JP2000283205A - Seal structure of slide part - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the sealing property by forming a slide seal member by providing a protruding streak protruding in the direction of an inner peripheral face like circular arc on a slide seal face facing an inner peripheral face like circular arc of a pressure chamber in a seal structure of a slide part between the pressure chamber in a rotary damper and a bulkhead sealing the slide part by liquid pressure. SOLUTION: A pair of right and left oscillation vanes 2a of a rotary damper are formed like a fan whose width in the direction of turn increases when approaching a tip, and a slide seal member 11 slide-sealing between an inner peripheral face of a through hole 1a and a mounting groove 2d formed in the axial direction on its outer peripheral face is mounted in the mounting groove 2d. The slide seal member 11 is formed by polyprostyrene resin which is not deformed by fluid pressure generated between a first pressure chamber and a second pressure chamber in such a way that its cross section is substantially square, and a protruding streak 11a protruding in the direction of the inner peripheral face like circular arc of the through hole 1a more than a central part along both end fringe parts having a width in the direction of slide is provided on a slide seal face facing the inner peripheral face like circular arc of the through hole 1a constituting the pressure chambers.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】本発明は、回動方向の外部入
力に対し緩衝力（減衰力）を発生させるベーンタイプの
ロータリダンパ等におけるように、圧力室の円弧状内周
面と隔壁（揺動ベーン）との間の摺動部を液圧シールす
るための摺動部シール構造に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an arc-shaped inner peripheral surface of a pressure chamber and a partition wall (swinging) such as a vane type rotary damper which generates a damping force (damping force) against an external input in a rotating direction. The present invention relates to a sliding portion sealing structure for hydraulically sealing a sliding portion between the sliding portion and the moving vane.

【０００２】[0002]

【従来の技術】従来、ロータリダンパとしては、例え
ば、実開平１−８０８４１号公報に記載されたものが知
られている。この従来のロータリダンパは、円筒状のケ
ーシング内に形成された圧力室と、この圧力室内にその
軸線に沿って挿通された回動軸と、この回動軸と圧力室
内壁との間に設けられた固定型の隔壁と、前記回動軸に
その回動動作に伴って回動できるように取付られたベー
ンとを有し、前記ベーンの先端部には圧力室の円弧状内
周面との間を液圧シールする摺動シール部材が設けられ
ると共に前記隔壁の先端部には回動軸外周面との間を液
圧シールする摺動シール部材が設けられることにより、
前記ベーンと隔壁とによって圧力室内が仕切られるよう
に設定され、前記隔壁またはハウジングの一部に前記仕
切られた両圧力室間を連通させる複数のオリフィスが形
成された構造となっていた。2. Description of the Related Art Conventionally, as a rotary damper, for example, a rotary damper described in Japanese Utility Model Laid-Open No. 1-80841 is known. This conventional rotary damper is provided with a pressure chamber formed in a cylindrical casing, a rotation shaft inserted into the pressure chamber along an axis thereof, and between the rotation shaft and the pressure chamber wall. Fixed vane, and a vane attached to the pivot shaft so as to be able to rotate along with the pivoting operation, and an arc-shaped inner peripheral surface of a pressure chamber at a tip end of the vane. A sliding seal member that hydraulically seals the space between the rotating shaft is provided, and a sliding seal member that hydraulically seals the space between the rotating shaft and the outer peripheral surface is provided at the tip of the partition wall.
The pressure chamber is set so as to be partitioned by the vane and the partition, and a plurality of orifices are formed in a part of the partition or the housing to communicate between the partitioned pressure chambers.

【０００３】[0003]

【発明が解決しようとする課題】しかしながら、上述の
ような従来例のロータリダンパにあっては、特にベーン
の先端部に設けられる摺動シール部材の摺動面全体が、
図 の要部拡大断面図に示すように、圧力室の円弧状内
周面と略同一の曲率に形成されていたため、円弧内周面
との接触面積が大きくなり、このため、単位面積あたり
の面圧が低くなってシール性が悪くなると共に、摺動フ
リクションが大きくなってしまうという問題点があっ
た。However, in the above-described conventional rotary damper, the entire sliding surface of the sliding seal member provided at the tip of the vane is particularly difficult.
As shown in the enlarged cross-sectional view of the main part of the figure, since the pressure chamber was formed to have substantially the same curvature as the arc-shaped inner peripheral surface, the contact area with the arc inner peripheral surface became large, and as a result, There is a problem that the surface pressure is reduced, the sealing performance is deteriorated, and the sliding friction is increased.

【０００４】本発明は、上述の従来の問題点に着目して
なされたもので、摺動シール部材による隔壁と圧力室の
円弧状内周面との間のシール性を高めると共に、摺動フ
リクションを低下させることができる摺動部シール構造
を提供することを目的とするものである。SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned conventional problems. The present invention has been made to improve the sealing performance between a partition wall and an arc-shaped inner peripheral surface of a pressure chamber by a sliding seal member, and to improve sliding friction. It is an object of the present invention to provide a sliding portion seal structure capable of reducing the sliding force.

【０００５】[0005]

【課題を解決するための手段】上述の目的を達成するた
めに、本発明請求項１記載の摺動部シール構造は、流体
を充填する圧力室を構成するケーシングの円弧状内周面
に沿って回動する隔壁により前記圧力室が２つの圧力室
に画成され、前記隔壁における前記圧力室の円弧状内周
面との摺動対向面には該円弧状内周面との間を液圧シー
ルする摺動シール部材が設けられ、該摺動シール部材が
少なくとも前記２つの圧力室内で発生する流体圧力では
変形しない材料で形成されると共に、前記圧力室の円弧
状内周面と対面する前記摺動シール部材の摺動シール面
にはその摺動方向幅の両端縁部に沿って前記円弧状内周
面方向へ突出する突条がそれぞれ設けられている手段と
した。In order to achieve the above-mentioned object, according to a first aspect of the present invention, there is provided a sliding portion sealing structure which is formed along an arc-shaped inner peripheral surface of a casing constituting a pressure chamber filled with fluid. The pressure chamber is defined as two pressure chambers by the partition wall that rotates. The sliding opposing surface of the partition wall with the arcuate inner peripheral surface of the pressure chamber has a liquid between the arcuate inner peripheral surface. A sliding seal member for pressure sealing is provided, and the sliding seal member is formed of a material that is not deformed by fluid pressure generated in at least the two pressure chambers, and faces the arc-shaped inner peripheral surface of the pressure chamber. The sliding seal surface of the sliding seal member is provided with ridges protruding in the direction of the arc-shaped inner peripheral surface along both end edges of the sliding direction width.

【０００６】請求項２記載の摺動部シール構造は、請求
項１記載の摺動部シール構造において、前記突条の先端
摺動面が、前記圧力室の円弧状内周面の円弧と同一曲率
に形成されている手段とした。According to a second aspect of the present invention, in the first aspect, the tip sliding surface of the ridge is the same as the arc of the arc-shaped inner peripheral surface of the pressure chamber. Means formed to have a curvature.

【０００７】請求項３記載の摺動部シール構造は、請求
項１記載の摺動部シール構造において、前記突条の先端
摺動面が、前記圧力室の円弧状内周面の円弧の曲率半径
より小さな曲率半径の円弧状に形成されている手段とし
た。According to a third aspect of the present invention, there is provided the sliding portion seal structure according to the first aspect, wherein a tip end sliding surface of the ridge has a curvature of an arc of an arcuate inner peripheral surface of the pressure chamber. The means is formed in an arc shape having a radius of curvature smaller than the radius.

【０００８】請求項４記載の摺動部シール構造は、流体
を充填する圧力室を構成するケーシングの円弧状内周面
に沿って回動する隔壁により前記圧力室が２つの圧力室
に画成され、前記隔壁における前記圧力室の円弧状内周
面との摺動対向面には該円弧状内周面との間を液圧シー
ルする摺動シール部材が設けられ、該摺動シール部材が
少なくとも前記２つの圧力室内で発生する流体圧力では
変形しない材料で断面略方形状に形成され、該摺動シー
ル部材は前記隔壁に形成された装着溝内に収容された状
態で設けられ、該装着溝の両内側面と摺動シール部材に
おける両外側面と間に装着溝底部から開口部方向へ向か
うにつれて次第に広くなる隙間がそれぞれ形成されてい
る手段とした。According to a fourth aspect of the present invention, the pressure chamber is defined as two pressure chambers by a partition wall which rotates along an arcuate inner peripheral surface of a casing constituting a pressure chamber filled with fluid. A sliding seal member for hydraulically sealing between the arc-shaped inner peripheral surface and the arc-shaped inner peripheral surface of the pressure chamber in the partition wall is provided on the sliding opposing surface. The sliding seal member is formed in a substantially rectangular cross section with a material that is not deformed by a fluid pressure generated in at least the two pressure chambers, and the sliding seal member is provided in a mounting groove formed in the partition wall. A gap is formed between both inner side surfaces of the groove and both outer side surfaces of the sliding seal member, the gap gradually increasing from the bottom of the mounting groove toward the opening.

【０００９】請求項５記載の摺動部シール構造は、請求
項４記載の摺動部シール構造において、前記圧力室の円
弧状内周面と対面する前記摺動シール部材の摺動シール
面にはその摺動方向幅の両端縁部に沿って前記円弧状内
周面方向へ突出する突条がそれぞれ設けられ、前記突条
の先端摺動面が、前記圧力室の円弧状内周面の円弧の曲
率半径より小さな曲率半径の円弧状に形成されている手
段とした。According to a fifth aspect of the present invention, in the sliding portion seal structure according to the fourth aspect, a sliding seal surface of the sliding seal member facing the arcuate inner peripheral surface of the pressure chamber is provided. Are provided along the both ends of the width in the sliding direction, projecting ridges projecting in the direction of the arc-shaped inner peripheral surface, and the tip sliding surface of the ridge is formed on the arc-shaped inner peripheral surface of the pressure chamber. The means is formed in an arc shape having a smaller radius of curvature than the radius of curvature of the arc.

