JP2020128774A - Plate fastener joint structure and elastic body for plate fastener - Google Patents

Plate fastener joint structure and elastic body for plate fastener Download PDF

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JP2020128774A
JP2020128774A JP2019021324A JP2019021324A JP2020128774A JP 2020128774 A JP2020128774 A JP 2020128774A JP 2019021324 A JP2019021324 A JP 2019021324A JP 2019021324 A JP2019021324 A JP 2019021324A JP 2020128774 A JP2020128774 A JP 2020128774A
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fastened
elastic body
dish
elastic
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JP7228399B2 (en
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拓史 杉山
Takushi Sugiyama
拓史 杉山
邦宏 森下
Kunihiro Morishita
邦宏 森下
良輔 橋爪
Ryosuke Hashizume
良輔 橋爪
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Abstract

To prevent damage of a plate fastener joint structure by reducing a stress which is generated with sliding even if the sliding occurs in a fastening member which is fastened by a plate fastener.SOLUTION: A plate fastener joint structure 1 comprises: a plate fastener 10 including a plate head 12 in an inverted truncated cone shape; multiple fastened members 21 and 22 to be fastened by the plate fastener 10; and an elastic body 30 disposed between a seating face 12B of the plate head 12 and a receiving face 21A which is formed in one fastened member 21 and receives the seating face 12B. The elastic body 30 includes a radially inner first region 31 and a radially outer second region 32. With regard to both the first region 31 and the second region 32, the rigidity in a thickness direction of the elastic body 30 is low in comparison with the plate fastener 10 and the fastened members 21 and 22 in which the receiving face 21A is formed. A maximum elastic deformation amount, in the thickness direction, that is set to the second region 32 is greater in comparison with a maximum elastic deformation amount, in the thickness direction, that is set to the first region 31.SELECTED DRAWING: Figure 1

Description

本発明は、皿頭を有するボルトやリベット等の皿ファスナ、および被締結部材を含む皿ファスナ継手構造と、皿ファスナ継手構造に用いられる弾性体とに関する。 The present invention relates to a dish fastener joint structure including a dish fastener such as a bolt and a rivet having a dish head, and a member to be fastened, and an elastic body used in the dish fastener joint structure.

逆円錐台状の皿頭を有する皿ボルトが種々の部材を締結するために用いられている。例えば、航空機の機体表面の空気抵抗を低減するため、機体の外皮（skin）に皿ボルトが用いられている。皿ボルトの皿頭のテーパ状の座面は、被締結部材に皿取り加工によりテーパ状に形成された受け面の内側に収められる。 Countersunk bolts with inverted frustoconical countersunk heads are used to fasten various members. For example, countersunk bolts are used on the skin of aircraft to reduce air resistance on the surface of the aircraft. The tapered seat surface of the countersunk head of the countersunk bolt is housed inside the receiving surface which is formed into a tapered shape on the member to be fastened by dishing.

特許文献１は、鋳造によるエクステリア部材を締結するための皿ボルト用テーパワッシャを開示する。特許文献１では、被締結部材の孔心のずれに対応するため、皿ボルトの軸部が挿入される孔よりも径が大きい孔に皿ボルトの皿頭を配置し、皿頭には、鍔部を有する円錐形のテーパワッシャを装着している。
この特許文献１では、被締結部材の円筒形の孔に皿頭の全体が配置されるため、皿頭はフリーの状態にある。テーパワッシャの鍔部は、鍔部よりも大きい被締結部材の凹部内に余裕をもって配置される。被締結部材に係合する鍔部と、他の被締結部材に係合するボルトの軸部とにより、被締結部材に締結力が作用する。 Patent Document 1 discloses a tapered washer for a countersunk bolt for fastening an exterior member by casting. In Patent Document 1, in order to cope with the deviation of the hole center of the member to be fastened, the countersunk head of the countersunk bolt is arranged in a hole having a diameter larger than the hole into which the shaft portion of the countersunk bolt is inserted, and the countersunk head is provided with a collar. A conical taper washer with a section is attached.
In Patent Document 1, since the entire dish head is arranged in the cylindrical hole of the member to be fastened, the dish head is in a free state. The flange portion of the taper washer is arranged with a margin in the recess of the member to be fastened, which is larger than the flange portion. A fastening force acts on the fastened member by the flange portion that engages the fastened member and the shaft portion of the bolt that engages with the other fastened member.

特許文献１の記載によれば、被締結部材の熱膨張が起こっても、皿ボルトに、被締結部材の貫通孔内で相対的な位置を変えるだけの余裕が与えられているから、皿ボルトは、無理な拘束に強いられて応力を集中させることなく、応力の負荷する方向へテーパワッシャの摺動と共に傾動する。 According to the description of Patent Document 1, even if thermal expansion of the member to be fastened occurs, the countersunk bolt is provided with a margin for changing the relative position in the through hole of the member to be fastened. Is tilted together with the sliding of the taper washer in the direction in which the stress is applied without forcing the stress to concentrate due to the excessive constraint.

特開平９−１７０６１７号公報JP, 9-170617, A

航空機等の輸送機をはじめ、種々の装置の部材に用いられているアルミニウム合金、あるいは炭素繊維等の強化繊維を含む繊維強化樹脂は、鉄や鋼等と比べると一般に強度が低い。
そのため、アルミニウム合金または繊維強化樹脂が用いられた被締結部材を皿ボルトにより締結する場合は、鉄や鋼等が用いられた被締結部材を皿ボルトにより締結する場合と同等の大きさの締結力を被締結部材に与えることが難しい。
そうすると、皿ボルトの軸方向の締結力に対して直交する方向の荷重により、皿ボルトの軸部と被締結部材の挿入孔の内周部との間に設定されているクリアランスの分だけ被締結部材が互いに滑る。孔心位置の公差に対応するため、また、皿ボルトの挿入や取り外しの作業を容易に行うために、皿ボルトの軸部と挿入孔の内周部との間にはクリアランスを設定することができる。
被締結部材の滑りに伴い、皿ボルトが挿入孔に対して傾き、軸部にせん断応力を発生させながら被締結部材に荷重を伝達する。さらに、ボルト皿頭の座面が突き当てられる被締結部材の受け面からの反力によって、皿頭に曲げ応力が生じる。 A fiber-reinforced resin containing a reinforcing fiber such as an aluminum alloy or carbon fiber, which is used as a member of various devices such as an aircraft or the like, is generally lower in strength than iron or steel.
Therefore, when fastening a fastened member made of aluminum alloy or fiber reinforced resin with flathead bolts, a fastening force equivalent to that of fastening a fastened member made of iron or steel with flathead bolts. Is difficult to give to the fastened member.
Then, due to the load in the direction orthogonal to the axial fastening force of the countersunk bolt, only the clearance set between the shaft portion of the countersunk bolt and the inner peripheral portion of the insertion hole of the fastened member is fastened. The parts slide on each other. To accommodate the tolerance of the hole center position and to facilitate the work of inserting and removing the countersunk bolt, a clearance should be set between the shaft of the countersunk bolt and the inner circumference of the insertion hole. it can.
With the slip of the member to be fastened, the countersunk bolt tilts with respect to the insertion hole, and the load is transmitted to the member to be fastened while generating shear stress in the shaft portion. Furthermore, a bending stress is generated in the countersunk head by the reaction force from the receiving surface of the member to be fastened against which the seat surface of the bolt head is abutted.

皿ボルトの皿頭の強度が被締結部材の強度よりも低い場合がある。その場合も、上記のように被締結部材にアルミニウム合金や繊維強化樹脂が用いられる場合と同様に、十分な締結力を被締結部材に与えることが難しい。そのため、軸部に対して直交する方向の荷重により被締結部材が互いに滑り、皿ボルトが挿入孔に対して傾き、受け面からの反力によりボルト皿頭に曲げ応力が生じる。 The strength of the countersunk head of the countersunk bolt may be lower than the strength of the member to be fastened. Also in that case, it is difficult to give a sufficient fastening force to the fastened member, as in the case where the fastened member is made of an aluminum alloy or a fiber reinforced resin as described above. Therefore, the tightened members slide with each other due to the load in the direction orthogonal to the shaft portion, the countersunk bolt tilts with respect to the insertion hole, and a bending stress is generated in the bolt countersunk head by the reaction force from the receiving surface.

特許文献１の皿ボルト継手構造とは異なり、テーパ状の座面が被締結部の受け面により拘束される皿ボルトに特有の事象として、図９に、皿ボルト８および被締結部材９１，９２の変形を誇張して示している。図９は応力解析例に基づく模式図である。
図９に示すように、被締結部材９１，９２の滑りおよび皿ボルト８の傾きに伴う受け面９１Ａからの反力により、皿頭８１に曲げ応力が生じる。図９に示す湾曲した矢印は、皿ボルト８の傾きによって皿頭８１が二点鎖線で示す形状から実線で示す形状に曲げ変形したことで生じる曲げ応力に関する曲げモーメントＭを示している。図９に示す例では、特に皿頭８１の首部８１Ａの曲げ応力が大きい。
特許文献１の構成によれば、被締結部材の滑りにより皿ボルトが傾く際に、皿頭が拘束されていないため皿頭の曲げ応力の増大を回避できる反面、軸部と直交する方向の荷重に対する接合強度には劣る。 Unlike the countersunk bolt joint structure of Patent Document 1, as a phenomenon unique to the countersunk bolt in which the tapered seat surface is constrained by the receiving surface of the portion to be fastened, FIG. 9 shows the flat head bolt 8 and the fastened members 91, 92. The variation is exaggerated. FIG. 9 is a schematic diagram based on a stress analysis example.
As shown in FIG. 9, a bending stress is generated in the countersunk head 81 due to the reaction force from the receiving surface 91A caused by the slippage of the members to be fastened 91, 92 and the inclination of the countersunk bolt 8. The curved arrow shown in FIG. 9 indicates the bending moment M relating to the bending stress generated by the dish head 81 being bent and deformed from the shape indicated by the two-dot chain line to the shape indicated by the solid line by the inclination of the countersunk bolt 8. In the example shown in FIG. 9, the bending stress of the neck portion 81A of the countersunk head 81 is particularly large.
According to the configuration of Patent Document 1, when the countersunk bolt tilts due to slippage of the member to be fastened, it is possible to avoid an increase in the bending stress of the countersunk head because the countersunk head is not restrained, but a load in the direction orthogonal to the shaft portion. Is inferior to the bonding strength.

以上より、本発明は、皿頭を有する皿ファスナにより締結された締結部材に滑りが生じるとしても、滑りに伴い発生する応力を低減して皿ファスナ継手構造の破損を防止することを目的とする。 In view of the above, the present invention has an object to prevent damage to the dish fastener joint structure by reducing the stress caused by the slip even if the fastening member fastened by the dish fastener having the dish head slips. ..

本発明の皿ファスナ継手構造は、軸部、および軸部から頂面に向かうにつれて径が拡大した逆円錐台状の皿頭を含む皿ファスナと、皿ファスナにより締結される複数の被締結部材と、皿頭の座面、および一の被締結部材に形成されて座面を受ける受け面の間に配置される弾性体と、を備える。
そして、本発明は、弾性体が、径方向内側の第１領域と、径方向外側の第２領域と、を含み、第１領域および第２領域のいずれも、皿ファスナ、および受け面が形成される被締結部材と比べて弾性体の肉厚方向の剛性が低く、第１領域に設定された肉厚方向への最大弾性変形量と比べて、第２領域に設定された肉厚方向への最大弾性変形量が大きいことを特徴とする。 The dish fastener joint structure of the present invention includes a dish fastener including a shaft portion and an inverted frustoconical dish head whose diameter increases from the shaft portion toward the top surface, and a plurality of fastened members fastened by the dish fastener. A seat surface of the countersunk head, and an elastic body which is formed between the one receiving member and a receiving surface which receives the seat surface.
Further, in the present invention, the elastic body includes a first region on the inner side in the radial direction and a second region on the outer side in the radial direction, and the dish fastener and the receiving surface are formed in both the first region and the second region. The rigidity of the elastic body in the thickness direction is lower than that of the fastened member, and compared with the maximum elastic deformation amount in the thickness direction set in the first region, in the thickness direction set in the second region. Is characterized by a large maximum amount of elastic deformation.

「ファスナ」は、ボルトやリベット等、複数の部材間の締結に用いられる部材を包含する。「皿ファスナ」は、逆円錐台状の皿頭を含むファスナを意味するものとする。 "Fastener" includes members used for fastening between a plurality of members such as bolts and rivets. "Dish fastener" shall mean a fastener that includes an inverted frustoconical dish head.

本発明の皿ファスナの継手構造において、皿ファスナは、被締結部材に対する着脱が可能なボルトであることが好ましい。 In the joint structure of the dish fastener of the present invention, it is preferable that the dish fastener is a bolt that can be attached to and detached from a member to be fastened.

本発明の皿ファスナの継手構造において、皿ファスナが挿入される被締結部材の挿入孔の軸線に対して座面がなす角度をθ１、軸線に対して受け面がなす角度をθ２、とすると、θ１＜θ２であることが好ましい。 In the joint structure of the dish fastener of the present invention, when the angle formed by the seat surface with respect to the axis of the insertion hole of the fastening member into which the dish fastener is inserted is θ1 and the angle formed by the receiving surface with respect to the axis is θ2, It is preferable that θ1<θ2.

