JPH04131587A - Hose joint structure - Google Patents
Hose joint structureInfo
- Publication number
- JPH04131587A JPH04131587A JP2252707A JP25270790A JPH04131587A JP H04131587 A JPH04131587 A JP H04131587A JP 2252707 A JP2252707 A JP 2252707A JP 25270790 A JP25270790 A JP 25270790A JP H04131587 A JPH04131587 A JP H04131587A
- Authority
- JP
- Japan
- Prior art keywords
- hose
- angle
- outer cylinder
- end part
- joint structure
- 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.)
- Pending
Links
- 230000002093 peripheral effect Effects 0.000 claims description 6
- 238000007789 sealing Methods 0.000 abstract description 14
- 239000002184 metal Substances 0.000 abstract description 5
- 238000002788 crimping Methods 0.000 description 7
- 238000003780 insertion Methods 0.000 description 6
- 230000037431 insertion Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 210000000078 claw Anatomy 0.000 description 1
Landscapes
- Joints That Cut Off Fluids, And Hose Joints (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、機器類の油圧配管等に用いられるホース継手
構造の改良に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a hose joint structure used for hydraulic piping of equipment, etc.
従来の技術
周知のように、例えば車両のパワーステアリング装置等
に用いられる油圧配管は、耐圧ホースの端部がシール性
の高いホース継手金具によってベーンポンプ等に連結さ
れるようになっており、その−例として実公平2−81
56号公報等に記載されたものがある。As is well known in the art, for example, in hydraulic piping used in vehicle power steering systems, the end of a pressure-resistant hose is connected to a vane pump or the like using a highly sealable hose fitting. As an example, Jikko 2-81
Some of these are described in Publication No. 56, etc.
即ち、従来のホース継手構造は、第4図に示すように、
先端部の雄ねじ部3がベーンポンプの吐出口に接続され
る金属製の内筒1と、該内筒1の外周に配置されて、前
記雄ねじ部3介して一体に形成された金属製の外筒2と
から主として構成され、該両者1.2間には耐圧ホース
4の一端部4aが挿通される円環状の挿通穴5が形成さ
れている。That is, the conventional hose joint structure, as shown in FIG.
A metal inner cylinder 1 having a male threaded part 3 at its tip connected to a discharge port of a vane pump, and a metal outer cylinder arranged on the outer periphery of the inner cylinder 1 and integrally formed through the male threaded part 3. 2, and an annular insertion hole 5 through which one end 4a of the pressure hose 4 is inserted is formed between the two.
そして、該挿通穴5内にホース4の一端部4aが挿通さ
れた後に、外筒2の外周面2a軸方向の前後2ケ所を、
平爪タイプの加締め治具によって所定トルクで縦断面略
V字形に加締めることにより、ホース4が内筒1と外筒
2に圧着して連結されるようになっている。After the one end 4a of the hose 4 is inserted into the insertion hole 5, the outer circumferential surface 2a of the outer cylinder 2 is inserted at two places in the axial direction, front and rear.
The hose 4 is crimped and connected to the inner cylinder 1 and the outer cylinder 2 by crimping them into a substantially V-shaped vertical section with a flat claw type crimping jig at a predetermined torque.
発明が解決しようとする課題
ところで、前述のようなホース継手構造において、油圧
や液圧が加わる耐圧ホース4の密封条件としては、加締
め部6,7等で発生したいずれか−ケ所のホース4外周
面への接触圧力が該ホース4の円周上で途切れなく連続
して作用し、かつ油圧以上であることが必要である。Problems to be Solved by the Invention By the way, in the above-described hose joint structure, the sealing conditions for the pressure-resistant hose 4 to which hydraulic pressure or hydraulic pressure is applied are such that the hose 4 is sealed at any of the locations where the pressure is applied, such as at the crimped portions 6 and 7. It is necessary that the contact pressure to the outer circumferential surface acts continuously on the circumference of the hose 4 without interruption, and that it is equal to or higher than the hydraulic pressure.