【００１０】請求項６記載の摺動部シール構造は、請求
項１〜５のいずれかに記載の摺動部シール構造におい
て、前記隔壁と摺動シール部材との間には、該摺動シー
ル部材を圧力室の円弧状内周面方向に押圧付勢する付勢
部材が設けられている手段とした。According to a sixth aspect of the present invention, in the sliding portion seal structure according to any one of the first to fifth aspects, the sliding seal is provided between the partition and the sliding seal member. The means is provided with an urging member for urging the member in the direction of the arc-shaped inner peripheral surface of the pressure chamber.

【００１１】[0011]

【作用】本発明請求項１記載の摺動部シール構造では、
上述のように構成されるため、前記摺動シール部材にお
ける摺動方向幅の両端縁部に沿って突設された両突条の
先端摺動面が圧力室の円弧状内周面に当接することで、
両圧力室間の液圧シールが行われるもので、その際、圧
力室の円弧状内周面に対する両突条の接触面積が小さ
く、面圧が高くなるため、摺動シール部材による液圧シ
ール性が高められると共に、摺動フリクションも小さく
なり、また、シール箇所が２箇所となるため、高い液圧
シール性が確保される。また、ケーシングと隔壁との相
対回動によるフリクションおよび該相対回動による両圧
力室間で発生する差圧によって摺動シール部材に倒れが
生じた場合においても、両突条のうちのいずれか一方が
必ず圧力室の円弧状内周面に当接することで面圧がさら
に大きくなるもので、これにより、さらに高い液圧シー
ル性が確保される。According to the first aspect of the present invention, in the sliding portion seal structure,
Because of the above-described configuration, the sliding surfaces at the distal ends of the two protruding ridges protruding along both end edges of the sliding seal member in the sliding direction width abut against the arc-shaped inner peripheral surface of the pressure chamber. By that
A hydraulic seal between the two pressure chambers is performed. At this time, the contact area of the two ridges with the arc-shaped inner peripheral surface of the pressure chamber is small, and the surface pressure is high. The sealing performance is enhanced, the sliding friction is reduced, and the number of sealing locations is two, so that high hydraulic sealing performance is ensured. Further, even when the sliding seal member falls down due to the friction caused by the relative rotation between the casing and the partition and the pressure difference generated between the two pressure chambers due to the relative rotation, one of the two ridges is used. Are always in contact with the arc-shaped inner peripheral surface of the pressure chamber, so that the surface pressure is further increased, thereby ensuring a higher hydraulic sealing property.

【００１２】請求項２記載の摺動部シール構造では、請
求項１記載の摺動部シール構造において、前記突条の先
端摺動面が、前記圧力室内周面の円弧と同一曲率に形成
されることで、圧力室の円弧状内周面に対する面圧は少
し低下するものの、摺動シール面積がある程度確保され
るため、液圧シール性が向上する。According to a second aspect of the present invention, in the first aspect of the present invention, the tip sliding surface of the ridge has the same curvature as the arc of the peripheral surface of the pressure chamber. By doing so, although the surface pressure on the arc-shaped inner peripheral surface of the pressure chamber slightly decreases, the sliding seal area is secured to some extent, and the hydraulic sealability is improved.

【００１３】請求項３記載の摺動部シール構造は、請求
項１記載の摺動部シール構造において、前記突条の先端
摺動面が、前記圧力室内周面の円弧の曲率半径より小さ
な曲率半径の円弧状に形成されることで、圧力室の円弧
状内周面に対する接触が点接触状態となり、これによ
り、面圧が高くなって液圧シール性が向上すると共に、
フリクション低減効果が向上する。According to a third aspect of the present invention, there is provided the sliding portion seal structure according to the first aspect, wherein a tip end sliding surface of the ridge has a curvature smaller than a radius of curvature of an arc of the pressure chamber peripheral surface. By being formed in the shape of an arc of a radius, the contact of the pressure chamber with the arc-shaped inner peripheral surface becomes a point contact state, thereby increasing the surface pressure and improving the hydraulic sealability,
The effect of reducing friction is improved.

【００１４】請求項４記載の摺動部シール構造は、摺動
シール部材が断面略方形状に形成されると共に、隔壁に
形成された装着溝内に収容された状態で設けられ、該装
着溝の両内側面と摺動シール部材における両外側面と間
に装着溝底部から開口部方向へ向かうにつれて次第に広
くなる隙間がそれぞれ形成されているため、ケーシング
と隔壁との相対回動によるフリクションおよび該相対回
動による両圧力室間で発生する差圧によって摺動シール
部材に必ず倒れが生じ、摺動シール部材におけるいずれ
か一方のコーナー部分のみが必ず圧力室の円弧状内周面
に当接する状態となるもので、これにより、面圧が大き
くなって、高い液圧シール性が確保される。According to a fourth aspect of the present invention, in the sliding portion seal structure, the sliding seal member is formed in a substantially rectangular cross section and provided in a state housed in a mounting groove formed in the partition wall. Gaps gradually increasing from the bottom of the mounting groove toward the opening are formed between both inner side surfaces of the sliding seal member and the outer side surfaces of the sliding seal member. A state in which the sliding seal member always falls due to the differential pressure generated between the two pressure chambers due to the relative rotation, and only one corner portion of the sliding seal member always contacts the arc-shaped inner peripheral surface of the pressure chamber. As a result, the surface pressure is increased, and high hydraulic pressure sealing is ensured.

【００１５】請求項５記載の摺動部シール構造は、請求
項４記載の摺動部シール構造において、前記圧力室の内
周面と対面する前記摺動シール部材の摺動シール面には
その摺動方向幅の両端縁部に沿って圧力室の円弧状内周
面方向へ突出する突条がそれぞれ設けられ、該突条の先
端摺動面が、前記圧力室内周面の円弧の曲率半径より小
さな曲率半径の円弧状に形成されることで、圧力室の円
弧状内周面に対する接触が点接触状態となり、これによ
り、面圧が高くなって液圧シール性が向上すると共に、
フリクション低減効果が向上する。According to a fifth aspect of the present invention, there is provided the sliding portion seal structure according to the fourth aspect, wherein the sliding seal surface of the sliding seal member facing the inner peripheral surface of the pressure chamber has the same structure. Protrusions that protrude in the direction of the arc-shaped inner peripheral surface of the pressure chamber are provided along both end edges of the sliding direction width, and the tip sliding surface of the ridge has a radius of curvature of an arc of the pressure chamber peripheral surface. By being formed in an arc shape having a smaller radius of curvature, the contact of the pressure chamber with the arc-shaped inner peripheral surface becomes a point contact state, thereby increasing the surface pressure and improving the hydraulic sealability,
The effect of reducing friction is improved.

【００１６】請求項６記載の摺動部シール構造は、請求
項１〜５のいずれかに記載の摺動部シール構造におい
て、前記隔壁と摺動シール部材との間には、該摺動シー
ル部材を圧力室の円弧状内周面方向に押圧付勢する付勢
部材が設けられることで、摺動シール部材が変形しなく
ても圧力室の円弧状内周面に対する押し付け力が作用す
るため、液圧シール性が向上する。According to a sixth aspect of the present invention, in the sliding portion seal structure according to any one of the first to fifth aspects, the sliding seal is provided between the partition and the sliding sealing member. Since the urging member for urging the member in the direction of the arc-shaped inner peripheral surface of the pressure chamber is provided, the pressing force acts on the arc-shaped inner peripheral surface of the pressure chamber even if the sliding seal member is not deformed. And the hydraulic sealability is improved.

【００１７】[0017]

【発明の実施の形態】本発明の実施の形態を図面に基づ
いて説明する。 （発明の実施の形態１）この発明の実施の形態１は本発
明の摺動部シール構造をロータリダンパにおける摺動部
シール構造に適用した例を示す。即ち、この発明の実施
の形態１のロータリダンパにおける摺動部シール構造は
請求項１、２に記載の発明に対応するものであって、図
１は、本発明の実施の形態１のロータリダンパＲＤの構
成のうち、主に油圧回路構成を説明するための概略図、
図２は、本発明の実施の形態１のロータリダンパＲＤを
示す縦断面図（図２のＣ−Ｃ線における縦断面図）、図
３は、図２のＡ−Ａ’線における縦断面図、図４は、図
２のＢ−Ｂ’線における横断面図、図５は、図２のＡ−
Ｂ線における断面図であり、これらの図において、１は
ケーシング、２ａ、２ｂは左右１対の揺動ベーン（隔
壁）、３、３は左右１対のサイドカバーである。Embodiments of the present invention will be described with reference to the drawings. (Embodiment 1) Embodiment 1 of the present invention shows an example in which the sliding portion seal structure of the present invention is applied to a sliding portion seal structure in a rotary damper. That is, the sliding portion seal structure in the rotary damper according to the first embodiment of the present invention corresponds to the invention described in claims 1 and 2. FIG. 1 shows the rotary damper according to the first embodiment of the present invention. Schematic diagram for mainly explaining the hydraulic circuit configuration of the RD configuration,
FIG. 2 is a longitudinal sectional view (longitudinal sectional view taken along line CC of FIG. 2) showing the rotary damper RD according to the first embodiment of the present invention, and FIG. 3 is a longitudinal sectional view taken along line AA 'of FIG. FIG. 4 is a cross-sectional view taken along line BB ′ of FIG. 2, and FIG.
It is sectional drawing in the B line, In these figures, 1 is a casing, 2a, 2b is a pair of right and left swing vanes (partition), 3, 3 is a pair of right and left side covers.

