JP2009287659A - Sliding seal - Google Patents

Sliding seal Download PDF

Info

Publication number
JP2009287659A
JP2009287659A JP2008140464A JP2008140464A JP2009287659A JP 2009287659 A JP2009287659 A JP 2009287659A JP 2008140464 A JP2008140464 A JP 2008140464A JP 2008140464 A JP2008140464 A JP 2008140464A JP 2009287659 A JP2009287659 A JP 2009287659A
Authority
JP
Japan
Prior art keywords
sliding
lips
circumferential groove
basic
groove
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
Application number
JP2008140464A
Other languages
Japanese (ja)
Inventor
Atsushi Hosokawa
敦 細川
Hideo Nagaoka
秀夫 長岡
Kiyotsugu Takazawa
清継 高沢
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Cable Industries Ltd
Nihon Pisco Co Ltd
Original Assignee
Mitsubishi Cable Industries Ltd
Nihon Pisco Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mitsubishi Cable Industries Ltd, Nihon Pisco Co Ltd filed Critical Mitsubishi Cable Industries Ltd
Priority to JP2008140464A priority Critical patent/JP2009287659A/en
Publication of JP2009287659A publication Critical patent/JP2009287659A/en
Pending legal-status Critical Current

Links

Images

Landscapes

  • Sealing With Elastic Sealing Lips (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a sliding seal exhibiting a stable sealing function over a long period of time by having a sliding lip in contact with a mating member with low contact surface pressure and in a stable attitude. <P>SOLUTION: The sliding seal includes a base X-part 10, and strut projecting parts 20, 21 provided nearer toward fixed lips 4, 5 than a central line C. The projecting parts 20, 21 strut on groove side faces 14, 15 of a recessed peripheral groove 3 and stabilize the attitude of the sliding seal. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、摺動シールに係り、特に、往復運動用、又は、回転運動用に使用できる流体密封のための（正圧・負圧の両方に対応できる）摺動シール（摺動パッキン）に関する。   The present invention relates to a sliding seal, and more particularly to a sliding seal (sliding packing) for fluid sealing (compatible with both positive pressure and negative pressure) that can be used for reciprocating motion or rotational motion. .

従来のこの種の摺動シールとしては、図12に示すように、同図（ａ）のＯリング41や、同図（ｂ）のＤリング42や、同図（ｃ）又は（ｄ）に示すＸリング43, 44が、知られている。同図（ｄ）のＸリング44は、例えば、特許文献１に記載されている。
特開平８−８６３６３号公報 As a conventional sliding seal of this type, as shown in FIG. 12, an O-ring 41 in FIG. 12A, a D-ring 42 in FIG. 12B, and FIG. 12C or FIG. The X-rings 43, 44 shown are known. The X ring 44 shown in FIG. 4D is described in Patent Document 1, for example.
JP-A-8-86363

しかしながら、従来の図12（ａ）（ｂ）のＯリング41，Ｄリング42は、コンプレッションシールであって、未受圧装着状態下で、シール用凹周溝45の溝底46と、回転等の運動を行う軸（ロッド）47の外周面との間で弾性的に圧縮され、これによって、流体の洩れを防ぐ密封作用を行う。
このようなコンプレッションシールのＯリング41やＤリング42では、摺動抵抗が大きく、摩耗も多く、短寿命であるという問題がある。また、Ｏリング41は、回転軸47用としては、捩れによって破損する虞もある。 However, the conventional O-ring 41 and D-ring 42 in FIGS. 12 (a) and 12 (b) are compression seals. It is compressed elastically with the outer peripheral surface of a shaft (rod) 47 that moves, thereby performing a sealing action to prevent fluid leakage.
The compression ring O-ring 41 and D-ring 42 have problems that they have a large sliding resistance, a lot of wear, and a short life. Further, the O-ring 41 may be damaged by twisting for the rotating shaft 47.

そして、図12（ｃ）又は（ｄ）に示したＸリング43, 44では、その側面の谷部（側溝部）に、点在状に突起部（突片部）48, 48が一体に形成され、凹周溝45の姿勢を正常に保つと共に、軸（ロッド）47と連れ廻りをしないようにしていた。
しかしながら、受圧状態下で、周方向に点在する突起部48が凹周溝45の低圧側の側面に接触して、ラジアル外方から見た展開図で、凹凸波形状となる（蛇行する）。このように、凹周溝45内で姿勢が不安定となり、２個の摺接リップ49, 49が周方向に不均一に軸（ロッド）47に圧接して、偏摩耗等を発生し寿命が短いといった問題があった。 In the X rings 43 and 44 shown in FIG. 12 (c) or (d), projections (projection pieces) 48 and 48 are integrally formed in the valley portions (side groove portions) on the side surfaces in a dotted manner. Thus, the posture of the concave groove 45 is kept normal, and the shaft (rod) 47 is not rotated.
However, in the pressure receiving state, the protrusions 48 that are scattered in the circumferential direction come into contact with the side surface on the low-pressure side of the concave groove 45, and in a development view viewed from the radial outside, it has an uneven wave shape (meanders). . Thus, the posture becomes unstable in the concave circumferential groove 45, and the two sliding contact lips 49, 49 are non-uniformly pressed against the shaft (rod) 47 in the circumferential direction, causing uneven wear, etc. There was a problem of being short.

そこで、本発明は、従来のこのような問題を解決して、摺動抵抗が小さく、長期間にわたって安定した良好なシール性能（密封性）を発揮できる摺動シール（摺動パッキンともいう）を提供することを、目的とする。   Accordingly, the present invention provides a sliding seal (also referred to as a sliding packing) that solves such a conventional problem and has a small sliding resistance and can exhibit a stable and stable sealing performance (sealing performance) over a long period of time. The purpose is to provide.

上記目的を達成するため、本発明に係る摺動シールは、凹周溝の溝底側の２個の固定リップと摺動側の２個の摺接リップを有する横断面Ｘ字状の基本Ｘ部を備え、かつ、上記凹周溝の軸心方向溝側面に接触して上記基本Ｘ部の上記凹周溝内の姿勢を保つための突張り用突隆部を、上記基本Ｘ部と一体として、かつ、自由状態の厚さ寸法の中央線よりも、上記固定リップ寄りに偏在して設けたものである。
また、凹周溝の溝底側の２個の固定リップと摺動側の２個の摺接リップを有する横断面Ｘ字状の基本Ｘ部を備え、かつ、上記凹周溝の軸心方向溝側面に接触して上記基本Ｘ部の上記凹周溝内の姿勢を保つための突張り用突隆部を、上記基本Ｘ部と一体として、かつ、自由状態の厚さ寸法の中央線よりも、上記固定リップ寄りに偏在して設け、さらに、上記固定リップのつぶし代を、上記凹周溝の深さ寸法の10％〜25％と大きく設定し、かつ、上記摺接リップのつぶし代を零乃至マイナスに設定したものである。 In order to achieve the above object, a sliding seal according to the present invention is a basic X having a cross-sectional X shape having two fixed lips on the groove bottom side of the concave circumferential groove and two sliding contact lips on the sliding side. And a projecting ridge for contacting the axial groove side surface of the concave groove and maintaining the posture of the basic X portion in the concave circumferential groove integrally with the basic X portion. In addition, it is unevenly provided closer to the fixed lip than the center line of the thickness dimension in the free state.
And a basic X portion having an X-shaped cross section having two fixed lips on the groove bottom side of the concave circumferential groove and two sliding contact lips on the sliding side, and the axial direction of the concave circumferential groove A projecting bulge for contacting the side surface of the groove to maintain the posture of the basic X portion in the concave circumferential groove is integrated with the basic X portion and from the center line of the thickness dimension in a free state. Are also provided in the vicinity of the fixed lip, and the crushing margin of the fixed lip is set to be as large as 10% to 25% of the depth of the concave circumferential groove, and the crushing margin of the sliding contact lip is set. Is set to zero or minus.