然し乍ら、実際の車両の走行中や機器類の作動中である
ことを想定して油圧が変動しかつ加振条件が加わった状
態下でのホースの油漏れ試験においては、ホース4は内
筒、外筒1.2に対して微小ではあるが軸方向へ往復運
動(振動)しており、そのため、密封条件は必ずしも前
記の条件のみならず、内筒、外筒1,2とホース4との
シール面での接触圧力分布形状を十分条件として考慮す
ることも必要であることが明白となった。However, in an oil leak test of the hose under conditions where the oil pressure fluctuates and vibration conditions are applied, assuming that the vehicle is actually running or equipment is in operation, the hose 4 was There is a slight reciprocating motion (vibration) in the axial direction relative to the outer cylinder 1.2, so the sealing conditions are not necessarily limited to the above conditions, but also the conditions between the inner cylinder, the outer cylinders 1 and 2, and the hose 4. It became clear that it was also necessary to consider the shape of the contact pressure distribution on the sealing surface as a sufficient condition.
そして、オイルシール等の往復動シールの密封理論によ
れば、シール接触圧力分布形状において、油圧側接触圧
力勾配を(di)/dx)oil、大気側接触圧力勾配
を(dp/clx)airとしたときの密封条件は、d
p/dx l oi l−M^X≧l dp/dx l
air−MAXの式に表された条件であると解釈され
ている。According to the sealing theory of reciprocating seals such as oil seals, in the seal contact pressure distribution shape, the hydraulic side contact pressure gradient is (di)/dx)oil, and the atmospheric side contact pressure gradient is (dp/clx)air. The sealing conditions are d
p/dx l oi l-M^X≧l dp/dx l
This is interpreted as a condition expressed in the air-MAX formula.
(p−接触圧力、x=接触部の座標、 d=微分の記号
)
一方、このようなシール接触圧力分布形状は、加締め部
6,7の形状つまり夫々の対向する傾斜面8,9.’t
o、11の各角度の如何によって支配されている。(p-contact pressure, x=coordinates of the contact portion, d=sign of differential) On the other hand, such a seal contact pressure distribution shape is based on the shape of the caulking portions 6, 7, that is, the opposing inclined surfaces 8, 9, . 't
It is governed by the angles o and 11.
ところが、前記従来のホース継手構造にあっては、前述
のようなオイルシール等の密封理論が全く考慮されずに
、前後の傾斜面8,9,10.11角度が路間−に設定
されている。つまり、第5図にも示すように外筒2の前
端側の第1加締め部6の内筒1の中心軸Oに対する垂直
平面XIを基準とした前側の第1傾斜面8角度θ1と後
側の第2傾斜面9角度θ、とが略等しく設定され、また
、後端側の第2加締め部7の前記垂直平面X、を基準と
した前側の第3傾斜面10角度θ3と後側の第4傾斜面
11角度θ4も略等しく設定されている。However, in the conventional hose joint structure, the angles of the front and rear slopes 8, 9, 10, and 11 are set to be between the paths, without taking into account the sealing theory of oil seals, etc. as described above. There is. In other words, as shown in FIG. The angle θ of the second inclined surface 9 on the side is set to be approximately equal, and the angle θ3 of the third inclined surface 10 on the front side with respect to the vertical plane X of the second crimped portion 7 on the rear end side The angle θ4 of the fourth inclined surface 11 on the side is also set substantially equal.
したがって、前記音イルシールの密封理論の条件を満足
できず、内筒1.外筒2とホース4間の良好なシール性
能を維持できない。Therefore, the conditions of the sealing theory of the sound seal cannot be satisfied, and the inner cylinder 1. Good sealing performance between the outer cylinder 2 and the hose 4 cannot be maintained.
課題を解決するための手段
本発明は、前記従来のホース構造における問題点に鑑み
て案出されたもので、とりわけ外筒の加締め部の略■字
形の傾斜面中、内筒の中心軸に対する垂直平面を基準と
して外筒の前端部側の傾斜面角度を後端部側の傾斜面角
度よりも大きく設定したことを特徴としている。Means for Solving the Problems The present invention has been devised in view of the problems in the conventional hose structure, and in particular, the central axis of the inner cylinder is fixed on the approximately ■-shaped inclined surface of the crimped portion of the outer cylinder. It is characterized in that the angle of the inclined surface on the front end side of the outer cylinder is set larger than the angle of the inclined surface on the rear end side with respect to a plane perpendicular to the outer cylinder.
作用
前記構成によれば、前述のようなオイルシールの密封理
論から導かれる条件を満足することができる。つまり、
加締め部の外筒前端部側の傾斜面角度を後端部の傾斜面
角度よりも大きく設定することにより、接触圧力がホー
スの挿通方向と反対方向に強く作用することとなり、こ
れによって良好なシール性能が維持できる。Effect: According to the above configuration, the conditions derived from the oil seal sealing theory as described above can be satisfied. In other words,
By setting the slope angle of the front end of the outer cylinder of the caulking part to be larger than the slope angle of the rear end, the contact pressure acts strongly in the opposite direction to the hose insertion direction, which results in a good Seal performance can be maintained.