【００１８】前記ケーシング１は、車体側に固定される
部材であり、その一側部（図２の左側部）上下２個所に
は、車体側に固定された図外のブラケットに対し弾性的
に連結固定するための車体側取付用ブッシュ５、５が装
着固定されている。また、ケーシング１の中央部には、
圧力室を形成するための水平方向の貫通穴１ａが形成さ
れ、該貫通穴１ａの内周面上下部分には、貫通穴１ａの
軸心方向に向かう固定ベーン１ｂ、１ｃがそれぞれ一体
に突出形成されている。The casing 1 is a member fixed to the vehicle body, and has two upper and lower portions on one side (left side in FIG. 2) elastically with respect to a bracket (not shown) fixed to the vehicle body. Body-side mounting bushes 5, 5 for connection and fixing are mounted and fixed. In the center of the casing 1,
A horizontal through hole 1a for forming a pressure chamber is formed, and fixed vanes 1b, 1c extending in the axial direction of the through hole 1a are integrally formed at upper and lower portions of an inner peripheral surface of the through hole 1a. Have been.

【００１９】前記ケーシング１における貫通穴１ａの両
開口端面には該貫通穴１ａの最大直径より大径で貫通穴
１ａとは同心円状の円形穴１ｄ、１ｅが形成されてい
る。前記各サイドカバー３、３は、前記各円形穴１ｄ、
１ｅ内に回動自在に装着されることによって貫通穴１ａ
の両端開口面を閉塞するもので円板状に形成され、その
外周面には内側から順に、円形穴１ｄ、１ｅ内周面との
摺動を案内するブッシュベアリング６、６と、回転シー
ル部材７、７と、ダストシール部材８、８とが装着され
ている。また、両サイドカバー３、３の外面上下両端部
には、図外のアッパリンクアームを締結ボルトにより締
結固定するための雌ねじ穴３ｃが形成されている。On both end surfaces of the opening of the through hole 1a in the casing 1, there are formed circular holes 1d and 1e having a diameter larger than the maximum diameter of the through hole 1a and concentric with the through hole 1a. Each of the side covers 3, 3 is provided with each of the circular holes 1d,
1e so as to be rotatably mounted in the through hole 1a.
Bush bearings 6 for guiding sliding with the inner peripheral surfaces of the circular holes 1d and 1e in order from the inner side, and a rotary seal member. 7, 7 and dust seal members 8, 8 are mounted. Female screw holes 3c for fastening and fixing an upper link arm (not shown) with fastening bolts are formed at the upper and lower ends of the outer surfaces of both side covers 3, 3.

【００２０】前記左右１対の揺動ベーン２ａ、２ｂは、
回動軸心部２ｃを中心としてその左右側面から一体に突
出形成され、各揺動ベーン２ａ、２ｂは、先端に向かう
につれて回動方向幅が大きくなる扇状に形成されてい
る。そして、回動軸心部２ｃを貫通穴１ａの軸心部を貫
通する状態で、その両端部をサイドカバー３、３の軸心
部に形成された軸心穴３ａ、３ｂに嵌装すると共に、両
揺動ベーン２ａ、２ｂをそれぞれサイドカバー３、３と
ボルト・ナット９、１０で締結することにより、両サイ
ドカバー３、３間に一体に挟持固定され、これにより、
ケーシング１に対し、両サイドカバー３、３と両揺動ベ
ーン２ａ、２ｂとが、回動軸心部２ｃを中心として回動
自在に組み付けられている。The pair of left and right swing vanes 2a, 2b
The swinging vanes 2a, 2b are formed in a fan shape whose width in the rotating direction increases toward the tip end, and is integrally formed so as to protrude from the left and right side surfaces around the rotating shaft center portion 2c. In a state where the rotation axis 2c passes through the axis of the through hole 1a, both ends thereof are fitted into the axis holes 3a and 3b formed in the axis of the side covers 3 and 3, respectively. By fastening the swinging vanes 2a and 2b to the side covers 3 and 3 with the bolts and nuts 9 and 10, respectively, the two swinging vanes 2a and 2b are integrally clamped and fixed between the both side covers 3 and 3.
Both side covers 3, 3 and both swinging vanes 2a, 2b are attached to the casing 1 so as to be rotatable about a rotation axis 2c.

【００２１】前記左右一対の揺動ベーン２ａ、２ｂの外
周面に軸方向に形成された装着溝２ｄ、２ｅには、貫通
穴１ａ内周面との間を摺動シールする摺動シール部材１
１、１１が装着されている。また、前記上下一対の固定
ベーン１ｂ、１ｃの先端面に軸方向に形成された装着溝
２ｆ、２ｇには、回動軸心部２ｃ外周面との間を摺動シ
ールする摺動シール部材１３、１３が装着されている。A mounting groove 2d, 2e formed in the outer peripheral surface of the pair of left and right swinging vanes 2a, 2b in the axial direction has a sliding seal member 1 for slidingly sealing between the inner peripheral surface of the through hole 1a.
1 and 11 are mounted. The mounting grooves 2f and 2g formed in the tip surfaces of the pair of upper and lower fixed vanes 1b and 1c in the axial direction have sliding seal members 13 for slidingly sealing between the outer peripheral surfaces of the rotating shaft portion 2c. , 13 are mounted.

【００２２】前記摺動シール部材１１は、図６、図７に
その要部拡大断面図を示すように、第１圧力室１５ａ、
１５ｂと第２圧力室１６ａ、１６ｂとの間で発生する流
体圧力では変形しないポリプロスチレン樹脂（ＰＰＳ樹
脂）で断面略方形状に形成されると共に、前記圧力室１
５ａ、１５ｂ、１６ａ、１６ｂを構成する貫通穴１ａの
円弧状内周面と対面する摺動シール部材１１の摺動シー
ル面にはその摺動方向幅の両端縁部に沿って中央部より
は前記貫通穴１ａの円弧状内周面方向へ突出する突条１
１ａ、１１ａがそれぞれ設けられている。The sliding seal member 11 has a first pressure chamber 15a, as shown in FIG. 6 and FIG.
The pressure chamber 1 is formed of a polystyrene resin (PPS resin) which is not deformed by a fluid pressure generated between the pressure chamber 15b and the second pressure chambers 16a, 16b.
The sliding seal surface of the sliding seal member 11 facing the arc-shaped inner peripheral surface of the through-hole 1a constituting 5a, 15b, 16a, 16b has a smaller width than the central portion along both edges of the sliding direction width. A ridge 1 protruding toward the arc-shaped inner peripheral surface of the through hole 1a.
1a and 11a are provided respectively.

【００２３】そして、前記突条１１ａ、１１ａの先端摺
動面が、前記貫通穴１ａの円弧状内周面の円弧と同一曲
率半径Ｒｈの円弧状に形成されている。また、前記摺動
シール部材１１における摺動シール面の中央部の窪み部
１１ｂを回動軸心部２ｃの外周円弧面と同一の曲率半径
Ｒｓの円弧状に形成することにより、前記摺動シール部
材１３との部品の共用化を図っている（図９参照）。The leading end sliding surfaces of the ridges 11a are formed in an arc shape having the same radius of curvature Rh as the arc of the arc-shaped inner peripheral surface of the through hole 1a. Further, the sliding seal member 11 is formed such that the recessed portion 11b at the center of the sliding seal surface is formed in an arc shape having the same radius of curvature Rs as the outer peripheral arc surface of the rotating shaft center portion 2c. Parts are shared with the member 13 (see FIG. 9).

【００２４】なお、図７の要部拡大断面図に示すよう
に、前記装着溝２ｄ、２ｅと摺動シール部材１１、１１
との間には、該摺動シール部材１１、１１が円周方向お
よび半径方向に移動可能な微小なクリアランスが形成さ
れるように組み付けられている。As shown in an enlarged sectional view of a main part of FIG. 7, the mounting grooves 2d, 2e and the sliding seal members 11, 11
The sliding seal members 11, 11 are assembled so as to form a small clearance between the sliding seal members 11 and 11 that can move in the circumferential direction and the radial direction.

【００２５】以上のような組み付け構造により、上下一
対の固定ベーン１ｂ、１ｃと左右一対の揺動ベーン２
ａ、２ｂとの間に該揺動ベーン２ａ、２ｂの回動により
一方の体積が増加した時には他方が減少する上下一対の
第１圧力室１５ａ、１５ｂと上下一対の第２圧力室１６
ａ、１６ｂに区画形成され、該各圧力室１５ａ、１５
ｂ、１６ａ、１６ｂ内には粘性オイル（流体）Ｏが充填
されている。With the above assembly structure, a pair of upper and lower fixed vanes 1b and 1c and a pair of right and left swing vanes 2
a and a pair of upper and lower first pressure chambers 15a and 15b and a pair of upper and lower second pressure chambers 16 that decrease when the volume of one increases due to the rotation of the swing vanes 2a and 2b.
a, 16b, and each of the pressure chambers 15a, 15b
Viscous oil (fluid) O is filled in b, 16a and 16b.

【００２６】即ち、前記２対の各圧力室１５ａ、１５
ｂ、１６ａ、１６ｂがロータリダンパＲＤの取付状態に
おいて前記各揺動ベーン２ａ、２ｂによりそれぞれ上下
方向に上部の第１圧力室５ａおよび上部の第２圧力室６
ａと、下部の第１圧力室５ｂおよび下部の第２圧力室６
ｂとに区画形成されている。That is, the two pairs of pressure chambers 15a, 15a
When the rotary damper RD is mounted, the swinging vanes 2a and 2b vertically move the upper first pressure chamber 5a and the upper second pressure chamber 6 respectively.
a, a lower first pressure chamber 5b and a lower second pressure chamber 6
b.

