寸法は、例えば上記したＭ１０サイズのフランジ付き六角ボルト１０と同一にしても構わない。すなわち、本体部２２は、平面視で対辺間の距離Ｗ１が、Ｗ１＝１４．０ｍｍ、対角間の距離Ｗ２が、Ｗ２＝１６．１６６ｍｍとされている。 Here, although an example of the dimension of the main-body part 22 and the flange part 26 in the hexagon nut 20 with a flange is shown, you may make the dimension of each part the same as the hexagon bolt 10 with a flange mentioned above, for example. That is, the main body 22 has a distance W1 between opposite sides in a plan view of W1 = 14.0 mm and a distance W2 between diagonals W2 = 16.666 mm.
そして、フランジ部２６は、平面視でその直径Ｒが、Ｒ＝２１．５ｍｍとされ、外周縁部２９における最小板厚Ｄ１が、Ｄ１＝１．４ｍｍ、山部２８Ｂにおける最大板厚Ｄ２が、Ｄ２＝４．１ｍｍ、谷部２８Ａにおける最大板厚Ｄ３が、Ｄ３＝２．３７１ｍｍとされている。なお、谷部２８Ａにおけるフランジ部２６の板厚は、従来のフランジ部の板厚と同じにしてもよい。 The flange portion 26 has a diameter R of R = 21.5 mm in plan view, a minimum plate thickness D1 at the outer peripheral edge 29 is D1 = 1.4 mm, and a maximum plate thickness D2 at the peak portion 28B is D2 = 4.1 mm, and the maximum thickness D3 in the valley portion 28A is D3 = 2.371 mm. The plate thickness of the flange portion 26 in the valley portion 28A may be the same as the plate thickness of the conventional flange portion.
また、フランジ部２６の波型形状とされた上面２８の谷部２８Ａにおける底部（本体部２２との境界部分）は、側面視で曲率半径３．５ｍｍの曲面とされており、山部２８Ｂにおける頂部（本体部２２との境界部分）は、側面視で曲率半径０．９ｍｍの曲面とされている。更に、側面視で、山部２８Ｂにおける上面２８の傾斜角度θ１は、θ１＝３５．７５４°とされ、谷部２８Ａにおける上面２８の傾斜角度θ２は、θ２＝１９．９９９°とされている。なお、これらの寸法は一例であり、特に限定されるものではない。 Moreover, the bottom part (boundary part with the main-body part 22) in the trough part 28A of the upper surface 28 made into the waveform shape of the flange part 26 is made into the curved surface with a curvature radius of 3.5 mm by side view, The top portion (the boundary portion with the main body portion 22) is a curved surface having a curvature radius of 0.9 mm in a side view. Furthermore, when viewed from the side, the inclination angle θ1 of the upper surface 28 at the peak portion 28B is θ1 = 35.754 °, and the inclination angle θ2 of the upper surface 28 at the valley portion 28A is θ2 = 19.999 °. In addition, these dimensions are examples and are not particularly limited.
以上のような構成とされたフランジ付き六角ボルト１０及びフランジ付き六角ナット２０において、次にその締結時における作用について、主に図６、図７を基に説明する。図６は被締結部材３０、３２をフランジ付き六角ボルト１０及びフランジ付き六角ナット２０で締結したときのＦＥＭ応力分布を正面から示す説明図であり、図７は同じくフランジ部１６のＦＥＭ応力分布を平面で示す説明図である。 In the flanged hexagon bolt 10 and the flanged hexagon nut 20 configured as described above, the operation at the time of fastening will be described mainly with reference to FIGS. FIG. 6 is an explanatory view showing the FEM stress distribution from the front when the fastened members 30 and 32 are fastened by the flanged hexagon bolt 10 and the flanged hexagon nut 20, and FIG. 7 similarly shows the FEM stress distribution of the flange portion 16. It is explanatory drawing shown by a plane.