本発明の皿ファスナの継手構造において、無負荷の状態における第１領域の肉厚をｔ１、無負荷の状態における第２領域の肉厚をｔ２、とすると、ｔ１＜ｔ２であることが好ましい。 In the joint structure of the dish fastener according to the present invention, when the wall thickness of the first region in the unloaded state is t1 and the wall thickness of the second region in the unloaded state is t2, it is preferable that t1<t2.

本発明の皿ファスナ継手構造において、第１領域の剛性をｋ１、第２領域の剛性をｋ２、とすると、ｋ１＞ｋ２であることが好ましい。 In the dish fastener joint structure of the present invention, when the rigidity of the first region is k1 and the rigidity of the second region is k2, it is preferable that k1>k2.

本発明の皿ファスナの継手構造において、弾性体は、肉厚方向の剛性が異なる第１弾性部および第２弾性部を備え、第１弾性部の剛性ｋａに対して、第２弾性部の剛性ｋｂが小さく、第１弾性部および第２弾性部の体積比率に基づいて、ｋ１＞ｋ２であることが好ましい。 In the joint structure of the dish fastener of the present invention, the elastic body includes the first elastic portion and the second elastic portion having different rigidity in the thickness direction, and the rigidity of the second elastic portion is different from the rigidity ka of the first elastic portion. It is preferable that kb is small and k1>k2 based on the volume ratio of the first elastic portion and the second elastic portion.

本発明の皿ファスナ継手構造は、軸部と、軸部が挿入される被締結部材の挿入孔の内周部との間に配置され、軸部および被締結部材と比べて肉厚方向の剛性が低い第２の弾性体を備えることが好ましい。 The dish fastener joint structure of the present invention is arranged between the shaft portion and the inner peripheral portion of the insertion hole of the member to be fastened into which the shaft portion is inserted, and has rigidity in the thickness direction as compared with the shaft portion and the member to be fastened. It is preferable to provide a second elastic body having a low

本発明の皿ファスナの継手構造において、弾性体は、頂面を覆うカバー領域を含むことが好ましい。 In the joint structure of the dish fastener of the present invention, it is preferable that the elastic body includes a cover region that covers the top surface.

本発明の皿ファスナの継手構造において、被締結部材は、航空機の機体を構成する部材であることが好ましい。 In the joint structure of the dish fastener of the present invention, it is preferable that the member to be fastened is a member that constitutes a body of the aircraft.

また、本発明は、皿ファスナの皿頭の座面、および皿ファスナにより締結される複数の被締結部材の一つに形成されて座面を受ける受け面の間に配置される弾性体であって、径方向内側の第１領域と、径方向外側の第２領域と、を含み、第１領域および第２領域のいずれも、皿ファスナ、および受け面が形成される被締結部材と比べて肉厚方向の剛性が低く、第１領域に設定された肉厚方向への最大弾性変形量と比べて、第２領域に設定された肉厚方向への最大弾性変形量が大きいことを特徴とする。 Further, the present invention is an elastic body disposed between a seat surface of a dish head of a dish fastener and a receiving surface formed on one of a plurality of members to be fastened which are fastened by the dish fastener and receiving the seat surface. And a first region on the inner side in the radial direction and a second region on the outer side in the radial direction, both of the first region and the second region being compared with the fastening member on which the dish fastener and the receiving surface are formed. The rigidity in the thickness direction is low, and the maximum elastic deformation amount in the thickness direction set in the second region is larger than the maximum elastic deformation amount in the thickness region set in the first region. To do.

本発明の皿ファスナ継手構造および皿ファスナ用弾性体によれば、被締結部材の滑りが生じたとしても、滑りに伴う皿頭の傾きの変位が弾性体の弾性変形により吸収されることで皿頭の曲げ変形が緩和されるため、皿頭の首部等に発生する応力を低減することができる。したがって、皿ファスナ継手構造の疲労破壊等の破損を未然に防ぐことができる。 According to the dish fastener joint structure and the elastic body for a dish fastener of the present invention, even if slippage of the member to be fastened occurs, the displacement of the inclination of the dish head due to the slippage is absorbed by the elastic deformation of the elastic body, so that the dish Since the bending deformation of the head is alleviated, the stress generated in the neck of the dish head and the like can be reduced. Therefore, damage such as fatigue failure of the dish fastener joint structure can be prevented in advance.

（ａ）および（ｂ）は、本発明の第１実施形態に係る皿ファスナ継手構造を示す断面図である。（ｂ）は、（ａ）の部分拡大模式図である。(A) And (b) is sectional drawing which shows the dish fastener joint structure which concerns on 1st Embodiment of this invention. (B) is a partially enlarged schematic view of (a). （ａ）は、皿ファスナおよび弾性体の締結前の状態を示す断面図である。（ｂ）は、被締結部材および弾性体の締結前の状態を示す断面図である。(A) is sectional drawing which shows the state before fastening of a dish fastener and an elastic body. (B) is sectional drawing which shows the state before fastening of a to-be-fastened member and an elastic body. 被締結部材の滑りに伴い皿ファスナが傾いた状態を模式的に示す図である。It is a figure which shows typically the state which the dish fastener inclined with the sliding of a to-be-fastened member. 弾性体の変形例を示す断面図である。It is sectional drawing which shows the modification of an elastic body. 第２実施形態に係る皿ファスナ継手構造を示す模式図である。It is a schematic diagram which shows the dish fastener joint structure which concerns on 2nd Embodiment. 第３実施形態に係る皿ファスナ継手構造を示す模式図である。It is a schematic diagram which shows the dish fastener joint structure which concerns on 3rd Embodiment. 第１実施形態および第２実施形態の組み合わせによる第４実施形態の皿ファスナ継手構造を示す模式図である。It is a schematic diagram which shows the dish fastener joint structure of 4th Embodiment by the combination of 1st Embodiment and 2nd Embodiment. （ａ）および（ｂ）はいずれも、皿ファスナの軸部の周りに配置される第２の弾性体を備えた第５実施形態を示す図である。(A) And (b) is a figure which shows 5th Embodiment provided with the 2nd elastic body arrange|positioned around the shaft part of a dish fastener. 従来の皿ファスナ継手構造を示す模式図である。It is a schematic diagram which shows the conventional dish fastener joint structure.

以下、添付図面を参照しながら、本発明の一実施形態について説明する。
以下に説明する皿ファスナ継手構造１〜４のいずれも、後述するように、皿ボルト１０の座面１２Ｂと被締結部材２１の受け面２１Ａとの間に配置される弾性体の構成要件に主要な特徴を有する。 An embodiment of the present invention will be described below with reference to the accompanying drawings.
As will be described later, all of the dish fastener joint structures 1 to 4 described below mainly relate to the constituent requirements of the elastic body arranged between the seat surface 12B of the dish bolt 10 and the receiving surface 21A of the fastened member 21. It has various characteristics.

〔共通の構成要素〕
まず、図１（ａ）および（ｂ）に示す第１実施形態の皿ファスナ継手構造１を例に取り、本発明の全ての実施形態に共通する構成要素を説明する。
図１（ａ）および（ｂ）に示すように、皿ファスナ継手構造１は、軸部１１および逆円錐台状の皿頭１２を有した皿ファスナとしての皿ボルト１０と、皿ボルト１０に設けられるナット１８と、皿ボルト１０およびナット１８により締結される複数の被締結部材２１，２２と、弾性体３０とを備えている。 [Common components]
First, taking the dish fastener joint structure 1 of the first embodiment shown in FIGS. 1A and 1B as an example, the components common to all the embodiments of the present invention will be described.
As shown in FIGS. 1( a) and 1 (b ), a dish fastener joint structure 1 is provided with a dish bolt 10 as a dish fastener having a shaft portion 11 and an inverted frustoconical dish head 12, and a dish bolt 10. A nut 18, a plurality of tightened members 21, 22 fastened by the countersunk bolt 10 and the nut 18, and an elastic body 30.

本実施形態の皿ファスナ継手構造１は、航空機の機体を構成する部材に適用することができる。
その場合において、被締結部材２１，２２は、航空機の胴体や主翼等の部材である。こうした被締結部材２１，２２は、複数の皿ボルト１０を用いて複数の箇所で締結されている。
例えば、被締結部材２１は、主翼のスキンであり、被締結部材２２は、スキンを裏側から支持するストリンガまたはリブである。あるいは、被締結部材２１が胴体のスキンであり、被締結部材２２がスキンを裏側から支持するフレームであってもよい。
同一の皿ボルト１０により締結される被締結部材（２１，２２）の数は、２つに限らず、３つ以上であってもよい。 The dish fastener joint structure 1 of the present embodiment can be applied to a member forming a body of an aircraft.
In that case, the fastened members 21 and 22 are members such as a fuselage and a main wing of an aircraft. The fastened members 21, 22 are fastened at a plurality of locations using a plurality of flat head bolts 10.
For example, the fastened member 21 is a skin of the main wing, and the fastened member 22 is a stringer or a rib that supports the skin from the back side. Alternatively, the fastened member 21 may be a body skin and the fastened member 22 may be a frame that supports the skin from the back side.
The number of members to be fastened (21, 22) fastened by the same flat head bolt 10 is not limited to two, and may be three or more.

（被締結部材）
被締結部材２１，２２は、鉄や鋼等と比べて比強度の大きい材料、例えば、アルミニウム合金または繊維強化樹脂を用いて形成されることが好ましい。繊維強化樹脂は、炭素繊維、ガラス繊維、アラミド繊維等の強化繊維からなる繊維基材と、繊維基材に含侵したマトリクス樹脂とを含む。 (Fastened member)
The members to be fastened 21 and 22 are preferably formed using a material having a larger specific strength than iron, steel, or the like, for example, an aluminum alloy or a fiber reinforced resin. The fiber reinforced resin includes a fiber base material made of reinforcing fibers such as carbon fiber, glass fiber, and aramid fiber, and a matrix resin impregnated in the fiber base material.

被締結部材２１，２２のうち、機体の外表面に配置される一の被締結部材２１には、皿ボルト１０の皿頭１２の座面１２Ｂを受ける受け面２１Ａが形成されている。受け面２１Ａの内側の開口の径は、皿頭１２の高さに応じた深さのテーパ状のザグリ加工（皿取り加工）により、ボルト挿入孔２０に向かうにつれて次第に縮小している。
受け面２１Ａには、弾性体３０を介して座面１２Ｂが押圧される。 A receiving surface 21A that receives a seat surface 12B of the countersunk head 12 of the flat head bolt 10 is formed on one of the fastened members 21, 22 that is arranged on the outer surface of the machine body. The diameter of the opening inside the receiving surface 21</b>A is gradually reduced toward the bolt insertion hole 20 by the tapered counterbore processing (dish removal processing) having a depth corresponding to the height of the dish head 12.
The seat surface 12B is pressed against the receiving surface 21A via the elastic body 30.

被締結部材２１，２２に亘り貫通したボルト挿入孔２０に皿ボルト１０の軸部１１が挿入されると、皿ボルト１０の皿頭１２は、被締結部材２１の表面２１Ｂから窪んだ受け面２１Ａの内側に収められる。このとき、皿頭１２は、被締結部材２１の表面２１Ｂから突出しない。そのため、機体の外表面に露出する部材の締結に皿ボルト１０を使用することで、機体の空気抵抗を低減することができる。 When the shaft portion 11 of the flat head bolt 10 is inserted into the bolt insertion hole 20 that penetrates through the fastened members 21, 22, the countersunk head 12 of the flat bolt 10 has a receiving surface 21A recessed from the surface 21B of the fastened member 21. Is housed inside. At this time, the countersunk head 12 does not protrude from the surface 21B of the member 21 to be fastened. Therefore, by using the flat head bolt 10 to fasten the member exposed on the outer surface of the machine body, the air resistance of the machine body can be reduced.

ボルト挿入孔２０は、被締結部材２１に形成された挿入孔２０１と、被締結部材２２に形成された挿入孔２０２とからなる。このボルト挿入孔２０の断面中心を通る軸線をＡと称する。
ボルト挿入孔２０の内周部と軸部１１の外周部との間には、所定の寸法のクリアランスＣが設定されている。クリアランスＣの寸法は、皿ボルト１０をボルト挿入孔２０に挿入したりボルト挿入孔２０から皿ボルト１０を取り外したりする作業の容易性と、寸法や組立の公差による挿入孔２０１，２０２の断面中心の位置の公差を考慮して設定されている。 The bolt insertion hole 20 includes an insertion hole 201 formed in the member 21 to be fastened and an insertion hole 202 formed in the member 22 to be fastened. An axis line passing through the center of the cross section of the bolt insertion hole 20 is referred to as A.
A clearance C having a predetermined dimension is set between the inner peripheral portion of the bolt insertion hole 20 and the outer peripheral portion of the shaft portion 11. The size of the clearance C is determined by the ease of the work of inserting the countersunk bolt 10 into the bolt insertion hole 20 and the removal of the countersunk bolt 10 from the bolt insertion hole 20, and the center of the cross section of the insertion holes 201, 202 due to the size and assembly tolerance. It is set in consideration of the position tolerance.