【００２７】そして、前記各圧力室１５ａ、１５ｂ、１
６ａ、１６ｂのうち容積変化が互いに一致する上下一対
の第１圧力室１５ａ、１５ｂ同士および上下一対の第２
圧力室１６ａ、１６ｂ同士をそれぞれ連通する１対の第
１の連通路１５、１６が設けられている。The pressure chambers 15a, 15b, 1
A pair of upper and lower first pressure chambers 15a and 15b and a pair of upper and lower second pressure chambers 6a and 16b whose volume changes match each other.
A pair of first communication passages 15 and 16 for communicating the pressure chambers 16a and 16b with each other are provided.

【００２８】前記上下各固定ベーン１ｂ、１ｃの基部に
は、該固定ベーン１ｂ、１ｃを軸方向に貫通する上部貫
通穴１９および下部貫通穴２０が形成されている。そし
て、この上部貫通穴１９の両端開口部は、上部固定ベー
ン１ｂの軸方向両端面の基部にそれぞれ形成された上部
連通溝２１、２２により、上部の第１圧力室１５ａと上
部の第２圧力室１６ａの最上部にそれぞれ連通され、ま
た、下部貫通穴２０の両端開口部は、下部固定ベーン１
ｃの軸方向両端面の基部にそれぞれ形成された下部連通
溝２３、２４により、下部の第１圧力室１５ｂと下部の
第２圧力室１６ｂの最下部にそれぞれ連通されている。
また、前記上部貫通穴１９の軸方向中央部の上端部と下
部貫通穴２０の軸方向中央部の下端部との間が、ケーシ
ング１内に形成されたコ字状穴２５により連結されるこ
とにより、このコ字状穴２５と、上部貫通穴１９と、下
部貫通穴２０と、各連通溝２１、２２、２３、２４によ
り、各揺動ベーン２ａ、２ｂを介して容積変化が互いに
逆になる圧力室（１５ａ−１６ｂ、１６ａ−１５ｂ）同
士をそれぞれ連通する１対の第２の連通路Ｃが構成され
ている。なお、この発明の実施の形態１では、コ字状穴
２５で１対の第２の連通路Ｃの一部を共用すると共に、
このコ字状穴２５の下部側を粘性オイルＯを収容した下
部流体室２５ｂとし、上部側を空気Ａを封入した上部空
気室２５ａとすることにより、リザーバ室Ｒを構成させ
ている。At the base of each of the upper and lower fixed vanes 1b, 1c, there are formed an upper through hole 19 and a lower through hole 20 which penetrate the fixed vanes 1b, 1c in the axial direction. Openings at both ends of the upper through hole 19 are formed by upper communication grooves 21 and 22 formed at bases of both end surfaces in the axial direction of the upper fixed vane 1b, respectively, so that the upper first pressure chamber 15a and the upper second pressure chamber 15a are formed. The upper ends of the chambers 16a are communicated with each other.
The lower communication grooves 23 and 24 formed at the bases of both end surfaces in the axial direction of c respectively communicate with the lowermost of the lower first pressure chamber 15b and the lower second pressure chamber 16b.
The upper end of the upper through hole 19 in the axial center and the lower end of the lower through hole 20 in the axial center are connected by a U-shaped hole 25 formed in the casing 1. Thus, the U-shaped holes 25, the upper through holes 19, the lower through holes 20, and the communication grooves 21, 22, 23, and 24 cause the volume changes to be opposite to each other via the swinging vanes 2a and 2b. A pair of second communication passages C that communicate the pressure chambers (15a-16b, 16a-15b) with each other are formed. In the first embodiment of the present invention, the U-shaped hole 25 shares a part of the pair of second communication paths C, and
A reservoir chamber R is formed by forming a lower fluid chamber 25b containing viscous oil O on the lower side of the U-shaped hole 25 and an upper air chamber 25a containing air A on the upper side.

【００２９】前記上部貫通穴１９における両端開口部と
中央部との間には、上部の第１圧力室１５ａからリザー
バ室Ｒ方向への粘性オイルＯの流通のみを制限的に許容
する伸側ディスクバルブ２６ａと伸側オリフィス２６
ｂ、および、上部の第２圧力室６ａからリザーバ室Ｒ方
向への粘性オイルＯの流通のみを制限的に許容する圧側
ディスクバルブ２７ａと圧側オリフィス２７ｂとがそれ
ぞれ直列状態で収容固定されている。即ち、この発明の
実施の形態１では、第３の連通路が前記第２の連通路Ｃ
と共通流路で構成されている。An extension-side disk between the openings at both ends and the center of the upper through hole 19, which restricts only the flow of the viscous oil O from the upper first pressure chamber 15a toward the reservoir chamber R. Valve 26a and extension orifice 26
b, and a pressure-side disc valve 27a and a pressure-side orifice 27b which restrict and allow only the flow of the viscous oil O from the upper second pressure chamber 6a toward the reservoir chamber R are accommodated and fixed in series. That is, in the first embodiment of the present invention, the third communication path is the second communication path C
And a common flow path.

【００３０】前記下部貫通穴２０における両端開口部と
中央部との間には、リザーバ室Ｒから下部の第１圧力室
１５ｂおよび下部の第２圧力室１６ｂ方向への粘性オイ
ルＯの流通のみを許容する伸側チェックバルブ２８、お
よび、圧側チェックバルブ２９がそれぞれ収容固定され
ている。Only the flow of the viscous oil O from the reservoir chamber R to the lower first pressure chamber 15b and the lower second pressure chamber 16b is provided between the opening at both ends and the center of the lower through hole 20. A permissible extension side check valve 28 and a compression side check valve 29 are accommodated and fixed, respectively.

【００３１】次に、この発明の実施の形態１の作用・効
果を説明する。 （イ）減衰力発生作用 ばね下のホイール側に対し車体側が上昇するロータリダ
ンパＲＤの伸行程においては、図１および図２において
ケーシング１に対し両サイドカバー３、３が時計方向に
回動し、これにより、両サイドカバー３、３に対して一
体に固定された両揺動ベーン２ａ、２ｂが回動軸心部２
ｃを中心として時計方向に回動し、回動方向側である第
１圧力室１５ａ、１５ｂ内の粘性オイルＯが加圧される
一方、回動方向とは反対方向側である第２圧力室１６
ａ、１６ｂ内の粘性オイルＯが減圧されるため、加圧側
である第１圧力室１５ａ、１５ｂ内の粘性オイルＯが第
３の連通路Ｃにおける、伸側オリフィス２６ｂ、伸側デ
ィスクバルブ２６ａ、リザーバ室Ｒ、伸側チェックバル
ブ２８を経由して減圧側である第２圧力室１６ａ、１６
ｂ側に流通するが、その粘性オイルＯの流通が第３の連
通路Ｃと共通の第２の連通路に介装された伸側オリフィ
ス２６ｂおよび伸側ディスクバルブ２６ａで制限される
ことにより、第１圧力室１５ａ、１５ｂと第２圧力室１
６ａ、１６ｂとの間に差圧が発生し、この差圧により揺
動ベーン２ａ、２ｂの時計方向の回動、即ちロータリダ
ンパＲＤの伸行程方向の回動において所定の伸側減衰力
を発生させる。Next, the operation and effect of the first embodiment of the present invention will be described. (A) Damping force generating action In the extension stroke of the rotary damper RD in which the vehicle body side rises with respect to the unsprung wheel side, the both side covers 3, 3 rotate clockwise with respect to the casing 1 in FIGS. Thereby, the two swinging vanes 2a and 2b integrally fixed to the both side covers 3 and 3 are rotated.
and the viscous oil O in the first pressure chambers 15a and 15b, which is on the rotation direction side, is pressurized, while the second pressure chamber is on the opposite side to the rotation direction. 16
Since the viscous oil O in the first and second pressure chambers 15a and 15b is pressurized, the viscous oil O in the first pressure chambers 15a and 15b in the third communication path C extends the orifice 26b, the disc valve 26a, The second pressure chambers 16a, 16 on the decompression side via the reservoir chamber R and the extension side check valve 28
Although the fluid flows to the b side, the flow of the viscous oil O is restricted by the expansion-side orifice 26b and the expansion-side disc valve 26a interposed in the second communication path common to the third communication path C, First pressure chamber 15a, 15b and second pressure chamber 1
A differential pressure is generated between the rotary vanes 6a and 16b, and the differential pressure generates a predetermined expansion-side damping force in the clockwise rotation of the swing vanes 2a and 2b, that is, in the rotation of the rotary damper RD in the expansion stroke direction. Let it.

【００３２】以上とは逆に、ばね下のホイール３２側に
対し車体側が下降するロータリダンパＲＤの圧行程にお
いては、図１および図２においてケーシング１に対し両
サイドカバー３、３が反時計方向に回動し、これによ
り、両サイドカバー３、３に対して一体に固定された両
揺動ベーン２ａ、２ｂが回動軸心部２ｃを中心として反
時計方向に回動し、回動方向側である第２圧力室１６
ａ、１６ｂ内の粘性オイルＯが加圧される一方、回動方
向とは反対方向側である第１圧力室１５ａ、１５ｂ内の
粘性オイルＯが減圧されるため、加圧側である第２圧力
室１６ａ、１６ｂ内の粘性オイルＯが第３の連通路Ｃに
おける圧側オリフィス２７ｂ、圧側ディスクバルブ２７
ａ、リザーバ室Ｒ、圧側チェックバルブ２９を経由して
減圧側である第１圧力室１５ａ、１５ｂ側に流通する
が、その粘性オイルＯの流通が第３の連通路Ｃと共通の
第２の連通路に介装された圧側オリフィス２７ｂおよび
圧側ディスクバルブ２７ａで制限されることにより、第
２圧力室１６ａ、１６ｂと第１圧力室１５ａ、１５ｂと
の間に差圧が発生し、この差圧により揺動ベーン２ａ、
２ｂの反時計方向の回動、即ちロータリダンパＲＤの圧
行程において所定の圧側減衰力を発生させる。Contrary to the above, in the pressure stroke of the rotary damper RD in which the vehicle body side descends with respect to the unsprung wheel 32 side, in FIG. 1 and FIG. As a result, the swinging vanes 2a, 2b integrally fixed to the both side covers 3, 3 rotate counterclockwise about the rotation axis 2c, and rotate in the rotation direction. The second pressure chamber 16 on the side
While the viscous oil O in the first and second pressure chambers 15a and 15b is depressurized while the viscous oil O in the first and second pressure chambers 15a and 15b is depressurized, the second pressure on the pressurized side is reduced. The viscous oil O in the chambers 16a and 16b is supplied to the pressure side orifice 27b and the pressure side disc valve 27
a, flows through the reservoir chamber R and the pressure side check valve 29 to the first pressure chambers 15a and 15b, which are on the pressure reducing side, and the flow of the viscous oil O flows through the second communication path C common to the third communication path C. The pressure difference is generated between the second pressure chambers 16a, 16b and the first pressure chambers 15a, 15b by being limited by the pressure-side orifice 27b and the pressure-side disc valve 27a interposed in the communication passage. Swing vane 2a,
A predetermined pressure-side damping force is generated in the counterclockwise rotation of 2b, that is, in the pressure stroke of the rotary damper RD.

