JPH0451258Y2 - - Google Patents
Info
- Publication number
- JPH0451258Y2 JPH0451258Y2 JP1987164171U JP16417187U JPH0451258Y2 JP H0451258 Y2 JPH0451258 Y2 JP H0451258Y2 JP 1987164171 U JP1987164171 U JP 1987164171U JP 16417187 U JP16417187 U JP 16417187U JP H0451258 Y2 JPH0451258 Y2 JP H0451258Y2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- seal
- slope
- atmosphere
- reinforcing ring
- 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
Links
- 230000003014 reinforcing effect Effects 0.000 claims description 19
- 230000002093 peripheral effect Effects 0.000 claims description 8
- 239000006096 absorbing agent Substances 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
Landscapes
- Sealing With Elastic Sealing Lips (AREA)
Description
【考案の詳細な説明】
「産業上の利用分野」
この考案は、シヨツクアブソーバー等の油圧機
器用耐圧シールに関するものである。[Detailed description of the invention] "Field of industrial application" This invention relates to a pressure-resistant seal for hydraulic equipment such as a shock absorber.
「従来の技術、考案が解決せんとする問題点」
従来、内部に高圧を発生する油圧機器において
は、第４図に示すように、シヤフト７をシールす
るオイルシール９に圧力が作用することを防止す
るために、オイルシール９の圧力側に耐圧シール
を設けている。"Problems to be solved by conventional techniques and ideas" Conventionally, in hydraulic equipment that generates high pressure internally, as shown in FIG. In order to prevent this, a pressure-resistant seal is provided on the pressure side of the oil seal 9.
ところで、従来の油圧機器用耐圧シールは、Ｌ
型補強環２の水平部２ａの内周縁部から圧力が作
用する側に向つて斜めにシールリツプ４を設けた
ものであるため、圧力がシールリツプ４の外周面
側に作用してシールリツプ４をシヤフト７に押圧
し、これによつてシールリツプ４の摩擦力が増大
すると共に、先端の摩耗が激しい等の問題があつ
た。 By the way, the conventional pressure seal for hydraulic equipment is L
Since the seal lip 4 is provided obliquely from the inner peripheral edge of the horizontal portion 2a of the mold reinforcing ring 2 toward the side on which pressure is applied, the pressure acts on the outer peripheral surface of the seal lip 4, causing the seal lip 4 to move toward the shaft 7. This caused problems such as an increase in the frictional force of the seal lip 4 and severe wear at the tip.
「問題点を解決するための手段」
この考案は前記従来の課題を解決するために、
Ｌ型補強環２の内外周部にゴム３，３′を焼付け
てなる環状のシール本体１の内周面５における補
強環２の水平部２ａよりも大気側Ｈの位置に、大
気側Ｈと加圧側Ｇの両基端からそれぞれリツプ先
端に向つて相反方向に上り勾配をなす大気側斜面
４ｂ及び加圧側斜面４ａを有するシールリツプ４
を設け、シール本体１の加圧側斜面４ａのシヤフ
ト７に対する傾斜角αと、前記大気側斜面４ｂの
シヤフト３に対する傾斜角βを90°≧α≧βに設
定してなる耐圧シールを提案するものである。"Means for solving the problem" This invention aims to solve the above-mentioned conventional problem.
An annular seal body 1 is formed by baking rubber 3, 3' onto the inner and outer peripheries of the L-shaped reinforcing ring 2, and on the inner circumferential surface 5 of the reinforcing ring 2, a ring is attached at a position closer to the atmosphere than the horizontal part 2a of the reinforcing ring 2. A seal lip 4 having an atmosphere side slope 4b and a pressure side slope 4a that slope upward in opposite directions from both base ends of the pressure side G toward the tip of the lip.
A pressure-resistant seal is proposed in which the inclination angle α of the pressure side slope 4a of the seal body 1 with respect to the shaft 7 and the inclination angle β of the atmosphere side slope 4b with respect to the shaft 3 are set to 90°≧α≧β. It is.
