JP2016095029A - Method for fastening seal washer and fluid pipe flange - Google Patents
Method for fastening seal washer and fluid pipe flange Download PDFInfo
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- JP2016095029A JP2016095029A JP2015249379A JP2015249379A JP2016095029A JP 2016095029 A JP2016095029 A JP 2016095029A JP 2015249379 A JP2015249379 A JP 2015249379A JP 2015249379 A JP2015249379 A JP 2015249379A JP 2016095029 A JP2016095029 A JP 2016095029A
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- 239000012530 fluid Substances 0.000 title claims description 28
- 238000000034 method Methods 0.000 title claims description 13
- 230000002093 peripheral effect Effects 0.000 claims abstract description 44
- 238000003780 insertion Methods 0.000 claims abstract description 17
- 230000037431 insertion Effects 0.000 claims abstract description 17
- 238000007789 sealing Methods 0.000 claims abstract description 12
- 125000006850 spacer group Chemical group 0.000 claims description 7
- 125000004122 cyclic group Chemical group 0.000 claims 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 18
- 239000002184 metal Substances 0.000 description 8
- 238000004519 manufacturing process Methods 0.000 description 6
- 238000005452 bending Methods 0.000 description 4
- 230000003014 reinforcing effect Effects 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 230000002787 reinforcement Effects 0.000 description 3
- 239000000853 adhesive Substances 0.000 description 2
- 230000001070 adhesive effect Effects 0.000 description 2
- 238000012937 correction Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000012856 packing Methods 0.000 description 2
- 230000032683 aging Effects 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 238000012790 confirmation Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
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- 230000001105 regulatory effect Effects 0.000 description 1
- 230000035882 stress Effects 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
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- Bolts, Nuts, And Washers (AREA)
- Gasket Seals (AREA)
Abstract
Description
本発明は、水道管等を代表とする流体管のフランジ部に形成されたボルト孔を密封するためのシールワッシャ及び流体管フランジ部の締結方法に関する。 The present invention relates to a seal washer for sealing a bolt hole formed in a flange portion of a fluid pipe typified by a water pipe or the like, and a fastening method of the fluid pipe flange portion.
水道管等の流体管同士は、流体管の端部に設けられたフランジ部同士をナット及びボルト等の固着具を用いて締結することで接合されるのが通例である。 Usually, fluid pipes such as water pipes are joined together by fastening flange portions provided at end parts of the fluid pipes using fasteners such as nuts and bolts.
フランジ接合された流体管は、地震等の外力や老朽化によりフランジ部同士の間から流体（水）が漏出する場合がある。この流体漏出を未然に防止するため、又は、現に流体の漏出が発生している場合に漏出を止めるための一つの有効な手段として、例えば特許文献１には、フランジ部の径方向先端同士の間を密封すべく、フランジ部の径方向先端同士の間を閉塞する位置に巻き付けたパッキンをフランジ部に押圧した状態で固定するための配管補強金具が開示されている。 The fluid pipes that are flange-bonded may leak fluid (water) from between the flange portions due to external force such as an earthquake or aging. As one effective means for preventing the fluid leakage in advance or for stopping the leakage when the fluid leakage actually occurs, for example, Patent Document 1 discloses that the radial ends of the flange portion are In order to seal the gap, there is disclosed a pipe reinforcing metal fitting for fixing a packing wound around a position where the gap between the radial ends of the flange portion is pressed against the flange portion.
上記に併せて、フランジ部に形成されたボルト孔からの流体漏出を防止するために、図７の部分断面図で示すように、ボルト２又はナット３の座面２０・３０とフランジ部４０との間にボルト孔４０ｓを密封するためのシールワッシャ１０１を介在する。シールワッシャ１０１は、フランジ部側となる端面にボルト孔４０ｓの周縁部位４０ｆと密接するためのシール面１１０ｆが設定され、弾性部材で形成され且つボルト２の軸部２１を挿通させる挿通孔１１０ｓを有する環状をなすシール部材１１０と、シール部材１１０よりも硬質の枠部材１１１とを有する。ボルト２及びナット３を締め付けると、枠部材１１１を介してシール部材１１０のシール面１１０ｆがフランジ部４０に押圧され、フランジ部４０のボルト孔の周縁部位４０ｆとシール面１１０ｆが密接して、ボルト孔４０ｓが密封される。 In addition to the above, in order to prevent fluid leakage from the bolt hole formed in the flange portion, as shown in the partial sectional view of FIG. A seal washer 101 for sealing the bolt hole 40s is interposed between the two. The seal washer 101 is provided with an insertion hole 110s that is formed of an elastic member and through which the shaft part 21 of the bolt 2 is inserted, in which an end surface on the flange portion side is set to be in close contact with the peripheral portion 40f of the bolt hole 40s. The seal member 110 has an annular shape, and the frame member 111 is harder than the seal member 110. When the bolt 2 and the nut 3 are tightened, the seal surface 110f of the seal member 110 is pressed against the flange portion 40 via the frame member 111, and the peripheral portion 40f of the bolt hole of the flange portion 40 and the seal surface 110f are brought into close contact with each other. The hole 40s is sealed.