実施例 以下、本発明の一実施例を図面に基づいて詳述する。Example Hereinafter, one embodiment of the present invention will be described in detail based on the drawings.
第1図は本発明に係るホース継手構造の一実施例を示し
、図中21は金属製の内筒、22は内筒21の外周面2
3を被う金属製の外筒であって、この内筒21と外筒2
2とは互いの前端部21a。FIG. 1 shows an embodiment of the hose joint structure according to the present invention, in which reference numeral 21 indicates a metal inner cylinder, and 22 indicates an outer peripheral surface 2 of the inner cylinder 21.
This is a metal outer cylinder that covers the inner cylinder 21 and the outer cylinder 2.
2 is the front end portion 21a of each other.
22aに有するねじ部材24を介して一体に形成されて
いると共に、両者21.22の間には耐圧ホース25の
一端部25aが挿通される円環状の挿通穴26が形成さ
れている。また、前記ねじ部材24は、スパナ等の工具
が係着する六角頭部24aと、該六角頭部24aの先端
に有しパワーステアリング装置のベーンポンプ等に螺着
される中空状の雄ねじ部24bとから構成されている。21 and 22, and an annular insertion hole 26 through which one end 25a of the pressure hose 25 is inserted is formed between the two 21 and 22. The screw member 24 also includes a hexagonal head 24a to which a tool such as a spanner is engaged, and a hollow male threaded portion 24b at the tip of the hexagonal head 24a to be screwed onto a vane pump or the like of a power steering device. It consists of
前記外筒22は、外周面27の略中央位置に軸方向へ2
つの加締め部28.29が円周方向に沿って形成されて
おり、この前後の第1.第2加締め部28.29は、挿
通穴26にホース25の一端部25aを挿通した後に所
定の加締め治具によって縦断面略V字形に絞り形成され
ている。 そして、この外筒22前端側の第1加締め部
28は、第2図にも示すように内筒21の中心軸Oに対
する垂直平面X1を基準として前端部22a側の第1傾
斜面30角度θI(油圧側接触圧力勾配)が後端部22
b側の第2傾斜面31角度θ、(大気側接触圧力勾配)
よりも小さく設定されている。The outer cylinder 22 has two parts extending in the axial direction approximately at the center of the outer circumferential surface 27.
Two caulking portions 28 and 29 are formed along the circumferential direction, and the first and second caulking portions 28 and 29 are formed along the circumferential direction. The second crimping portions 28 and 29 are formed by inserting one end portion 25a of the hose 25 into the insertion hole 26, and then constricting the second crimping portions 28, 29 to have a substantially V-shaped longitudinal section using a predetermined crimping jig. The first caulking portion 28 on the front end side of the outer cylinder 22 is formed at a first inclined surface 30 at an angle of 30 degrees on the front end part 22a side with respect to a plane X1 perpendicular to the central axis O of the inner cylinder 21, as shown in FIG. θI (hydraulic side contact pressure gradient) is
b side second inclined surface 31 angle θ, (atmosphere side contact pressure gradient)
is set smaller than.
即ち、第1傾斜面30は、中心軸Oに対して略垂直状に
形成されて小さな角度θ、に設定されている一方、第2
傾斜面31は第1傾斜面30よりも緩やかに形成されて
大きな角度θ、に設定されている。That is, the first inclined surface 30 is formed substantially perpendicular to the central axis O and is set at a small angle θ, while the second
The inclined surface 31 is formed more gently than the first inclined surface 30 and is set at a larger angle θ.
また、後端側の第2加締め部29は、内[21の中心軸
Oに対する垂直平面X、を基準として前端部22a側の
第3傾斜面32角度θ、(油圧側接触圧力勾配)が後端
部22b側の第4傾斜面33角度θ4(大気側接触圧力
勾配)よりも大きく設定されている。即ち、第3傾斜面
32は、第2傾斜面31と同様に緩やかに形成されて大
きな角度θ3に設定されている一方、第4傾斜面33は
、第1傾斜面30と同様に中心軸Oに対して略垂直状に
形成されて小さな角度θ4に設定されている。In addition, the second crimped portion 29 on the rear end side has an angle θ of the third inclined surface 32 on the front end portion 22a side (hydraulic side contact pressure gradient) with respect to the vertical plane X with respect to the central axis O of the inner [21]. The angle θ4 of the fourth inclined surface 33 on the rear end portion 22b side is set larger than the angle θ4 (atmospheric side contact pressure gradient). That is, like the second inclined surface 31, the third inclined surface 32 is formed gently and set at a large angle θ3, while the fourth inclined surface 33, like the first inclined surface 30, is formed with a large angle θ3. It is formed substantially perpendicular to the angle θ4 and set at a small angle θ4.