【００３３】（ロ）摺動部の液圧シール作用 前記左右一対の揺動ベーン２ａ、２ｂの外周面に軸方向
に形成された装着溝２ｄ、２ｅにそれぞれ装着された摺
動シール部材１１、１１により、貫通穴１ａ内周面と揺
動ベーン２ａ、２ｂの外周面との間が液圧シールされる
と共に、前記上下一対の固定ベーン１ｂ、１ｃの先端面
に軸方向に形成された装着溝２ｆ、２ｇにそれぞれ装着
された摺動シール部材１３、１３により、回動軸心部２
ｃの外周面と固定ベーン１ｂ、１ｃの先端面との間が液
圧シールされた状態となる。(B) Hydraulic sealing action of the sliding part The sliding seal members 11, which are respectively mounted in mounting grooves 2d, 2e formed in the axial direction on the outer peripheral surfaces of the pair of right and left swing vanes 2a, 2b. 11, a hydraulic pressure seal is provided between the inner peripheral surface of the through hole 1a and the outer peripheral surfaces of the swinging vanes 2a, 2b, and a mounting formed axially on the distal end surfaces of the pair of upper and lower fixed vanes 1b, 1c. The sliding shaft members 2 and 3 attached to the grooves 2f and 2g respectively cause the pivot shaft portion 2 to rotate.
c between the outer peripheral surface and the front end surfaces of the fixed vanes 1b and 1c are in a state of being hydraulically sealed.

【００３４】即ち、例えば、両揺動ベーン２ａが回動軸
心部２ｃを中心として反時計方向に回動するロータリダ
ンパＲＤの圧行程においては、図７に示すように、回動
方向側である第２圧力室１６ｂ内の粘性オイルＯが加圧
される一方、回動方向とは反対方向側である第１圧力室
１５ａ内の粘性オイルＯが減圧されるため、差圧ΔＰが
発生し、この差圧ΔＰが、摺動シール部材１１の左側面
と底面に作用することで、摺動シール部材１１の右側側
面が装着溝２ｄの右側内壁面に押し付けられると共に、
摺動シール部材１１における両突条１１ａ、１１ａの先
端摺動面が貫通穴１ａの円弧状内周面に押し付けられる
ことで、第２圧力室１６ｂと第１圧力室１５ａとの間が
液圧シールされた状態となる。That is, for example, in the pressure stroke of the rotary damper RD in which the two swinging vanes 2a rotate counterclockwise about the rotation axis 2c, as shown in FIG. While the viscous oil O in the certain second pressure chamber 16b is pressurized, the viscous oil O in the first pressure chamber 15a, which is on the opposite side to the rotating direction, is depressurized, and a differential pressure ΔP is generated. When the differential pressure ΔP acts on the left side surface and the bottom surface of the sliding seal member 11, the right side surface of the sliding seal member 11 is pressed against the right inner wall surface of the mounting groove 2d.
By pressing the sliding surfaces at the distal ends of the ridges 11a, 11a in the sliding seal member 11 against the arc-shaped inner peripheral surface of the through hole 1a, the hydraulic pressure between the second pressure chamber 16b and the first pressure chamber 15a is increased. It will be in a sealed state.

【００３５】そして、その際、貫通穴１ａの円弧状内周
面に対する両突条１１ａ、１１ａの接触面積が小さく、
面圧が高くなるため、摺動シール部材１１による液圧シ
ール性が高められると共に、摺動フリクションも小さく
なり、また、シール箇所が２箇所となるため、高い液圧
シール性を確保することができるようになる。At this time, the contact area of the two ridges 11a with the arcuate inner peripheral surface of the through hole 1a is small,
Since the surface pressure is increased, the hydraulic sealing performance of the sliding seal member 11 is enhanced, and the sliding friction is reduced. In addition, since two sealing locations are provided, high hydraulic sealing performance can be ensured. become able to.

【００３６】なお、両突条１１ａ、１１ａの先端摺動面
が、貫通穴１ａの円弧状内周面の円弧と同一曲率に形成
されることで、該円弧状内周面に対する面圧は少し低下
するものの、摺動シール面積がある程度確保されるた
め、高い液圧シール性が得られる。It is to be noted that the sliding surface at the tip end of each of the ridges 11a, 11a is formed to have the same curvature as the arc of the arc-shaped inner peripheral surface of the through hole 1a, so that the surface pressure on the arc-shaped inner peripheral surface is small. Although reduced, the sliding seal area is secured to some extent, so that high hydraulic sealability can be obtained.

【００３７】また、前記装着溝２ｄ、２ｅと摺動シール
部材１１、１１との間には、該摺動シール部材１１、１
１が円周方向および半径方向に移動可能な微小なクリア
ランスが形成されるように組み付けられている関係で、
貫通穴１ａの円弧状内周面と突条１１ａ、１１ａとの摺
動フリクションおよび第２圧力室１６ｂと第１圧力室１
５ａとの間で発生する差圧ΔＰにより摺動シール部材１
１に倒れが生じた場合においても、図８に示すように、
両突条１１ａ、１１ａのうちのいずれか一方が必ず貫通
穴１ａの円弧状内周面に当接することで面圧がさらに大
きくなるもので、これにより、さらに高い液圧シール性
が確保されることになる。The sliding seal members 11, 1 are provided between the mounting grooves 2d, 2e and the sliding seal members 11, 11.
1 is assembled so that a minute clearance movable in the circumferential direction and the radial direction is formed,
Sliding friction between the arc-shaped inner peripheral surface of the through hole 1a and the ridges 11a, 11a, and the second pressure chamber 16b and the first pressure chamber 1
5a and the sliding pressure of the sliding seal member 1
Even when the device 1 falls down, as shown in FIG.
One of the two ridges 11a, 11a always comes into contact with the arc-shaped inner peripheral surface of the through hole 1a, so that the surface pressure is further increased, thereby ensuring a higher hydraulic sealing property. Will be.

【００３８】次に、本発明の他の実施の形態について説
明する。なお、この他の実施の形態の説明に当たって
は、前記発明の実施の形態１と同様の構成部分には同一
の符号を付してその説明を省略し、相違点についてのみ
説明する。Next, another embodiment of the present invention will be described. In the description of the other embodiments, the same components as those in the first embodiment of the present invention will be denoted by the same reference numerals, and the description thereof will be omitted, and only different points will be described.

【００３９】（発明の実施の形態２）図１０〜図１２に
示すこの発明の実施の形態２のロータリダンパの摺動部
シール構造は、請求項３に記載の発明に対応するもので
あって、これらの図に示すように、前記摺動シール部材
１１における両突条１１ａ、１１ａの先端摺動面が、貫
通穴１ａの円弧状内周面の円弧の曲率半径より小さな曲
率半径の円弧状に形成されている点が、前記発明の実施
の形態１とは相違したものである。(Embodiment 2) A seal structure for a sliding portion of a rotary damper according to Embodiment 2 of the present invention shown in FIGS. 10 to 12 corresponds to the invention described in claim 3. As shown in these drawings, the sliding surfaces of the sliding protrusions 11a, 11a of the sliding seal member 11 have a smaller radius of curvature than the radius of curvature of the arc of the arc-shaped inner peripheral surface of the through hole 1a. Is different from the first embodiment of the present invention.

【００４０】即ち、この発明の実施の形態２では、上述
にように、両突条１１ａ、１１ａの先端摺動面が、貫通
穴１ａの円弧状内周面の円弧の曲率半径より小さな曲率
半径の円弧状に形成されているため、図１１、１２に示
すように、貫通穴１ａの円弧状内周面に対する接触が点
接触状態となり、これにより、面圧が高くなって液圧シ
ール性をさらに向上させることができると共に、フリク
ション低減効果をさらに向上させることができるように
なる。That is, in the second embodiment of the present invention, as described above, the tip sliding surfaces of the two ridges 11a, 11a have a radius of curvature smaller than the radius of curvature of the arc of the arc-shaped inner peripheral surface of the through hole 1a. 11 and 12, the contact of the through-hole 1a with the arc-shaped inner peripheral surface becomes a point contact state as shown in FIGS. 11 and 12, thereby increasing the surface pressure and improving the hydraulic sealability. This can be further improved, and the effect of reducing friction can be further improved.