ところが、現場には、実際のボルト孔の径が製造誤差により規格径と若干異なる場合や、フランジ部同士が相対的に径方向にオフセットしている場合、フランジ面同士が平行ではなく若干の開き姿勢にある場合などの種々の環境があり、環境に応じてボルト孔とボルトの軸部との間の隙間の大きさが種々変わり得る。この隙間が、例えば図７に示すように、シール部材１１０の軸心ＣＬ１とボルト孔４０ｓの軸ＣＬ２とのズレを許容してしまう。仮に、同図に示すように、シール部材１１０のボルト孔４０ｓに対するオフセットが大きくなると、シール面１１０ｆがボルト孔周縁部位４０ｆから脱落したり、シール面１１０ｆによる密封が不十分になったりして、その部位から液体漏出を招来してしまうおそれがある。シール部材１１０（ボルトの軸部２１）とボルト孔４０ｓとが同軸になるように位置合わせしながら、ボルト２及びナット３を締め付けるのが望ましいが、現場においては難しい作業となる。特に、現に液体漏出が生じている場合には目視が難しいので困難を極める作業である。 However, at the site, when the actual bolt hole diameter is slightly different from the standard diameter due to manufacturing errors, or when the flange portions are relatively offset in the radial direction, the flange surfaces are not parallel but slightly open. There are various environments such as the case of being in the posture, and the size of the gap between the bolt hole and the shaft portion of the bolt can be variously changed according to the environment. For example, as shown in FIG. 7, this gap allows a deviation between the axis CL1 of the seal member 110 and the axis CL2 of the bolt hole 40s. If the offset of the seal member 110 with respect to the bolt hole 40s increases as shown in the figure, the seal surface 110f may drop off from the bolt hole peripheral portion 40f, or the seal by the seal surface 110f may be insufficiently sealed. There is a risk of liquid leakage from the site. It is desirable to tighten the bolt 2 and the nut 3 while aligning the seal member 110 (bolt shaft portion 21) and the bolt hole 40s so as to be coaxial, but this is a difficult task in the field. In particular, when liquid leakage actually occurs, it is difficult to visually check, so this is an extremely difficult task.
一方、シール部材１１０の軸心ＣＬ１がボルト孔４０ｓの軸ＣＬ２に対して径方向のいずれかにオフセットしても、シール面１１０ｆがボルト孔周縁部位４０ｆから脱落することを防止するためには、シール部材１１０の外径を大きくしてシール面１１０ｆの面積を増大させることが一つの有効な手段として挙げられる。しかし、ボルト及びナットを締めるための工具代となるスペースを水道管４（流体管）の本体との間に確保しなければならず、シール部材の外径の上限にもおのずと限度がある。 On the other hand, in order to prevent the seal surface 110f from falling off the bolt hole peripheral portion 40f even if the axial center CL1 of the seal member 110 is offset in any of the radial directions with respect to the axis CL2 of the bolt hole 40s, Increasing the outer diameter of the seal member 110 to increase the area of the seal surface 110f is an effective means. However, a space as a tool cost for tightening the bolts and nuts must be secured between the main body of the water pipe 4 (fluid pipe), and the upper limit of the outer diameter of the seal member is naturally limited.
本発明は、このような課題に着目してなされたものであって、その目的は、シールワッシャを大径化することなく、シール面がボルト孔周縁部位から脱落することを抑制可能なシールワッシャ及び流体管フランジ部の締結方法を提供することである。 The present invention has been made paying attention to such a problem, and the object thereof is to provide a seal washer that can prevent the seal surface from falling off from the peripheral portion of the bolt hole without increasing the diameter of the seal washer. And a method of fastening a fluid pipe flange.
本発明は、かかる目的を達成するために、次のような手段を講じたものである。 In order to achieve this object, the present invention takes the following measures.
すなわち、本発明のシールワッシャは、ボルト又はナットの座面と前記ボルト及びナットにより締め付けられる流体管のフランジ部との間に介在し、前記フランジ部に形成されたボルト孔を密封するためのシールワッシャであって、前記フランジ部側となる端部に前記ボルト孔の周縁部位と密接するためのシール面が設定され、弾性部材で形成され且つ前記ボルトの軸部を挿通させる挿通孔を有する環状をなすシール部材と、前記シール部材よりも前記ボルト又はナットの座面側に配置され且つ前記シール部材よりも硬質の枠部材とを具備し、前記シール部材の前記挿通孔の周縁部には、外力が作用しない自然状態において前記シール面から軸方向に突出し、前記ボルト孔と前記ボルトの軸部との間の隙間に挿入可能なヒレ部が設けられていることを特徴とする。 That is, the seal washer according to the present invention is interposed between the seat surface of the bolt or nut and the flange portion of the fluid pipe fastened by the bolt and nut, and seals the bolt hole formed in the flange portion. An annular ring having a sealing surface for being in contact with the peripheral portion of the bolt hole at the end on the flange portion side, formed of an elastic member, and through which the shaft portion of the bolt is inserted. And a frame member that is disposed closer to the bearing surface side of the bolt or nut than the seal member and is harder than the seal member, and a peripheral edge portion of the insertion hole of the seal member includes: There is provided a fin portion that protrudes in the axial direction from the seal surface in a natural state where no external force is applied and can be inserted into a gap between the bolt hole and the shaft portion of the bolt. It is characterized in.
このように、シール部材のうちボルト孔を挿通する挿通孔の周縁部には、外力が作用しない自然状態においてシール面から軸方向に突出し、ボルト孔とボルトの軸部との間の隙間に挿入可能なヒレ部が設けてあるので、ヒレ部をボルト孔に挿入すれば、シール部材のボルト孔に対する径方向移動がヒレ部によって或る程度規制されることになり、シール部材のシール面がフランジ部のボルト孔周縁部位から脱落することを抑制することが可能となる。 In this way, the peripheral portion of the insertion hole through which the bolt hole of the seal member is inserted projects in the axial direction from the seal surface in a natural state where no external force acts, and is inserted into the gap between the bolt hole and the bolt shaft portion. Since the possible fin portion is provided, if the fin portion is inserted into the bolt hole, the radial movement of the seal member with respect to the bolt hole is restricted to some extent by the fin portion, and the seal surface of the seal member becomes the flange. It is possible to suppress falling off from the bolt hole peripheral part of the part.