また、凹周溝の溝底側の２個の固定リップと摺動側の２個の摺接リップを有する横断面Ｘ字状の基本Ｘ部を備え、かつ、上記凹周溝の軸心方向溝側面に接触して上記基本Ｘ部の上記凹周溝内の姿勢を保つための突張り用突隆部を、上記基本Ｘ部と一体として、かつ、自由状態の厚さ寸法の中央線よりも、上記固定リップ寄りに偏在して設け、さらに、上記突隆部は、軸心方向から見て同一円上に配設した複数本の円弧体をもって、合計中心角度が 270°〜 350°を占める略円環状に、配設されている。
また、凹周溝の溝底側の２個の固定リップと摺動側の２個の摺接リップを有する横断面Ｘ字状の基本Ｘ部を備え、かつ、上記凹周溝の軸心方向溝側面に接触して上記基本Ｘ部の上記凹周溝内の姿勢を保つための突張り用突隆部を、上記基本Ｘ部と一体として、かつ、自由状態の厚さ寸法の中央線よりも、上記固定リップ寄りに偏在して設け、装着受圧状態において上記摺接リップは上記凹周溝の溝側面から常に遊離しているように、上記２個の摺接リップの幅寸法を小さく設定したものである。 And a basic X portion having an X-shaped cross section having two fixed lips on the groove bottom side of the concave circumferential groove and two sliding contact lips on the sliding side, and the axial direction of the concave circumferential groove A projecting bulge for contacting the side surface of the groove to maintain the posture of the basic X portion in the concave circumferential groove is integrated with the basic X portion and from the center line of the thickness dimension in a free state. The ridge is provided with a plurality of arcuate bodies arranged on the same circle when viewed from the axial direction, and has a total central angle of 270 ° to 350 °. It is arranged in a generally annular shape.
And a basic X portion having an X-shaped cross section having two fixed lips on the groove bottom side of the concave circumferential groove and two sliding contact lips on the sliding side, and the axial direction of the concave circumferential groove A projecting bulge for contacting the side surface of the groove to maintain the posture of the basic X portion in the concave circumferential groove is integrated with the basic X portion and from the center line of the thickness dimension in a free state. The width of the two sliding contact lips is set to be small so that the sliding contact lip is always separated from the groove side surface of the concave circumferential groove in the mounted pressure receiving state. It is a thing.

そして、自由状態の横断面において、ラジアル方向の中間位置の軸心方向両側面に形成される側凹部の最奥部の軸心方向位置が、上記固定リップの頂点及び摺接リップの頂点よりも、シール中心寄りに存在するように、上記側凹部を深く形成する。
また、自由状態における固定リップの間の谷部の谷底外径寸法が、凹周溝の溝底の外径寸法よりも、小さく設定され、装着状態において固定リップのつぶしの影響が、摺接リップへ及ばないように構成した。 And in the transverse cross section of the free state, the axial direction position of the innermost part of the side recess formed on both axial sides in the axial direction of the intermediate position in the radial direction is more than the apex of the fixed lip and the sliding contact lip. The side recesses are formed deeply so as to exist near the center of the seal.
In addition, the outer diameter dimension of the valley bottom between the fixed lips in the free state is set smaller than the outer diameter dimension of the groove bottom of the concave circumferential groove, and the influence of the crushing of the fixed lip in the mounted state is It was configured not to reach.

本発明は、次のような著大な効果を奏する。
凹周溝内の溝底寄りの位置で、突隆部によって、安定姿勢を保持でき、しかも、両圧対応可能として、摺接リップは低圧（負圧）から比較的高圧まで、軸（ロッド）に対して低い接触面圧にて摺接し、摺動抵抗が小さく（低摺動摩擦）、安定した優れた密封性（シール性能）を、長期間にわたって発揮し、耐久性にも優れている。
また、凹周溝の溝底へ常に強く接触して、連れ廻りも生じず、一層安定姿勢を保持できる。 The present invention has the following remarkable effects.
A stable position can be maintained by the ridge at the position near the bottom of the groove in the concave circumferential groove, and the sliding contact lip has a shaft (rod) from low pressure (negative pressure) to relatively high pressure so that both pressures can be supported. Slidably contacted at a low contact surface pressure, low sliding resistance (low sliding friction), stable and excellent sealing performance (sealing performance) over a long period of time, and excellent durability.
Further, it is always in strong contact with the groove bottom of the concave circumferential groove, and no rotation occurs, so that a more stable posture can be maintained.

以下、図示の実施の形態に基づき本発明を詳説する。
図１〜図６は、本発明の実施の一形態を示す。本発明に係る摺動シール（摺動パッキンともいう）Ｓは、第１部材１に形成された短形状の凹周溝３内に装着されて、回転自在、及び／又は、軸心方向に往復動自在な軸（ロッド）や筒状体や円盤体等の第２部材２の外周面に摺動自在に接触して密封作用をなす。なお、第１部材１と第２部材２とは、相対的に回転運動、及び／又は、直線的往復運動する箇所に、本発明に係る摺動シールＳは適用可能であり、以下の説明に於て、一例として、第２部材２が運動する場合について、説明する。 Hereinafter, the present invention will be described in detail based on the illustrated embodiment.
1 to 6 show an embodiment of the present invention. The sliding seal (also referred to as sliding packing) S according to the present invention is mounted in a short concave groove 3 formed in the first member 1 so as to be rotatable and / or reciprocating in the axial direction. A slidable contact is made with the outer peripheral surface of the second member 2 such as a movable shaft (rod), a cylindrical body, a disk body or the like, thereby performing a sealing action. Note that the sliding seal S according to the present invention can be applied to a location where the first member 1 and the second member 2 relatively rotate and / or linearly reciprocate, and will be described below. As an example, the case where the second member 2 moves will be described.

この摺動シールＳは、凹周溝３の溝底13側の２個の固定リップ４，５と、摺動（摺接）側の２個の摺接リップ６，７を有する横断面Ｘ字状の基本Ｘ部10を、備えている。
そして、上記凹周溝３の軸心方向溝側面14, 15に接触して、基本Ｘ部10の凹周溝３内の姿勢を（倒れたり傾斜したりしないように）保つための突張り用突隆部（リッジ部）20, 21を、基本Ｘ部10と一体として有している。この摺動シールＳは、ゴム又はプラスチック製であり、一体成型により上記基本Ｘ部10と突隆部20, 21とが、形成される。
また、図１と図２と図３は、自由状態の摺動シールＳを示し、この自由状態での厚さ寸法Ｔ0 の中央線Ｃよりも、固定リップ４，５寄り───ラジアル方向外方───に偏在して設ける。 This sliding seal S has an X-shaped cross section having two fixed lips 4, 5 on the groove bottom 13 side of the concave circumferential groove 3 and two sliding contact lips 6, 7 on the sliding (sliding contact) side. The basic X section 10 is provided.
And, for the tension to maintain the posture in the concave circumferential groove 3 of the basic X portion 10 (so as not to fall down or incline) by contacting the axial groove side surfaces 14 and 15 of the concave circumferential groove 3 The ridges (ridges) 20 and 21 are integrated with the basic X part 10. The sliding seal S is made of rubber or plastic, and the basic X portion 10 and the protruding portions 20 and 21 are formed by integral molding.
1, 2, and 3 show the sliding seal S in a free state, which is closer to the fixed lips 4 and 5 than the center line C of the thickness dimension T 0 in this free state. Established unevenly on the outside.