クリアランスＣが設定されているため、ボルト挿入孔２０の内周部と軸部１１の外周部との間には空隙２４が存在する。被締結部材２１，２２は、外力の軸線Ａに対して直交する方向に作用する成分である荷重Ｆ１（図３）により、被締結部材２１，２２間の摩擦力に抗して、空隙２４の分だけ、滑りつつ相対的に変位する。
滑りを引き起こす荷重Ｆ１は、例えば機外と機内の圧力差により機体のスキンに作用する張力である。または、荷重Ｆ１は、例えば主翼に生じる空力的荷重により主翼が曲がり、主翼スキンに作用する張力である。
ボルト挿入孔２０の内周部と軸部１１の外周部との間は、空隙２４であって、例えば鋼材から形成された筒体等、被締結部材２１，２２の滑りに抵抗する部材は配置されていない。 Since the clearance C is set, there is a gap 24 between the inner peripheral portion of the bolt insertion hole 20 and the outer peripheral portion of the shaft portion 11. The fastened members 21, 22 resist the frictional force between the fastened members 21, 22 by the load F1 (FIG. 3), which is a component acting in a direction orthogonal to the axis A of the external force, to prevent the voids 24 from moving. It is relatively displaced while sliding.
The load F1 that causes slippage is, for example, the tension that acts on the skin of the machine body due to the pressure difference between the outside and the inside of the machine. Alternatively, the load F1 is, for example, a tension that acts on the main wing skin due to the main wing bending due to an aerodynamic load generated on the main wing.
Between the inner peripheral portion of the bolt insertion hole 20 and the outer peripheral portion of the shaft portion 11, there is a gap 24, and a member that resists slippage of the fastened members 21, 22 such as a tubular body formed of steel is disposed. It has not been.

（皿ボルト）
さて、皿ボルト１０は、雄ねじ１１Ａが形成された軸部１１（shank）と、頂面１２Ａに向かうにつれて軸部１１の径に対して径が次第に拡大した逆円錐台状の皿頭１２（flush head）とを備えている。
皿ボルト１０により被締結部材２１，２２が締結された状態において、皿ボルト１０の軸線は、基本的にはボルト挿入孔２０の軸線Ａと一致している。
本実施形態の雄ねじ１１Ａは、軸部１１における先端部１１Ｂ側の所定範囲に亘り形成されているが、雄ねじ１１Ａが軸部１１の全長に亘り形成されていてもよい。 (Counter bolt)
Now, the countersunk bolt 10 includes a shank 11 having a male screw 11A and an inverted truncated cone-shaped countersunk head 12 (flush) whose diameter gradually increases with respect to the diameter of the shank 11 toward the top surface 12A. head).
In the state in which the tightened members 21, 22 are fastened by the countersunk bolt 10, the axis of the countersunk bolt 10 basically coincides with the axis A of the bolt insertion hole 20.
The male screw 11A of the present embodiment is formed over a predetermined range on the tip portion 11B side of the shaft portion 11, but the male screw 11A may be formed over the entire length of the shaft portion 11.

皿頭１２は、機体の外表面に位置する頂面１２Ａと、頂面１２Ａから軸部１１までテーパ状に形成された座面１２Ｂとを備えている。本実施形態の頂面１２Ａは、軸線Ａと直交する面に沿って平坦に形成されている。頂面１２Ａが周りの表面２１Ｂと面一であることが好ましい。
皿頭１２には、締結時に工具が挿入される溝１２Ｄ（recess）が頂面１２Ａから窪んで形成されている。
図１（ｂ）や、図２、図３等において溝１２Ｄの図示を省略する。 The countersunk head 12 includes a top surface 12A located on the outer surface of the machine body, and a seat surface 12B formed in a tapered shape from the top surface 12A to the shaft portion 11. The top surface 12A of this embodiment is formed flat along a surface orthogonal to the axis A. The top surface 12A is preferably flush with the surrounding surface 21B.
A groove 12D (recess) into which a tool is inserted at the time of fastening is formed in the plate head 12 so as to be recessed from the top surface 12A.
The illustration of the groove 12D is omitted in FIG. 1B, FIG. 2, FIG.

皿ボルト１０が、被締結部材２１，２２のボルト挿入孔２０に挿入されると、受け面２１Ａに皿頭１２の座面１２Ｂが配置されて、軸部１１の雄ねじ１１Ａが被締結部材２２から機内側に突出する。軸部１１の雄ねじ１１Ａに、ナット１８の図示しない雌ねじを係合させると、図１（ａ）に白抜き矢印で示すように、皿ボルト１０の軸線Ａの方向に締結力Ｆ０が作用する。締結力Ｆ０により被締結部材２１と被締結部材２２とが締結される。 When the countersunk bolt 10 is inserted into the bolt insertion holes 20 of the fastened members 21, 22, the seat surface 12B of the countersunk head 12 is arranged on the receiving surface 21A, and the male screw 11A of the shaft portion 11 moves from the fastened member 22. Project inside the machine. When a male screw 11A of the shaft portion 11 is engaged with a female screw (not shown) of the nut 18, a fastening force F0 acts in the direction of the axis A of the flat head bolt 10 as shown by a white arrow in FIG. The fastened member F and the fastened member 22 are fastened by the fastening force F0.

なお、ナット１８の端面１８Ａと被締結部材２２の機内側の面２２Ａとの間に、図示しないワッシャを挟むことができる。このワッシャは、金属材料、樹脂材料、あるいはゴム材料等から構成することができる。
また、ナット１８および軸部１１の先端部１１Ｂを覆う図示しないキャップを被締結部材２２の機内側に設けることができる。 A washer (not shown) may be sandwiched between the end surface 18A of the nut 18 and the inboard side surface 22A of the fastened member 22. This washer can be made of a metal material, a resin material, a rubber material, or the like.
Further, a cap (not shown) that covers the nut 18 and the tip portion 11B of the shaft portion 11 can be provided inside the fastening target member 22.

皿ボルト１０は、被締結部材２１，２２の締結に必要な剛性に加え、必要に応じて耐食性、耐熱性、耐候性等を備えた適宜な材料から形成することができる。典型的には、鉄、ニッケル、チタン、これらの合金等の金属材料を用いて皿ボルト１０を構成することができる。アルミニウム合金や繊維強化樹脂が用いられた被締結部材２１，２２の剛性に対して、皿ボルト１０の剛性は一般に高いが、これに限られない。皿ボルト１０に樹脂材料を用いることも許容される。
ナット１８も、皿ボルト１０と同様の材料を用いて構成することができる。 The countersunk bolt 10 can be formed from an appropriate material having corrosion resistance, heat resistance, weather resistance, and the like, in addition to the rigidity required for fastening the members to be fastened 21, 22 as required. Typically, the countersunk bolt 10 can be made of a metal material such as iron, nickel, titanium, or an alloy thereof. Although the rigidity of the countersunk bolt 10 is generally higher than the rigidity of the fastened members 21, 22 made of aluminum alloy or fiber reinforced resin, the present invention is not limited to this. It is also permissible to use a resin material for the countersunk bolt 10.
The nut 18 can also be made of the same material as the countersunk bolt 10.

被締結部材２１，２２の剛性、および皿ボルト１０やナット１８の剛性を考慮した所定の締め付けトルクが皿ボルト１０に与えられる。継手として確実に接合可能なトルクを与えることにより、座面１２Ｂが受け面２１Ａに対して押圧され、ナット１８が被締結部材２２の機内側の面２２Ａに対して押圧されることで締結による接合強度が確保される。皿頭１２およびナット１８からの押圧による被締結部材２１，２２の変形を弾性域に留めることが可能なトルクを限度として、皿ボルト１０に適切な締め付けトルクを与えることができる。 A predetermined tightening torque in consideration of the rigidity of the fastened members 21, 22 and the rigidity of the flat head bolt 10 and the nut 18 is applied to the flat head bolt 10. The seating surface 12B is pressed against the receiving surface 21A and the nut 18 is pressed against the machine-side surface 22A of the fastened member 22 by applying a torque capable of reliably joining as a joint, thereby joining by fastening. The strength is secured. Appropriate tightening torque can be applied to the countersunk bolt 10 within the limit of the torque that can keep the deformation of the fastened members 21, 22 due to the pressure from the countersunk head 12 and the nut 18 in the elastic region.

アルミニウム合金や繊維強化樹脂が用いられた被締結部材２１，２２の強度（面圧強度）が鉄等と比べて低いため、皿ボルト１０により締結された被締結部材２１，２２間に、鉄等を用いる場合と比べて低い締結力Ｆ０しか与えることができない。それゆえ、アルミニウム合金や繊維強化樹脂が用いられた被締結部材２１，２２間の摩擦力は、鉄等が被締結部材に用いられた場合よりも低くなる。しかも、軸部１１の外周部とボルト挿入孔２０の内周部との間にはクリアランスＣに相当する空隙２４が存在している。そのため、例えば、振動や、空力荷重等による外的な荷重Ｆ１により被締結部材２１，２２が互いに滑り易い。 The strength (contact pressure strength) of the fastened members 21, 22 made of aluminum alloy or fiber reinforced resin is lower than that of iron or the like, so that the fastened members 21, 22 fastened by the countersunk bolt 10 are made of iron, etc. Only a lower fastening force F0 can be applied as compared with the case of using. Therefore, the frictional force between the fastened members 21, 22 made of aluminum alloy or fiber reinforced resin is lower than that when iron or the like is used as the fastened member. Moreover, a gap 24 corresponding to the clearance C exists between the outer peripheral portion of the shaft portion 11 and the inner peripheral portion of the bolt insertion hole 20. Therefore, for example, the fastened members 21 and 22 are likely to slip with each other due to an external load F1 due to vibration or an aerodynamic load.

（弾性体）
次に、弾性体３０について説明する。弾性体３０は、ゴム等の弾性材料から環状に形成されて座面１２Ｂと受け面２１Ａとの間に配置される部材である。弾性体３０の外径も内径も、軸部１１から頂面１２Ａに向かうにつれて次第に拡大している。
弾性体３０のほぼ無負荷の状態が図２（ａ）および（ｂ）に示されている。 (Elastic body)
Next, the elastic body 30 will be described. The elastic body 30 is a member formed in an annular shape from an elastic material such as rubber and arranged between the seat surface 12B and the receiving surface 21A. Both the outer diameter and the inner diameter of the elastic body 30 gradually increase from the shaft portion 11 toward the top surface 12A.
The substantially unloaded state of the elastic body 30 is shown in FIGS. 2(a) and 2(b).

弾性体３０は、後述するように皿頭１２の曲げ変位を吸収して応力低減を図るため、皿ボルト１０の皿頭１２の座面１２Ｂと被締結部材２１の受け面２１Ａとの間のほぼ全域に亘り配置されることが好ましい。但し、これは必須ではなく、弾性体３０が、皿頭１２の首部１２Ｃの近傍および頂面１２Ａの近傍の一方または両方において配置されないことも許容される。 The elastic body 30 absorbs the bending displacement of the countersunk head 12 to reduce the stress as described later, and therefore, the elastic body 30 is disposed between the seat surface 12B of the countersunk head 12 of the countersunk bolt 10 and the receiving surface 21A of the fastened member 21. It is preferable to be arranged over the entire area. However, this is not essential, and it is acceptable that the elastic body 30 is not arranged in one or both of the vicinity of the neck portion 12C of the countersunk head 12 and the vicinity of the top surface 12A.

弾性体３０は、皿ボルト１０および被締結部材２１の両者に対して、少なくとも肉厚方向の剛性が低い。
弾性体３０は、締結時に座面１２Ｂと受け面２１Ａとの間に押圧されることで弾性変形する。加えて、弾性体３０は、被締結部材２１，２２が互いに滑ることで皿ボルト１０が傾くことによっても、座面１２Ｂと受け面２１Ａとの間に押圧されて弾性変形する。 The elastic body 30 has low rigidity at least in the thickness direction with respect to both the flat head bolt 10 and the member 21 to be fastened.
The elastic body 30 is elastically deformed by being pressed between the seat surface 12B and the receiving surface 21A during fastening. In addition, the elastic body 30 is elastically deformed by being pressed between the seat surface 12B and the receiving surface 21A even when the countersunk bolts 21 and 22 slide with each other and the countersunk bolt 10 tilts.

弾性体３０により座面１２Ｂと受け面２１Ａとの間が封止される。座面１２Ｂと受け面２１Ａとの間が封止されることで、機体表面の隙間の存在による空気抵抗を低減することができる。 The elastic body 30 seals between the seating surface 12B and the receiving surface 21A. By sealing the space between the seat surface 12B and the receiving surface 21A, it is possible to reduce air resistance due to the existence of a gap on the surface of the machine body.