「作用」
機器の作動時に発生する圧力はその大部分が端
面６に作用することになるが、一部の圧力はシー
ル本体１の内周面５及びシールリツプ４の加圧側
Ｇの斜面４ａに作用し、この圧力によつて補強環
２の内周側のゴム３′を圧縮しながらシールリツ
プ４をシヤフト７から後退させる方向に変位させ
る結果、シールリツプ４のシヤフト７に対する摩
擦が軽減されると共に、90°≧α≧βの関係によ
りシールリツプ４がオイルを容易に洩らさないよ
うに適度な耐圧性能を維持することになる。"Function" Most of the pressure generated during operation of the equipment acts on the end face 6, but some pressure acts on the inner peripheral surface 5 of the seal body 1 and the slope 4a of the pressure side G of the seal lip 4. This pressure compresses the rubber 3' on the inner peripheral side of the reinforcing ring 2 and displaces the seal lip 4 in the direction of retreating from the shaft 7. As a result, the friction of the seal lip 4 against the shaft 7 is reduced, and the friction of the seal lip 4 against the shaft 7 is reduced. Due to the relationship °≧α≧β, the seal lip 4 maintains appropriate pressure resistance so that oil does not easily leak.
なお、90°≧α≧βの関係を生かすために、設
計上補強環２の水平部２ａの先端からシールリツ
プ４の先端間のＡ寸法をできるだけ小さく設定し
（補強環２の水平部２ａの先端に面するゴムの厚
さを薄くする）、内周面５側に作用する圧力の大
部分を補強環で受け、加圧側Ｇに面する斜面４ａ
への圧力負担をできるだけ軽減する用に配慮する
ことは当然である。 In addition, in order to take advantage of the relationship of 90°≧α≧β, the dimension A between the tip of the horizontal portion 2a of the reinforcing ring 2 and the tip of the seal lip 4 is set as small as possible (the tip of the horizontal portion 2a of the reinforcing ring 2). (to reduce the thickness of the rubber facing the pressure side G), most of the pressure acting on the inner circumferential surface 5 side is received by the reinforcing ring, and the slope 4a facing the pressure side G is
Naturally, consideration should be given to reducing the pressure burden on the body as much as possible.
第３図は、この考案と従来の耐圧シールにおけ
る圧力Ｐと摩擦力Ｆとの関係を実験した結果を示
したもので、この結果から従来の耐圧シールが圧
力Ｐの増大につれて摩擦力Ｆが増加するのに対し
て、この考案の耐圧シールは圧力Ｐの増大につれ
て徐々に摩擦力Ｆが減少することが分る。 Figure 3 shows the results of an experiment on the relationship between pressure P and frictional force F in this invention and a conventional pressure-resistant seal.The results show that as the pressure P increases, the frictional force F increases in the conventional pressure-resistant seal. In contrast, it can be seen that in the pressure-resistant seal of this invention, the frictional force F gradually decreases as the pressure P increases.
この場合、この考案の耐圧シールにおいては、
その耐圧限界圧力P2において圧力が大気側Ｈに
抜けてオイルシールに圧力が作用することによつ
て摩擦力Ｆが急増することになるが、この耐圧限
界圧力P2を実際の使用圧力範囲の最大値P1に安
全率を掛けた値よりも大きくとることによつて、
使用圧力の範囲内において摩擦力の小さいシール
が可能となる。 In this case, in the pressure-resistant seal of this invention,
At the withstand pressure limit P 2 , the pressure is released to the atmosphere side H and the pressure acts on the oil seal, causing a sudden increase in the frictional force F. By taking a value larger than the maximum value P 1 multiplied by the safety factor,
A seal with low frictional force is possible within the working pressure range.
この耐圧限界圧力P2は、Ａ，Ｂ，Ｃ，Ｄの各
寸法及びシールリツプ４の傾斜角α，βの設定に
より自在に調整することができ、耐圧限界圧力
P2を定めることによつて実用上の使用圧力の範
囲に適宜設定することができる。 This pressure limit P2 can be freely adjusted by setting the dimensions A, B, C, and D and the angles of inclination α and β of the seal lip 4.
By determining P 2 , it can be set appropriately within the practical working pressure range.
「実施例」
以下この考案を図面に示す実施例について説明
すると、耐圧シール本体１はＬ型補強環２の外周
及び内周側にゴム３，３′を焼付けて環状に形成
されている。``Embodiment'' The present invention will be described below with reference to an embodiment shown in the drawings.The pressure-resistant seal body 1 is formed into an annular shape by baking rubber 3, 3' onto the outer and inner peripheries of an L-shaped reinforcing ring 2.
内周側のゴム３′は、補強環２の水平部２ａの
先端からその内面側及び外周の垂直部２ｂの内面
側にかけて焼付けられ、その内周面５にはシール
リツプ４が一体に形成されている。 The inner rubber 3' is baked from the tip of the horizontal portion 2a of the reinforcing ring 2 to its inner surface and to the inner surface of the outer vertical portion 2b, and a seal lip 4 is integrally formed on the inner surface 5 thereof.