図２は軸心方向から見た説明図であって、斜線にて示す部位は、突隆部20, 21を示す。即ち、軸心方向から見ると、同一円上に配設された複数本の円弧体８をもって───図２では６本の円弧体８をもって───、合計中心角度が 270°〜 350°を占める略円環状に、配設される。
図１は、図２に於て、（斜線にて示した）円弧体８を切断した摺動シール要部横断面であり、図３は、円弧体８と円弧体８の間隔部９を切断した摺動シール要部横断面である。 そして、図１と図２で明らかなように、固定リップ４，５のつぶし代ΔＴ4 を、十分に大きく設定し、凹周溝３の深さ寸法Ｈ3 の10％〜25％とする。好ましくは、13％〜22％とする。しかも、摺接リップ６，７のつぶし代ΔＴ6 はマイナスに設定する。即ち、摺接リップ７の自由状態の内径寸法は、第２部材２の外径寸法よりも、僅かに大きく設定する。なお、つぶし代ΔＴ6 を零としても良く、そのときは、摺接リップ７の自由状態の内径寸法と、第２部材２の外径寸法とは、同じとなる。 FIG. 2 is an explanatory diagram viewed from the axial direction, and the hatched portions indicate the protruding portions 20 and 21. That is, when viewed from the axial direction, with a plurality of arcuate bodies 8 arranged on the same circle --- with 6 arcuate bodies 8 in FIG. 2, the total center angle is 270 ° to 350 ° Is disposed in a substantially annular shape.
1 is a cross-sectional view of the main part of the sliding seal obtained by cutting the circular arc body 8 (shown by oblique lines) in FIG. 2, and FIG. 3 is a sectional view of the space 9 between the circular arc body 8 and the circular arc body 8. FIG. As apparent from FIGS. 1 and 2, the crushing margin ΔT 4 of the fixed lips 4 and 5 is set sufficiently large so as to be 10% to 25% of the depth dimension H 3 of the concave circumferential groove 3. Preferably, it is 13% to 22%. Moreover, squeeze ΔT 6 of the sliding lip 6 and 7 is set to minus. That is, the inner diameter dimension of the sliding contact lip 7 in the free state is set slightly larger than the outer diameter dimension of the second member 2. The crushing allowance ΔT 6 may be zero, and in that case, the inner diameter dimension of the sliding contact lip 7 in the free state and the outer diameter dimension of the second member 2 are the same.

ところで、図１と図３に示すように、自由状態下で、基本Ｘ部10は外径側（ラジアル方向外方側）の固定リップ４，５の幅寸法Ｗ4 よりも、内径側（ラジアル方向内方側）の摺接リップ６，７の幅寸法Ｗ6 を（十分な差をもって）小さく設定する。言い換えると、基本Ｘ部10の横断面形状は、凹周溝３の溝底13側は軸心方向に大きく翼を拡げ、（第２部材２に対応する）凹周溝３の開口側は、軸心方向に小さく拡げられ、かつ、横断面積の比較に於て、前者の方が大きく設定される。 By the way, as shown in FIGS. 1 and 3, in the free state, the basic X portion 10 has an inner diameter side (radial) than the width dimension W 4 of the fixed lips 4 and 5 on the outer diameter side (radial direction outer side). the width W 6 of the sliding lip 6 and 7 of the inward side) (with sufficient difference) is set small. In other words, the cross-sectional shape of the basic X portion 10 is such that the groove bottom 13 side of the concave circumferential groove 3 greatly expands the wing in the axial direction, and the opening side of the concave circumferential groove 3 (corresponding to the second member 2) is In the comparison with the cross-sectional area, the former is set to be larger in the axial direction.

また、図１〜図５に示す実施の形態では、突隆部20, 21の形状は、軸心方向から見た形状は（既述のように）複数本の円弧体８をもって構成され、合計中心角度が 270°〜 350°を占める略円環状であるが、図１と図４に示すように、摺動シール横断面に於て、軸心方向両側面に形成された側凹部11, 12に対応した、固定リップ４，５の内側面４ａ，５ａに連設（一体形成）されている。なお、突隆部20，21が溝側面14, 15に対応する接触面は、図１，図４では、固定リップ４，５の側方端面４ｂ，５ｂよりも僅かに突出状としている。これを、側方端面４ｂ，５ｂから突出状とせずに、側方端面４ｂ，５ｂと連続面に形成することも好ましい（図示省略）。   In the embodiment shown in FIGS. 1 to 5, the shapes of the protruding portions 20 and 21 are configured with a plurality of arcuate bodies 8 as viewed from the axial direction (as described above). As shown in FIGS. 1 and 4, the side recesses 11 and 12 formed on both side surfaces in the axial center direction in the cross section of the sliding seal, as shown in FIGS. 1 and 4, have a center angle of 270 ° to 350 °. Corresponding to the inner side surfaces 4 a and 5 a of the fixed lips 4 and 5. In addition, the contact surface in which the protruding parts 20 and 21 correspond to the groove side surfaces 14 and 15 is slightly protruded from the side end surfaces 4b and 5b of the fixed lips 4 and 5 in FIGS. It is also preferable to form this on a continuous surface with the side end surfaces 4b, 5b without projecting from the side end surfaces 4b, 5b (not shown).

また、図１と図３に示した自由状態の横断面における、ラジアル方向の中間部位に、側凹部11, 12が、基本Ｘ部10の軸心方向両側面に、形成されているが、この側凹部11, 12の最奥部11Ａ，12Ａの軸心方向位置は、固定リップ４，５の径方向の頂点４Ｅ，５Ｅ、及び、摺接リップ６，７の径方向の頂点６Ｅ，７Ｅよりも、シール中心寄りに存在する。つまり、側凹部11, 12を、従来例の図12（ｃ）（ｄ）よりも、十分に深く形成する。
さらに詳しく図１と図３にて説明すれば、側凹部11の最奥部11Ａは、頂点４Ｅ，６Ｅよりも、軸心方向寸法Ｇ1 ，Ｇ2 だけシール中心寄りに配設され、かつ、側凹部12の最奥部12Ａは、頂点５Ｅ，７Ｅよりも軸心方向寸法Ｇ3 ，Ｇ4 だけシール中心寄りに配設されている。
ここで、Ｇ1 ＝Ｇ3 ，Ｇ2 ＝Ｇ4 ，Ｇ1 ＞Ｇ2 ，Ｇ3 ＞Ｇ4 なる関係式が成立する。 Further, side recesses 11 and 12 are formed on both side surfaces in the axial direction of the basic X portion 10 in the radial intermediate portion in the transverse cross section in the free state shown in FIG. 1 and FIG. The axial positions of the innermost portions 11A and 12A of the side recesses 11 and 12 are from the radial vertices 4E and 5E of the fixed lips 4 and 5, and the radial vertices 6E and 7E of the sliding contact lips 6 and 7, respectively. Is also near the center of the seal. In other words, the side recesses 11 and 12 are formed sufficiently deeper than the conventional examples shown in FIGS.
1 and 3, the innermost part 11A of the side recess 11 is disposed closer to the center of the seal than the apexes 4E and 6E by the axial direction dimensions G 1 and G 2 , and The innermost portion 12A of the side recess 12 is disposed closer to the center of the seal than the apexes 5E and 7E by the axial direction dimensions G 3 and G 4 .
Here, the relational expressions G 1 = G 3 , G 2 = G 4 , G 1 > G 2 , G 3 > G 4 hold.

そして、図４の未受圧装着状態、及び、図５の装着受圧状態（矢印Ｐ0 は流体の圧力を示す）に於て、摺接リップ６，７は、凹周溝３の溝側面14, 15から常に遊離しているように、２個の摺接リップ６，７の幅寸法Ｗ6 を、小さく設定している。
また、２つの固定リップ４，５の間の（外径方向の）谷部16は、図１と図３に示すように、２点鎖線の凹周溝３の外径寸法よりも僅かに小さな外径寸法に設定して、大き目のつぶし代ΔＴ4 をもって、凹周溝３へ装着されたとき、固定リップ４，５のつぶし（ラジアル方向内方向への押圧）の影響が、摺接リップ６，７へ及ばないようにする。このようにして、摺接リップ６，７の第２部材２への接触面圧Ｐ6 ，Ｐ7 を、図４に示す接触面圧グラフの如く、低く（小さく）抑えている。 4 and the mounting pressure receiving state of FIG. 5 (the arrow P 0 indicates the fluid pressure), the sliding lips 6 and 7 are connected to the groove side surfaces 14 and 14 of the concave circumferential groove 3, respectively. as always free from 15, the width W 6 of the two sliding lip 6 is set to be smaller.
Further, the valley portion 16 (in the outer diameter direction) between the two fixed lips 4 and 5 is slightly smaller than the outer diameter dimension of the concave circumferential groove 3 of the two-dot chain line, as shown in FIGS. When the outer diameter dimension is set and a large crushing allowance ΔT 4 is attached to the concave circumferential groove 3, the influence of crushing of the fixed lips 4, 5 (pressing inward in the radial direction) affects the sliding contact lip 6. , 7 so that it does not reach. In this manner, the second contact surface pressure P 6, P 7 to member 2 of the sliding lip 6, as the contact surface pressure graph shown in FIG. 4, is kept low (less).