ボルト孔を均一に密封して安定性を向上させるためには、前記ヒレ部は、前記挿通孔の周縁部に沿って環状をなすと共に、先端から基端に向かうにつれて内周面との間の径方向厚みが太くなるテーパ状の外周面を有することが好ましい。 In order to improve the stability by uniformly sealing the bolt holes, the fin portion has an annular shape along the peripheral edge portion of the insertion hole and between the inner peripheral surface and the base end. It is preferable to have a tapered outer peripheral surface in which the radial thickness is increased.
このように構成すれば、ボルト及びナットを締め付けるのに伴って、ヒレ部がボルト孔の奥側へ向けて押圧される。ヒレ部は、先端から基端に向かうにつれて内周面との間の径方向厚みが太くなるテーパ状の外周面を有するので、弾性反発力を蓄積する。このとき、ボルト孔の軸に対してシール部材の軸心が径方向一方にズレていると、ヒレ部のうち径方向一方側にある部位の方が他端側にある部位に比して圧縮される。この圧縮量の差に起因して、ボルト軸部の軸心をボルト孔の軸に一致させる方向に弾性反発力が作用し、シール部材とボルト孔の芯ズレが補正される。したがって、締着時にボルト孔とボルト軸部とが芯ズレようとしても、シール部材の弾性反発力によりシール部材とボルト孔の芯ズレが適切に補正されるので、ボルト孔を均一に密封でき、安定性を向上させることが可能となる。このような芯ズレ防止機能を発揮するので、特に、位置合わせしにくい漏出状態での作業時やボルト孔径に製造誤差が存在するとき、フランジ同士が相対的な位置ズレしている場合に好適となる。 If comprised in this way, a fin part will be pressed toward the back | inner side of a bolt hole with tightening a bolt and a nut. Since a fin part has a taper-shaped outer peripheral surface where radial direction thickness between the inner peripheral surfaces becomes thicker as it goes to a base end from a front-end | tip, it accumulates elastic repulsion. At this time, if the shaft center of the seal member is displaced in one radial direction with respect to the bolt hole shaft, the portion on the one radial side of the fin portion is compressed compared to the portion on the other end side. Is done. Due to this difference in compression amount, an elastic repulsive force acts in the direction in which the axis of the bolt shaft portion coincides with the axis of the bolt hole, and the misalignment between the seal member and the bolt hole is corrected. Therefore, even if the bolt hole and the bolt shaft portion are misaligned at the time of fastening, the seal member and the bolt hole are properly corrected by the elastic repulsion force, so that the bolt hole can be uniformly sealed, Stability can be improved. Because it exhibits such a misalignment prevention function, it is particularly suitable when working in a leaky state that is difficult to align or when there is a manufacturing error in the bolt hole diameter and when the flanges are relatively misaligned. Become.
また、締結後（施工後）においても、流体管へ荷重が作用してボルト軸部に曲げ荷重が作用したとしても、ヒレ部によりボルト軸部の軸をボルト孔の軸に一致させる方向に弾性反発力が作用するので、曲げ荷重による芯ズレを抑制又は防止することが可能となる。 Even after fastening (after construction), even if a load is applied to the fluid pipe and a bending load is applied to the bolt shaft, the fin portion is elastic in the direction to align the axis of the bolt shaft with the axis of the bolt hole. Since the repulsive force acts, it is possible to suppress or prevent the misalignment due to the bending load.
本発明の流体管フランジ部の締結方法は、流体管のフランジ部に形成されたボルト孔にボルトを挿通し、前記ボルトの先端部にナットを取り付けて、前記ボルト及び前記ナットを締め付けて前記フランジ部を締結する流体管フランジ部の締結方法であって、前記フランジ部と前記ボルト又はナットの座面との間に、弾性部材で形成されたシール部材を有するシールワッシャを介在させるとともに、前記シール部材に突設されたヒレ部を前記ボルト孔と前記ボルトの軸部との間の隙間に挿入し、前記ボルト及びナットを締め付けて前記フランジ部を締結することを特徴とする。 The fluid pipe flange portion fastening method according to the present invention includes inserting a bolt into a bolt hole formed in the flange portion of the fluid pipe, attaching a nut to the front end portion of the bolt, and tightening the bolt and the nut. A fluid pipe flange part fastening method for fastening a part, wherein a seal washer having a seal member formed of an elastic member is interposed between the flange part and a seat surface of the bolt or nut, and the seal A fin portion protruding from the member is inserted into a gap between the bolt hole and the shaft portion of the bolt, and the flange portion is fastened by tightening the bolt and nut.
このように、シールワッシャを構成するシール部材に突設されたヒレ部をボルト孔に挿入すれば、シール部材のボルト孔に対する径方向移動がヒレ部によって或る程度規制されることになるので、シール部材のシール面がフランジ部のボルト孔周縁部位から脱落することを抑制することが可能となる。 Thus, if the fin portion protruding from the seal member constituting the seal washer is inserted into the bolt hole, the radial movement of the seal member with respect to the bolt hole is regulated to some extent by the fin portion. It is possible to suppress the seal surface of the seal member from falling off from the bolt hole peripheral portion of the flange portion.