座面１２Ｂと受け面２１Ａとの間がより十分に封止されるように、ポリサルファイド系合成ゴム等からなるシーラントを用いることができる。シーラントは、流動性を有する状態で座面１２Ｂや受け面２１Ａに塗布、あるいは座面１２Ｂと受け面２１Ａとの間に充填され、固化することで、座面１２Ｂと受け面２１Ａとの間を封止する。 A sealant made of polysulfide-based synthetic rubber or the like can be used so that the space between the seat surface 12B and the receiving surface 21A can be more sufficiently sealed. The sealant is applied to the seating surface 12B or the receiving surface 21A in a fluid state, or is filled between the seating surface 12B and the receiving surface 21A and solidified, so that the space between the seating surface 12B and the receiving surface 21A is increased. Seal.

弾性体３０は、径方向内側（軸部１１側）の第１領域３１と、径方向外側（頂面１２Ａ側）の第２領域３２とを含む。
第１領域３１の剛性と、第２領域３２の剛性のいずれも、皿ボルト１０および被締結部材２１の両者に対して剛性が低い。ここでは、弾性体３０の肉厚方向の剛性を比較している。
第１領域３１および第２領域３２は、想定される最大の締結力Ｆ０と、被締結部材２１，２２の滑りに伴い弾性体３０を押圧する想定の最大荷重とが作用したとしても弾性域内で弾性変形し、弾性変形した状態から除荷により復元する。これを実現するための肉厚および剛性が第１領域３１および第２領域３２のそれぞれに確保されている。 The elastic body 30 includes a first region 31 on the radially inner side (shaft 11 side) and a second region 32 on the radially outer side (top surface 12A side).
Both the rigidity of the first region 31 and the rigidity of the second region 32 are low with respect to both the flat head bolt 10 and the fastened member 21. Here, the rigidity of the elastic body 30 in the thickness direction is compared.
The first region 31 and the second region 32 are within the elastic range even if the assumed maximum fastening force F0 and the assumed maximum load that presses the elastic body 30 due to the sliding of the fastened members 21 and 22 act. It is elastically deformed and restored from the elastically deformed state by unloading. The thickness and rigidity for realizing this are ensured in each of the first region 31 and the second region 32.

第１領域３１と第２領域３２とのそれぞれには、肉厚および剛性に基づいて、弾性体３０の肉厚方向の適切な弾性変形量が設定されている。
ここで、負荷が加えられていない無負荷時から、弾性限まで肉厚方向に最大限に弾性変形した時までの弾性変形量を「最大弾性変形量」と定義するものとする。
第１領域３１の最大弾性変形量δ１と、第２領域３２の最大弾性変形量δ２とは相違している。 In each of the first region 31 and the second region 32, an appropriate amount of elastic deformation in the thickness direction of the elastic body 30 is set based on the thickness and rigidity.
Here, the amount of elastic deformation from when no load is applied to when elastically deformed to the maximum in the thickness direction up to the elastic limit is defined as “maximum elastic deformation amount”.
The maximum elastic deformation amount δ1 of the first region 31 and the maximum elastic deformation amount δ2 of the second region 32 are different.

荷重Ｆ１が入力されることで被締結部材２１，２２が滑った際に、弾性体３０の第１領域３１および第２領域３２の弾性変形により皿頭１２の曲げ応力が低減される。 When the fastened members 21, 22 slip due to the input of the load F1, elastic deformation of the first region 31 and the second region 32 of the elastic body 30 reduces the bending stress of the dish head 12.

弾性体３０は、皿ファスナ継手構造１を備える機械や装置に対応した使用条件等に応じて、ゴム材料をはじめとする適宜な材料を用いて構成することができる。
例えば、スチレンブタジエンゴム、イソプレンゴム、ブタジエンゴム、クロロプレンゴム、アクリロニトリルブタジエンゴム、イソブチエンイソプレンゴム、エチレンプロピレンゴム、エチレンプロピレンジエンゴム、ウレタンゴム、シリコーンゴム、フッ素ゴム等のゴム材料から、弾性体３０に使用する材料を選定することができる。 The elastic body 30 can be configured by using an appropriate material such as a rubber material in accordance with a use condition or the like corresponding to a machine or an apparatus including the dish fastener joint structure 1.
For example, rubber material such as styrene butadiene rubber, isoprene rubber, butadiene rubber, chloroprene rubber, acrylonitrile butadiene rubber, isobutene isoprene rubber, ethylene propylene rubber, ethylene propylene diene rubber, urethane rubber, silicone rubber, fluororubber, etc. The material used for 30 can be selected.

弾性体３０は、必ずしもゴム材料には限定されない。ポリテトラフルオロエチレン、ポリアミド等の樹脂系材料を弾性体３０に用いることもできる。 The elastic body 30 is not necessarily limited to the rubber material. A resin material such as polytetrafluoroethylene or polyamide may be used for the elastic body 30.

被締結部材２１，２２および皿ボルト１０の剛性と比べて低い剛性が得られる限りにおいて、金属材料を弾性体３０に用いることもできる。例えば、皿ボルト１０がチタン合金から構成され、被締結部材２１がアルミニウム合金から構成されている場合は、アルミニウム合金と比べて縦弾性係数等の弾性率が小さい金属材料、例えば、マグネシウム、りん、錫、これらの合金等から弾性体３０を構成することができる。
あるいは、中実の構造で考えると被締結部材２１のアルミニウム合金と比べて弾性率が大きい金属材料であるとしても、当該金属材料からなる金網状、メッシュ状の素材を用いて弾性体３０の形状に成形することにより、弾性体３０に皿ボルト１０および被締結部材２１，２２の両者よりも低い剛性を与えるようにしてもよい。 A metal material may be used for the elastic body 30 as long as a rigidity lower than that of the fastened members 21, 22 and the countersunk bolt 10 is obtained. For example, when the countersunk bolt 10 is made of a titanium alloy and the fastened member 21 is made of an aluminum alloy, a metal material having a smaller elastic modulus such as a longitudinal elastic modulus than that of the aluminum alloy, for example, magnesium, phosphorus, The elastic body 30 can be made of tin, an alloy thereof, or the like.
Alternatively, considering a solid structure, even if the elastic material 30 is a metal material having a higher elastic modulus than the aluminum alloy of the fastened member 21, the shape of the elastic body 30 is formed by using a metal mesh-like or mesh-like material made of the metal material. The elastic body 30 may be formed with a lower rigidity than the countersunk bolt 10 and the fastened members 21, 22.

適用対象が航空機である場合は、耐候性や剛性等の必要な特性を備えたゴム材料を弾性体３０に用いるとよい。例えば、シリコーンゴム、エチレンプロピレンジエンゴム等が好適である。 When the application target is an aircraft, a rubber material having necessary properties such as weather resistance and rigidity may be used for the elastic body 30. For example, silicone rubber and ethylene propylene diene rubber are suitable.

以下に述べるように、本発明の各実施形態では、弾性体３０の第１、第２領域３１，３２にそれぞれ適切な最大弾性変形量を実現する方法が異なる。 As described below, the respective embodiments of the present invention differ in the method for realizing the appropriate maximum elastic deformation amounts in the first and second regions 31 and 32 of the elastic body 30, respectively.

〔第１実施形態〕
図１〜図３に示す第１実施形態では、後述する第２実施形態および第３実施形態とは異なり、皿ボルト１０の座面１２Ｂのテーパの角度と、被締結部材２１の受け面２１Ａのテーパの角度とが相違している。
座面１２Ｂおよび受け面２１Ａのいずれも、軸部１１側から頂面１２Ａに向かうにつれて径が拡大しているように傾斜しているが、傾斜の角度（θ１，θ２）が相違している。
つまり、図１（ｂ）に示すように、座面１２Ｂが軸線Ａに対してなす角度をθ１、受け面２１Ａが軸線Ａに対してなす角度をθ２とすると、θ１＜θ２である。 [First Embodiment]
In the first embodiment shown in FIGS. 1 to 3, unlike the second and third embodiments described later, the taper angle of the seat surface 12B of the flat head bolt 10 and the receiving surface 21A of the fastened member 21 are different. The taper angle is different.
Both the seating surface 12B and the receiving surface 21A are inclined so that the diameter increases from the shaft portion 11 side toward the top surface 12A, but the inclination angles (θ1, θ2) are different.
That is, as shown in FIG. 1B, if the angle formed by the bearing surface 12B with respect to the axis A is θ1 and the angle formed by the receiving surface 21A with respect to the axis A is θ2, then θ1<θ2.

これに伴い、座面１２Ｂと受け面２１Ａとの間の間隙の寸法が、径方向内側（軸部１１側）と、径方向外側（頂面１２Ａ側）とでは相違することとなる。
そのため、第１実施形態では、弾性体３０に負荷が加えられていない無負荷の状態において、径方向内側の第１領域３１と径方向外側の第２領域３２とに異なる肉厚を与えている。座面１２Ｂと受け面２１Ａとの間に配置される弾性体３０の肉厚は、径方向の内側から外側に向かうにつれて次第に増加している。このため、弾性体３０の最大弾性変形量が、径方向の内側から外側に向かうにつれて増加している。 Along with this, the size of the gap between the seat surface 12B and the receiving surface 21A is different between the radially inner side (shaft portion 11 side) and the radially outer side (top surface 12A side).
Therefore, in the first embodiment, in the unloaded state where no load is applied to the elastic body 30, different thicknesses are given to the first region 31 on the radially inner side and the second region 32 on the radially outer side. .. The thickness of the elastic body 30 arranged between the seat surface 12B and the receiving surface 21A gradually increases from the radially inner side toward the outer side. Therefore, the maximum elastic deformation amount of the elastic body 30 increases from the inner side to the outer side in the radial direction.

以上より、図１（ｂ）に示すように、第１領域３１の肉厚をｔ１、第２領域３２の肉厚をｔ２とすると、ｔ１＜ｔ２である。無負荷時の肉厚ｔ１，ｔ２も、同じくｔ１＜ｔ２である。無負荷時の弾性体３０の状態は、図２（ａ）および（ｂ）に示す状態とほぼ同様である。 From the above, as shown in FIG. 1B, when the thickness of the first region 31 is t1 and the thickness of the second region 32 is t2, t1<t2. The thicknesses t1 and t2 under no load are also t1<t2. The state of the elastic body 30 under no load is almost the same as the state shown in FIGS. 2(a) and 2(b).

第１実施形態の弾性体３０によれば、肉厚方向における第１領域３１の剛性と第２領域３２の剛性とが同一であっても、肉厚ｔ１，ｔ２の違いにより、第２領域３２に得られる最大弾性変形量δ２が第１領域３１に得られる最大弾性変形量δ１よりも大きい。
第１実施形態では、第１領域３１および第２領域３２を含む弾性体３０の全体を単一の材料から構成することができる。 According to the elastic body 30 of the first embodiment, even if the rigidity of the first region 31 and the rigidity of the second region 32 in the thickness direction are the same, the second region 32 is different due to the difference in the thicknesses t1 and t2. The maximum elastic deformation amount δ2 obtained in the above is larger than the maximum elastic deformation amount δ1 obtained in the first region 31.
In the first embodiment, the entire elastic body 30 including the first region 31 and the second region 32 can be made of a single material.

無負荷の状態において（図２（ａ）および（ｂ）参照）、弾性体３０の外周部３０Ａは、軸線Ａに対して受け面２１Ａの角度θ２（図１（ｂ））とほぼ同じ角度をなしている。弾性体３０の内周部３０Ｂは、軸線Ａに対して座面１２Ｂの角度θ１（図１（ｂ））とほぼ同じ角度をなしている。
角度θ２とは異なる傾斜角度を外周部３０Ａに与えたり、角度θ１とは異なる傾斜角度を内周部３０Ｂに与えたりすることができる。内周部３０Ｂの傾斜角度は、第１、第２領域３１，３２のうち特に第２領域３２に与えたい肉厚に応じて適宜に定めることができる。 In the unloaded state (see FIGS. 2(a) and 2(b)), the outer peripheral portion 30A of the elastic body 30 forms an angle approximately equal to the angle θ2 (FIG. 1(b)) of the receiving surface 21A with respect to the axis A. I am doing it. The inner peripheral portion 30B of the elastic body 30 makes an angle with the axis A that is substantially the same as the angle θ1 (FIG. 1B) of the seat surface 12B.
An inclination angle different from the angle θ2 can be given to the outer peripheral portion 30A, and an inclination angle different from the angle θ1 can be given to the inner peripheral portion 30B. The inclination angle of the inner peripheral portion 30B can be appropriately determined according to the wall thickness to be given to the second region 32 among the first and second regions 31 and 32.

締結前において、弾性体３０を図２（ａ）に示すように皿ボルト１０の皿頭１２に装着することができる。皿ボルト１０の軸部１１の径や皿頭１２の径に対して弾性体３０の内周部の径を小さく設定することで、弾性体３０の弾性力により、弾性体３０を皿ボルト１０に保持することができる。そうすると、皿ボルト１０および弾性体３０を一体に取り扱えるため締結作業が容易である。 Before fastening, the elastic body 30 can be attached to the countersunk head 12 of the countersunk bolt 10 as shown in FIG. By setting the diameter of the inner peripheral portion of the elastic body 30 smaller than the diameter of the shaft portion 11 of the flat head bolt 10 and the diameter of the flat head 12, the elastic force of the elastic body 30 causes the elastic body 30 to move to the flat head bolt 10. Can be held. Then, since the countersunk bolt 10 and the elastic body 30 can be handled integrally, the fastening work is easy.