そして、図４に示す未受圧装着状態、及び、図５に示す装着受圧状態の各々に於て、前記摺接リップ６，７の第２部材２への接触面圧Ｐ6 ，Ｐ7 、及び、固定リップ４，５の溝底13への接触面圧Ｐ4 ，Ｐ5 、さらに、突張り用突隆部20, 21の溝側面14, 15への接触面圧Ｐ20，Ｐ21の各々の面圧グラフから、以下の点が明らかとなる。（なお、各面圧グラフは、ＦＥＭ解析法によって解析した。）
(ｉ) 図４の未受圧装着状態下で、突隆部20, 21の接触面圧Ｐ20，Ｐ21は微小である。
(ii) 摺接リップ６，７の接触面圧Ｐ6 ，Ｐ7 は、常に、固定リップ４，５の接触面圧Ｐ 4 ，Ｐ5 よりも小さく、かつ、通常の従来のＸリングよりも、十分に小さい（低い ）。
(iii) 図５の受圧状態では、低圧側の摺接リップ７の接触面圧が微小となる。しかも、図 ４の未受圧装着状態と比較して、両摺接リップ６，７の接触面圧Ｐ6 ，Ｐ7 の差が ほとんど無い。
(iｖ) 図５の受圧状態では、（外径側の）固定リップ４，５の接触面圧Ｐ4 ，Ｐ5 が（未 受圧状態よりも）かなり高くなるが、（内径側の）摺接リップ６の接触面圧Ｐ6 は ほとんど変化せず、逆に、摺接リップ７の接触面圧Ｐ7 は低下する。 Then, non-pressure bearing mounting state shown in FIG. 4 and, At a respective mounting pressure state shown in FIG. 5, the sliding contact second member contact surface pressure P 6, P 7 to the second lip 6 and, , Contact surface pressures P 4 , P 5 to the groove bottom 13 of the fixed lips 4, 5 , and contact surface pressures P 20 , P 21 to the groove side surfaces 14, 15 of the projecting ridges 20, 21. From the surface pressure graph, the following points become clear. (In addition, each surface pressure graph was analyzed by the FEM analysis method.)
(i) The contact surface pressures P 20 and P 21 of the ridges 20 and 21 are very small under the non-pressure receiving state of FIG.
(ii) The contact surface pressures P 6 , P 7 of the sliding contact lips 6, 7 are always smaller than the contact surface pressures P 4 , P 5 of the fixed lips 4 , 5 , and more than a normal conventional X ring. Small enough (low).
(iii) In the pressure receiving state of FIG. 5, the contact surface pressure of the sliding contact lip 7 on the low pressure side is very small. Moreover, there is almost no difference between the contact surface pressures P 6 and P 7 of the sliding contact lips 6 and 7 as compared with the non-pressure receiving mounting state of FIG.
(iv) In the pressure receiving state of FIG. 5, the contact surface pressures P 4 and P 5 of the fixed lips 4 and 5 (outside the diametric side) are considerably higher (than in the non-pressure receiving state). contact pressure P 6 of the lip 6 hardly changes. Conversely, the contact surface pressure P 7 of the sliding lip 7 is reduced.

このような (ｉ) 〜(iｖ) の結果は、相対的に回転運動、及び／又は、直線往復運動する、摺接リップ６，７と第２部材２との間の摩擦抵抗が十分低く抑えることができて、円滑に相対運動が実現でき、摩耗量も減少して、長期間にわたって優れたシール性（密封性能）を発揮できる。また、図２で述べたように突隆部20, 21は 360°（全周）の内の十分大きな中心角度を占めるように構成したので、図５のように受圧状態で大きな接触面圧Ｐ21をもって溝側面15に突隆部21が圧接（押圧）状態となった際、周方向に沿って、蛇行する従来例（図12（ｃ））の現象を完全に防ぐことができ、かつ、溝側面14, 15との固着も発生しない。 As a result of (i) to (iv), the frictional resistance between the sliding contact lips 6 and 7 and the second member 2 that relatively rotate and / or reciprocate linearly is kept sufficiently low. Therefore, the relative movement can be realized smoothly, the amount of wear can be reduced, and excellent sealing performance (sealing performance) can be exhibited over a long period of time. Further, as described in FIG. 2, the ridges 20 and 21 are configured to occupy a sufficiently large center angle within 360 ° (entire circumference), so that a large contact surface pressure P in the pressure receiving state as shown in FIG. When the protruding portion 21 is pressed (pressed) on the groove side surface 15 with 21 , the phenomenon of the conventional example (FIG. 12 (c)) meandering along the circumferential direction can be completely prevented, and Adherence to the groove side surfaces 14 and 15 does not occur.

また、図１〜図５の実施の形態では、凹周溝３の溝底13側───固定リップ４，５側───が、基本Ｘ部10の幅寸法Ｗ4 も、断面積も、開口端側───摺動リップ６，７側───よりも、十分に大きく、しかも、突隆部20, 21は、固定リップ４，５の内側面４ａ，５ａに一体に突出状に形成され、さらに、固定リップ４，５のつぶし代ΔＴ4 を十分に大きく設定し、かつ、側凹部11, 12を十分に深く形成して固定リップ４，５の変形の影響が摺接リップ６，７に及ばぬよう遮断できるように構成したことによって、第２部材２に対応する小型断面形状の摺接リップ６，７は、比較的自由に弾性変形が可能で、小さな接触面圧力Ｐ6 ，Ｐ7 を常に保ちつつ第２部材２と回転摺動（又は直線往復摺動）を行って、低摩擦抵抗を実現し、かつ、低摩耗及び長寿命を実現する。さらに、固定リップ４，５が溝底13に対して（回転）摺動するようなこと（共廻り）は全く発生しない。 In the embodiment shown in FIGS. 1 to 5, the groove bottom 13 side of the recessed circumferential groove 3—the fixed lip 4, 5 side—has both the width dimension W 4 of the basic X portion 10 and the cross-sectional area. The opening end side is sufficiently larger than the sliding lips 6 and 7 side, and the ridges 20 and 21 protrude integrally with the inner side surfaces 4a and 5a of the fixed lips 4 and 5, respectively. Further, the crushing allowance ΔT 4 of the fixed lips 4 and 5 is set sufficiently large, and the side recesses 11 and 12 are formed sufficiently deep so that the deformation of the fixed lips 4 and 5 is affected by the sliding lip. 6 and 7, the sliding contact lips 6 and 7 having a small cross-sectional shape corresponding to the second member 2 can be elastically deformed relatively freely and have a small contact surface pressure P. 6, carried out while always maintaining a P 7 second member 2 and the rotary slide (or linear reciprocating sliding) to achieve low friction and low wear and long Life to achieve. Further, it does not occur that the fixed lips 4 and 5 slide (rotate) with respect to the groove bottom 13 (co-rotation).

ところで、図６は未受圧装着状態に於ても、図１で既述の関係式が成立することを示す。即ち、図６に於て、各接触面圧グラフの重心点Ｚの位置を、図１の既述の頂点４Ｅ，５Ｅ，６Ｅ，７Ｅの位置に置き換えて、軸心方向寸法Ｇ1 ，Ｇ2 ，Ｇ3 ，Ｇ4 を採用すれば、Ｇ1 ＝Ｇ3 ，Ｇ2 ＝Ｇ4 ，Ｇ1 ＞Ｇ2 ，Ｇ3 ＞Ｇ4 なる関係式が成立する。このように凹周溝３内に於て、断面積も大きく、つぶし代ΔＴ4 も大きく、かつ、幅寸法Ｗ4 も大きいところの、溝底13側への固定リップ４，５の接触位置が、シール中心から軸心方向左右へ大きく離れていることにより、一層、摺動シールＳは凹周溝３内での姿勢が常に安定する。なお、図６に於て、２個の摺接リップ６，７の間の谷部にはグリースを充填して、グリースポケットとすることもできる。 By the way, FIG. 6 shows that the relational expression already described in FIG. 1 is established even in the non-pressure receiving state. That is, At a 6, the position of the center of gravity Z of the contact surface pressure graph, above the vertex 4E in FIG. 1, 5E, 6E, substituting the position of 7E, axial dimension G 1, G 2 , G 3 , G 4 , the following relational expressions are established: G 1 = G 3 , G 2 = G 4 , G 1 > G 2 , G 3 > G 4 . Thus At a concave peripheral groove 3, the cross-sectional area is large, squeeze [Delta] T 4 is large, and, where larger width dimension W 4, the contact position of the fixed lip 4,5 to groove bottom 13 side The position of the sliding seal S in the concave circumferential groove 3 is always stabilized further by being far away from the center of the seal to the left and right in the axial direction. In FIG. 6, the valley between the two sliding contact lips 6 and 7 can be filled with grease to form a grease pocket.