シール本体１は、補強環２の水平部２ａの端面
６に機器内の圧力が作用し、また補強環２の水平
部２ａの内周面側の端面６′は大気側Ｈに位置す
るように構成され、シールリツプ４はシール本体
１の内周面５においてこの加圧側Ｇの端面６より
も離れた位置、即ち補強環２の水平部２ａの先端
に対面する部分よりも大気側Ｈに偏つた位置（第
２図におけるＢ寸法＜Ｃ寸法）に突設されてい
る。 The seal body 1 is designed so that the pressure inside the device acts on the end face 6 of the horizontal part 2a of the reinforcing ring 2, and the end face 6' on the inner peripheral surface side of the horizontal part 2a of the reinforcing ring 2 is located on the atmospheric side H. The seal lip 4 is located on the inner circumferential surface 5 of the seal body 1 at a position farther away from the end face 6 on the pressure side G, that is, closer to the atmosphere side H than the part facing the tip of the horizontal portion 2a of the reinforcing ring 2. It is provided protrudingly at a position (B dimension <C dimension in FIG. 2).
そして、シールリツプ４は、加圧側及び大気側
の基端からそれぞれ先端に向つて相反方向に上り
勾配をなす斜面４ａ，４ｂを有し、その加圧側Ｇ
に面する斜面４ａ及び大気側Ｈに面する斜面４ｂ
のシヤフト７に対する角度α及びβは90°≧α≧
βの関係に設定されており、また補強環２の水平
部２ａの先端からシールリツプ４の先端間のＡ寸
法は設計上できるだけ小さく設定されている。 The seal lip 4 has slopes 4a and 4b that slope upward in opposite directions from the base end on the pressure side and the atmosphere side, respectively, toward the tip.
A slope 4a facing the atmosphere side H and a slope 4b facing the atmosphere side H
The angles α and β with respect to the shaft 7 are 90°≧α≧
The relationship is β, and the dimension A between the tip of the horizontal portion 2a of the reinforcing ring 2 and the tip of the seal lip 4 is set to be as small as possible in terms of design.
このように構成されたシール本体１は、第２図
に示すように外筒８の上部に装着されたオイルシ
ール９と軸受１０との間に装着され、シールリツ
プ４の先端をシヤフト７に圧接してシールしてい
る。 The seal body 1 constructed in this way is installed between the oil seal 9 installed on the upper part of the outer cylinder 8 and the bearing 10, as shown in FIG. 2, and the tip of the seal lip 4 is pressed against the shaft 7. It is sealed.
「考案の効果」
以上の通りこの考案によれば、Ｌ型補強環の内
外周部にゴムを焼付けてなる環状のシール本体の
内周面における補強環の水平部よりも大気側の位
置に、大気側と加圧側の両基端からそれぞれリツ
プ先端に向つて相反方向に上り勾配をなす大気側
斜面及び加圧側斜面を有するシールリツプを設
け、加圧側斜面のシヤフトに対する傾斜角αと、
大気側傾斜角βを90°≧α≧βに設定してなるの
で、圧力の一部がシール本体の内周面及びシール
リツプの加圧側の斜面に作用し、この圧力によつ
て補強環の内周側のゴムを圧縮しながらシールリ
ツプをシヤフトから後退させる方向に変位させ、
シールリツプのシヤフトに対する摩擦を軽減する
ことができると共に、90°≧α≧βの関係によつ
てシールリツプにオイルが容易に洩れないように
適度な耐圧性能を維持させることができる。``Effects of the invention'' As described above, according to this invention, on the inner circumferential surface of the annular seal body, which is formed by baking rubber onto the inner and outer peripheries of the L-shaped reinforcing ring, at a position closer to the atmosphere than the horizontal part of the reinforcing ring. A seal lip is provided having an atmosphere side slope and a pressure side slope that slope upward in opposite directions from both the base ends on the atmosphere side and the pressure side toward the tip of the lip, respectively, and an inclination angle α of the pressure side slope with respect to the shaft,
Since the atmospheric side inclination angle β is set to 90°≧α≧β, a part of the pressure acts on the inner peripheral surface of the seal body and the slope on the pressure side of the seal lip, and this pressure causes the inside of the reinforcing ring to Displace the seal lip in the direction of retreating from the shaft while compressing the rubber on the circumference,
The friction of the seal lip against the shaft can be reduced, and due to the relationship of 90°≧α≧β, it is possible to maintain appropriate pressure resistance so that oil does not easily leak from the seal lip.