弾性体３０は必ずしも皿ボルト１０に装着される必要はない。図２（ｂ）に示すように、締結時に弾性体３０を受け面２１Ａに配置し、弾性体３０の内端３０Ｃの内側の孔に、皿ボルト１０の軸部１１を通してもよい。 The elastic body 30 does not necessarily need to be attached to the flat head bolt 10. As shown in FIG. 2B, the elastic body 30 may be disposed on the receiving surface 21A at the time of fastening, and the shaft portion 11 of the flat head bolt 10 may be inserted into the hole inside the inner end 30C of the elastic body 30.

図２（ａ）または（ｂ）に示す例では、無負荷の状態において、弾性体３０の頂部３０Ｄが皿頭１２の頂面１２Ａおよび被締結部材２１の表面２１Ｂに対して低く設定されている。その例では、締結時に頂部３０Ｄが座面１２Ｂと受け面２１Ａとの間から押し上げられることで、弾性体３０の頂部３０Ｄが、皿頭１２の頂面１２Ａと同様に、被締結部材２１の表面２１Ｂと面一に配置される。
但し、弾性体３０の頂部３０Ｄが必ずしも表面２１Ｂと面一に配置される必要はない。頂部３０Ｄが表面２１Ｂよりも下方に位置していたとしても、例えばシーラントを頂部３０Ｄに塗布することで、機体表面の平滑化を図ることができる。 In the example shown in FIG. 2A or 2B, the top portion 30D of the elastic body 30 is set lower than the top surface 12A of the countersunk head 12 and the surface 21B of the fastened member 21 in the unloaded state. .. In that example, the top portion 30D is pushed up from between the seat surface 12B and the receiving surface 21A during fastening, so that the top portion 30D of the elastic body 30 is the same as the top surface 12A of the countersunk head 12 on the surface of the fastened member 21. 21B and the same plane.
However, the top portion 30D of the elastic body 30 does not necessarily have to be flush with the surface 21B. Even if the top portion 30D is located below the surface 21B, the surface of the machine body can be smoothed by applying, for example, a sealant to the top portion 30D.

図２（ａ）および（ｂ）のいずれの状態を経るにしても、皿ボルト１０をボルト挿入孔２０に挿入し、皿ボルト１０およびナット１８の一方を他方に対して軸回りに回転させて、雄ねじ１１Ａとナット１８の雌ねじとが係合することで、図１（ａ）および（ｂ）に示すように被締結部材２１，２２が締結される。
締結時には、被締結部材２１，２２に対して皿ボルト１０が軸部１１の軸方向に変位することで、弾性体３０が受け面２１Ａと座面１２Ｂとの間に押圧されて弾性変形する。このとき弾性体３０は、径方向内側から外側までの全体に亘り、肉厚方向に一定の変形量により弾性変形するとみなすことができる。皿ボルト１０の締結力Ｆ０により、弾性体３０が弾性変形した状態に維持される。 2(a) and 2(b), the countersunk bolt 10 is inserted into the bolt insertion hole 20 and one of the countersunk bolt 10 and the nut 18 is rotated around the axis with respect to the other. By engaging the male screw 11A and the female screw of the nut 18, the fastened members 21, 22 are fastened as shown in FIGS. 1(a) and 1(b).
At the time of fastening, the countersunk bolt 10 is displaced in the axial direction of the shaft portion 11 with respect to the fastened members 21, 22, so that the elastic body 30 is pressed between the receiving surface 21A and the seat surface 12B and elastically deforms. At this time, it can be considered that the elastic body 30 elastically deforms in the wall thickness direction by a constant deformation amount over the whole from the radially inner side to the outer side. The fastening force F0 of the flat head bolt 10 keeps the elastic body 30 elastically deformed.

締結により弾性変形しても、第１領域３１，３２のそれぞれの弾性変形量は、最大弾性変形量には至らない。つまり、第１領域３１および第２領域３２は、さらに荷重が加えられることで肉厚方向に弾性変形可能である。
なお、弾性体３０によって座面１２Ｂと受け面２１Ａとの間を封止することが必要ない場合は、締結完了時に弾性体３０が無負荷の状態であっても許容される。 Even if elastically deformed by fastening, the elastic deformation amount of each of the first regions 31 and 32 does not reach the maximum elastic deformation amount. That is, the first region 31 and the second region 32 can be elastically deformed in the thickness direction by further applying a load.
If it is not necessary to seal between the seating surface 12B and the receiving surface 21A with the elastic body 30, even if the elastic body 30 is unloaded at the time of completion of fastening, it is permissible.

図３および図９を参照し、弾性体３０による主な作用を説明する。以下に述べる作用は、第２実施形態以降の弾性体にも該当する。
図３に示すように、空力荷重等の外的な荷重Ｆ１により、軸部１１の外周部とボルト挿入孔２０の内周部との間の空隙２４の分、被締結部材２１，２２が互いに滑る。それに伴い、皿ボルト１０がボルト挿入孔２０の軸線Ａに対して傾く。
そうすると、軸部１１にせん断応力を発生させながら荷重Ｆ１が軸部１１から被締結部材２１，２２に伝達されるとともに、皿頭１２の座面１２Ｂが突き当てられる受け面２１Ａからの反力が生じる。このとき、受け面２１Ａからの反力によって皿頭１２に生じる曲げ変形が、弾性体３０の肉厚方向への弾性変形により緩和される。 Main actions of the elastic body 30 will be described with reference to FIGS. 3 and 9. The operation described below also applies to the elastic body of the second and subsequent embodiments.
As shown in FIG. 3, due to an external load F1 such as an aerodynamic load, the fastened members 21, 22 are separated from each other by the space 24 between the outer peripheral portion of the shaft portion 11 and the inner peripheral portion of the bolt insertion hole 20. slide. Along with this, the flat head bolt 10 tilts with respect to the axis A of the bolt insertion hole 20.
Then, the load F1 is transmitted from the shaft portion 11 to the fastened members 21, 22 while generating shear stress in the shaft portion 11, and the reaction force from the receiving surface 21A against which the seat surface 12B of the countersunk head 12 is abutted. Occurs. At this time, the bending deformation generated in the countersunk head 12 by the reaction force from the receiving surface 21A is alleviated by the elastic deformation of the elastic body 30 in the thickness direction.

図９に示すように、弾性体３０が存在していない場合は、被締結部材９１，９２の滑りに伴い皿ボルト８が傾くことで、受け面９１Ａからの反力により皿頭８１に曲げ変形が生じるとしても、本実施形態によれば、図３に示すように弾性体３０により皿頭１２の曲げ変形を緩和して応力を低減することができる。換言すれば、皿頭１２が変形する代わりに弾性体３０が弾性変形することで、皿頭１２の曲げ応力が低減される。 As shown in FIG. 9, when the elastic body 30 is not present, the countersunk bolts 9 are tilted as the fastened members 91 and 92 slide, and the countersunk force from the receiving surface 91A causes the countersunk head 81 to bend and deform. Even if this occurs, according to the present embodiment, as shown in FIG. 3, the elastic body 30 can reduce the bending deformation of the dish head 12 to reduce the stress. In other words, the elastic stress of the elastic body 30 is elastically deformed instead of the dish head 12, whereby the bending stress of the dish head 12 is reduced.

図３に示す例では、軸線Ａに対して皿頭１２が図３の右側にシフトするように皿ボルト１０が全体的に傾いており、曲げ変形していない皿頭１２が弾性体３０を介して受け面２１Ａに押し付けられている。そのため、図１（ｂ）に示す状態から、図３の右側では弾性体３０が圧縮され、図３の左側では弾性体３０が伸長する。 In the example shown in FIG. 3, the countersunk bolt 10 is entirely inclined with respect to the axis A so that the countersunk head 12 shifts to the right side in FIG. And is pressed against the receiving surface 21A. Therefore, from the state shown in FIG. 1B, the elastic body 30 is compressed on the right side of FIG. 3, and the elastic body 30 is extended on the left side of FIG.

図９に、曲げ変形していない皿頭８１の二点鎖線で示す形状と実線で示す形状とから理解されるように、本実施形態の皿頭１２が曲げ変形するとしたならば、皿頭１２の変位は、首部１２Ｃから皿頭１２の径方向外側へ向かうほど大きい。弾性体３０の第１領域３１および第２領域３２のそれぞれの最大弾性変形量は、皿頭１２の曲げ変位量の分布に対応している。つまり、皿頭１２の曲げ変位量が相対的に大きい径方向外側の第２領域３２における最大弾性変形量δ２が、径方向内側の第１領域３１の最大弾性変形量δ１と比べて大きい。 As can be understood from FIG. 9 showing the shape of the dish head 81 which is not bent and deformed by the two-dot chain line and the shape of which is shown by the solid line, if the plate head 12 of the present embodiment is bent and deformed, the plate head 12 The displacement becomes larger from the neck portion 12C toward the outer side in the radial direction of the countersunk head 12. The maximum elastic deformation amount of each of the first region 31 and the second region 32 of the elastic body 30 corresponds to the distribution of the bending displacement amount of the dish head 12. That is, the maximum elastic deformation amount δ2 in the radially outer second region 32 where the bending displacement amount of the countersunk head 12 is relatively large is larger than the maximum elastic deformation amount δ1 in the radially inner first region 31.

そのため、皿頭１２において相対的に大きい径方向外側の曲げ変位が、第１領域３１と比べてより大きい変形量を弾性域に残していた第２領域３２の弾性変形により吸収されることとなる。そうすると、皿頭１２の曲げ変形を弾性体３０により第１領域３１から第２領域３２までの全体に亘り緩和することができる。その結果、皿頭１２の曲げ応力を低減し、特に首部１２Ｃへの応力の集中を避けることができる。 Therefore, the relatively large radial outward bending displacement of the countersunk head 12 is absorbed by the elastic deformation of the second region 32 which leaves a larger amount of deformation in the elastic region than that of the first region 31. .. Then, the bending deformation of the countersunk head 12 can be alleviated by the elastic body 30 from the first region 31 to the second region 32. As a result, the bending stress of the countersunk head 12 can be reduced, and the concentration of stress particularly on the neck 12C can be avoided.

被締結部材２１および皿ボルト１０のそれぞれの剛性によっては、弾性体３０が用いられていない場合で、被締結部材２１，２２の滑りに伴い皿ボルト１０が傾いた際に、皿頭１２が曲げ変形しないで、受け面２１Ａからの反力を上回る力で被締結部材２１に押し付けられることがあり得る。そうした場合でも、弾性体３０を受け面２１Ａと座面１２Ｂとの間に介在させる。そうすることで、皿ボルト１０が傾いた際に、受け面２１Ａに対して相対的に大きい皿頭１２の径方向外側の変位が、弾性体３０の第２領域３２の弾性変形により吸収されるので、被締結部材２１の応力を低減して受け面２１Ａの圧縮破壊を防ぐことができる。 Depending on the rigidity of each of the fastened member 21 and the flat head bolt 10, when the elastic body 30 is not used and the flat head bolt 10 is tilted as the fastened members 21 and 22 slide, the flat head 12 bends. It may be pressed against the member to be fastened 21 with a force exceeding the reaction force from the receiving surface 21A without being deformed. Even in such a case, the elastic body 30 is interposed between the receiving surface 21A and the seat surface 12B. By doing so, when the countersunk bolt 10 is tilted, the radially outer displacement of the countersunk head 12 that is relatively large with respect to the receiving surface 21A is absorbed by the elastic deformation of the second region 32 of the elastic body 30. Therefore, the stress of the member to be fastened 21 can be reduced and the compressive fracture of the receiving surface 21A can be prevented.

以上より、弾性体３０を備えた皿ファスナ継手構造１によれば、弾性体３０の径方向外側の第２領域３２に、径方向内側の第１領域３１の最大弾性変形量δ１と比べて大きな最大弾性変形量δ２設定されているため、被締結部材２１，２２の滑りと、それに伴う皿ボルト１０の傾きが生じるとしても、皿ファスナ継手構造１に生じる応力を低減することができる。
仮に、本実施形態とは逆に、皿頭１２の曲げ変位が小さい径方向内側の第１領域３１に、第２領域３２の最大弾性変形量よりも大きな最大弾性変形量が設定されていたとすれば、応力低減の効果は本実施形態と比べて小さい。 As described above, according to the dish fastener joint structure 1 including the elastic body 30, the maximum elastic deformation amount δ1 in the second area 32 on the radially outer side of the elastic body 30 is larger than that in the first area 31 on the radially inner side. Since the maximum elastic deformation amount δ2 is set, even if slippage of the members to be fastened 21 and 22 and inclination of the countersunk bolt 10 accompanying it occur, the stress generated in the countersunk fastener joint structure 1 can be reduced.
Contrary to the present embodiment, it is assumed that the maximum elastic deformation amount larger than the maximum elastic deformation amount of the second region 32 is set in the radially inner first region 31 where the bending displacement of the countersunk head 12 is small. For example, the effect of reducing stress is smaller than that of the present embodiment.