次に、図７〜図11は、本発明の他の実施の形態を示す。この摺動シールＳも原則的に前述の実施例と同様の基本構成を有している。
即ち、この摺動シールＳも、凹周溝３の溝底13側の２個の固定リップ４，５と、摺動（摺接）側の２個の摺接リップ６，７を有する横断面Ｘ字状の基本Ｘ部10を、備えている。但し、この基本Ｘ部10は全幅寸法Ｗ4 は、図１〜図６に比較して小さ目である。
そして、上記凹周溝３の軸心方向溝側面14, 15に接触して、基本Ｘ部10の凹周溝３内の姿勢を（倒れたり傾斜したりしないように）保つための突張り用突隆部（リッジ部）20, 21を、基本Ｘ部10から一体に突設される。
この摺動シールＳも、ゴム又はプラスチック製であり、一体成型される。 7 to 11 show another embodiment of the present invention. This sliding seal S also basically has the same basic configuration as that of the above-described embodiment.
That is, this sliding seal S also has a cross section having two fixed lips 4, 5 on the groove bottom 13 side of the concave circumferential groove 3 and two sliding contact lips 6, 7 on the sliding (sliding contact) side. An X-shaped basic X portion 10 is provided. However, overall width dimension W 4 The basic X portion 10 is smaller in comparison to FIGS. 1 to 6.
And, for the tension to maintain the posture in the concave circumferential groove 3 of the basic X portion 10 (so as not to fall down or incline) by contacting the axial groove side surfaces 14 and 15 of the concave circumferential groove 3 The protruding portions (ridge portions) 20 and 21 are integrally projected from the basic X portion 10.
This sliding seal S is also made of rubber or plastic and is integrally molded.

また、図７は、自由状態の摺動シールＳを示し、この自由状態での厚さ寸法Ｔ0 の中央線Ｃよりも、固定リップ４，５寄り───ラジアル方向外方───に突隆部20, 21は、偏在して、かつ、基本Ｘ部10から大きく軸心方向に突設している。
図８は軸心方向から見た説明図であって、斜線にて示す部位は、突隆部20, 21を示す。即ち、軸心方向から見ると、同一円上に配設された複数本の円弧体８をもって───図８では６本の円弧体８をもって───、合計中心角度が 270°〜 350°を占める略円環状に、配設される。 FIG. 7 shows the sliding seal S in the free state, and is closer to the fixed lips 4 and 5 than the center line C of the thickness dimension T 0 in this free state: outward in the radial direction. The protruding portions 20 and 21 are unevenly distributed and project from the basic X portion 10 in the axial direction.
FIG. 8 is an explanatory view seen from the axial direction, and the hatched portions indicate the ridges 20 and 21. In other words, when viewed from the axial direction, with a plurality of arcuate bodies 8 arranged on the same circle --- with 6 arcuate bodies 8 in FIG. 8, the total center angle is 270 ° to 350 °. Is disposed in a substantially annular shape.

図７は、図８に於て、（斜線にて示した）円弧体８を切断した摺動シール要部横断面である。この図７と図８で明らかなように、固定リップ４，５のつぶし代ΔＴ4 を、十分に大きく設定し、凹周溝３の深さ寸法Ｈ3 の10％〜25％とする。好ましくは、13％〜22％とする。しかも、摺接リップ６，７のつぶし代ΔＴ6 は零乃至マイナスに設定する。即ち、摺接リップ７の自由状態の内径寸法は、第２部材２の外径寸法よりも、僅かに大きく（又は同径に）設定する。 FIG. 7 is a cross-sectional view of the main part of the sliding seal obtained by cutting the circular arc body 8 (shown by oblique lines) in FIG. As apparent from FIGS. 7 and 8, the crushing margin ΔT 4 of the fixed lips 4 and 5 is set sufficiently large so as to be 10% to 25% of the depth dimension H 3 of the concave circumferential groove 3. Preferably, it is 13% to 22%. Moreover, squeeze [Delta] T 6 of the sliding lip 6 and 7 is set at zero or negative. That is, the inner diameter dimension of the sliding contact lip 7 in the free state is set slightly larger (or the same diameter) as the outer diameter dimension of the second member 2.

ところで、図７に示すように、自由状態下で、基本Ｘ部10は外径側（ラジアル方向外方側）の固定リップ４，５の幅寸法Ｗ4 と、内径側（ラジアル方向内方側）の摺接リップ６，７の幅寸法Ｗ6 を略等しく設定している。
この実施の形態では、突隆部20, 21の形状は、軸心方向から見た形状は（既述のように）複数本の円弧体８をもって構成され、略円環状であるが、図７に示すように、摺動シール横断面に於て、固定リップ４，５の内側面４ａ，５ａから大きく軸心両方向に突出状に一体形成されている。 By the way, as shown in FIG. 7, in the free state, the basic X portion 10 has a width W 4 of the fixed lips 4 and 5 on the outer diameter side (radially outward side) and an inner diameter side (radial inner side). The width dimension W 6 of the sliding contact lips 6, 7 is set substantially equal.
In this embodiment, the protrusions 20 and 21 are formed in a shape of a plurality of arcuate bodies 8 as viewed from the axial direction (as described above) and are substantially annular. As shown in FIG. 3, the sliding seal is integrally formed so as to protrude from the inner side surfaces 4a and 5a of the fixed lips 4 and 5 in both axial directions in the transverse cross section.

また、図７に示した自由状態の横断面における、ラジアル方向の中間部位に、側凹部11, 12が、基本Ｘ部10の軸心方向両側面に、形成されているが、この側凹部11, 12の最奥部11Ａ，12Ａの軸心方向位置は、固定リップ４，５の径方向の頂点４Ｅ，５Ｅ、及び、摺接リップ６，７の径方向の頂点６Ｅ，７Ｅよりも、シール中心寄りに存在する。つまり、側凹部11, 12を、十分に深く形成する。
さらに詳しく図７にて説明すれば、側凹部11の最奥部11Ａは、頂点４Ｅ，６Ｅよりも、軸心方向寸法Ｇ1 ，Ｇ2 だけシール中心寄りに配設され、かつ、側凹部12の最奥部12Ａは、頂点５Ｅ，７Ｅよりも軸心方向寸法Ｇ3 ，Ｇ4 だけシール中心寄りに配設されている。 Further, side recesses 11 and 12 are formed on both side surfaces in the axial direction of the basic X portion 10 in the radial intermediate portion in the transverse cross section in the free state shown in FIG. , 12 in the axial direction of the innermost portion 11A, 12A is more sealed than the radial vertices 4E, 5E of the fixed lips 4, 5 and the radial vertices 6E, 7E of the sliding contact lips 6, 7. It exists near the center. That is, the side recesses 11 and 12 are formed sufficiently deep.
More specifically, referring to FIG. 7, the innermost portion 11A of the side recess 11 is disposed closer to the center of the seal than the apexes 4E and 6E by the axial center dimensions G 1 and G 2 , and the side recess 12 The innermost portion 12A is disposed closer to the center of the seal than the vertices 5E and 7E by the axial direction dimensions G 3 and G 4 .