上記方法において、ボルト孔を均一に密封して安定性を向上させるためには、前記ヒレ部は、前記挿通孔の周縁部に沿って環状をなすと共に、先端から基端に向かうにつれて内周面との間の径方向厚みが太くなるテーパ状の外周面を有することが好ましい。 In the above method, in order to improve the stability by uniformly sealing the bolt hole, the fin portion forms an annular shape along the peripheral portion of the insertion hole, and the inner peripheral surface from the distal end toward the proximal end. It is preferable to have a taper-shaped outer peripheral surface where the thickness in the radial direction is increased.
上記方法において、ボルト及びナットを共通化して製造コストを低減させるためには、前記ボルト又はナットの座面と前記シールワッシャとの間にスペーサを介在させていることが好ましい。このようにスペーサを用いることで、厚みの異なる種々のフランジ部に対して共通のボルト及びナットを利用でき、部品共通化により製造コストを低減させることが可能となる。 In the above method, in order to reduce the manufacturing cost by using the same bolt and nut, it is preferable that a spacer is interposed between the seat surface of the bolt or nut and the seal washer. By using the spacers in this way, common bolts and nuts can be used for various flange portions having different thicknesses, and it becomes possible to reduce manufacturing costs by sharing parts.
以下、本発明の実施形態について図面を参照しながら説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
図１に示すように、シールワッシャ１は、水道管４（流体管の一例）の端部に設けられたフランジ部同士４０・４０をボルト２及びナットを用いて締結することで水道管同士４・４を接合する際に用いられるもので、具体的には、図２に示すように、ボルト２又はナット３の座面２０・３０とボルト２及びナット３により締め付けられる水道管４のフランジ部４０との間に介在し、フランジ部４０に形成されたボルト孔４０ｓを密封するために使用される。なお、図２は、図１におけるＡ−Ａ部位の部分断面図である。 As shown in FIG. 1, the seal washer 1 is formed by fastening the flange portions 40 and 40 provided at the ends of the water pipe 4 (an example of a fluid pipe) with bolts 2 and nuts. . Used to join 4, specifically, as shown in FIG. 2, the bearing surface 20, 30 of the bolt 2 or nut 3 and the flange portion of the water pipe 4 tightened by the bolt 2 and nut 3 40, and is used to seal the bolt hole 40s formed in the flange portion 40. 2 is a partial cross-sectional view taken along the line AA in FIG.
シールワッシャ１は、図２及び図３に示すように、ゴム等の弾性部材で形成され且つボルト２の軸部２１を挿通させる挿通孔１０ｓを有する環状をなすシール部材１０と、シール部材１０よりもボルト２又はナット３の座面２０・３０側に配置される枠部材１１とを有する。なお、図３（ａ）は、シールワッシャ１をフランジ部側から視た正面図であり、図３（ｂ）は、シールワッシャ１の軸心ＣＬ１を通る断面図である。 As shown in FIGS. 2 and 3, the seal washer 1 includes an annular seal member 10 formed of an elastic member such as rubber and having an insertion hole 10 s through which the shaft portion 21 of the bolt 2 is inserted. And the frame member 11 arranged on the side of the bearing surface 20/30 of the bolt 2 or the nut 3. 3A is a front view of the seal washer 1 viewed from the flange portion side, and FIG. 3B is a cross-sectional view of the seal washer 1 passing through the axis CL1.
シール部材１０は、フランジ部側となる端部にボルト孔周縁部位４０ｆと密接するためのシール面１０ｆが設定されており、シール面１０ｆは軸心ＣＬ１に直交する平坦面をなしている。シール部材１０に形成された挿通孔１０ｓは、ボルト２の軸部２１との間を密封するためにボルト２の軸部２１の外径にほぼ一致する径に設定されている。 The seal member 10 is provided with a seal surface 10f that is in close contact with the bolt hole peripheral portion 40f at the end on the flange portion side, and the seal surface 10f is a flat surface orthogonal to the axis CL1. The insertion hole 10 s formed in the seal member 10 is set to a diameter that substantially matches the outer diameter of the shaft portion 21 of the bolt 2 in order to seal between the shaft portion 21 of the bolt 2.
シール部材１０の挿通孔１０ｓの周縁部には、外力が作用しない自然状態においてシール面１０ｆから軸方向に突出するヒレ部１２が設けられている。ヒレ部１２は、少なくともその先端部がボルト孔４０ｓとボルト２の軸部２１との間の隙間に挿入可能な寸法に設定されている。ヒレ部１２は、挿通孔１０ｓの周縁部に沿って環状をなしており、先端から基端に向かうにつれて内周面１２ａとの間の径方向厚みが太くなるテーパ状の外周面１２ｂを有する。ヒレ部１２は、軸心ＣＬ１を通る断面形状は周方向のいずれの部位でも同一になるように、軸心ＣＬ１回りの対称形状にされている。また、テーパ状の外周面１２ｂの径方向外側端とシール面１０ｆの径方向内側端とは円弧面で接続されており、テーパ状の外周面１２ｂとシール面１０ｆとの接続部位に応力が集中することを避けている。 At the peripheral edge of the insertion hole 10s of the seal member 10, there is provided a fin 12 that protrudes in the axial direction from the seal surface 10f in a natural state where no external force acts. The fin portion 12 is set so that at least a tip portion thereof can be inserted into a gap between the bolt hole 40 s and the shaft portion 21 of the bolt 2. The fin portion 12 has an annular shape along the peripheral edge portion of the insertion hole 10s, and has a tapered outer peripheral surface 12b that increases in thickness in the radial direction from the inner peripheral surface 12a toward the base end. The fin portion 12 has a symmetrical shape around the axis CL1 so that the cross-sectional shape passing through the axis CL1 is the same in any part in the circumferential direction. Further, the radially outer end of the tapered outer peripheral surface 12b and the radially inner end of the seal surface 10f are connected by a circular arc surface, and stress is concentrated on the connection portion between the tapered outer peripheral surface 12b and the seal surface 10f. Avoid doing that.