【００４１】（発明の実施の形態３）この発明の実施の
形態３のロータリダンパの摺動部シール構造は、請求項
４、５に記載の発明に対応するものであって、図１３に
示すように、装着溝２ｄ（２ｅ）における溝断面形状を
底部の幅Ｂｈより開口部の幅Ｂｓが広い台形状に形成す
ることにより、装着溝２ｄ（２ｅ）の両内側面と摺動シ
ール部材１１における両外側面との間に形成されるクリ
アランスを、装着溝２ｄ（２ｅ）の底部から開口部方向
へ向かうにつれて次第に広くなるように形成したもので
ある。(Embodiment 3) A sliding part seal structure of a rotary damper according to Embodiment 3 of the present invention corresponds to the invention described in claims 4 and 5, and is shown in FIG. As described above, by forming the cross-sectional shape of the mounting groove 2d (2e) into a trapezoidal shape in which the width Bs of the opening is wider than the width Bh of the bottom, both inner surfaces of the mounting groove 2d (2e) and the sliding seal member 11 are formed. Is formed so as to gradually increase from the bottom of the mounting groove 2d (2e) toward the opening.

【００４２】この発明の実施の形態３では、以上のよう
に構成したことで、貫通穴１ａの円弧状内周面と突条１
１ａ、１１ａとの摺動フリクションおよび第２圧力室１
６ｂと第１圧力室１５ａとの間で発生する差圧ΔＰによ
り、図１４に示すように、摺動シール部材１１に必ず倒
れが生じるため、摺動シール部材１１におけるいずれか
一方の突条１１ａ、１１ａのみが必ず貫通穴１ａの円弧
状内周面に当接する状態となるもので、これにより、面
圧が大きくなって、高い液圧シール性を確保することが
できるようになる。According to the third embodiment of the present invention, the arc-shaped inner peripheral surface of the through hole 1a and the ridge 1
Sliding friction with 1a, 11a and second pressure chamber 1
As shown in FIG. 14, the sliding seal member 11 always falls down due to the pressure difference ΔP generated between the sliding seal member 11 and the first pressure chamber 15a. , 11a always come into contact with the arc-shaped inner peripheral surface of the through hole 1a, whereby the surface pressure is increased and a high hydraulic sealability can be secured.

【００４３】（発明の実施の形態４）この発明の実施の
形態４のロータリダンパの摺動部シール構造は、請求項
４、５に記載の発明に対応するものであって、図１５に
示すように、摺動シール部材１１の断面形状を装着溝２
ｄ（２ｅ）の底部側の幅Ｃｈより開口部側の幅Ｃｓが狭
い台形状に形成することにより、装着溝２ｄ（２ｅ）の
両内側面と摺動シール部材１１における両外側面との間
に形成されるクリアランスを、装着溝２ｄ（２ｅ）の底
部から開口部方向へ向かうにつれて次第に広くなるよう
に形成したものである。(Embodiment 4) A sliding part seal structure of a rotary damper according to Embodiment 4 of the present invention corresponds to the invention described in Claims 4 and 5, and is shown in FIG. Thus, the sectional shape of the sliding seal member 11 is
By forming the width Cs on the opening side narrower than the width Ch on the bottom side of d (2e), a gap between both inner side surfaces of the mounting groove 2d (2e) and both outer side surfaces of the sliding seal member 11 is formed. Is formed so as to gradually increase from the bottom of the mounting groove 2d (2e) toward the opening.

【００４４】従って、この発明の実施の形態４では、前
記発明の実施の形態３と同様に、貫通穴１ａの円弧状内
周面と突条１１ａ、１１ａとの摺動フリクションおよび
第２圧力室１６ｂと第１圧力室１５ａとの間で発生する
差圧ΔＰにより、図１６に示すように、摺動シール部材
１１に必ず倒れが生じるため、摺動シール部材１１にお
けるいずれか一方の突条１１ａ、１１ａのみが必ず貫通
穴１ａの円弧状内周面に当接する状態となるもので、こ
れにより、面圧が大きくなって、高い液圧シール性を確
保することができるようになる。Therefore, in the fourth embodiment of the present invention, as in the third embodiment of the present invention, the sliding friction between the arc-shaped inner peripheral surface of the through hole 1a and the ridges 11a, 11a and the second pressure chamber are provided. As shown in FIG. 16, the sliding seal member 11 always falls down due to the differential pressure ΔP generated between the sliding seal member 11 and the first pressure chamber 15a. , 11a always come into contact with the arc-shaped inner peripheral surface of the through hole 1a, whereby the surface pressure is increased and a high hydraulic sealability can be secured.

【００４５】（発明の実施の形態５）この発明の実施の
形態５のロータリダンパＲＤは、請求項６に記載の発明
に対応するものであって、図１７に示すように、前記装
着溝２ｄ（２ｅ）の底部に摺動シール部材１１を貫通穴
１ａの内周面方向に押圧付勢するバックアップスプリン
グ（押圧手段）１２を介装した構造としたものである。(Fifth Embodiment) A rotary damper RD according to a fifth embodiment of the present invention corresponds to the invention described in claim 6, and as shown in FIG. The backup spring (pressing means) 12 which presses and biases the sliding seal member 11 toward the inner peripheral surface of the through hole 1a is provided at the bottom of (2e).

【００４６】従って、摺動シール部材１１が変形しない
材料で形成されていても、貫通穴１ａの円弧状内周面に
対する押し付け力が作用するため、液圧シール性を向上
させることができるようになる。Therefore, even if the sliding seal member 11 is formed of a material that does not deform, a pressing force acts on the arc-shaped inner peripheral surface of the through hole 1a, so that the hydraulic sealability can be improved. Become.

【００４７】以上、発明の実施の形態について説明して
きたが具体的な構成は前記発明の実施の形態に限られる
ものではなく、本発明の要旨を逸脱しない範囲の設計変
更等があっても本発明に含まれる。Although the embodiments of the present invention have been described above, the specific configuration is not limited to the embodiments of the present invention, and even if there is a design change or the like within a range not departing from the gist of the present invention. Included in the invention.

【００４８】例えば、発明の実施の形態では、ロータリ
ダンパに適用した例を示したが、その他、流体を充填す
る圧力室を構成するケーシングの円弧状内周面に沿って
回動する隔壁により前記圧力室が２つの圧力室に画成さ
れたものにおいて、円弧状内周面と隔壁との間を液圧シ
ールする場合に全て適用することができる。For example, in the embodiment of the present invention, an example in which the invention is applied to a rotary damper has been described. However, in addition to the above, a partition wall which rotates along an arc-shaped inner peripheral surface of a casing constituting a pressure chamber for filling a fluid may be used. In the case where the pressure chamber is defined by two pressure chambers, the present invention can be applied to all cases where a liquid pressure seal is provided between the arc-shaped inner peripheral surface and the partition.

【００４９】また、発明の実施の形態では、摺動シール
部材をポリプロスチレン樹脂で形成したが、その他の樹
脂や金属等で形成することもできる。Further, in the embodiment of the present invention, the sliding seal member is formed of a polystyrene resin, but may be formed of another resin or metal.

【００５０】[0050]

【発明の効果】以上説明してきたように、本発明請求項
１記載のロータリダンパの摺動部シール構造では、前述
のように、流体を充填する圧力室を構成するケーシング
の円弧状内周面に沿って回動する隔壁により前記圧力室
が２つの圧力室に画成され、前記隔壁における前記圧力
室の円弧状内周面との摺動対向面には該円弧状内周面と
の間を液圧シールする摺動シール部材が設けられ、該摺
動シール部材が少なくとも前記２つの圧力室内で発生す
る流体圧力では変形しない材料で形成されると共に、前
記圧力室の円弧状内周面と対面する前記摺動シール部材
の摺動シール面にはその摺動方向幅の両端縁部に沿って
前記円弧状内周面方向へ突出する突条がそれぞれ設けら
れている構成としことで、圧力室の円弧状内周面に対す
る両突条の接触面積が小さく、面圧が高くなるため、摺
動シール部材による液圧シール性が高められると共に、
摺動フリクションも小さくなり、また、シール箇所が２
箇所となるため、高い液圧シール性を確保できるように
なるという効果が得られる。As described above, in the sliding portion seal structure of the rotary damper according to the first aspect of the present invention, as described above, the arc-shaped inner peripheral surface of the casing forming the pressure chamber filled with the fluid. The pressure chamber is defined as two pressure chambers by a partition wall that rotates along the axis, and a sliding opposing surface of the partition wall with the arcuate inner peripheral surface of the pressure chamber is between the pressure chamber and the arcuate inner peripheral surface. A sliding seal member for hydraulically sealing the pressure chamber, the sliding seal member is formed of a material that is not deformed by fluid pressure generated in at least the two pressure chambers, and an arc-shaped inner peripheral surface of the pressure chamber. The sliding seal surface of the facing sliding seal member is provided with ridges protruding in the direction of the arc-shaped inner peripheral surface along both end portions of the width in the sliding direction, thereby reducing the pressure. Contact surface of both ridges on the arcuate inner peripheral surface of the chamber Is small, the surface pressure is high, with hydraulic seal is enhanced by the sliding seal member,
The sliding friction is small, and the
Since it is a location, an effect that a high hydraulic sealing property can be secured can be obtained.

【００５１】また、ケーシングと隔壁との相対回動によ
るフリクションおよび該相対回動による両圧力室間で発
生する差圧によって摺動シール部材に倒れが生じた場合
においても、両突条のうちのいずれか一方が必ず圧力室
の円弧状内周面に当接することで面圧がさらに大きくな
るもので、これにより、さらに高い液圧シール性を確保
することができるようになる。Further, even when the sliding seal member falls down due to the friction caused by the relative rotation between the casing and the partition wall and the differential pressure generated between the two pressure chambers due to the relative rotation, the sliding protrusions of the two ridges are also provided. One of them always comes into contact with the arcuate inner peripheral surface of the pressure chamber, so that the surface pressure is further increased, so that a higher hydraulic sealing property can be secured.