まず、図６で示すように、フランジ付き六角ボルト１０の本体部１４を被締結部材３０に形成された貫通孔３４に挿通し、更に被締結部材３２に形成された貫通孔３６に挿通する。そして、その被締結部材３２の貫通孔３６から突出した本体部１４の雄ネジ部１５に、フランジ付き六角ナット２０の雌ネジ部２４を螺合する。 First, as shown in FIG. 6, the main body portion 14 of the flanged hexagon bolt 10 is inserted into a through hole 34 formed in the fastened member 30, and further inserted into a through hole 36 formed in the fastened member 32. Then, the female screw portion 24 of the flanged hexagon nut 20 is screwed into the male screw portion 15 of the main body portion 14 protruding from the through hole 36 of the fastened member 32.
なお、このとき、フランジ付き六角ナット２０は、そのフランジ部２６が上側（被締結部材３２側）に来るように、図４、図５で示した上下方向を逆にしてフランジ付き六角ボルト１０の本体部１４に螺合される。そして、フランジ付き六角ボルト１０及びフランジ付き六角ナット２０の何れか一方を固定し、何れか他方を回転させて締結することにより、被締結部材３０、３２は、各フランジ部１６、２６間に狭持された状態で締め付け固定される。 At this time, the flanged hexagonal nut 20 of the flanged hexagonal bolt 10 is turned upside down as shown in FIGS. 4 and 5 so that the flange portion 26 is on the upper side (fastened member 32 side). Screwed onto the main body 14. Then, either one of the flanged hexagon bolt 10 and the flanged hexagon nut 20 is fixed, and the other is rotated and fastened, whereby the fastened members 30 and 32 are narrowed between the flange portions 16 and 26. It is fastened and fixed while being held.
ここで、図２（Ａ）で示すように、フランジ付き六角ボルト１０では、頭部１２の各稜線１２Ａ間における外周面１２Ｂからフランジ部１６の外周縁部１９までの径方向における距離Ｓ１（対辺部分）と、頭部１２の各稜線１２Ａ部分からフランジ部１６の外周縁部１９までの径方向における距離Ｓ２（対角部分）とは異なる（Ｓ１＞Ｓ２）。 Here, as shown in FIG. 2 (A), in the hexagon bolt 10 with flange, the radial distance S1 (opposite side) from the outer peripheral surface 12B to the outer peripheral edge portion 19 of the flange portion 16 between the ridge lines 12A of the head portion 12. Portion) and a distance S2 (diagonal portion) in the radial direction from each ridge line 12A portion of the head 12 to the outer peripheral edge portion 19 of the flange portion 16 (S1> S2).
また、図５（Ａ）で示すように、フランジ付き六角ナット２０でも、本体部２２の各稜線２２Ａ間における外周面２２Ｂからフランジ部２６の外周縁部２９までの径方向における距離Ｓ１（対辺部分）と、本体部２２の各稜線２２Ａ部分からフランジ部２６の外周縁部２９までの径方向における距離Ｓ２（対角部分）とは異なる（Ｓ１＞Ｓ２）。 Further, as shown in FIG. 5A, even in the flanged hexagon nut 20, the radial distance S 1 (the opposite side portion) from the outer peripheral surface 22 B to the outer peripheral edge portion 29 of the flange portion 26 between the ridge lines 22 A of the main body portion 22. ) And a distance S2 (diagonal portion) in the radial direction from each ridge line 22A portion of the main body portion 22 to the outer peripheral edge portion 29 of the flange portion 26 (S1> S2).
したがって、フランジ部１６と頭部１２とがつながるフランジ付け根部と、フランジ部２６と本体部２２とがつながるフランジ付け根部に作用する曲げモーメントは、対辺部分（距離Ｓ１部分）及び対角部分（距離Ｓ２部分）で異なり、各フランジ部１６、２６の曲げ変形量も、対辺部分及び対角部分で異なる。つまり、各フランジ部１６、２６のモーメント長は、対辺部分が対角部分よりも長いため、周方向において板厚が一定のフランジ部の場合には、対辺部分が対角部分に比べて変形しやすく、その変形量も大きい。 Therefore, the bending moment acting on the flange root portion where the flange portion 16 and the head portion 12 are connected and the flange root portion where the flange portion 26 and the main body portion 22 are connected is the opposite side portion (distance S1 portion) and the diagonal portion (distance). S2 part), and the bending deformation amount of each flange part 16, 26 also differs between the opposite side part and the diagonal part. That is, the moment lengths of the flange portions 16 and 26 are longer at the opposite side portions than at the diagonal portions. Therefore, when the flange portion has a constant thickness in the circumferential direction, the opposite side portions are deformed compared to the diagonal portions. Easy and large deformation.