本実施形態では、図３（ｂ）に例示するように、ボルトの軸部外径Ｄ１をφ16mmとし、規格となるボルト孔径をφ19mmとした場合に、ヒレ部１２の先端部の外径Ｄ２をφ17.5ｍｍ（＝ボルトの軸部外径＋1.5ｍｍ）とし、ヒレ部１２の基端部の外径Ｄ３をφ19.5ｍｍ（＝ボルト孔径＋0.5mm）にしている。ヒレ部１２のシール面１０ｆからの突出距離Ｄ４は、3mmである。このように、ヒレ部をボルト孔４０ｓとボルト軸部２１との間の隙間に挿入可能にするために、ヒレ部１２の先端部の外径をボルト孔径よりも小さく設定している。さらに、締結に伴いボルト孔４０ｓの周縁を密接するために、ヒレ部１２の基端部の外径をボルト孔４０ｓよりも大きく設定している。これにより、ボルト孔径が規格の値よりも小さい場合や大きい場合でも、ボルト・ナット締結時においてヒレ部１２がボルト孔に嵌入するため、締結に伴ってヒレ部１２が捻れることなく密封することが可能となる。 In this embodiment, as illustrated in FIG. 3B, when the bolt shaft outer diameter D 1 is φ16 mm and the standard bolt hole diameter is φ19 mm, the outer diameter D of the tip portion of the fin portion 12. 2 and φ17.5mm (= axial outer diameter + 1.5 mm of the bolt), and an outer diameter D 3 of the base end portion of the fin portion 12 in φ19.5mm (= V pore diameter + 0.5 mm). Protrusion distance D 4 from the sealing surface 10f of the fin portion 12 is 3 mm. Thus, in order to allow the fin portion to be inserted into the gap between the bolt hole 40s and the bolt shaft portion 21, the outer diameter of the tip portion of the fin portion 12 is set smaller than the bolt hole diameter. Further, the outer diameter of the base end portion of the fin portion 12 is set larger than that of the bolt hole 40 s in order to closely contact the peripheral edge of the bolt hole 40 s with the fastening. As a result, even when the bolt hole diameter is smaller or larger than the standard value, the fin portion 12 is fitted into the bolt hole when the bolt and nut are fastened, so that the fin portion 12 is sealed without being twisted with the fastening. Is possible.
図２及び図３に示すように、枠部材１１は、シール部材１０よりも硬質な材料（例えば金属）で形成されており、例えば板金加工や鋳造により製造される。枠部材１１は、ボルト２の軸部２１を挿通するための孔１１ｓが形成された環状の底壁１１ａと、底壁１１ａの周縁から軸方向に起立する側壁１１ｂとを有し、底壁１１ａ及び側壁１１ｂとでシール部材１０の一部を収容する形状をなしている。側壁１１ｂの軸方向厚みは、シール部材１０の反フランジ部側端面からシール面１０ｆまでの厚みよりも薄く設定されており、これにより、枠部材１１（側壁１１ｂの先端）とフランジ部４０との間に間隙を設けて、シール部材１０を圧縮するための圧縮代を設定している。なお、使用時には、シール部材１０と枠部材１１とは接着剤で接着されることが好ましい。接着することで水圧により枠部材１１からシール部材１０が外れて破損するおそれを防止することが可能となる。 As shown in FIGS. 2 and 3, the frame member 11 is formed of a material (for example, metal) harder than the seal member 10, and is manufactured by sheet metal processing or casting, for example. The frame member 11 has an annular bottom wall 11a in which a hole 11s for inserting the shaft portion 21 of the bolt 2 is formed, and a side wall 11b that rises in the axial direction from the periphery of the bottom wall 11a. And the side wall 11b has a shape for accommodating a part of the seal member 10. The axial thickness of the side wall 11b is set to be thinner than the thickness from the end surface on the side opposite to the flange of the seal member 10 to the seal surface 10f, whereby the frame member 11 (the tip of the side wall 11b) and the flange 40 A compression margin for compressing the seal member 10 is set by providing a gap therebetween. In use, the seal member 10 and the frame member 11 are preferably bonded with an adhesive. By adhering, it is possible to prevent the seal member 10 from being detached from the frame member 11 due to water pressure and being damaged.
次に上記構成のシールワッシャ１を用いて、図２に示すように、水道管４のフランジ部４０に形成されたボルト孔４０ｓにボルト２を挿通し、ボルト２の先端部にナット３を取り付けて、ボルト２及びナット３を締め付けてフランジ部４０を締結する方法について説明する。ここでは、ボルト側とナット側とにそれぞれシールワッシャ１を配置するため、二つのシールワッシャを用いる例を示す。まず、ボルト孔に挿通された既存のボルトおよびナットを１本ずつ取り出し、フランジの座面を清掃する。その後、シールワッシャ１を介在させたボルト及びナットで接続する。 Next, using the seal washer 1 having the above configuration, as shown in FIG. 2, the bolt 2 is inserted into the bolt hole 40 s formed in the flange portion 40 of the water pipe 4, and the nut 3 is attached to the tip of the bolt 2. A method of fastening the flange portion 40 by fastening the bolt 2 and the nut 3 will be described. Here, an example is shown in which two seal washers are used in order to dispose the seal washers 1 on the bolt side and the nut side, respectively. First, existing bolts and nuts inserted through the bolt holes are taken out one by one, and the seating surface of the flange is cleaned. Then, it connects with the bolt and nut which interposed the seal washer 1.