第１図はこの考案の実施例を示す部分縦断側面
図、第２図はこの考案の耐圧シールを装着した状
態を示す縦断側面図、第３図はこの考案と従来の
耐圧シールにおける圧力Ｐと摩擦力Ｆとの関係を
示す線図、第４図は従来の耐圧シールの装着状態
を示す縦断側面図である。
１……シール本体、２……補強環、２ａ……水
平部、２ｂ……垂直部、３，３′……ゴム、４…
…シールリツプ、５……内周面、６，６′……端
面、７……シヤフト、８……ケース、９……オイ
ルシール、１０……軸受、Ｇ……加圧側、Ｈ……
大気側。
Fig. 1 is a partial longitudinal side view showing an embodiment of this invention, Fig. 2 is a longitudinal sectional side view showing the state in which the pressure seal of this invention is installed, and Fig. 3 shows the pressure P in this invention and the conventional pressure seal. A diagram showing the relationship with the frictional force F, and FIG. 4 is a longitudinal sectional side view showing a state in which a conventional pressure-resistant seal is installed. 1...Seal body, 2...Reinforcement ring, 2a...Horizontal part, 2b...Vertical part, 3, 3'...Rubber, 4...
... Seal lip, 5 ... Inner peripheral surface, 6, 6' ... End surface, 7 ... Shaft, 8 ... Case, 9 ... Oil seal, 10 ... Bearing, G ... Pressure side, H ...
Atmospheric side.
Claims (1)
状のシール本体の内周面における前記補強環の水
平部よりも大気側の位置に、大気側と加圧側の両
基端からそれぞれリツプ先端に向つて相反方向に
上り勾配をなす大気側斜面及び油側斜面を有する
シールリツプを設け、前記シール本体の加圧側斜
面のシヤフトに対する傾斜角αと、前記大気側斜
面のシヤフトに対する傾斜角βを90°≧α≧βに
設定してなることを特徴とする油圧機器用耐圧シ
ール。 At a position on the atmosphere side of the horizontal part of the reinforcing ring on the inner peripheral surface of the annular seal body made by baking rubber on the inner and outer peripheries of the L-shaped reinforcing ring, lip tips are attached from both base ends on the atmosphere side and the pressure side, respectively. A seal lip is provided with an atmosphere-side slope and an oil-side slope that slope upward in opposite directions toward the seal body, and an inclination angle α of the pressure-side slope of the seal body with respect to the shaft and an inclination angle β of the atmosphere-side slope with respect to the shaft are 90. A pressure-resistant seal for hydraulic equipment, characterized by setting °≧α≧β.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1987164171U JPH0451258Y2 (en) | 1987-10-26 | 1987-10-26 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1987164171U JPH0451258Y2 (en) | 1987-10-26 | 1987-10-26 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0167378U JPH0167378U (en) | 1989-04-28 |
| JPH0451258Y2 true JPH0451258Y2 (en) | 1992-12-02 |
Family
ID=31449549
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1987164171U Expired JPH0451258Y2 (en) | 1987-10-26 | 1987-10-26 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0451258Y2 (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58163866A (en) * | 1982-03-18 | 1983-09-28 | カ−ル・フロイデンベルク | Packing ring for radial shaft |
-
1987
- 1987-10-26 JP JP1987164171U patent/JPH0451258Y2/ja not_active Expired
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58163866A (en) * | 1982-03-18 | 1983-09-28 | カ−ル・フロイデンベルク | Packing ring for radial shaft |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0167378U (en) | 1989-04-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH0328005U (en) | ||
| JPH02118177U (en) | ||
| US4208060A (en) | Sealed shaft | |
| JPH0451258Y2 (en) | ||
| JP3425756B2 (en) | Dust cover | |
| JP2557336Y2 (en) | Hydraulic packing for rotary valve | |
| JPH0213812Y2 (en) | ||
| JPH1151194A (en) | Piston packing | |
| JPS6332460Y2 (en) | ||
| JPH0141975Y2 (en) | ||
| JPH0158864U (en) | ||
| JPH0341114Y2 (en) | ||
| US2326355A (en) | Hydraulic packing | |
| JPH074364Y2 (en) | Sealing device | |
| JPH0339638Y2 (en) | ||
| JPH07317911A (en) | Packing for piston | |
| JPH054616Y2 (en) | ||
| JPH0240137U (en) | ||
| JPH053817Y2 (en) | ||
| JP4465738B2 (en) | Sealing device | |
| JPS6318861Y2 (en) | ||
| JPS6133328Y2 (en) | ||
| JPS6249057U (en) | ||
| JPS579361A (en) | Oil seal | |
| JPS62174169U (en) |