【００５２】請求項２記載の摺動部シール構造では、請
求項１記載の摺動部シール構造において、前記突条の先
端摺動面が、前記圧力室の円弧状内周面の円弧と同一曲
率に形成されている構成としたことで、圧力室の円弧状
内周面に対する面圧は少し低下するものの、摺動シール
面積がある程度確保されるため、液圧シール性が向上す
る。According to a second aspect of the present invention, in the first aspect of the present invention, the sliding surface at the tip end of the ridge is the same as the arc of the arc-shaped inner peripheral surface of the pressure chamber. Although the surface pressure on the arc-shaped inner peripheral surface of the pressure chamber is slightly reduced due to the configuration having the curvature, the sliding seal area is secured to some extent, so that the hydraulic sealability is improved.

【００５３】請求項３記載の摺動部シール構造では、請
求項１記載の摺動部シール構造において、前記突条の先
端摺動面が、前記圧力室の円弧状内周面の円弧の曲率半
径より小さな曲率半径の円弧状に形成されている構成と
したことで、圧力室の円弧状内周面に対する接触が点接
触状態となり、これにより、面圧が高くなって液圧シー
ル性が向上すると共に、フリクション低減効果が向上す
る。According to a third aspect of the present invention, in the first aspect of the present invention, the tip sliding surface of the ridge has a curvature of an arc of an arcuate inner peripheral surface of the pressure chamber. The pressure chamber is in point contact with the arc-shaped inner peripheral surface by adopting a configuration that is formed in an arc shape with a radius of curvature smaller than the radius, thereby increasing the surface pressure and improving the hydraulic sealability. In addition, the effect of reducing friction is improved.

【００５４】請求項４記載の摺動部シール構造では、流
体を充填する圧力室を構成するケーシングの円弧状内周
面に沿って回動する隔壁により前記圧力室が２つの圧力
室に画成され、前記隔壁における前記圧力室の円弧状内
周面との摺動対向面には該円弧状内周面との間を液圧シ
ールする摺動シール部材が設けられ、該摺動シール部材
が少なくとも前記２つの圧力室内で発生する流体圧力で
は変形しない材料で断面略方形状に形成され、該摺動シ
ール部材は前記隔壁に形成された装着溝内に収容された
状態で設けられ、該装着溝の両内側面と摺動シール部材
における両外側面と間に装着溝底部から開口部方向へ向
かうにつれて次第に広くなる隙間がそれぞれ形成されて
いる構成としたことで、ケーシングと隔壁との相対回動
によるフリクションおよび該相対回動による両圧力室間
で発生する差圧によって摺動シール部材に必ず倒れが生
じ、摺動シール部材におけるいずれか一方のコーナー部
分のみが必ず圧力室の円弧状内周面に当接する状態とな
るため、面圧が大きくなって、高い液圧シール性を確保
することができるようになるという効果が得られる。According to the fourth aspect of the present invention, the pressure chamber is defined as two pressure chambers by a partition wall which rotates along an arcuate inner peripheral surface of a casing constituting a pressure chamber filled with fluid. A sliding seal member for hydraulically sealing between the arc-shaped inner peripheral surface and the arc-shaped inner peripheral surface of the pressure chamber in the partition wall is provided on the sliding opposing surface. The sliding seal member is formed in a substantially rectangular cross section with a material that is not deformed by a fluid pressure generated in at least the two pressure chambers, and the sliding seal member is provided in a mounting groove formed in the partition wall. A gap that gradually increases from the bottom of the mounting groove toward the opening is formed between both inner surfaces of the groove and both outer surfaces of the sliding seal member, so that the relative rotation between the casing and the partition wall is increased. Friction due to motion And the differential pressure generated between the two pressure chambers due to the relative rotation always causes the sliding seal member to fall, and only one corner portion of the sliding seal member always hits the arc-shaped inner peripheral surface of the pressure chamber. Since the contact state is established, the surface pressure is increased, and an effect that a high hydraulic sealing property can be secured can be obtained.

【００５５】請求項５記載の摺動部シール構造では、請
求項４記載の摺動部シール構造において、前記圧力室の
円弧状内周面と対面する前記摺動シール部材の摺動シー
ル面にはその摺動方向幅の両端縁部に沿って前記円弧状
内周面方向へ突出する突条がそれぞれ設けられ、前記突
条の先端摺動面が、前記圧力室の円弧状内周面の円弧の
曲率半径より小さな曲率半径の円弧状に形成されている
構成としたことで、圧力室の円弧状内周面に対する接触
が点接触状態となり、これにより、面圧が高くなって液
圧シール性が向上すると共に、フリクション低減効果が
向上する。According to a fifth aspect of the present invention, in the sliding portion seal structure according to the fourth aspect, a sliding sealing surface of the sliding sealing member facing the arcuate inner peripheral surface of the pressure chamber is provided. Are provided along the both ends of the width in the sliding direction, projecting ridges projecting in the direction of the arc-shaped inner peripheral surface, and the tip sliding surface of the ridge is formed on the arc-shaped inner peripheral surface of the pressure chamber. The pressure chamber has a point of contact with the arc-shaped inner peripheral surface due to the arc-shaped configuration having a smaller radius of curvature than the radius of curvature of the arc. And the friction reduction effect is improved.

【００５６】請求項６記載の摺動部シール構造では、請
求項１〜５のいずれかに記載の摺動部シール構造におい
て、前記隔壁と摺動シール部材との間には、該摺動シー
ル部材を圧力室の円弧状内周面方向に押圧付勢する付勢
部材が設けられている構成としたことで、摺動シール部
材を弾性体とした時のようにシール自体が弾性変形しな
くても圧力室の円弧状内周面に対する押し付け力が作用
するため、特に低圧時における液圧シール性が向上する
と共に、高圧時において摺動シール部材の変形によるリ
ークが発生しなくなるため、低圧時から高圧にかけて良
好なシール性が確保できる。According to a sixth aspect of the present invention, in the sliding part seal structure according to any one of the first to fifth aspects, the sliding seal is provided between the partition and the sliding sealing member. With the configuration in which the urging member for urging the member in the direction of the arc-shaped inner peripheral surface of the pressure chamber is provided, the seal itself does not elastically deform as in the case where the sliding seal member is made of an elastic body. Even when the pressure is applied to the arc-shaped inner peripheral surface of the pressure chamber, the hydraulic sealing property is improved especially at low pressure, and the leakage due to the deformation of the sliding seal member does not occur at high pressure. To high pressure to ensure good sealing properties.

【図面の簡単な説明】[Brief description of the drawings]

【図１】本発明の実施の形態１のロータリダンパの構成
のうち、主に油圧回路構成を説明するための概略図であ
る。FIG. 1 is a schematic diagram for mainly explaining a hydraulic circuit configuration in a configuration of a rotary damper according to a first embodiment of the present invention.

【図２】本発明の実施の形態１のロータリダンパを示す
縦断面図（図３のＣ−Ｃ線における縦断面図）である。FIG. 2 is a longitudinal sectional view (a longitudinal sectional view taken along line CC in FIG. 3) showing the rotary damper according to the first embodiment of the present invention.

【図３】図２のＡ−Ａ’線における縦断面図である。FIG. 3 is a longitudinal sectional view taken along line A-A 'of FIG.

【図４】図２のＢ−Ｂ’線における横断面図である。FIG. 4 is a transverse sectional view taken along line B-B 'of FIG.

【図５】図２のＡ−Ｂ線における断面図である。FIG. 5 is a sectional view taken along line AB in FIG. 2;

【図６】本発明の実施の形態１のロータリダンパにおけ
る摺動シール部材を示す拡大断面図である。FIG. 6 is an enlarged sectional view showing a sliding seal member in the rotary damper according to the first embodiment of the present invention.

【図７】本発明の実施の形態１のロータリダンパにおけ
る摺動シール部材部分の詳細を示す要部拡大断面図であ
る。FIG. 7 is an enlarged sectional view of a main part showing details of a sliding seal member in the rotary damper according to the first embodiment of the present invention.

【図８】本発明の実施の形態１のロータリダンパにおけ
る摺動シール部材部分の詳細を示す要部拡大断面図であ
る。FIG. 8 is an enlarged sectional view of a main part showing details of a sliding seal member in the rotary damper according to the first embodiment of the present invention.

【図９】本発明の実施の形態１のロータリダンパにおけ
る摺動シール部材の共用状態を示す説明図である。FIG. 9 is an explanatory diagram showing a shared state of a sliding seal member in the rotary damper according to the first embodiment of the present invention.

【図１０】本発明の実施の形態２のロータリダンパにお
ける摺動シール部材を示す拡大断面図である。FIG. 10 is an enlarged sectional view showing a sliding seal member in a rotary damper according to a second embodiment of the present invention.

【図１１】本発明の３実施の形態２のロータリダンパに
おける摺動シール部材部分の詳細を示す要部拡大断面図
である。FIG. 11 is an enlarged sectional view of a main part showing details of a sliding seal member in a rotary damper according to a third embodiment of the present invention.

【図１２】本発明の実施の形態２のロータリダンパにお
ける摺動シール部材部分の詳細を示す要部拡大断面図で
ある。FIG. 12 is an enlarged sectional view of a main part showing details of a sliding seal member in a rotary damper according to a second embodiment of the present invention.

【図１３】本発明の実施の形態３のロータリダンパにお
ける摺動シール部材部分の詳細を示す要部拡大断面図で
ある。FIG. 13 is an enlarged sectional view of a main part showing details of a sliding seal member in a rotary damper according to a third embodiment of the present invention.

【図１４】本発明の実施の形態３のロータリダンパにお
ける摺動シール部材部分の詳細を示す要部拡大断面図で
ある。FIG. 14 is an enlarged sectional view of a main part showing details of a sliding seal member in a rotary damper according to a third embodiment of the present invention.

【図１５】本発明の実施の形態４のロータリダンパにお
ける摺動シール部材部分の詳細を示す要部拡大断面図で
ある。FIG. 15 is an enlarged sectional view of a main part showing details of a sliding seal member in a rotary damper according to a fourth embodiment of the present invention.