まず、第一のシールワッシャ１ａ（１）を挿通したボルト軸部２１をボルト孔４０ｓに通し、フランジ部４０とボルト２の座面２０との間に第一のシールワッシャ１ａを介在させた状態とする。このとき、シール部材１０に突設されたヒレ部１２をボルト孔４０ｓとボルトの軸部２１との間の隙間に挿入する。これにより、シール部材１０のボルト孔４０ｓに対する径方向移動がヒレ部１２によって或る程度規制されることになる。なお、ボルト２の座面２０と第一のシールワッシャ１ａとの間に、必要に応じてスペーサ５を介在させてもよい。 First, the bolt shaft portion 21 through which the first seal washer 1a (1) is inserted is passed through the bolt hole 40s, and the first seal washer 1a is interposed between the flange portion 40 and the seat surface 20 of the bolt 2. And At this time, the fin portion 12 projecting from the seal member 10 is inserted into the gap between the bolt hole 40 s and the bolt shaft portion 21. As a result, the radial movement of the seal member 10 with respect to the bolt hole 40 s is restricted to some extent by the fin portion 12. In addition, you may interpose the spacer 5 between the bearing surface 20 of the volt | bolt 2 and the 1st seal washer 1a as needed.
次に、ボルト軸部２１の先端に第二のシールワッシャ１ｂ（１）を挿通し、ボルト２の先端にナット３を取り付ける。このとき、シール部材１０に突設されたヒレ部１２をボルト孔４０ｓとボルト軸部２１との間の隙間に挿入する。これにより、シール部材１０のボルト孔４０ｓに対する径方向移動がヒレ部１２によって或る程度規制されることになる。なお、ナット３の座面３０と第二のシールワッシャ１ｂとの間に、必要に応じてスペーサ５を介在させてもよい。このようにスペーサ５を用いることで、厚みの異なる種々のフランジ部に対して共通のボルト及びナットを利用でき、部品共通化により製造コストを低減させることが可能となる。 Next, the second seal washer 1 b (1) is inserted into the tip of the bolt shaft portion 21, and the nut 3 is attached to the tip of the bolt 2. At this time, the fin portion 12 protruding from the seal member 10 is inserted into the gap between the bolt hole 40 s and the bolt shaft portion 21. As a result, the radial movement of the seal member 10 with respect to the bolt hole 40 s is restricted to some extent by the fin portion 12. In addition, you may interpose the spacer 5 between the seat surface 30 of the nut 3, and the 2nd seal washer 1b as needed. By using the spacer 5 in this way, common bolts and nuts can be used for various flange portions having different thicknesses, and it becomes possible to reduce manufacturing costs by sharing parts.
そして、ボルト２及びナット３を締め付けてフランジ部４０を締結する。ボルト２及びナット３を締め付けるのに伴って、ヒレ部１２がボルト孔４０ｓの奥側へ向けて押圧され、若干弾性変形する。ヒレ部１２は、図３（ｂ）に示すように、先端から基端に向かうにつれて内周面１２ａとの間の径方向厚みが太くなるテーパ状の外周面１２ｂを有するので、弾性変形に伴い弾性反発力を蓄積する。このとき、例えば図４に模式的に示すように、ボルト孔４０ｓの軸ＣＬ２に対してシール部材の軸心ＣＬ１が径方向一方側にズレていると、ヒレ部１２のうち径方向一方側の部位Ｐ１が径方向他方側の部位Ｐ２に比して多く圧縮される。この圧縮量の差に起因して、シール部材１０の軸心ＣＬ１をボルト孔４０ｓの軸ＣＬ２に一致させる方向に弾性反発力Ｆが作用し、シール部材１０とボルト孔４０ｓの芯ズレが補正される。 Then, the bolt 2 and the nut 3 are tightened to fasten the flange portion 40. As the bolt 2 and the nut 3 are tightened, the fin portion 12 is pressed toward the back side of the bolt hole 40s and slightly elastically deformed. As shown in FIG. 3 (b), the fin portion 12 has a tapered outer peripheral surface 12b in which the radial thickness between the inner peripheral surface 12a and the inner peripheral surface 12a increases from the distal end toward the proximal end. Accumulate elastic repulsion. At this time, for example, as schematically shown in FIG. 4, if the shaft center CL <b> 1 of the seal member is displaced to one side in the radial direction with respect to the axis CL <b> 2 of the bolt hole 40 s, The part P1 is compressed more than the part P2 on the other side in the radial direction. Due to the difference in the compression amount, the elastic repulsive force F acts in the direction in which the axis CL1 of the seal member 10 coincides with the axis CL2 of the bolt hole 40s, and the misalignment between the seal member 10 and the bolt hole 40s is corrected. The
したがって、締結時にボルト孔４０ｓとシール部材１０（ボルト軸部２１）とが芯ズレしようとしても、ヒレ部１２によりシール部材１０とボルト孔４０ｓの芯ズレを無くす方向に弾性反発力Ｆが作用して、シール部材１０とボルト孔４０ｓの芯ズレが補正されるので、ボルト孔４０ｓを周方向に亘り均一に密封でき、安定性を向上させることが可能となる。特に、位置合わせし難い漏出状態での作業時やボルト孔の製造誤差が存在するとき、フランジ部同士が相対的に位置ズレしている場合に好適である。 Therefore, even if the bolt hole 40s and the seal member 10 (bolt shaft portion 21) are about to be misaligned at the time of fastening, the elastic repulsive force F acts in a direction that eliminates the misalignment between the seal member 10 and the bolt hole 40s. Thus, since the misalignment between the seal member 10 and the bolt hole 40s is corrected, the bolt hole 40s can be uniformly sealed in the circumferential direction, and the stability can be improved. In particular, it is suitable when the flange portions are relatively misaligned when working in a leak state that is difficult to align or when there is a manufacturing error of the bolt hole.