例えば図８で示すように、フランジ部４６の板厚が周方向において一定の従来のフランジ付き六角ボルト４０の場合では、フランジ部４６に締結時の締付力や外力が負荷されたときには、そのフランジ部４６の対辺部分の曲げ剛性が、対角部分の曲げ剛性よりも低いため、フランジ部４６の対辺部分は反り上がるように変形してしまい、その座面４７の面圧が、対角部分である頭部４２の各稜線４２Ａ直下に集中してしまう（不均一に内当たりしてしまう）。 For example, as shown in FIG. 8, in the case of the conventional flanged hexagon bolt 40 in which the plate thickness of the flange portion 46 is constant in the circumferential direction, when the fastening force or external force at the time of fastening is loaded on the flange portion 46, Since the bending rigidity of the opposite side portion of the flange portion 46 is lower than the bending rigidity of the diagonal portion, the opposite side portion of the flange portion 46 is deformed so as to warp, and the surface pressure of the seating surface 47 is changed to the diagonal portion. Are concentrated just below each ridgeline 42A of the head 42 (is unevenly hitting).
そこで、本実施形態に係るフランジ付き六角ボルト１０及びフランジ付き六角ナット２０の各フランジ部１６、２６では、曲げモーメントが大きくなる対辺部分（各稜線１２Ａ、２２Ａ間部分）の板厚が、対角部分（各稜線１２Ａ、２２Ａ直下部分）の板厚よりも厚くなるように、その各上面１８、２８が、側面視略波型形状に形成されるとともに、各外周縁部１９、２９から各外周面１２Ｂ、２２Ｂに向かって徐々に板厚が厚くなるような傾斜面に形成されている。 Therefore, in the flange portions 16 and 26 of the flanged hexagon bolt 10 and the flanged hexagon nut 20 according to the present embodiment, the plate thickness of the opposite side portion (the portion between the ridge lines 12A and 22A) where the bending moment increases is diagonal. The upper surfaces 18 and 28 are formed in a substantially wave shape when viewed from the side so as to be thicker than the plate thickness of the portion (the portion immediately below the ridge lines 12A and 22A), and the outer periphery from the outer peripheral edge portions 19 and 29. It is formed in the inclined surface which plate | board thickness becomes thick gradually toward the surface 12B and 22B.
これによれば、各フランジ部１６、２６の変形し難い対角部分（距離Ｓ２部分）の曲げ剛性に、対辺部分（距離Ｓ１部分）の曲げ剛性を近づけることができる。つまり、このような構成にすることにより、各フランジ部１６、２６の座面１７、２７全体の曲げ剛性を周方向及び径方向において、ほぼ均一化することができる。 According to this, the bending stiffness of the opposite side portion (distance S1 portion) can be made closer to the bending stiffness of the diagonal portion (distance S2 portion) where the flange portions 16 and 26 are difficult to deform. That is, by adopting such a configuration, the bending rigidity of the entire bearing surfaces 17 and 27 of the flange portions 16 and 26 can be made substantially uniform in the circumferential direction and the radial direction.
したがって、図６、図７のＦＥＭ応力分布（色の濃い方が応力は高く、色の薄い方が応力は低い）で示すように、被締結部材３０、３２をフランジ付き六角ボルト１０とフランジ付き六角ナット２０で締め付けても（或いは各フランジ部１６、２６に外力が負荷されても）、各フランジ部１６、２６の変形量を抑制することができ、各フランジ部１６、２６の座面１７、２７の面圧を周方向及び径方向において、ほぼ均一にすることができる。 Therefore, as shown in the FEM stress distribution of FIGS. 6 and 7 (the darker the color is the higher the stress and the lighter the color is the lower the stress), the fastened members 30 and 32 are attached to the flanged hexagon bolt 10 and the flange. Even if it tightens with the hexagon nut 20 (or even if external force is loaded to each flange part 16 and 26), the deformation amount of each flange part 16 and 26 can be suppressed, and the seating surface 17 of each flange part 16 and 26 can be suppressed. , 27 can be made substantially uniform in the circumferential direction and the radial direction.