そして、図９の未受圧装着状態、及び、図10の装着受圧状態（矢印Ｐ0 は流体の圧力を示す）に於て、摺接リップ６，７は、凹周溝３の溝側面14, 15から常に遊離しているように、２個の摺接リップ６，７の幅寸法Ｗ6 を、凹周溝３の幅寸法よりも十分に小さく設定している。また、図９に於て、２個の摺接リップ６，７の間の谷部にはグリースを充填して、グリースポケットとすることもできる。
また、２つの固定リップ４，５の間の（外径方向の）谷部16は、図７に示すように、２点鎖線の凹周溝３の外径寸法と略等しい外径寸法に設定している。 9 and the mounting pressure receiving state of FIG. 10 (arrow P 0 indicates the fluid pressure), the sliding contact lips 6, 7 are the groove side surfaces 14, 14 of the concave circumferential groove 3. as always free from 15, the width W 6 of the two sliding lip 6, is set sufficiently smaller than the width dimension of the concave peripheral groove 3. In FIG. 9, the valley between the two sliding contact lips 6 and 7 can be filled with grease to form a grease pocket.
Further, the valley portion 16 (in the outer diameter direction) between the two fixed lips 4 and 5 is set to an outer diameter dimension substantially equal to the outer diameter dimension of the recessed circumferential groove 3 of the two-dot chain line, as shown in FIG. is doing.

そして、図９に示す未受圧装着状態、及び、図10に示す装着受圧状態の各々に於て、前記摺接リップ６，７の第２部材２への接触面圧Ｐ6 ，Ｐ7 、及び、固定リップ４，５の溝底13への接触面圧Ｐ4 ，Ｐ5 、さらに、突張り用突隆部20, 21の溝側面14, 15への接触面圧Ｐ20，Ｐ21の各々の面圧グラフから、以下の点が明らかとなる。
(ｉ) 図９の未受圧装着状態下で、突隆部20, 21の接触面圧Ｐ20，Ｐ21は微小（又は、若 干のスキマを形成して、零）である。
(ii) 摺接リップ６，７の接触面圧Ｐ6 ，Ｐ7 は、常に、固定リップ４，５の接触面圧Ｐ 4 ，Ｐ5 よりも小さく、かつ、通常の従来のＸリングよりも、十分に小さい（低い ）。
(iii) 図10の受圧状態では、低圧側の摺接リップ７の接触面圧が図９によりも低下する。 しかも、図９の未受圧装着状態と比較して、両摺接リップ６，７の接触面圧Ｐ6 ， Ｐ7 の差がほとんど無い。
(iｖ) 図10の受圧状態では、（内径側の）摺接リップ６の接触面圧Ｐ6 はほとんど変化せ ず、逆に、摺接リップ７の接触面圧Ｐ7 は低下する。 Then, non-pressure bearing mounting state shown in FIG. 9 and, At a respective mounting pressure state shown in FIG. 10, the sliding contact second member contact surface pressure P 6, P 7 to the second lip 6 and, , Contact surface pressures P 4 , P 5 to the groove bottom 13 of the fixed lips 4, 5 , and contact surface pressures P 20 , P 21 to the groove side surfaces 14, 15 of the projecting ridges 20, 21. From the surface pressure graph, the following points become clear.
(i) The contact surface pressures P 20 and P 21 of the ridges 20 and 21 are minute (or form a slight gap and zero) under the non-pressure-receiving state of FIG.
(ii) The contact surface pressures P 6 , P 7 of the sliding contact lips 6, 7 are always smaller than the contact surface pressures P 4 , P 5 of the fixed lips 4 , 5 , and more than a normal conventional X ring. Small enough (low).
(iii) In the pressure receiving state of FIG. 10, the contact surface pressure of the sliding contact lip 7 on the low pressure side is lower than that of FIG. In addition, there is almost no difference between the contact surface pressures P 6 and P 7 of the sliding contact lips 6 and 7 as compared with the non-pressure receiving mounting state of FIG.
(iv) In the pressure receiving state of FIG. 10, the contact surface pressure P 6 of the sliding contact lip 6 (on the inner diameter side) hardly changes, and conversely, the contact surface pressure P 7 of the sliding contact lip 7 decreases.

このような (ｉ) 〜(iｖ) の結果は、相対的に回転運動、及び／又は、直線往復運動する、摺接リップ６，７と第２部材２との間の摩擦抵抗が十分低く抑えることができて、円滑に相対運動が実現でき、摩耗量も減少して、長期間にわたって優れたシール性（密封性能）を発揮できる。また、図８で述べたように突隆部20, 21は 360°（全周）の内の十分大きな中心角度を占めるように構成したので、図10のように受圧状態で大きな接触面圧Ｐ21をもって溝側面15に突隆部21が圧接（押圧）状態となった際、周方向に沿って、蛇行する従来例（図12（ｃ））の現象を完全に防ぐことができる。 As a result of (i) to (iv), the frictional resistance between the sliding contact lips 6 and 7 and the second member 2 that relatively rotate and / or reciprocate linearly is kept sufficiently low. Therefore, the relative movement can be realized smoothly, the amount of wear can be reduced, and excellent sealing performance (sealing performance) can be exhibited over a long period of time. Further, as described in FIG. 8, the ridges 20 and 21 are configured to occupy a sufficiently large center angle within 360 ° (entire circumference), so that a large contact surface pressure P in the pressure receiving state as shown in FIG. When the protruding portion 21 is pressed (pressed) on the groove side surface 21 with 21 , the phenomenon of the conventional example (FIG. 12C) meandering along the circumferential direction can be completely prevented.

また、図７〜図10の実施の形態では、突隆部20, 21は、固定リップ４，５の内側面４ａ，５ａに大きく突出状に形成され、さらに、固定リップ４，５のつぶし代ΔＴ4 を十分に大きく設定し、かつ、側凹部11, 12を十分に深く形成して固定リップ４，５の変形の影響が摺接リップ６，７に及ばぬよう遮断できるように構成したことによって、第２部材２に対応する摺接リップ６，７は、比較的自由に弾性変形が可能で、小さな接触面圧力Ｐ6 ，Ｐ7 を常に保ちつつ第２部材２と回転摺動（又は直線往復摺動）を行って、低摩擦抵抗を実現し、かつ、低摩耗及び長寿命を実現する。さらに、固定リップ４，５が溝底13に対して（回転）摺動するようなこと（共廻り）は全く発生しない。 Further, in the embodiment shown in FIGS. 7 to 10, the protruding portions 20 and 21 are formed in a projecting shape on the inner side surfaces 4 a and 5 a of the fixed lips 4 and 5. ΔT 4 is set to be sufficiently large and the side recesses 11 and 12 are formed to be sufficiently deep so that the influence of the deformation of the fixed lips 4 and 5 does not reach the sliding lips 6 and 7. Accordingly, the sliding contact lips 6 and 7 corresponding to the second member 2 can be elastically deformed relatively freely, and rotate and slide with the second member 2 while maintaining a small contact surface pressure P 6 , P 7 (or Performs linear reciprocating sliding) to achieve low frictional resistance and low wear and long life. Further, it does not occur that the fixed lips 4 and 5 slide (rotate) with respect to the groove bottom 13 (co-rotation).

なお、図11に示した未受圧装着状態に於て、各接触面圧グラフの重心点Ｚの軸心方向の位置を、図７の頂点４Ｅ，５Ｅ，６Ｅ，７Ｅの軸心方向位置に置き換えて判断すると、図７と同様の配置関係にある。即ち、側凹部11, 12の最奥部11Ａ，12Ａは、各重心点Ｚよりもシール中心寄りに在り、側凹部11, 12が十分に深いことが明らかとなる。これによって、特に、固定リップ４，５側の大き目のつぶし代ΔＴ4 の影響が、摺接リップ６，７に波及せず、従って、第２部材２との摺動摩擦抵抗が小さい。 In the non-pressure receiving state shown in FIG. 11, the position in the axial direction of the center of gravity Z of each contact surface pressure graph is replaced with the axial position of the vertices 4E, 5E, 6E, and 7E in FIG. As a result, the same arrangement relationship as in FIG. 7 is obtained. That is, it is clear that the innermost portions 11A and 12A of the side recesses 11 and 12 are closer to the center of the seal than the center of gravity Z, and the side recesses 11 and 12 are sufficiently deep. Thereby, in particular, the influence of the large crushing margin ΔT 4 on the fixed lips 4 and 5 side does not affect the sliding contact lips 6 and 7, and therefore the sliding frictional resistance with the second member 2 is small.