以上で説明したように、本実施形態の皿ファスナ継手構造１によれば、弾性体３０の作用により、皿ファスナ継手構造１に発生する応力を低減することができる。そのため、曲げ応力による皿ボルト１０の破損や、皿頭１２が突き当てられる被締結部材２１の圧縮破壊を防いで、皿ファスナ継手構造１を健全な状態に維持することができる。
被締結部材２１，２２の滑りは、皿ファスナ継手構造１を備える装置等の振動や、航空機の場合で言えば飛行時の圧力変動に伴う繰り返しの荷重Ｆ１により生じうる。弾性体３０の作用により、皿ファスナ継手構造１の疲労破壊を防ぐことができる。 As described above, according to the dish fastener joint structure 1 of the present embodiment, the action of the elastic body 30 can reduce the stress generated in the dish fastener joint structure 1. Therefore, damage to the countersunk bolt 10 due to bending stress and compression failure of the fastened member 21 against which the countersunk head 12 abuts can be prevented, and the countersunk fastener joint structure 1 can be maintained in a sound state.
The slippage of the fastened members 21, 22 may be caused by vibration of a device or the like including the dish fastener coupling structure 1 or, in the case of an aircraft, repeated load F1 accompanying pressure fluctuation during flight. Due to the action of the elastic body 30, it is possible to prevent fatigue breakage of the dish fastener joint structure 1.

弾性体３０の第１領域３１および第２領域３２のそれぞれの肉厚ｔ１，ｔ２は、必ずしもｔ１＜ｔ２の関係にある必要はない。
但し、ｔ１＜ｔ２の場合と同様に、第１領域３１に設定された最大弾性変形量δ１と比べて第２領域３２に設定された最大弾性変形量δ２が大きく、かつ、締結後に第１、第２領域３１，３２においてさらなる弾性変形が可能であることが要件である。 The wall thicknesses t1 and t2 of the first region 31 and the second region 32 of the elastic body 30 do not necessarily have to satisfy the relationship of t1<t2.
However, as in the case of t1<t2, the maximum elastic deformation amount δ2 set in the second region 32 is larger than the maximum elastic deformation amount δ1 set in the first region 31, and the first and It is a requirement that further elastic deformation is possible in the second regions 31 and 32.

〔弾性体の変形例〕
図４に示す弾性体３５は、第１領域３１および第２領域３２に加え、皿頭１２の頂面１２Ａを覆うカバー領域３３を備えている。カバー領域３３により頂面１２Ａが全域に亘り覆われている。この弾性体３５の内端３０Ｃの内側に皿頭１２を挿入することで、弾性体３５が皿頭１２の周りに装着されている。弾性体３５の装着された皿ボルト１０に対してナット１８を回転させることで、被締結部材２１，２２を締結することができる。カバー領域３３の周りにはシーラントＳを充填している。
なお、図１（ａ）に示すように工具挿入用の溝１２Ｄが皿頭１２に形成されている場合は、カバー領域３３における溝１２Ｄに対応する箇所を欠損させることにより、締結前に弾性体３５を皿頭１２に装着しつつ、溝１２Ｄへの工具の挿入により締結作業を行うことができる。溝１２Ｄに対応する欠損箇所にシーラント等を充填すると、頂面１２Ａが全域に亘り覆われる。 [Modification of elastic body]
The elastic body 35 shown in FIG. 4 includes a cover region 33 that covers the top surface 12A of the countersunk head 12 in addition to the first region 31 and the second region 32. The top surface 12A is entirely covered by the cover region 33. By inserting the countersunk head 12 into the inner end 30C of the elastic body 35, the elastic body 35 is mounted around the countersunk head 12. By rotating the nut 18 with respect to the flat head bolt 10 to which the elastic body 35 is mounted, the members to be fastened 21 and 22 can be fastened. A sealant S is filled around the cover area 33.
When the groove 12D for tool insertion is formed in the countersunk head 12 as shown in FIG. 1(a), the portion corresponding to the groove 12D in the cover region 33 is cut off so that the elastic body is not tightened before fastening. It is possible to perform the fastening work by inserting the tool into the groove 12D while mounting 35 on the countersunk head 12. When the sealant or the like is filled in the defective portion corresponding to the groove 12D, the top surface 12A is entirely covered.

弾性体３５は、典型的には絶縁性のゴム材料や樹脂材料を用いて構成される。絶縁性の弾性体３５により皿頭１２を覆うことで、導電性の皿頭１２が被締結部材２１の表面に露出するのを避けて、被雷時に皿ボルト１０に過大な電流が流れることを防止することができる。特に、被締結部材２１が、金属材料と比べると導電率が小さい繊維強化樹脂から形成されており、皿ボルト１０に雷の電流が集中し易い場合に弾性体３５を採用すると、シーラント等を用いる場合と比べ、皿ボルト１０に安定して絶縁性を与えることができる。 The elastic body 35 is typically made of an insulating rubber material or resin material. By covering the countersunk head 12 with the insulating elastic body 35, it is possible to prevent the conductive countersunk head 12 from being exposed on the surface of the fastened member 21, and to prevent an excessive current from flowing through the countersunk bolt 10 during a lightning strike. Can be prevented. In particular, when the member 21 to be fastened is formed of a fiber reinforced resin having a conductivity lower than that of a metal material, and when the lightning current is likely to concentrate on the flat head bolt 10, if the elastic body 35 is adopted, a sealant or the like is used. Compared with the case, the countersunk bolt 10 can be stably provided with insulating properties.

弾性体３５は、第１実施形態の弾性体３０と同様に、第１領域３１よりも第２領域３２が厚肉に構成されているが、これに限られない。
第２実施形態以降における弾性体にカバー領域３３を与えることもできる。 Like the elastic body 30 of the first embodiment, the elastic body 35 is configured such that the second region 32 is thicker than the first region 31, but is not limited to this.
The cover region 33 may be provided to the elastic body in the second and subsequent embodiments.

〔第２実施形態〕
次に、図５を参照し、第２実施形態に係る皿ファスナ継手構造２を説明する。
以下、第１実施形態とは異なる事項を中心に説明する。第１実施形態と同様の構成要素には同じ符号を付している。
皿ファスナ継手構造２は、受け面２１Ａと座面１２Ｂとの間に配置される弾性体４０を備えている。第２実施形態では、軸線Ａに対する座面１２Ｂの角度θ１と、軸線Ａに対する受け面２１Ａの角度θ２とが同一である。なお、座面１２Ｂや受け面２１Ａの寸法形状や組み付けの公差により角度θ１と角度θ２とが若干異なっていてもよい。 [Second Embodiment]
Next, with reference to FIG. 5, the dish fastener joint structure 2 according to the second embodiment will be described.
Hereinafter, items different from those of the first embodiment will be mainly described. The same components as those in the first embodiment are designated by the same reference numerals.
The dish fastener joint structure 2 includes an elastic body 40 arranged between the receiving surface 21A and the seating surface 12B. In the second embodiment, the angle θ1 of the seat surface 12B with respect to the axis A and the angle θ2 of the receiving surface 21A with respect to the axis A are the same. The angle θ1 and the angle θ2 may be slightly different from each other depending on the size and shape of the seat surface 12B and the receiving surface 21A and the tolerance of assembly.

角度θ１と角度θ２とが同一であることにより、皿ボルト１０により被締結部材２１，２２が締結された状態において受け面２１Ａと座面１２Ｂとの間に挟まれる弾性体４０の肉厚は一定である。そのため、図５に示される弾性体４０の径方向内側の第１領域４１の肉厚ｔ１と径方向外側の第２領域４２の肉厚ｔ２とは同一である。無負荷時における第１領域４１および第２領域４２のそれぞれの肉厚ｔ１，ｔ２も、第１領域４１および第２領域４２に亘り一定であってよい。なお、弾性体４０の寸法公差により、第１領域４１の肉厚ｔ１と第２領域４２の肉厚ｔ２とが若干異なっていてもよい。 Since the angle θ1 and the angle θ2 are the same, the thickness of the elastic body 40 sandwiched between the receiving surface 21A and the seating surface 12B is constant when the tightened members 21, 22 are fastened by the flat head bolt 10. Is. Therefore, the thickness t1 of the first region 41 on the radially inner side of the elastic body 40 and the thickness t2 of the second region 42 on the radially outer side of the elastic body 40 shown in FIG. 5 are the same. The thicknesses t1 and t2 of the first region 41 and the second region 42 when no load is applied may also be constant over the first region 41 and the second region 42. The thickness t1 of the first region 41 and the thickness t2 of the second region 42 may be slightly different due to the dimensional tolerance of the elastic body 40.

第２実施形態の皿ファスナ継手構造２は、弾性体４０の肉厚方向における第１領域４１の剛性をｋ１、第２領域４２の剛性をｋ２とすると、ｋ１＞ｋ２であることを特徴とする。剛性ｋ１，ｋ２は、弾性体４０の肉厚方向における皿ボルト１０の剛性および被締結部材２１の剛性のいずれと比較しても低い。 The dish fastener joint structure 2 of the second embodiment is characterized in that k1>k2, where k1 is the rigidity of the first region 41 and k2 is the rigidity of the second region 42 in the thickness direction of the elastic body 40. .. The rigidity k1 and k2 are lower than both the rigidity of the flat head bolt 10 and the rigidity of the fastened member 21 in the thickness direction of the elastic body 40.

第２実施形態では、弾性体４０の肉厚が一定であっても、第１領域４１の剛性ｋ１に対して第２領域４２の剛性ｋ２が低いため、第１実施形態の弾性体３０の第１、第２領域３１，３２と同様に、第１領域４１の最大弾性変形量δ１に対して第２領域４２の最大弾性変形量δ２が大きい。 In the second embodiment, even if the thickness of the elastic body 40 is constant, the rigidity k2 of the second region 42 is lower than the rigidity k1 of the first region 41. Similar to the first and second regions 31 and 32, the maximum elastic deformation amount δ2 of the second region 42 is larger than the maximum elastic deformation amount δ1 of the first region 41.

第１領域４１および第２領域４２はそれぞれ、上述したゴム材料や樹脂材料等から適宜に選定された材料を用いて成形することができる。弾性率が異なる材料のうち、相対的に弾性率が大きい一の材料を第１領域４１に使用し、相対的に弾性率が小さい他の材料を第２領域４２に使用することができる。
あるいは、第１領域４１および第２領域４２に同一の材料を使用しつつ、例えば、第１領域４１を中実に形成し、第２領域４２を中空やメッシュ状に形成することにより、ｋ１＞ｋ２の要件を満足することができる。 Each of the first region 41 and the second region 42 can be molded using a material appropriately selected from the above-mentioned rubber material, resin material, and the like. Among the materials having different elastic moduli, one material having a relatively large elastic modulus can be used for the first region 41, and another material having a relatively small elastic modulus can be used for the second region 42.
Alternatively, by using the same material for the first region 41 and the second region 42, for example, the first region 41 is formed solid and the second region 42 is formed in a hollow or mesh shape, so that k1>k2. Can meet the requirements of.

第１領域４１および第２領域４２は、別々に成形されて接合されることで一体化されていてもよいし、２つの材料を用いる射出成形である二色成形や、積層造形等により一体に成形されていてもよい。積層造形によれば、第１、第２領域４１，４２として、剛性の異なる構造（中実、メッシュ等）を容易に成形することができる。
なお、第１領域４１と第２領域４２とが必ずしも一体化されている必要はない。弾性体４０は、分離した第１領域４１と第２領域４２とからなるものであってもよい。 The first region 41 and the second region 42 may be integrally formed by separately molding and joining, or may be integrally formed by two-color molding, which is injection molding using two materials, or additive manufacturing. It may be molded. According to the additive manufacturing, structures having different rigidity (solid, mesh, etc.) can be easily formed as the first and second regions 41, 42.
The first region 41 and the second region 42 do not necessarily have to be integrated. The elastic body 40 may be composed of a first region 41 and a second region 42 which are separated from each other.

第２実施形態においても、第１実施形態と同様に、弾性体４０を受け面２１Ａと座面１２Ｂとの間に介在させた状態で皿ボルト１０およびナット１８を係合させて被締結部材２１，２２を締結する。
そして、被締結部材２１，２２が締結された状態で弾性体４０が第１実施形態の弾性体３０と同様に機能することにより、皿ファスナ継手構造２に生じる応力を低減することができる。 Also in the second embodiment, similarly to the first embodiment, the flat head bolt 10 and the nut 18 are engaged with the elastic member 40 interposed between the receiving surface 21A and the seating surface 12B to be fastened to the fastened member 21. , 22 are fastened.
The elastic body 40 functions in the same manner as the elastic body 30 of the first embodiment with the fastened members 21 and 22 fastened, whereby the stress generated in the dish fastener coupling structure 2 can be reduced.

なお、弾性体４０が、第１領域４１と、第２領域４２と、これら第１、第２領域４１，４２の間の中間の領域とを備えていてもよい。この場合、中間領域の肉厚方向における剛性がｋ３であるとすると、ｋ１＞ｋ３＞ｋ２、つまり各領域の剛性が径方向内側から外側に向けて段階的に低くなるように設定すればよい。 The elastic body 40 may include a first area 41, a second area 42, and an intermediate area between the first and second areas 41 and 42. In this case, assuming that the rigidity of the intermediate region in the thickness direction is k3, k1>k3>k2, that is, the rigidity of each region may be set to gradually decrease from the radially inner side to the outer side.