また、このように、各フランジ部１６、２６の座面１７、２７における面圧が、径方向において（軸心部から外周縁部１９、２９にかけて）ほぼ均一に掛かるようになると、各フランジ部１６、２６の座面１７、２７全体に応力を分散させることができるため、各フランジ部１６、２６全体の曲げ剛性を向上させることができる。 As described above, when the surface pressures on the bearing surfaces 17 and 27 of the flange portions 16 and 26 are applied substantially uniformly in the radial direction (from the axial center portion to the outer peripheral edge portions 19 and 29), the flange portions Since stress can be distributed over the entire seating surfaces 17 and 27 of the 16 and 26, the bending rigidity of the entire flange portions 16 and 26 can be improved.
したがって、被締結部材３０、３２に対するフランジ付き六角ボルト１０とフランジ付き六角ナット２０の結合剛性を向上させることができる。また、これにより、被締結部材３０、３２の限界面圧に対しても有利となり、フランジ付き六角ボルト１０及びフランジ付き六角ナット２０のゆるみ防止に対しても効果的となる。 Therefore, the coupling rigidity of the flanged hexagon bolt 10 and the flanged hexagon nut 20 with respect to the fastened members 30 and 32 can be improved. This is also advantageous for the limit surface pressure of the fastened members 30 and 32, and is effective for preventing loosening of the flanged hexagon bolt 10 and the flanged hexagon nut 20.
以上、説明したように、本実施形態に係るフランジ付きファスナー（六角ボルト１０及び六角ナット２０）によれば、締結時等におけるフランジ部１６、２６の変形量を抑制することができ、座面１７、２７の面圧をほぼ均一にすることができる。したがって、より高い結合剛性が得られるとともに、ゆるみ防止等に対しても有効となる。なお、本実施形態に係るフランジ付きファスナーは、図示のものに限定されるものではなく、本発明の要旨を逸脱しない範囲内において、適宜設計変更可能であることは言うまでもない。 As described above, according to the flanged fastener (the hexagon bolt 10 and the hexagon nut 20) according to the present embodiment, the deformation amount of the flange portions 16 and 26 at the time of fastening or the like can be suppressed, and the seat surface 17 , 27 can be made substantially uniform. Therefore, higher coupling rigidity can be obtained and effective for preventing loosening. The flanged fastener according to this embodiment is not limited to the illustrated one, and it goes without saying that the design can be changed as appropriate without departing from the scope of the present invention.
１０ フランジ付き六角ボルト（フランジ付きファスナー）
１２ 頭部
１２Ａ 稜線
１４ 本体部
１５ 雄ネジ部
１６ フランジ部
１７ 下面（座面）
１８ 上面（表面）
１８Ａ 谷部
１８Ｂ 山部
２０ フランジ付き六角ナット（フランジ付きファスナー）
２２ 本体部
２２Ａ 稜線
２４ 雌ネジ部
２６ フランジ部
２７ 下面（座面）
２８ 上面（表面）
２８Ａ 谷部
２８Ｂ 山部
３０ 被締結部材
３２ 被締結部材
10 Hexagon bolt with flange (Fastener with flange)
12 Head 12 A Ridge Line 14 Main Body 15 Male Thread 16 Flange 17 Bottom (Seat)
18 Top surface (surface)
18A Valley 18B Mountain 20 Flange hexagon nut (fastener with flange)
22 Main body 22A Ridge line 24 Female thread 26 Flange 27 Lower surface (seat surface)
28 Upper surface (surface)
28A Valley 28B Mountain 30 Fastened member 32 Fastened member
Claims (2)
前記頭部に一体に設けられるとともに、雄ネジ部が形成された本体部と、
前記頭部と前記本体部との間に一体に設けられ、該頭部側表面が、該頭部の外周面の稜線部分を谷部とし、該稜線間部分を山部とする側面視略波型形状とされたフランジ部と、
を有することを特徴とするフランジ付きファスナー。 A head shaped like a prism,
A body portion provided integrally with the head and formed with a male screw portion;
Side view rough wave provided integrally between the head and the main body, the head-side surface having a ridge line portion of the outer peripheral surface of the head as a trough portion and a portion between the ridge lines as a crest portion. A flange portion formed into a mold shape;
The fastener with a flange characterized by having.
