JPH0512593B2 - - Google Patents
Info
- Publication number
- JPH0512593B2 JPH0512593B2 JP60214797A JP21479785A JPH0512593B2 JP H0512593 B2 JPH0512593 B2 JP H0512593B2 JP 60214797 A JP60214797 A JP 60214797A JP 21479785 A JP21479785 A JP 21479785A JP H0512593 B2 JPH0512593 B2 JP H0512593B2
- Authority
- JP
- Japan
- Prior art keywords
- flange
- bolt
- surface pressure
- container
- containers
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Landscapes
- Connection Of Plates (AREA)
- Mutual Connection Of Rods And Tubes (AREA)
- Flanged Joints, Insulating Joints, And Other Joints (AREA)
Description
【発明の詳細な説明】
「産業上の利用分野」
本発明は大型工作機械（コラム、ブリツジ、ク
ロスレール等）、その他各種容器のフランジ継手
に関するものである。DETAILED DESCRIPTION OF THE INVENTION "Field of Industrial Application" The present invention relates to flange joints for large machine tools (columns, bridges, cross rails, etc.) and other various containers.
「従来の技術」
従来のフランジ継手の一例を第４図および第５
図に示す。"Prior art" An example of a conventional flange joint is shown in Figures 4 and 5.
As shown in the figure.
０１，０２は容器、０１ａ，０２ａはそれぞれ
容器０１，０２のフランジ、０１ｂ，０２ｂはそ
れぞれフランジ０１ａ，０２ａに穿けられたボル
ト孔、０３はボルト、０４はナツトである。 01 and 02 are containers, 01a and 02a are flanges of the containers 01 and 02, respectively, 01b and 02b are bolt holes drilled in the flanges 01a and 02a, respectively, 03 is a bolt, and 04 is a nut.
フランジ０１ａ，０２ａのボルト孔０１ｂ，０
２ｂの軸心は容器壁の中心からボルト０３が十分
締付けられるように距離ｌだけ離されている。フ
ランジ０１ａ，０２ａは幅に対して高さが同程度
以下である。 Bolt holes 01b, 0 of flanges 01a, 02a
The axis of 2b is spaced a distance l from the center of the container wall so that the bolt 03 can be sufficiently tightened. The flanges 01a and 02a have a height that is approximately the same or less than a width.
「発明が解決しようとする問題点」
フランジ継手は外力に対する剛性が直接的に加
工精度に影響を及ぼすため、特に注意をはらつて
いるが、第５図に示すように、外力Ｑが作用した
場合、これが容器壁を流れ、フランジ継手に作用
するが、力は図中の○ア部近傍を多く流れ、ボルト
０３の位置には殆んど流れない。"Problems to be Solved by the Invention" Particular attention must be paid to flange joints because the rigidity against external forces directly affects processing accuracy. However, as shown in Figure 5, when external force Q is applied, , this flows along the container wall and acts on the flange joint, but most of the force flows near the part ○ in the figure, and almost no force flows to the position of the bolt 03.
一方、ボルト０３の締付けによるフランジ０１
ａ，０２ａの合せ面の面圧はボルト０３に近い程
大きく、○ア部近傍には殆んど作用しない。 On the other hand, the flange 01 is tightened by tightening the bolt 03.
The contact pressure on the mating surfaces of a and 02a is greater as it is closer to the bolt 03, and it hardly acts near the part ○a.
従つて、外力Ｑが作用し、○ア部近傍に力が多く
流れると面圧が殆んどないため、○ア部近傍は開口
し、フランジ０１ａ，０２ａの曲げ変形抵抗で対
応することになるため、面圧が存在する場合の面
内剛性抵抗に比べて軸方向の変位δは極めて大き
くなり、即ち剛性は極端に小さくなる。 Therefore, when external force Q acts and a large amount of force flows near part ○A, there is almost no surface pressure, so the vicinity of part ○A opens and the bending deformation resistance of flanges 01a and 02a is used to cope with the problem. Therefore, the displacement δ in the axial direction becomes extremely large compared to the in-plane stiffness resistance when surface pressure is present, that is, the stiffness becomes extremely small.
大きな剛性を保つためには、容器壁の軸方向の
延長線上のフランジの合せ面が開口しないこと、
即ち、面内抵抗条件下に設計する必要があつた。 In order to maintain high rigidity, the mating surface of the flange on the axial extension of the container wall must not be open;
That is, it was necessary to design under in-plane resistance conditions.
「問題点を解決するための手段」
本発明は上記従来の問題点を解決したもので、
それぞれ端部にフランジを有し、フランジをボル
トにて締結する２箇の容器において、ボルトの軸
心を各容器の肉厚のほぼ中心とし、２箇の容器の
中、ボルトが貫通するフランジ側のボルト締結位
置に対応する容器のフランジとの連結部に切欠き
を設け、フランジのボルト締結部のボルト位置の
まわりに隙間を設けたフランジ継手である。"Means for Solving the Problems" The present invention solves the above-mentioned conventional problems.