したがって、この実施例によれば、前述の第2加締め部
29ではオイルシールの密封理論に沿った形となるが、
第1加締め部28ではその逆の条件となる。つまり、第
1加締め部28の第1傾斜面角度θ、を第2傾斜面角度
θ、よりも小さく設定することにより第3図の右欄に示
すように接触圧力がl dp/dx : oil−MA
X < l dp/dx l air−MAXとなる。Therefore, according to this embodiment, the second crimped portion 29 has a shape that conforms to the oil seal sealing theory;
In the first crimped portion 28, the opposite condition is met. That is, by setting the first inclined surface angle θ of the first crimped portion 28 to be smaller than the second inclined surface angle θ, the contact pressure is reduced to l dp/dx : oil as shown in the right column of FIG. -MA
X < l dp/dx l air-MAX.
したがって、第1加締め部28による圧力が、ホース2
5に対して該ホース25の抜は方向とは反対方向の先端
部方向に強く作用する。この結果、ホース継手が加振さ
れてホース25に軸方向への往復運動(振動)が継続的
に加わっても該ホース25が挿通穴26から不用意に抜
は出すことがなく、常時確実な連結状態が得られる。Therefore, the pressure caused by the first crimping portion 28 is applied to the hose 2
5, the removal of the hose 25 acts strongly in the direction opposite to the direction of the distal end. As a result, even if the hose joint is vibrated and the hose 25 is continuously subjected to reciprocating motion (vibration) in the axial direction, the hose 25 will not be accidentally pulled out of the insertion hole 26, and the hose 25 will always be reliably pulled out. A connected state is obtained.
一方、第2加締め部29の第3傾斜面角度θ。On the other hand, the third inclined surface angle θ of the second crimped portion 29.
を第4傾斜面角度θ4よりも大きく設定することにより
、第3図の左欄に示すように接触圧力がdp/dx l
oil−MAX> : dp/dx l air−M
AXとなる。したがって、第2加締め部29による圧力
が、ホース25の挿通方向とは反対方向に強く作用する
。この結果、第2加締め部29付近のホース25の内周
面と内筒21の外周面23との接触面圧が高くかつこの
面圧分布が第3傾斜面32側が大きくなるため、常時確
実かつ良好なシール性能が維持される。By setting θ4 to be larger than the fourth slope angle θ4, the contact pressure becomes dp/dxl as shown in the left column of FIG.
oil-MAX> : dp/dx l air-M
It becomes AX. Therefore, the pressure exerted by the second crimping portion 29 acts strongly in the direction opposite to the direction in which the hose 25 is inserted. As a result, the contact surface pressure between the inner circumferential surface of the hose 25 and the outer circumferential surface 23 of the inner tube 21 near the second crimped portion 29 is high, and this surface pressure distribution is larger on the third inclined surface 32 side, so that it is always reliable. And good sealing performance is maintained.
前、本発明は、前記実施例の構成に限定されるものでは
なく、他の油圧機器に適用できることは勿論である。It goes without saying that the present invention is not limited to the configuration of the embodiment described above, but can be applied to other hydraulic equipment.
発明の効果
以上の説明で明らかなように、本発明に係るホース継手
構造によれば、外筒の外周面に形成される前後の加締め
部の各傾斜角度を夫々所定の角度に設定したため、長期
に亘り良好なシール性能が維持できる。Effects of the Invention As is clear from the above explanation, according to the hose joint structure according to the present invention, since the inclination angles of the front and rear crimped parts formed on the outer peripheral surface of the outer cylinder are respectively set to predetermined angles, Good sealing performance can be maintained over a long period of time.