【図１６】本発明の実施の形態４のロータリダンパにお
ける摺動シール部材部分の詳細を示す要部拡大断面図で
ある。FIG. 16 is an enlarged sectional view of a main part showing details of a sliding seal member in a rotary damper according to a fourth embodiment of the present invention.

【図１７】本発明の実施の形態５のロータリダンパにお
ける摺動シール部材部分の詳細を示す要部拡大断面図で
ある。FIG. 17 is an enlarged sectional view of a main part showing details of a sliding seal member in a rotary damper according to a fifth embodiment of the present invention.

【符号の説明】[Explanation of symbols]

ＲＤ ロータリダンパ Ａ エア Ｂ 車体 Ｃ 第３の連通路 Ｄ 上部の連通路 Ｅ 第２の連通路 Ｆ バイパス流路 Ｇ エア抜き室 ｇ１ 下部流体溜め部 ｇ２ 上部空気溜め部 Ｈ 第２の連通路 Ｊ 伸側減衰力発生機構 Ｍ 圧側減衰力発生機構 Ｏ 粘性オイル（流体） Ｒ リザーバ室 Ｒａ 上部空気室 Ｒｂ 下部流体室 ＳＯ シリコーンオイル １ ケーシング １ａ 貫通穴 １ｂ 上部固定ベーン １ｃ 下部固定ベーン １ｄ 円形穴 １ｅ 円形穴 ２ａ 揺動ベーン ２ｂ 揺動ベーン ２ｃ 回動軸心部 ２ｄ 装着溝 ２ｅ 装着溝 ２ｆ 装着溝 ２ｇ 装着溝 ３ サイドカバー ３ａ 軸心穴 ３ｂ 軸心穴 ３ｃ 雌ねじ穴 ４ ブラケット ４ａ 取付フランジ部 ４ｂ ボルト挿通穴 ４ｃ ボルト挿通穴 ５ 車体取付用ブッシュ ６ ブッシュベアリング ７ 回転シール部材 ８ ダストシール部材 ９ ボルト・ナット １０ ボルト・ナット １１ 摺動シール部材 １１ａ 突条 １２ バックアップスプリング（付勢部材） １３ 摺動シール部材 １４ 板ばね １５ 第１の連通路 １５ａ 上部の第１圧力室 １５ｂ 下部の第１圧力室 １６ 第１の連通路 １６ａ 上部の第２圧力室 １６ｂ 下部の第２圧力室 １７ 案内用テーパ溝 １９ 上部貫通穴 １９ａ 環状段部 １９ｂ 環状段部 ２０ 下部貫通穴 ２１ 上部連通溝 ２２ 上部連通溝 ２３ 下部連通溝 ２４ 下部連通溝 ２５ コ字状穴 ２５ａ 上部空気室 ２５ｂ 下部流体室 ２６ａ 伸側ディスクバルブ ２６ｂ 伸側オリフィス ２７ａ 圧側ディスクバルブ ２７ｂ 圧側オリフィス ２８ 伸側チェックバルブ ２９ 圧側チェックバルブ RD Rotary damper A Air B Vehicle body C Third communication path D Upper communication path E Second communication path F Bypass flow path G Air release chamber g1 Lower fluid storage part g2 Upper air storage part H Second communication path J extension Side damping force generating mechanism M Compression side damping force generating mechanism O Viscous oil (fluid) R Reservoir chamber Ra Upper air chamber Rb Lower fluid chamber SO Silicone oil 1 Casing 1a Through hole 1b Upper fixed vane 1c Lower fixed vane 1d Circular hole 1e Circular hole 2a Swing vane 2b Swing vane 2c Rotating shaft center 2d Mounting groove 2e Mounting groove 2f Mounting groove 2g Mounting groove 3 Side cover 3a Shaft center hole 3b Shaft center hole 3c Female screw hole 4 Bracket 4a Mounting flange 4b Bolt insertion hole 4c Bolt insertion hole 5 Body mounting bush 6 Bush bearing 7 Rotary seal member 8 Dust seal member Reference Signs List 9 bolt / nut 10 bolt / nut 11 sliding seal member 11a ridge 12 backup spring (biasing member) 13 sliding seal member 14 leaf spring 15 first communication passage 15a upper first pressure chamber 15b lower first Pressure chamber 16 First communication path 16a Upper second pressure chamber 16b Upper second pressure chamber 17 Lower taper groove 19 Upper through hole 19a Annular step 19b Annular step 20 Lower through hole 21 Upper communication groove 22 Upper communication Groove 23 Lower communication groove 24 Lower communication groove 25 U-shaped hole 25a Upper air chamber 25b Lower fluid chamber 26a Expansion disk valve 26b Expansion orifice 27a Compression disk valve 27b Compression orifice 28 Expansion check valve 29 Compression check valve

Claims (6)

【特許請求の範囲】[Claims] 【請求項１】流体を充填する圧力室を構成するケーシン
グの円弧状内周面に沿って回動する隔壁により前記圧力
室が２つの圧力室に画成され、 前記隔壁における前記圧力室の円弧状内周面との摺動対
向面には該円弧状内周面との間を液圧シールする摺動シ
ール部材が設けられ、 該摺動シール部材が少なくとも前記２つの圧力室内で発
生する流体圧力では変形しない材料で形成されると共
に、前記圧力室の円弧状内周面と対面する前記摺動シー
ル部材の摺動シール面にはその摺動方向幅の両端縁部に
沿って前記円弧状内周面方向へ突出する突条がそれぞれ
設けられていることを特徴とする摺動部シール構造。The pressure chamber is defined as two pressure chambers by a partition wall that rotates along an arcuate inner peripheral surface of a casing that forms a pressure chamber filled with fluid, and the pressure chamber circle in the partition wall. A sliding seal member for hydraulically sealing the space between the arc-shaped inner peripheral surface and the arc-shaped inner peripheral surface is provided on a surface facing the arc-shaped inner peripheral surface, and the sliding seal member is a fluid generated in at least the two pressure chambers. The sliding seal surface of the sliding seal member, which is formed of a material that does not deform under pressure and faces the arc-shaped inner peripheral surface of the pressure chamber, extends along the both ends of the sliding direction width in the arc-shaped shape. A sliding portion sealing structure, wherein a ridge projecting toward the inner peripheral surface is provided. 【請求項２】前記突条の先端摺動面が、前記圧力室の円
弧状内周面の円弧と同一曲率に形成されていることを特
徴とする請求項１記載の摺動部シール構造。2. A sliding part seal structure according to claim 1, wherein a tip end sliding surface of said ridge is formed to have the same curvature as an arc of an arc-shaped inner peripheral surface of said pressure chamber. 【請求項３】前記突条の先端摺動面が、前記圧力室の円
弧状内周面の円弧の曲率半径より小さな曲率半径の円弧
状に形成されていることを特徴とする請求項１記載の摺
動部シール構造。3. The sliding surface at the distal end of the ridge has a radius of curvature smaller than the radius of curvature of the arc of the arc-shaped inner peripheral surface of the pressure chamber. Sliding part seal structure. 【請求項４】流体を充填する圧力室を構成するケーシン
グの円弧状内周面に沿って回動する隔壁により前記圧力
室が２つの圧力室に画成され、 前記隔壁における前記圧力室の円弧状内周面との摺動対
向面には該円弧状内周面との間を液圧シールする摺動シ
ール部材が設けられ、 該摺動シール部材が少なくとも前記２つの圧力室内で発
生する流体圧力では変形しない材料で断面略方形状に形
成され、 該摺動シール部材は前記隔壁に形成された装着溝内に収
容された状態で設けられ、該装着溝の両内側面と摺動シ
ール部材における両外側面と間に装着溝底部から開口部
方向へ向かうにつれて次第に広くなる隙間がそれぞれ形
成されていることを特徴とする摺動部シール構造。4. The pressure chamber is defined as two pressure chambers by a partition wall that rotates along an arcuate inner peripheral surface of a casing forming a pressure chamber filled with fluid, and the pressure chamber circle in the partition wall. A sliding seal member for hydraulically sealing the space between the arc-shaped inner peripheral surface and the arc-shaped inner peripheral surface is provided on a surface facing the arc-shaped inner peripheral surface, and the sliding seal member is a fluid generated in at least the two pressure chambers. The sliding seal member is formed in a substantially rectangular cross section from a material that does not deform under pressure. The sliding seal member is provided in a state housed in a mounting groove formed in the partition wall. Wherein a gap gradually increasing from the bottom of the mounting groove toward the opening is formed between both outer surfaces of the sliding portion. 【請求項５】前記圧力室の円弧状内周面と対面する前記
摺動シール部材の摺動シール面にはその摺動方向幅の両
端縁部に沿って前記円弧状内周面方向へ突出する突条が
それぞれ設けられ、 前記突条の先端摺動面が、前記圧力室の円弧状内周面の
円弧の曲率半径より小さな曲率半径の円弧状に形成され
ていることを特徴とする請求項４記載の摺動部シール構
造。5. A sliding seal surface of the sliding seal member facing the arcuate inner peripheral surface of the pressure chamber protrudes in the direction of the arcuate inner peripheral surface along both edges of the sliding direction width. Wherein each of the ridges has a radius of curvature smaller than the radius of curvature of the arc of the arc-shaped inner peripheral surface of the pressure chamber. Item 5. The sliding portion seal structure according to Item 4. 【請求項６】前記隔壁と摺動シール部材との間には、該
摺動シール部材を圧力室の円弧状内周面方向に押圧付勢
する付勢部材が設けられていることを特徴とする請求項
１〜５のいずれかに記載の摺動部シール構造。6. An urging member is provided between said partition and said sliding seal member for urging said sliding seal member in the direction of the arc-shaped inner peripheral surface of said pressure chamber. The sliding portion seal structure according to any one of claims 1 to 5.