In two containers each having a flange at the end and the flanges fastened together with bolts, the axis of the bolt is approximately the center of the wall thickness of each container, and the flange side of the two containers through which the bolt passes This is a flange joint in which a notch is provided at the connection part with the flange of the container corresponding to the bolt fastening position of the flange, and a gap is provided around the bolt position of the bolt fastening part of the flange.
「作用」
(1) ボルトの位置のまわりの一部に隙間を設けた
ため、フランジとの連結部の切欠いた孔の外側
にボルト締付け時の面圧（第３図ａのσ0）が大
きく発生する。``Effect'' (1) Because a gap is provided in a part around the bolt position, a large surface pressure (σ 0 in Figure 3 a) is generated on the outside of the notched hole in the connection with the flange when tightening the bolt. do.
(2) 外力Ｑが作用するとそれは切欠いてないとこ
ろ（第１図S2）を流れてから、フランジの合せ
面（第３図ａのσ1）に流れ込む。(2) When an external force Q is applied, it flows through the uncut area (S 2 in Figure 1) and then flows into the mating surface of the flange (σ 1 in Figure 3a).
(3) フランジのボルト孔の軸心が容器の肉厚の中
心に近付けたため、面圧（第３図ａのσ0）は容
器壁の軸方向の延長線上に大きく発生してい
る。(3) Since the axis of the bolt hole in the flange is brought closer to the center of the wall thickness of the container, a large surface pressure (σ 0 in FIG. 3a) is generated along the axial extension of the container wall.
(4) 従つて、フランジの合せ面に流れ込む力と、
ボルト締付けによる面圧は効率よく対応し、第
３図ａのσ0＋σ1の状態となり、合せ面には点線
に示すとおり面圧が残存する。(4) Therefore, the force flowing into the mating surface of the flange,
The surface pressure due to bolt tightening is efficiently dealt with, resulting in a state of σ 0 +σ 1 as shown in FIG. 3a, and surface pressure remains on the mating surfaces as shown by the dotted line.
(5) ボルトの位置のまわりの一部に隙間を設けな
かつた場合のボルト締付けによる面圧と、外力
による応力の関係を第３図のｂに示す。(5) Figure 3b shows the relationship between the surface pressure due to bolt tightening and the stress due to external force when no gap is provided in a part around the bolt position.
このように、隙間を設けなかつた場合には、
ボルト間の中央部近傍は面圧がなくなつて開口
し、剛性低下の起ることが判る。 In this way, if no gap is provided,
It can be seen that the area near the center between the bolts becomes open due to the loss of surface pressure, resulting in a decrease in rigidity.
(6) 本発明のように、面圧を有することは、面内
抵抗で外力に対応していることであり、従来の
面外曲げ変形抵抗のものに比べて軸方向剛性を
大幅に向上することができる。(6) Having surface pressure as in the present invention means that it can respond to external force with in-plane resistance, which greatly improves axial rigidity compared to conventional out-of-plane bending deformation resistance. be able to.
「実施例」
本発明の一実施例を第１図ないし第３図ａに示
す。"Embodiment" An embodiment of the present invention is shown in FIGS. 1 to 3a.
１，２は容器、１ａ，２ａはそれぞれ容器１，
２のフランジ、１ｂはフランジ１ａに穿けたボル
ト貫通孔、２ｂはフランジ２ａに穿けたボルトね
じ孔で、孔１ｂ，２ｂの軸心をそれぞれ容器１，
２の肉厚のほぼ中心とする。３は容器１のボルト
締付位置に対応するフランジ１ａとの連結部に設
けた切欠きで、幅S1と高さS3をボルト締結上必要
最小限にする。４はフランジ１ａの幅より若干直
径の小さい円形の隙間で、フランジ１ａ，２ａの
合せ面でフランジ１ａのボルト締結部のボルト位
置の囲りに設けている。５はボルトである。 1 and 2 are containers, 1a and 2a are containers 1 and 2a, respectively.
Flange 2, 1b is a bolt through hole drilled in flange 1a, 2b is a bolt screw hole drilled in flange 2a, and the axes of holes 1b and 2b are aligned with containers 1 and 2, respectively.
It should be approximately at the center of the wall thickness of 2. 3 is a notch provided at the connection part with the flange 1a corresponding to the bolt tightening position of the container 1, which minimizes the width S1 and height S3 necessary for bolt tightening. Reference numeral 4 denotes a circular gap having a diameter slightly smaller than the width of the flange 1a, and is provided around the bolt position of the bolted portion of the flange 1a on the mating surface of the flanges 1a and 2a. 5 is a bolt.