また、締結後においても、水道管４（流体管）への荷重によりボルト軸部２１に曲げ荷重が作用したとしても、ヒレ部１２による芯ズレ補正機能により、曲げ荷重に起因するシール部材１０の芯ズレを抑制又は防止することが可能となる。 Even after the fastening, even if a bending load acts on the bolt shaft portion 21 due to the load on the water pipe 4 (fluid pipe), the center misalignment correction function by the fin portion 12 causes the sealing member 10 caused by the bending load. It becomes possible to suppress or prevent the misalignment.
なお、予め、上記の手順でシールワッシャ付きのボルト・ナットに交換した後、意匠登録第１３０５８２５号公報に示す配管補強金具をフランジ部に取り付けることが好ましい。詳細な説明は省略するが、図５に示すように、ゴム板などのパッキン６１を接着剤にてリング状に接着してフランジ部４０の径方向先端部に配置し、図６に示すように、配管補強金具６０を構成する複数の分割片６０ａ・６０ｂ同士をボルト６２及びナット６３で締結する。フランジ部同士４０・４０の間から漏水が発生している場合は、複数のボルト孔のうち１箇所のボルト孔をシールワッシャ付きのボルト及びナットで締結せずに残しておき、そこから排水しながら配管補強金具６０を取り付けし、最後に残りのボルト孔にシールワッシャ付きのボルト及びナットで締め付けを行う。 In addition, it is preferable to attach the pipe reinforcement metal fitting shown in Design Registration No. 1305825 to the flange portion after exchanging the bolt and nut with the seal washer in advance by the above procedure. Although a detailed description is omitted, as shown in FIG. 5, a packing 61 such as a rubber plate is bonded in a ring shape with an adhesive and arranged at the distal end in the radial direction of the flange portion 40, as shown in FIG. The plurality of split pieces 60 a and 60 b constituting the pipe reinforcing metal fitting 60 are fastened with bolts 62 and nuts 63. If water leakage occurs between the flanges 40, 40, leave one bolt hole out of the multiple bolt holes without fastening with bolts and nuts with seal washers, and drain from there. Then, the pipe reinforcing metal fitting 60 is attached, and finally, the remaining bolt holes are tightened with bolts and nuts with seal washers.
ここで、上記配管補強金具を取り付け、上記ヒレ部の無いシール部材を有する従来のシールワッシャを用いた場合と、上記ヒレ部を設けたシール部材を有する本発明のシールワッシャを用いた場合とで漏水確認試験を行ったところ、ヒレ部を設けた場合の方がヒレ部の無い場合よりも１ＭＰａ程度耐圧を向上させることができた。上記比較は、ボルト及びナットの締め付けトルク等のその他条件を一致させてある。 Here, when the pipe reinforcing bracket is attached and the conventional seal washer having the seal member without the fin portion is used, and when the seal washer of the present invention having the seal member having the fin portion is used. When a water leakage confirmation test was performed, the pressure resistance was improved by about 1 MPa when the fin portion was provided than when the fin portion was not provided. In the above comparison, other conditions such as bolt and nut tightening torque are matched.
また、一般的な水道圧にてボルト孔から漏水している状態において、本発明のシールワッシャを用いたところ、手締めで止水することができた。これは、ヒレ部によるシール部材の芯ズレ補正が適切に発揮されたためと考える。 Further, when the seal washer of the present invention was used in a state where water leaked from the bolt hole due to a general water pressure, water could be stopped by hand tightening. This is considered to be because the misalignment correction of the seal member by the fin portion was appropriately exhibited.
本発明は上述した実施形態に何ら限定されるものではなく、本発明の趣旨を逸脱しない範囲内で種々の改良変更が可能である。 The present invention is not limited to the embodiment described above, and various improvements and modifications can be made without departing from the spirit of the present invention.
例えば、本実施形態において、ヒレ部１２は、先端から基端に向かうにつれて径方向厚みが太くなるいわゆる先細り形状をなしているが、ボルト孔とボルト軸部との間に挿入することができ、シール部材のボルト孔に対する径方向移動を或る程度抑制することができるのであれば、径方向厚みが変わらない形状であってもよい。また、本実施形態では、ヒレ部１２の外周面１２ｂとシール面１０ｆとは円弧面で連続しているが、これ以外の形状でもよい。また、本実施形態では、ヒレ部１２によるボルト孔４０ｓへの引っかかり効果を的確に得るために、少なくとも5mm以上突出していることが好ましい。 For example, in the present embodiment, the fin portion 12 has a so-called tapered shape in which the radial thickness increases from the distal end toward the proximal end, but can be inserted between the bolt hole and the bolt shaft portion, As long as the radial movement of the seal member with respect to the bolt hole can be suppressed to some extent, the shape in which the radial thickness does not change may be used. Moreover, in this embodiment, although the outer peripheral surface 12b of the fin part 12 and the sealing surface 10f are continuing on the circular arc surface, shapes other than this may be sufficient. Further, in the present embodiment, it is preferable that the protrusion protrudes at least 5 mm or more in order to accurately obtain the effect of catching the bolt hole 40s by the fin portion 12.
本発明において、流体管は、水道管に限定されるものではなく、各種の液体や気体が流れる流体管であってよい。 In the present invention, the fluid pipe is not limited to a water pipe, and may be a fluid pipe through which various liquids and gases flow.