第1図は本発明のホース継手構造の一実施例を示す部分
断面図、第2図は本実施例の要部説明図、第3図は本実
施例による加締め部の傾斜角度とホースと内筒の接触圧
力分布を示す特性図、第4図は従来のホース継手構造を
示す要部断面図、第5図は同従来の要部説明図である。
21・・・内筒、22・・・外筒、22a・・・前端部
、22b・・・後端部、23・・・内筒外周面、25・
・・ホース、25a・・・一端部、27・・・外筒外周
面、29・・・加締め部、32・・・第3傾斜面、33
・・第4傾斜面、O・・・中心軸、X・・・垂直平面。Fig. 1 is a partial sectional view showing an embodiment of the hose joint structure of the present invention, Fig. 2 is an explanatory diagram of the main parts of this embodiment, and Fig. 3 is a diagram showing the relationship between the inclination angle of the crimped part and the hose according to the present embodiment. A characteristic diagram showing the contact pressure distribution of the inner cylinder, FIG. 4 is a sectional view of a main part showing a conventional hose joint structure, and FIG. 5 is an explanatory diagram of the main part of the conventional hose joint structure. 21... Inner cylinder, 22... Outer cylinder, 22a... Front end, 22b... Rear end, 23... Inner cylinder outer peripheral surface, 25...
...Hose, 25a...One end, 27...Outer cylinder outer peripheral surface, 29...Clinching part, 32...Third slope, 33
... Fourth inclined plane, O... Central axis, X... Vertical plane.
Claims (1)
スの一端部を挿通し、前記外筒の外周面を縦断面略V字
形に加締めて前記内外筒とホースとを連結するホース継
手構造において、前記外筒の加締め部の略V字形の傾斜
面中、内筒の中心軸に対する垂直平面を基準として外筒
の前端部側の傾斜面角度を、後端部側の傾斜面角度より
も大きく設定したことを特徴とするホース継手構造。(1) One end of the hose is inserted between an inner cylinder and an outer cylinder that covers the outer peripheral surface of the inner cylinder, and the outer peripheral surface of the outer cylinder is crimped into a substantially V-shaped longitudinal section to connect the inner and outer cylinders. In a hose joint structure for connecting a hose, the angle of the inclined surface on the front end side of the outer cylinder is set at the rear of the substantially V-shaped slope of the caulked portion of the outer cylinder, with respect to a plane perpendicular to the central axis of the inner cylinder. A hose joint structure characterized by having a slope angle larger than that of the end side.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2252707A JPH04131587A (en) | 1990-09-21 | 1990-09-21 | Hose joint structure |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2252707A JPH04131587A (en) | 1990-09-21 | 1990-09-21 | Hose joint structure |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH04131587A true JPH04131587A (en) | 1992-05-06 |
Family
ID=17241134
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2252707A Pending JPH04131587A (en) | 1990-09-21 | 1990-09-21 | Hose joint structure |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH04131587A (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5797629A (en) * | 1996-04-16 | 1998-08-25 | Dana Corporation | Hose coupling and method of securing a hose to the coupling by crimping |
DE19824518A1 (en) * | 1998-06-02 | 1999-12-09 | Continental Teves Ag & Co Ohg | Method of connecting hydraulic pressure hose to hydraulic pipe, and especially for hydraulic brake systems or clutches of motor vehicles |
JP2013007749A (en) * | 2012-07-27 | 2013-01-10 | Nichirin Co Ltd | Outer diameter measuring apparatus and outer diameter measurement method using the same |
WO2016002809A1 (en) * | 2014-06-30 | 2016-01-07 | 株式会社ブリヂストン | Hose with joint |
-
1990
- 1990-09-21 JP JP2252707A patent/JPH04131587A/en active Pending
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5797629A (en) * | 1996-04-16 | 1998-08-25 | Dana Corporation | Hose coupling and method of securing a hose to the coupling by crimping |
DE19824518A1 (en) * | 1998-06-02 | 1999-12-09 | Continental Teves Ag & Co Ohg | Method of connecting hydraulic pressure hose to hydraulic pipe, and especially for hydraulic brake systems or clutches of motor vehicles |
DE19824518B4 (en) * | 1998-06-02 | 2007-06-06 | Continental Teves Ag & Co. Ohg | Fastening arrangement for connecting a hydraulic pressure hose with a hydraulic pipe |
JP2013007749A (en) * | 2012-07-27 | 2013-01-10 | Nichirin Co Ltd | Outer diameter measuring apparatus and outer diameter measurement method using the same |
WO2016002809A1 (en) * | 2014-06-30 | 2016-01-07 | 株式会社ブリヂストン | Hose with joint |
JPWO2016002809A1 (en) * | 2014-06-30 | 2017-04-27 | 株式会社ブリヂストン | Hose with fitting |
CN106662278A (en) * | 2014-06-30 | 2017-05-10 | 株式会社普利司通 | Hose with joint |
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