本発明は、左右対称形であり、正圧負圧用としても適用可能である。また、特に、摺接リップ６，７の摺動摩擦抵抗が、受圧状態でも低く（小さく）、例えば、回転継手等のシールとして、好適である。また、第１部材１を、軸（ロッド）や円筒体や円盤体としてその外周面に凹周溝３が凹設されると共に、第２部材２をケーシングやハウジングやヘッドやシリンダ等として内周面が摺接リップ６，７と相対的に摺接するように、逆に、配置することも、可能である。   The present invention is symmetrical and can be applied to positive and negative pressure. In particular, the sliding frictional resistance of the slidable contact lips 6 and 7 is low (small) even in the pressure-receiving state, which is suitable as a seal for a rotary joint, for example. Further, the first member 1 is a shaft (rod), cylinder or disk, and a concave groove 3 is provided on the outer peripheral surface thereof, and the second member 2 is an inner periphery using a casing, housing, head, cylinder or the like. It is also possible to dispose the surface so that the surface is in sliding contact with the sliding contact lips 6 and 7.

本発明の実施の一形態を示す自由状態の摺動シールの形状と寸法の説明図である。It is explanatory drawing of the shape and dimension of the sliding seal of the free state which show one Embodiment of this invention. 軸心方向から見た要部説明図である。It is principal part explanatory drawing seen from the axial center direction. 自由状態の基本Ｘ部の形状と寸法の説明図である。It is explanatory drawing of the shape and dimension of the basic X part of a free state. 未受圧装着状態の説明図である。It is explanatory drawing of a non-pressure receiving mounting state. 装着受圧状態の説明図である。It is explanatory drawing of a mounting pressure receiving state. 未受圧装着状態の説明図である。It is explanatory drawing of a non-pressure receiving mounting state. 他の実施の形態を示す自由状態の摺動シールの形状と寸法の説明図である。It is explanatory drawing of the shape and dimension of the sliding seal of the free state which show other embodiment. 軸心方向から見た要部説明図である。It is principal part explanatory drawing seen from the axial center direction. 未受圧装着状態の説明図である。It is explanatory drawing of a non-pressure receiving mounting state. 装着受圧状態の説明図である。It is explanatory drawing of a mounting pressure receiving state. 未受圧装着状態の説明図である。It is explanatory drawing of a non-pressure receiving mounting state. 従来例を示す説明図である。It is explanatory drawing which shows a prior art example.

符号の説明Explanation of symbols

３ 凹周溝
４，５ 固定リップ
４Ｅ，５Ｅ 頂点
６，７ 摺接リップ
６Ｅ，７Ｅ 頂点
８ 円弧体
10 基本Ｘ部
11, 12 側凹部
11Ａ，12Ａ 最奥部
13 溝底（面）
14, 15 溝側面
20, 21 突隆部
Ｃ 中央線
Ｈ3 深さ寸法
Ｓ 摺動シール
Ｔ0 厚さ寸法
ΔＴ4 ，ΔＴ6 つぶし代
Ｗ6 幅寸法 3 Concave groove 4, 5 Fixed lip 4E, 5E Vertex 6, 7 Sliding contact lip 6E, 7E Vertex 8 Arc
10 Basic X part
11, 12 side recess
11A, 12A innermost part
13 Groove bottom (surface)
14, 15 groove side
20, 21 Protrusion C Center line H 3 Depth dimension S Sliding seal T 0 Thickness dimension ΔT 4 , ΔT 6 Squeezing allowance W 6 Width dimension

Claims (6)

凹周溝（３）の溝底（13）側の２個の固定リップ (４)(５) と摺動側の２個の摺接リップ (６)(７) を有する横断面Ｘ字状の基本Ｘ部（10）を備え、かつ、上記凹周溝（３）の軸心方向溝側面 (14)(15) に接触して上記基本Ｘ部（10）の上記凹周溝（３）内の姿勢を保つための突張り用突隆部 (20)(21) を、上記基本Ｘ部（10）と一体として、かつ、自由状態の厚さ寸法（Ｔ0 ）の中央線（Ｃ）よりも、上記固定リップ (４)(５) 寄りに偏在して設けたことを特徴とする摺動シール。 Cross section X-shaped having two fixed lips (4) (5) on the groove bottom (13) side of the concave circumferential groove (3) and two sliding contact lips (6) (7) on the sliding side In the concave circumferential groove (3) of the basic X portion (10) provided with a basic X portion (10) and in contact with the axial groove side surface (14) (15) of the concave circumferential groove (3) The projecting ridges (20) and (21) for maintaining the posture of the body are integrated with the basic X part (10) and from the center line (C) of the thickness dimension (T 0 ) in the free state. Also, a sliding seal characterized by being provided unevenly near the fixed lip (4) (5). 凹周溝（３）の溝底（13）側の２個の固定リップ (４)(５) と摺動側の２個の摺接リップ (６)(７) を有する横断面Ｘ字状の基本Ｘ部（10）を備え、かつ、上記凹周溝（３）の軸心方向溝側面 (14)(15) に接触して上記基本Ｘ部（10）の上記凹周溝（３）内の姿勢を保つための突張り用突隆部 (20)(21) を、上記基本Ｘ部（10）と一体として、かつ、自由状態の厚さ寸法（Ｔ0 ）の中央線（Ｃ）よりも、上記固定リップ (４)(５) 寄りに偏在して設け、さらに、上記固定リップ (４)(５) のつぶし代（ΔＴ4 ）を、上記凹周溝３の深さ寸法（Ｈ3 ）の10％〜25％と大きく設定し、かつ、上記摺接リップ (６)(７) のつぶし代（ΔＴ6 ）を零乃至マイナスに設定したことを特徴とする摺動シール。 Cross section X-shaped having two fixed lips (4) (5) on the groove bottom (13) side of the concave circumferential groove (3) and two sliding contact lips (6) (7) on the sliding side In the concave circumferential groove (3) of the basic X portion (10) provided with a basic X portion (10) and in contact with the axial groove side surface (14) (15) of the concave circumferential groove (3) The projecting ridges (20) and (21) for maintaining the posture of the body are integrated with the basic X part (10) and from the center line (C) of the thickness dimension (T 0 ) in the free state. Are also provided in the vicinity of the fixed lip (4) (5). Further, the crushing margin (ΔT 4 ) of the fixed lip (4) (5) is set to the depth dimension (H 3 ) of the concave circumferential groove 3. ), And a crushing margin (ΔT 6 ) of the sliding contact lip (6) (7) is set to zero or minus. 凹周溝（３）の溝底（13）側の２個の固定リップ (４)(５) と摺動側の２個の摺接リップ (６)(７) を有する横断面Ｘ字状の基本Ｘ部（10）を備え、かつ、上記凹周溝（３）の軸心方向溝側面 (14)(15) に接触して上記基本Ｘ部（10）の上記凹周溝（３）内の姿勢を保つための突張り用突隆部 (20)(21) を、上記基本Ｘ部（10）と一体として、かつ、自由状態の厚さ寸法（Ｔ0 ）の中央線（Ｃ）よりも、上記固定リップ (４)(５) 寄りに偏在して設け、さらに、上記突隆部 (20)(21) は、軸心方向から見て同一円上に配設した複数本の円弧体（８）をもって、合計中心角度が 270°〜 350°を占める略円環状に、配設されていることを特徴とする摺動シール。 Cross section X-shaped having two fixed lips (4) (5) on the groove bottom (13) side of the concave circumferential groove (3) and two sliding contact lips (6) (7) on the sliding side In the concave circumferential groove (3) of the basic X portion (10) provided with a basic X portion (10) and in contact with the axial groove side surface (14) (15) of the concave circumferential groove (3) The projecting ridges (20) and (21) for maintaining the posture of the body are integrated with the basic X part (10) and from the center line (C) of the thickness dimension (T 0 ) in the free state. Are also provided in the vicinity of the fixed lips (4) and (5), and the ridges (20) and (21) are a plurality of arcuate bodies arranged on the same circle as viewed from the axial direction. The sliding seal is characterized by being arranged in a substantially annular shape having a total center angle of 270 ° to 350 °. 凹周溝（３）の溝底（13）側の２個の固定リップ (４)(５) と摺動側の２個の摺接リップ (６)(７) を有する横断面Ｘ字状の基本Ｘ部（10）を備え、かつ、上記凹周溝（３）の軸心方向溝側面 (14)(15) に接触して上記基本Ｘ部（10）の上記凹周溝（３）内の姿勢を保つための突張り用突隆部 (20)(21) を、上記基本Ｘ部（10）と一体として、かつ、自由状態の厚さ寸法（Ｔ0 ）の中央線（Ｃ）よりも、上記固定リップ (４)(５) 寄りに偏在して設け、装着受圧状態において上記摺接リップ (６)(７) は上記凹周溝（３）の溝側面 (14)(15) から常に遊離しているように、上記２個の摺接リップ (６)(７) の幅寸法（Ｗ6 ）を小さく設定したことを特徴とする摺動シール。 Cross section X-shaped having two fixed lips (4) (5) on the groove bottom (13) side of the concave circumferential groove (3) and two sliding contact lips (6) (7) on the sliding side In the concave circumferential groove (3) of the basic X portion (10) provided with a basic X portion (10) and in contact with the axial groove side surface (14) (15) of the concave circumferential groove (3) The projecting ridges (20) and (21) for maintaining the posture of the body are integrated with the basic X part (10) and from the center line (C) of the thickness dimension (T 0 ) in the free state. Also, the sliding lip (6) (7) is provided from the groove side surface (14) (15) of the concave circumferential groove (3) in the mounted pressure receiving state. A sliding seal characterized in that the width dimension (W 6 ) of the two sliding contact lips (6) and (7) is set to be small so as to be always free. 自由状態の横断面において、ラジアル方向の中間位置の軸心方向両側面に形成される側凹部 (11)(12) の最奥部 (11Ａ)(12Ａ) の軸心方向位置が、上記固定リップ (４)(５) の頂点 (４Ｅ)(５Ｅ) 及び摺接リップ (６)(７) の頂点 (６Ｅ)(７Ｅ) よりも、シール中心寄りに存在するように、上記側凹部 (11)(12) を深く形成した請求項１，２，３又は４記載の摺動シール。   In the cross section in the free state, the axial direction positions of the innermost portions (11A) and (12A) of the side recesses (11) and (12) formed on both side surfaces in the axial direction of the intermediate position in the radial direction are (4) The side recess (11) so that it is closer to the center of the seal than the vertices (4E) (5E) of (5) and the vertices (6E) (7E) of the sliding contact lips (6) (7). The sliding seal according to claim 1, 2, 3 or 4, wherein (12) is formed deep. 自由状態における固定リップ (４)(５) の間の谷部（16）の谷底外径寸法が、凹周溝（３）の溝底（13）の外径寸法よりも、小さく設定され、装着状態において固定リップ (４)(５) のつぶしの影響が、摺接リップ (６)(７) へ及ばないように構成した請求項１，２，３，４又は５記載の摺動シール。   The outer diameter of the valley bottom (16) between the fixed lips (4) and (5) in the free state is set to be smaller than the outer diameter of the groove bottom (13) of the concave circumferential groove (3). The sliding seal according to claim 1, 2, 3, 4 or 5, wherein the smashing of the fixed lip (4) (5) does not affect the sliding contact lip (6) (7) in a state.
JP2008140464A 2008-05-29 2008-05-29 Sliding seal Pending JP2009287659A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2008140464A JP2009287659A (en) 2008-05-29 2008-05-29 Sliding seal