１…シールワッシャ
１０…シール部材
１０ｆ…シール面
１０ｓ…挿通孔
１２…ヒレ部
１２ｂ…外周面
１２ａ…内周面
１１…枠部材
２…ボルト
２０…ボルトの座面
２１…ボルトの軸部
３…ナット
３０…ナットの座面
４…水道管（流体管）
４０…フランジ部
４０ｓ…ボルト孔
４０ｆ…ボルト孔の周縁部位
５…スペーサ
DESCRIPTION OF SYMBOLS 1 ... Seal washer 10 ... Seal member 10f ... Seal surface 10s ... Insertion hole 12 ... Fin part 12b ... Outer peripheral surface 12a ... Inner peripheral surface 11 ... Frame member 2 ... Bolt 20 ... Bolt seat surface 21 ... Bolt shaft part 3 ... Nut 30 ... Nut seat 4 ... Water pipe (fluid pipe)
40 ... Flange 40s ... Bolt hole 40f ... Peripheral part 5 of the bolt hole ... Spacer
Claims (5)
前記フランジ部側となる端部に前記ボルト孔の周縁部位と密接するためのシール面が設定され、弾性部材で形成され且つ前記ボルトの軸部を挿通させる挿通孔を有する環状をなすシール部材と、前記シール部材よりも前記ボルト又はナットの座面側に配置され且つ前記シール部材よりも硬質の枠部材とを具備し、
前記シール部材の前記挿通孔の周縁部には、外力が作用しない自然状態において前記シール面から軸方向に突出し、前記ボルト孔と前記ボルトの軸部との間の隙間に挿入可能なヒレ部が設けられていることを特徴とするシールワッシャ。 A seal washer interposed between a seat surface of a bolt or nut and a flange portion of a fluid pipe fastened by the bolt and nut, for sealing a bolt hole formed in the flange portion;
An annular sealing member having an insertion hole that is formed of an elastic member and has an insertion hole through which the shaft portion of the bolt is inserted, in which a sealing surface is set in close contact with the peripheral portion of the bolt hole at an end portion on the flange portion side; A frame member that is disposed closer to the bearing surface side of the bolt or nut than the seal member and is harder than the seal member;
In the peripheral portion of the insertion hole of the seal member, there is a fin portion that protrudes in the axial direction from the seal surface in a natural state where no external force acts, and can be inserted into a gap between the bolt hole and the shaft portion of the bolt. A seal washer characterized by being provided.
前記フランジ部と前記ボルト又はナットの座面との間に、弾性部材で形成されたシール部材を有するシールワッシャを介在させるとともに、前記シール部材に突設されたヒレ部を前記ボルト孔と前記ボルトの軸部との間の隙間に挿入し、前記ボルト及びナットを締め付けて前記フランジ部を締結することを特徴とする流体管フランジ部の締結方法。 A fluid pipe flange portion fastening method in which a bolt is inserted into a bolt hole formed in a flange portion of a fluid pipe, a nut is attached to a tip end portion of the bolt, and the bolt and the nut are fastened to fasten the flange portion. There,
A seal washer having a seal member formed of an elastic member is interposed between the flange portion and the seat surface of the bolt or nut, and a fin portion protruding from the seal member is inserted into the bolt hole and the bolt. A fastening method for a fluid pipe flange part, wherein the flange part is fastened by inserting the bolt and a nut into a gap between the shaft part and the bolt part.
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| JP2015249379A JP6157577B2 (en) | 2015-12-22 | 2015-12-22 | Fastening method for sealing member and water pipe flange |
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| JP2012071777A Division JP6026122B2 (en) | 2012-03-27 | 2012-03-27 | Fastening method of seal washer and fluid pipe flange |
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| JP2017111693A Division JP6751689B2 (en) | 2017-06-06 | 2017-06-06 | Fastening method of water pipe flange, seal member, and fastening structure of water pipe flange |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101828694B1 (en) * | 2016-08-23 | 2018-02-12 | 현대제철 주식회사 | Hold down device of shearing apparatus |
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|---|---|---|---|---|
| US4230326A (en) * | 1978-08-17 | 1980-10-28 | Lister Bolt & Chain Ltd. | Sealing assembly for ball or rod mills and the like |
| JPS5640217U (en) * | 1979-09-05 | 1981-04-14 | ||
| JPS60110708U (en) * | 1983-12-29 | 1985-07-27 | キ−パ−株式会社 | Seal washers |
| JPS6117516U (en) * | 1984-07-05 | 1986-02-01 | 内山工業株式会社 | Seal washers |
| JP2007063908A (en) * | 2005-09-01 | 2007-03-15 | Noriatsu Kojima | Drain pipe joint |
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- 2015-12-22 JP JP2015249379A patent/JP6157577B2/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4230326A (en) * | 1978-08-17 | 1980-10-28 | Lister Bolt & Chain Ltd. | Sealing assembly for ball or rod mills and the like |
| JPS5640217U (en) * | 1979-09-05 | 1981-04-14 | ||
| JPS60110708U (en) * | 1983-12-29 | 1985-07-27 | キ−パ−株式会社 | Seal washers |
| JPS6117516U (en) * | 1984-07-05 | 1986-02-01 | 内山工業株式会社 | Seal washers |
| JP2007063908A (en) * | 2005-09-01 | 2007-03-15 | Noriatsu Kojima | Drain pipe joint |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101828694B1 (en) * | 2016-08-23 | 2018-02-12 | 현대제철 주식회사 | Hold down device of shearing apparatus |
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