前記本体部の一端側に一体に設けられ、該本体部の他端側を向く表面が、該本体部の外周面の稜線部分を谷部とし、該稜線間部分を山部とする側面視略波型形状とされたフランジ部と、
を有することを特徴とするフランジ付きファスナー。 A main body portion formed in a rectangular tube shape and having an internal thread portion on the inner peripheral surface;
The surface provided integrally with one end side of the main body portion and facing the other end side of the main body portion is a side view in which the ridge line portion of the outer peripheral surface of the main body portion is a valley portion and the portion between the ridge lines is a mountain portion. A corrugated flange,
The fastener with a flange characterized by having.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008070757A JP4919997B2 (en) | 2008-03-19 | 2008-03-19 | Fastener with flange |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008070757A JP4919997B2 (en) | 2008-03-19 | 2008-03-19 | Fastener with flange |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2009222218A true JP2009222218A (en) | 2009-10-01 |
| JP4919997B2 JP4919997B2 (en) | 2012-04-18 |
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ID=41239205
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| Application Number | Title | Priority Date | Filing Date |
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| JP2008070757A Active JP4919997B2 (en) | 2008-03-19 | 2008-03-19 | Fastener with flange |
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| Country | Link |
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| JP (1) | JP4919997B2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102374221A (en) * | 2011-08-05 | 2012-03-14 | 徐尚仁 | Anti-theft screw provided with eccentric inner circular hole in screw top |
| CN102865280A (en) * | 2011-07-08 | 2013-01-09 | 孙兴植 | Screw with magnetic body |
| JP2013545058A (en) * | 2010-12-06 | 2013-12-19 | エヨット ゲーエムベーハー ウント カンパニー カーゲー | Screw with head, shaft and conical corrugated flange |
| JPWO2015075823A1 (en) * | 2013-11-22 | 2017-03-16 | 株式会社サンノハシ | Bolt, nut and strain measurement system |
| JP2021502530A (en) * | 2017-11-10 | 2021-01-28 | ソフト ロボティクス， インコーポレイテッド | Fasteners with reduced bacterial retention points, sealing capacity, and component protection features |
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| JPS5886916A (en) * | 1981-11-18 | 1983-05-24 | Hitachi Ltd | Hydraulic rolling down device |
| JPS58146112A (en) * | 1982-02-25 | 1983-08-31 | Nec Corp | Direct current coupling amplifier using gallium arsenic fet |
| JPH0132370B2 (en) * | 1979-04-20 | 1989-06-30 | Mac Lean Fogg Co | |
| JP2001124040A (en) * | 1999-10-22 | 2001-05-08 | Hino Motors Ltd | Flange-equipped bolt and nut and fastener as combination of them |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JPH0132370B2 (en) * | 1979-04-20 | 1989-06-30 | Mac Lean Fogg Co | |
| JPS5886916A (en) * | 1981-11-18 | 1983-05-24 | Hitachi Ltd | Hydraulic rolling down device |
| JPS58146112A (en) * | 1982-02-25 | 1983-08-31 | Nec Corp | Direct current coupling amplifier using gallium arsenic fet |
| JP2001124040A (en) * | 1999-10-22 | 2001-05-08 | Hino Motors Ltd | Flange-equipped bolt and nut and fastener as combination of them |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2013545058A (en) * | 2010-12-06 | 2013-12-19 | エヨット ゲーエムベーハー ウント カンパニー カーゲー | Screw with head, shaft and conical corrugated flange |
| CN102865280A (en) * | 2011-07-08 | 2013-01-09 | 孙兴植 | Screw with magnetic body |
| CN102374221A (en) * | 2011-08-05 | 2012-03-14 | 徐尚仁 | Anti-theft screw provided with eccentric inner circular hole in screw top |
| JPWO2015075823A1 (en) * | 2013-11-22 | 2017-03-16 | 株式会社サンノハシ | Bolt, nut and strain measurement system |
| JP2021502530A (en) * | 2017-11-10 | 2021-01-28 | ソフト ロボティクス， インコーポレイテッド | Fasteners with reduced bacterial retention points, sealing capacity, and component protection features |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4919997B2 (en) | 2012-04-18 |
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