〔第３実施形態〕
次に、図６を参照し、第３実施形態に係る皿ファスナ継手構造３を説明する。
以下、第２実施形態と相違する事項を中心に説明する。第２実施形態と同様の構成には同じ符号を付している。
皿ファスナ継手構造３に備わる弾性体５０は、第１弾性部５０Ａと、第２弾性部５０Ｂとを含んでいる。第１弾性部５０Ａを灰色で示し、第２弾性部５０Ｂを格子状のパターンで示している。
第１弾性部５０Ａの剛性ｋａおよび第２弾性部５０Ｂの剛性ｋｂは、皿ボルト１０および被締結部材２１のいずれに対しても小さい。
そして、弾性体５０の肉厚方向に関し、第２弾性部５０Ｂの剛性ｋｂが、第１弾性部５０Ａの剛性ｋａと比べて小さい（ｋａ＞ｋｂ）。 [Third Embodiment]
Next, with reference to FIG. 6, the dish fastener joint structure 3 according to the third embodiment will be described.
Hereinafter, items different from the second embodiment will be mainly described. The same components as those in the second embodiment are designated by the same reference numerals.
The elastic body 50 included in the dish fastener joint structure 3 includes a first elastic portion 50A and a second elastic portion 50B. The first elastic portion 50A is shown in gray and the second elastic portion 50B is shown in a grid pattern.
The rigidity ka of the first elastic portion 50A and the rigidity kb of the second elastic portion 50B are smaller than both the countersunk bolt 10 and the fastened member 21.
In the thickness direction of the elastic body 50, the rigidity kb of the second elastic portion 50B is smaller than the rigidity ka of the first elastic portion 50A (ka>kb).

第３実施形態では、第１弾性部５０Ａと第２弾性部５０Ｂとの体積比率に基づいて、弾性体５０の径方向内側の第１領域５１と、弾性体５０の径方向外側の第２領域５２とのそれぞれの剛性ｋ１，ｋ２が相違している。
第１弾性部５０Ａと第２弾性部５０Ｂとは、弾性体５０の肉厚方向に対して交差した境界Ｂにより区分されており、弾性体５０の径方向内側から外側に向かうにつれて第２弾性部５０Ｂの占める体積比率が増加している。 In the third embodiment, the first region 51 on the radially inner side of the elastic body 50 and the second region on the radially outer side of the elastic body 50 are based on the volume ratio of the first elastic portion 50A and the second elastic portion 50B. The respective stiffnesses k1 and k2 of 52 are different.
The first elastic portion 50A and the second elastic portion 50B are sectioned by a boundary B intersecting with the thickness direction of the elastic body 50, and the second elastic portion goes from the radial inner side to the outer side of the elastic body 50. The volume ratio occupied by 50B is increasing.

したがって、相対的に高い剛性ｋａである第１弾性部５０Ａが占める比率が大きい第１領域５１の剛性ｋ１と比べ、相対的に低い剛性ｋｂである第２弾性部５０Ｂが占める比率が大きい第２領域５２の剛性ｋ２は小さい（ｋ１＞ｋ２）。この点において、第３実施形態は上述の第２実施形態と同様である。
但し、第３実施形態では、弾性体５０の剛性が径方向内側から外側に向かうにつれて、ｋ１からｋ２へと次第に低くなっている。これに伴い、弾性体５０の最大弾性変形量が、径方向の内側から外側に向かうにつれて増加しているから、この点では、第３実施形態は第１実施形態と同様である。 Therefore, as compared with the rigidity k1 of the first region 51 in which the first elastic portion 50A having a relatively high rigidity ka occupies a large proportion, the second elastic portion 50B having a relatively low rigidity kb occupies a large second proportion. The rigidity k2 of the region 52 is small (k1>k2). In this respect, the third embodiment is similar to the above-described second embodiment.
However, in the third embodiment, the rigidity of the elastic body 50 gradually decreases from k1 to k2 as it goes from the radially inner side to the outer side. Along with this, the maximum elastic deformation amount of the elastic body 50 increases from the inner side to the outer side in the radial direction. Therefore, in this respect, the third embodiment is the same as the first embodiment.

第３実施形態の弾性体５０も、被締結部材２１，２２が締結された状態で第１実施形態の弾性体３０と同様に機能することにより、皿ファスナ継手構造３に生じる応力を低減することができる。
また、第２実施形態のように弾性体４０の肉厚方向に沿って設定される第１、第２領域の境界と比べ、第３実施形態の境界Ｂは弾性体５０の径方向全体に亘り広く延在しているため、第１弾性部５０Ａと第２弾性部５０Ｂとが接合される場合に、接合面積を広く確保して接合強度をより十分に確保することができる。 The elastic body 50 of the third embodiment also functions in the same manner as the elastic body 30 of the first embodiment with the fastened members 21, 22 fastened to reduce the stress generated in the dish fastener coupling structure 3. You can
Further, as compared with the boundary between the first and second regions set along the thickness direction of the elastic body 40 as in the second embodiment, the boundary B in the third embodiment extends over the entire radial direction of the elastic body 50. Since it extends widely, when the first elastic portion 50A and the second elastic portion 50B are joined together, it is possible to secure a large joint area and more sufficiently secure the joint strength.

第１弾性部５０Ａと第２弾性部５０Ｂとの境界Ｂは、図６に示す例には限らない。
第１弾性部５０Ａおよび第２弾性部５０Ｂの体積比率に基づいて、第１領域５１および第２領域５２の剛性に関してｋ１＞ｋ２が成り立つ限りにおいて、第１弾性部５０Ａと第２弾性部５０Ｂとの境界Ｂを適宜に定めることができる。 The boundary B between the first elastic portion 50A and the second elastic portion 50B is not limited to the example shown in FIG.
Based on the volume ratio of the first elastic portion 50A and the second elastic portion 50B, the first elastic portion 50A and the second elastic portion 50B as long as k1>k2 is satisfied with respect to the rigidity of the first region 51 and the second region 52. B can be set appropriately.

〔第４実施形態〕
図７に示す皿ファスナ継手構造４は、第１実施形態（図１）および第２実施形態（図５）のそれぞれの特徴を組み合わせることで構成されている。
すなわち、座面１２Ｂおよび受け面２１Ａの角度θ１，θ２に関し、θ１＜θ２であり、皿ファスナ継手構造４の弾性体６０が備える第１領域６１および第２領域６２の肉厚方向の剛性ｋ１，ｋ２に関してはｋ１＞ｋ２である。
第１、第２実施形態の特徴の掛け合わせにより、第１領域６１と第２領域６２とのそれぞれの最大弾性変形量δ１，δ２の差を拡大することができるので、第２領域６２に、上述した第２領域３２，４２に得られる最大弾性変形量よりも大きい最大弾性変形量を設定することが可能となる。 [Fourth Embodiment]
The dish fastener joint structure 4 shown in FIG. 7 is configured by combining the respective features of the first embodiment (FIG. 1) and the second embodiment (FIG. 5).
That is, with respect to the angles θ1 and θ2 of the seat surface 12B and the receiving surface 21A, θ1<θ2, and the rigidity k1 in the thickness direction of the first region 61 and the second region 62 included in the elastic body 60 of the dish fastener coupling structure 4. Regarding k2, k1>k2.
By combining the features of the first and second embodiments, it is possible to increase the difference between the maximum elastic deformation amounts δ1 and δ2 of the first region 61 and the second region 62, and therefore, in the second region 62, It is possible to set the maximum elastic deformation amount larger than the maximum elastic deformation amount obtained in the second regions 32 and 42 described above.

図示を省略するが、第１実施形態（図１）と第３実施形態（図６）とを組み合わせることによっても、第４実施形態と同様の効果を得ることができる。 Although illustration is omitted, the same effect as that of the fourth embodiment can be obtained by combining the first embodiment (FIG. 1) and the third embodiment (FIG. 6).

複数の実施形態の特徴を組み合わせることにより、継手構造の応力に関する設計の自由度が拡大するため、種々の皿ボルトや荷重等の条件に対して最適な構成を実現することができる。 By combining the features of the plurality of embodiments, the degree of freedom in design regarding the stress of the joint structure is expanded, so that an optimum configuration can be realized for various conditions such as countersunk bolts and loads.

〔第５実施形態〕
図８（ａ）に示す皿ファスナ継手構造５Ａは、座面１２Ｂと受け面２１Ａとの間に配置される第１弾性体３０に加えて、軸部１１の外周部とボルト挿入孔２０の内周部との間に配置される第２弾性体７０を備えている。
第１弾性体３０は、第１実施形態の弾性体３０と同様である。 [Fifth Embodiment]
The dish fastener joint structure 5A shown in FIG. 8A includes, in addition to the first elastic body 30 arranged between the seat surface 12B and the receiving surface 21A, the outer peripheral portion of the shaft portion 11 and the bolt insertion hole 20. A second elastic body 70 is provided between the second elastic body 70 and the peripheral portion.
The first elastic body 30 is similar to the elastic body 30 of the first embodiment.

図８（ｂ）に示す皿ファスナ継手構造５Ｂは、座面１２Ｂと受け面２１Ａとの間に配置される第１弾性体４０に加えて、軸部１１の外周部とボルト挿入孔２０の内周部との間に配置される第２弾性体７０を備えている。 8B includes a first elastic body 40 arranged between the seat surface 12B and the receiving surface 21A, as well as the outer peripheral portion of the shaft portion 11 and the bolt insertion hole 20. A second elastic body 70 is provided between the second elastic body 70 and the peripheral portion.

以下、図８（ａ）および（ｂ）に共通する第２弾性体７０の構成および作用効果を説明する。
第２弾性体７０は、第１実施形態の弾性体３０と同様に、ゴム材料、樹脂材料、あるいは金属材料を用いて構成することができる。第２弾性体７０の肉厚方向（軸部１１の径方向）の剛性は、同方向における軸部１１の剛性および被締結部材２１，２２の剛性と比べて低い。 Hereinafter, the configuration and the effect of the second elastic body 70 common to FIGS. 8A and 8B will be described.
The second elastic body 70 can be configured by using a rubber material, a resin material, or a metal material similarly to the elastic body 30 of the first embodiment. The rigidity of the second elastic body 70 in the thickness direction (the radial direction of the shaft portion 11) is lower than the rigidity of the shaft portion 11 and the rigidity of the fastened members 21, 22 in the same direction.

第２弾性体７０は、筒状の形態に成形することができる。この場合は、成形体である第２弾性体７０を軸部１１の周りに弾性力により装着することができる。成形体の第２弾性体７０は、雄ねじ１１Ａの領域を避けつつ、軸部１１の外周部の広い範囲に亘り配置されることが好ましい。第２弾性体７０が装着された軸部１１をボルト挿入孔２０に挿入し、軸部１１の雄ねじ１１Ａ（図１（ａ））にナット１８を係合させることで、皿ボルト１０により被締結部材２１，２２を締結することができる。
なお、軸部１１とボルト挿入孔２０の内周部との間にはクリアランスＣが設定されているため、第２弾性体７０を径方向に弾性変形させながら、クリアランスＣが設定されていない場合と比べて容易に軸部１１をボルト挿入孔２０に挿入することができる。 The second elastic body 70 can be molded into a tubular shape. In this case, the second elastic body 70, which is a molded body, can be mounted around the shaft portion 11 by elastic force. The second elastic body 70 of the molded body is preferably arranged over a wide range of the outer peripheral portion of the shaft portion 11 while avoiding the area of the male screw 11A. By inserting the shaft portion 11 on which the second elastic body 70 is mounted into the bolt insertion hole 20 and engaging the nut 18 with the male screw 11A (FIG. 1A) of the shaft portion 11, it is fastened with the countersunk bolt 10. The members 21, 22 can be fastened.
Since the clearance C is set between the shaft portion 11 and the inner peripheral portion of the bolt insertion hole 20, the clearance C is not set while elastically deforming the second elastic body 70 in the radial direction. The shaft portion 11 can be easily inserted into the bolt insertion hole 20 as compared with.

第２弾性体７０は、締結前に必ずしも成形されていなくてもよい。例えば、第２弾性体７０が、シーラントのように流動性を有した状態でボルト挿入孔２０の内側に施工されて、ボルト挿入孔２０の内側で固化したものであってもよい。流動性を有するシーラントがボルト挿入孔２０の内周部に付着した状態で軸部１１をボルト挿入孔２０に挿入し、雄ねじ１１Ａとナット１８を係合させることで、シーラントが軸部１１の外周部とボルト挿入孔２０の内周部との間に充填される。 The second elastic body 70 does not necessarily have to be molded before fastening. For example, the second elastic body 70 may be applied inside the bolt insertion hole 20 in a fluid state like a sealant and solidified inside the bolt insertion hole 20. By inserting the shaft portion 11 into the bolt insertion hole 20 with the fluid sealant attached to the inner peripheral portion of the bolt insertion hole 20 and engaging the male screw 11A and the nut 18, the sealant is applied to the outer periphery of the shaft portion 11. And the inner peripheral portion of the bolt insertion hole 20.