第３図ａ，ｂで、σ0が初締付け時の面圧分布、
σ1が設計条件の外力作用時の外力によるフランジ
面の引張応力、σ0＋σ1が設計条件の外力作用時の
残存面圧分布である。 In Figures 3a and b, σ 0 is the surface pressure distribution at the time of initial tightening,
σ 1 is the tensile stress on the flange surface due to an external force when an external force is applied under the design conditions, and σ 0 +σ 1 is the residual surface pressure distribution when the external force is applied under the design conditions.
第３図ａ，ｂはフランジ合せ面の面圧分布の説
明図で、ａは本実施例の場合、ｂは隙間４を設け
ない場合である。 3A and 3B are explanatory diagrams of the surface pressure distribution on the flange mating surfaces, where a shows the case of this embodiment and b shows the case where the gap 4 is not provided.
「発明の効果」
本発明は上記構成であるので、外力作用時のフ
ランジの合せ面には、全域面圧が残存し、面内変
形抵抗で外力に対応し、本実施例（第３図ｂは含
まれない）では軸方向剛性として一体形断面の80
％以上を達成することができるすぐれた効果を奏
するのである。"Effects of the Invention" Since the present invention has the above configuration, surface pressure remains in the entire area on the mating surfaces of the flanges when an external force is applied, and the external force can be coped with by in-plane deformation resistance. (not included), the axial stiffness is 80 for the integral cross section.
% or more.
第１図および第２図は本発明の一実施例で、第
１図は平面図、第２図は第１図のＡ−Ａ断面図、
第３図ａ、ｂはフランジ合せ面の面圧分布図で、
ａは本実施例のフランジ合せ面の面圧の状態、ｂ
はボルトの位置の囲りに隙間を設けない場合であ
る。第４図および第５図は従来のフランジ継手
で、第４図は斜視図、第５図は第４図のＢ−Ｂ断
面図である。
１，２…容器、１ａ，２ａ…フランジ、１ｂ…
ボルト貫通孔、２ｂ…ボルトねじ孔、３…切欠
き、４…隙間、５…ボルト。
1 and 2 show an embodiment of the present invention, in which FIG. 1 is a plan view, FIG. 2 is a sectional view taken along line AA in FIG. 1, and FIG.
Figures 3a and 3b are surface pressure distribution diagrams of the flange mating surfaces.
a is the state of surface pressure on the flange mating surface of this example, b
is the case where no gap is provided around the bolt position. 4 and 5 show a conventional flange joint, where FIG. 4 is a perspective view and FIG. 5 is a sectional view taken along line BB in FIG. 4. 1, 2... Container, 1a, 2a... Flange, 1b...
Bolt through hole, 2b... Bolt screw hole, 3... Notch, 4... Gap, 5... Bolt.
Claims (1)
をボルトにて締結する２箇の容器において、前記
ボルトの軸心を前記各容器の肉厚のほぼ中心と
し、前記２箇の容器の中、ボルトが貫通するフラ
ンジ側のボルト締結位置に対応する容器の前記フ
ランジとの連結部に切欠きを設け、前記フランジ
のボルト締結部のボルト位置のまわりに隙間を設
けたことを特徴とするフランジ継手。1. In two containers each having a flange at its end and the flanges fastened together with bolts, the axis of the bolt is approximately at the center of the wall thickness of each container, and the bolt is A flange joint characterized in that a notch is provided in a connecting portion of the container with the flange corresponding to a bolt fastening position on the flange side through which the flange passes, and a gap is provided around the bolt position of the bolt fastening portion of the flange.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60214797A JPS6275189A (en) | 1985-09-30 | 1985-09-30 | Flange joint |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60214797A JPS6275189A (en) | 1985-09-30 | 1985-09-30 | Flange joint |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6275189A JPS6275189A (en) | 1987-04-07 |
| JPH0512593B2 true JPH0512593B2 (en) | 1993-02-18 |
Family
ID=16661680
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60214797A Granted JPS6275189A (en) | 1985-09-30 | 1985-09-30 | Flange joint |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6275189A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4654514B2 (en) * | 2000-12-26 | 2011-03-23 | 日産自動車株式会社 | Piston crank mechanism for reciprocating internal combustion engine |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS631044Y2 (en) * | 1979-07-23 | 1988-01-12 | ||
| JPS584139A (en) * | 1981-06-30 | 1983-01-11 | Fujitsu Ltd | Formation of pattern |
| JPS60129507U (en) * | 1984-02-10 | 1985-08-30 | 三菱重工業株式会社 | bolted structure |
-
1985
- 1985-09-30 JP JP60214797A patent/JPS6275189A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6275189A (en) | 1987-04-07 |
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