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2008140464A JP2009287659A (en) 2008-05-29 2008-05-29 Sliding seal

Publications (1)

Publication Number Publication Date
JP2009287659A true JP2009287659A (en) 2009-12-10

Family

ID=41457070

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2008140464A Pending JP2009287659A (en) 2008-05-29 2008-05-29 Sliding seal

Country Status (1)

Country Link
JP (1) JP2009287659A (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018046196A1 (en) * 2016-09-08 2018-03-15 Zf Friedrichshafen Ag Frequency-selective damping valve assembly
WO2021095344A1 (en) * 2019-11-11 2021-05-20 パナソニックＩｐマネジメント株式会社 Motor and electrical equipment including same
US11293437B2 (en) 2018-12-27 2022-04-05 Kabushiki Kaisha Toyota Jidoshokki Fluid machine

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5540238U (en) * 1978-09-06 1980-03-14
JPS5719263U (en) * 1980-07-09 1982-02-01
JPS5732257U (en) * 1980-07-31 1982-02-19
JPS6021069U (en) * 1983-07-20 1985-02-13 三菱電線工業株式会社 Sliding seal
JPS61228166A (en) * 1985-04-01 1986-10-11 Mitsubishi Cable Ind Ltd Packing for slide
JPH029377U (en) * 1988-06-30 1990-01-22
JPH0586072U (en) * 1992-04-24 1993-11-19 三菱電線工業株式会社 Sliding packing
JPH0628431U (en) * 1992-09-08 1994-04-15 エヌオーケー株式会社 Sealing device
JPH09144889A (en) * 1995-11-20 1997-06-03 Nok Corp Sealing device
JP2006266279A (en) * 2005-03-22 2006-10-05 Nok Corp Packing

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5540238U (en) * 1978-09-06 1980-03-14
JPS5719263U (en) * 1980-07-09 1982-02-01
JPS5732257U (en) * 1980-07-31 1982-02-19
JPS6021069U (en) * 1983-07-20 1985-02-13 三菱電線工業株式会社 Sliding seal
JPS61228166A (en) * 1985-04-01 1986-10-11 Mitsubishi Cable Ind Ltd Packing for slide
JPH029377U (en) * 1988-06-30 1990-01-22
JPH0586072U (en) * 1992-04-24 1993-11-19 三菱電線工業株式会社 Sliding packing
JPH0628431U (en) * 1992-09-08 1994-04-15 エヌオーケー株式会社 Sealing device
JPH09144889A (en) * 1995-11-20 1997-06-03 Nok Corp Sealing device
JP2006266279A (en) * 2005-03-22 2006-10-05 Nok Corp Packing

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018046196A1 (en) * 2016-09-08 2018-03-15 Zf Friedrichshafen Ag Frequency-selective damping valve assembly
US10851865B2 (en) 2016-09-08 2020-12-01 Zf Friedrichshafen Ag Frequency-selective damping valve assembly
US11293437B2 (en) 2018-12-27 2022-04-05 Kabushiki Kaisha Toyota Jidoshokki Fluid machine
WO2021095344A1 (en) * 2019-11-11 2021-05-20 パナソニックＩｐマネジメント株式会社 Motor and electrical equipment including same

Similar Documents

Publication Publication Date Title
US7770898B2 (en) Stabilizing geometry for hydrodynamic rotary seals
JP4927889B2 (en) Rotating shaft seal
WO2018037918A1 (en) Sealing device
JP2012092976A (en) Rotating shaft seal
JP5839509B2 (en) Sealing device and sealing structure
JP2009287659A (en) Sliding seal
JP2010242874A (en) Sealing device for reciprocating motion
JP6779167B2 (en) Arrangement structure of sealing material
TWI591277B (en) Reciprocating seal
JP2012255495A (en) Seal ring
JP7163491B2 (en) sealing device
JP6735673B2 (en) Sealing assembly and actuator
JP6095905B2 (en) Sealing device
JP2005273691A (en) Shaft sealing structure by seal lip
JP5273243B2 (en) Sealing device
JP2006064111A (en) Sealing member mounting structure and shaft member for sealing member co-rotation prevention
JP2013032848A (en) U-shaped seal
JP2004332920A (en) Sealing structure and end-face seal
JP2020034039A (en) Packing
JP2009092112A (en) Sealing structure
CN204716767U (en) Sealing configuration
JP5211927B2 (en) Sealing device
JP2012047260A (en) Plane seal structure
JP6660759B2 (en) Sealing device
JP2007092791A (en) Seal ring

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20110421

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20120424

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20120508

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20120925