図３に示すように荷重Ｆ１により被締結部材２１，２２が互いに滑ると、第２弾性体７０が径方向に弾性変形することで皿ボルト１０の軸部１１が弾性的に支持されるため、皿ボルト１０の傾きの変位が緩和される。このとき、第２弾性体７０により間接的に被締結部材２１，２２の滑りが抑制されることとなる。
第５実施形態によれば、被締結部材２１，２２の滑りが生じたとしても、第２弾性体７０の弾性変形により皿ボルト１０の傾きの変位が緩和されるので、軸部１１の傾きに伴い座面１２Ｂと受け面２１Ａとが押し合うことで生じる皿頭１２の強制的な曲げ変形が緩和される。そのため、皿ファスナ継手構造５Ａ，５Ｂに生じる応力を第１〜第４実施形態よりもさらに低減することができる。 As shown in FIG. 3, when the members 21 and 22 to be fastened slide against each other due to the load F1, the second elastic body 70 is elastically deformed in the radial direction, so that the shaft portion 11 of the flat head bolt 10 is elastically supported. The inclination displacement of the flat head bolt 10 is alleviated. At this time, the second elastic body 70 indirectly suppresses the slippage of the fastened members 21, 22.
According to the fifth embodiment, even if the fastened members 21 and 22 slip, the inclination displacement of the flat head bolt 10 is alleviated by the elastic deformation of the second elastic body 70. Accordingly, the forced bending deformation of the countersunk head 12 caused by the pressing of the bearing surface 12B and the receiving surface 21A is relieved. Therefore, the stress generated in the dish fastener joint structures 5A and 5B can be further reduced as compared with the first to fourth embodiments.

上記以外にも、本発明の主旨を逸脱しない限り、上記実施形態で挙げた構成を取捨選択したり、他の構成に適宜変更したりすることが可能である。 Other than the above, the configurations described in the above embodiments can be selected or changed to other configurations without departing from the gist of the present invention.

皿ボルト１０の皿頭１２は、上記各実施形態のように平坦な頂面１２Ａを備えるものには限定されず、凸状に湾曲した頂面を備えるものであってもよい。
また、皿ボルト１０は、被締結部材に形成された雌ねじに係合されるものであってもよい。この場合はナット１８が必要ない。 The countersunk head 12 of the countersunk bolt 10 is not limited to one having the flat top surface 12A as in each of the above-described embodiments, but may be one having a convexly curved top surface.
Further, the flat head bolt 10 may be engaged with a female screw formed on the member to be fastened. In this case, the nut 18 is unnecessary.

本発明における皿ファスナは、被締結部材２１，２２に対する着脱が可能な皿ボルト１０には限定されず、皿頭１２を有する円柱状または円筒状のリベットであってもよい。
こうした皿リベットを用いており、皿リベットの軸部と挿入孔の内周部との間の隙間の存在により被締結部材２１，２２の滑りが生じ得る場合にも、皿頭１２の座面１２Ｂと受け面２１Ａとの間に介在する弾性体（３０等）の作用により、継手構造に生じる応力を低減することができる。 The dish fastener in the present invention is not limited to the dish bolt 10 that can be attached to and detached from the members to be fastened 21, 22 and may be a cylindrical or cylindrical rivet having the dish head 12.
Even when such a plate rivet is used and the gap between the shaft part of the plate rivet and the inner peripheral part of the insertion hole may cause the fastened members 21, 22 to slip, the seat surface 12B of the plate head 12 The stress generated in the joint structure can be reduced by the action of the elastic body (30 or the like) interposed between and the receiving surface 21A.

１〜４，５Ａ，５Ｂ 皿ファスナ継手構造
８ 皿ボルト
１０ 皿ボルト
１１ 軸部
１１Ａ 雄ねじ
１１Ｂ 先端部
１２ 皿頭
１２Ａ 頂面
１２Ｂ 座面
１２Ｃ 首部
１２Ｄ 溝
１８ ナット
１８Ａ 端面
２０ ボルト挿入孔（挿入孔）
２１ 被締結部材
２１Ａ 受け面
２１Ｂ 表面
２２ 被締結部材
２２Ａ 面
２４ 空隙
３０，３５，４０，５０，６０ 弾性体
３０Ａ 外周部
３０Ｂ 内周部
３０Ｃ 内端
３０Ｄ 頂部
３１，４１，５１，６１ 第１領域
３２，４２，５２，６２ 第２領域
３３ カバー領域
５０Ａ 第１弾性部
５０Ｂ 第２弾性部
７０ 第２弾性体
８１ 皿頭
８１Ａ 首部
８１Ｂ 座面
９１，９２ 被締結部材
９１Ａ 受け面
２０１，２０２ 挿入孔
Ａ 軸線
Ｂ 境界
Ｃ クリアランス
Ｆ０ 締結力
Ｆ１ 荷重
Ｍ モーメント
ｋ１，ｋ２ 剛性
ｋａ，ｋｂ 剛性
Ｓ シーラント
ｔ１，ｔ２ 肉厚
δ１，δ２ 最大弾性変形量
θ１，θ２ 角度 1-4, 5A, 5B Countersunk fastener joint structure 8 Countersunk bolt 10 Countersunk bolt 11 Shaft section 11A Male screw 11B Tip section 12 Countersunk head 12A Top surface 12B Seat surface 12C Neck section 12D Groove 18 Nut 18A End surface 20 Bolt insertion hole (insertion hole)
21 Fastened member 21A Receiving surface 21B Surface 22 Fastened member 22A Surface 24 Void 30, 35, 40, 50, 60 Elastic body 30A Outer peripheral portion 30B Inner peripheral portion 30C Inner end 30D Top portion 31, 41, 51, 61 First region 32, 42, 52, 62 2nd area|region 33 Cover area 50A 1st elastic part 50B 2nd elastic part 70 2nd elastic body 81 Countersunk head 81A Neck part 81B Seat surface 91,92 Fastened member 91A Receiving surface 201,202 Insertion hole A axis B B boundary C clearance F0 fastening force F1 load M moment k1, k2 rigidity ka, kb rigidity S sealant t1, t2 wall thickness δ1, δ2 maximum elastic deformation θ1, θ2 angle

Claims (10)

軸部、および前記軸部から頂面に向かうにつれて径が拡大した逆円錐台状の皿頭を含む皿ファスナと、
前記皿ファスナにより締結される複数の被締結部材と、
前記皿頭の座面、および一の前記被締結部材に形成されて前記座面を受ける受け面の間に配置される弾性体と、を備え、
前記弾性体は、径方向内側の第１領域と、径方向外側の第２領域と、を含み、
前記第１領域および前記第２領域のいずれも、前記皿ファスナ、および前記受け面が形成される前記被締結部材と比べて前記弾性体の肉厚方向の剛性が低く、
前記第１領域に設定された肉厚方向への最大弾性変形量と比べて、
前記第２領域に設定された肉厚方向への最大弾性変形量が大きい、
ことを特徴とする皿ファスナ継手構造。 A shaft fastener, and a dish fastener including an inverted frustoconical dish head whose diameter increases from the shaft portion toward the top surface,
A plurality of members to be fastened that are fastened by the dish fastener,
A seat surface of the countersunk head, and an elastic body that is formed between the one receiving member and a receiving surface that receives the seat surface,
The elastic body includes a first region on the radially inner side and a second region on the radially outer side,
In both the first region and the second region, the rigidity of the elastic body in the thickness direction is low as compared with the fastened member in which the dish fastener and the receiving surface are formed,
Compared with the maximum elastic deformation amount in the thickness direction set in the first region,
The maximum elastic deformation amount in the thickness direction set in the second region is large,
A dish fastener joint structure characterized in that 前記皿ファスナは、前記被締結部材に対する着脱が可能なボルトである、
請求項１に記載の皿ファスナ継手構造。 The countersunk fastener is a bolt that can be attached to and detached from the member to be fastened,
The countersunk fastener joint structure according to claim 1. 前記皿ファスナが挿入される前記被締結部材の挿入孔の軸線に対して前記座面がなす角度をθ１、
前記軸線に対して前記受け面がなす角度をθ２、とすると、
θ１＜θ２である、
請求項１または２に記載の皿ファスナ継手構造。 The angle formed by the seat surface with respect to the axis of the insertion hole of the member to be fastened into which the dish fastener is inserted is θ1,
If the angle formed by the receiving surface with respect to the axis is θ2,
θ1<θ2,
The countersunk fastener joint structure according to claim 1. 無負荷の状態における前記第１領域の肉厚をｔ１、
無負荷の状態における前記第２領域の肉厚をｔ２、とすると、
ｔ１＜ｔ２である、
請求項３に記載の皿ファスナ継手構造。 The thickness of the first region in the unloaded state is t1,
If the thickness of the second region in the unloaded state is t2,
t1<t2,
The dish fastener joint structure according to claim 3. 前記第１領域の剛性をｋ１、
前記第２領域の剛性をｋ２、とすると、
ｋ１＞ｋ２である、
請求項１から４のいずれか一項に記載の皿ファスナ継手構造。 The rigidity of the first region is k1,
If the rigidity of the second region is k2,
k1>k2,
The countersunk fastener joint structure according to any one of claims 1 to 4. 前記弾性体は、肉厚方向の剛性が異なる第１弾性部および第２弾性部を備え、
前記第１弾性部の剛性ｋａに対して、前記第２弾性部の剛性ｋｂが小さく、
前記第１弾性部および前記第２弾性部の体積比率に基づいて、ｋ１＞ｋ２である、
請求項５に記載の皿ファスナ継手構造。 The elastic body includes a first elastic portion and a second elastic portion having different rigidity in the thickness direction,
The rigidity kb of the second elastic portion is smaller than the rigidity ka of the first elastic portion,
K1>k2 based on the volume ratio of the first elastic portion and the second elastic portion,
The countersunk fastener joint structure according to claim 5. 前記軸部と、前記軸部が挿入される前記被締結部材の挿入孔の内周部との間に配置され、前記軸部および前記被締結部材と比べて肉厚方向の剛性が低い第２の弾性体を備える、
請求項１から６のいずれか一項に記載の皿ファスナ継手構造。 A second member that is disposed between the shaft portion and an inner peripheral portion of an insertion hole of the member to be fastened into which the shaft portion is inserted, and has a lower rigidity in a thickness direction than the shaft portion and the member to be fastened. Equipped with an elastic body,
The countersunk fastener joint structure according to any one of claims 1 to 6. 前記弾性体は、前記頂面を覆うカバー領域を含む、
請求項１から７のいずれか一項に記載の皿ファスナ継手構造。 The elastic body includes a cover region covering the top surface,
The countersunk fastener joint structure according to any one of claims 1 to 7. 前記被締結部材は、航空機の機体を構成する部材である、
請求項１から８のいずれか一項に記載の皿ファスナ継手構造。 The member to be fastened is a member constituting a body of an aircraft,
The countersunk fastener joint structure according to any one of claims 1 to 8. 皿ファスナの皿頭の座面、および前記皿ファスナにより締結される複数の被締結部材の一つに形成されて前記座面を受ける受け面の間に配置される弾性体であって、
径方向内側の第１領域と、
径方向外側の第２領域と、を含み、
前記第１領域および前記第２領域のいずれも、前記皿ファスナ、および前記受け面が形成される前記被締結部材と比べて肉厚方向の剛性が低く、
前記第１領域に設定された肉厚方向への最大弾性変形量と比べて、
前記第２領域に設定された肉厚方向への最大弾性変形量が大きい、
ことを特徴とする皿ファスナ用弾性体。 An elastic body disposed between a receiving surface of a dish head of a dish fastener and a receiving surface formed on one of a plurality of members to be fastened to be fastened by the dish fastener and receiving the seat surface,
A first region radially inward,
A second region on the radially outer side,
In both the first region and the second region, the rigidity in the thickness direction is lower than that of the dish fastener and the member to be fastened in which the receiving surface is formed,
Compared with the maximum elastic deformation amount in the thickness direction set in the first region,
The maximum elastic deformation amount in the thickness direction set in the second region is large,
An elastic body for dish fasteners, which is characterized in that
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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0525014U (en) * 1991-09-10 1993-04-02 オーパツク株式会社 Fastening parts such as bolts and rivets
JP2009227166A (en) * 2008-03-24 2009-10-08 Mitsubishi Heavy Ind Ltd Aircraft assembly
JP2014500444A (en) * 2010-10-08 2014-01-09 ウァイス，ウォルフガング Shape lock connection to correct position error
JP2018069903A (en) * 2016-10-28 2018-05-10 本田技研工業株式会社 Vehicle wheel

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0525014U (en) * 1991-09-10 1993-04-02 オーパツク株式会社 Fastening parts such as bolts and rivets
JP2009227166A (en) * 2008-03-24 2009-10-08 Mitsubishi Heavy Ind Ltd Aircraft assembly
JP2014500444A (en) * 2010-10-08 2014-01-09 ウァイス，ウォルフガング Shape lock connection to correct position error
JP2018069903A (en) * 2016-10-28 2018-05-10 本田技研工業株式会社 Vehicle wheel

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