JP5911730B2

JP5911730B2 - Vane Seal

Info

Publication number: JP5911730B2
Application number: JP2012014788A
Authority: JP
Inventors: 加納　康司; 康司加納; 泰司上杉; 智己西川
Original assignee: Mitsubishi Cable Industries Ltd
Current assignee: Mitsubishi Cable Industries Ltd
Priority date: 2012-01-27
Filing date: 2012-01-27
Publication date: 2016-04-27
Anticipated expiration: 2032-01-27
Also published as: JP2013155765A

Description

本発明は、ロータリアクチュエータ用のベーンシールに関する。 The present invention relates to a vane seal for a rotary actuator.

従来からロータリアクチュエータに於て、流体圧力を受けて所定角度を揺動するロータ
リのべーンには、門型のベーンシールが装着され、また、ケーシング側ソールには（固定
側の）ベーンシールが装着されている（例えば、特許文献１参照）。 Conventional rotary actuators have been equipped with a portal vane seal on the rotary vane that oscillates a predetermined angle in response to fluid pressure, and a (fixed) vane seal on the casing-side sole. (For example, refer to Patent Document 1).

実開平２−８１９０３号公報Japanese Utility Model Publication No. 2-81903

ところで、従来の上記べーンシールは、一般に材質はＰＴＦＥ等の樹脂をもって、横断
面矩形、かつ、全体門型に形成されていた。
そして、このような全体門型の形状のベーンシールでは、特に２個の角部が存在するた
めに、内部漏洩（内部リーク）を減少させることが極めて難しいと、従来から考えられて
いた。 By the way, the conventional vane seal is generally formed of a resin such as PTFE and has a rectangular cross section and an overall portal shape.
Further, it has been conventionally thought that it is extremely difficult to reduce internal leakage (internal leakage) in such a whole-portion-shaped vane seal because there are particularly two corner portions.

しかしながら、最近になってロータリアクチュエータの高圧化の要望が強まり、また、
内部漏洩が多いままでは、作動油の異常な昇温の問題、エネルギ損失の問題、作動の不正
確性や信頼性の問題が、最近クローズアップされつつある。 Recently, however, the demand for high pressure rotary actuators has increased,
As long as there are many internal leaks, the problem of abnormal temperature rise of hydraulic oil, the problem of energy loss, the problem of inaccuracy of operation, and the reliability are being highlighted recently.

そこで、本発明は、このような従来の問題点を解決して、ロータリアクチュエータの内
部漏洩を減少し、かつ、これに伴って、作動油の昇温を抑制し、エネルギ損失を低減し、
作動の正確性・信頼性を向上して、高圧化にも耐えるシール性を発揮するベーンシールを
提供することを目的とする。 Therefore, the present invention solves such conventional problems, reduces internal leakage of the rotary actuator, and accordingly, suppresses the temperature rise of the hydraulic oil, reduces energy loss,
The object is to provide a vane seal that improves the accuracy and reliability of operation and exhibits a sealing performance that can withstand high pressure.

そこで、本発明は、ロータリアクチュエータのベーンの門型凹溝に装着されるベーンシールに於て；上記凹溝の溝底は、直角状角部を両端に有する門型であり；さらに、全体が門型の弾性ゴムのシール本体と、ロータリアクチュエータのケーシングの内周面及び両内端面に摺接するように上記シール本体の反溝底側の外面に被覆される低摩擦性樹脂の全体が門型の被覆材と、から構成され；全体が門型の上記シール本体の溝底側の内面の両隅部の形状が、仮想直角隅部に肉盛りした形状であって、かつ、ケーシングの内部に組付けた状態で、上記直角状角部が上記シール本体の肉盛りを弾性圧縮変形させて、上記門型被覆材の直角状角部へ向かって弾発的付勢力を作用させ、上記直角状角部とその近傍の接触面圧が、上記直角状角部とその近傍を除いた部位の接触面圧よりも、高目になるように構成したものである。 Accordingly, the present invention provides a vane seal that is mounted in a gate-shaped concave groove of a vane of a rotary actuator; the groove bottom of the concave groove is a gate-type having right-angled corners at both ends; The elastic rubber seal body of the mold and the entire low friction resin coated on the outer surface of the seal groove on the side opposite the groove so as to be in sliding contact with the inner peripheral surface and both inner end surfaces of the casing of the rotary actuator The shape of both corners of the inner surface on the groove bottom side of the seal body, which is entirely gate-shaped, is a shape that is built up at a virtual right-angled corner, and is assembled inside the casing. In the attached state, the right-angled corner portion elastically compresses and deforms the build-up of the seal body, and exerts a resilient urging force toward the right-angled corner portion of the portal-type covering material. Contact surface pressure in the vicinity of the Than the contact surface pressure of the portion except for, which is constituted such that the relatively high value.

また、本発明は、ロータリアクチュエータのケーシング側のシューの門型凹溝に装着されるベーンシールに於て；上記凹溝の溝底は、直角状角部を両端に有する門型であり；さらに、全体が門型の弾性ゴムのシール本体と；ロータリ本体の回転主軸の外周面、及び、上記ケーシングの両内端面に接触するように、上記シール本体の反溝底側の外面に被覆される低摩擦性樹脂の被覆材と；から構成され；全体が門型の上記シール本体の溝底側の内面の両隅部の形状が、仮想直角隅部に肉盛りした形状であって、かつ、ロータリ本体をケーシングの内部に組付けた状態で、上記直角状角部が上記シール本体の肉盛りを弾性圧縮変形させて、上記門型被覆材の直角状角部へ向かって弾発的付勢力を作用させ、上記直角状角部とその近傍の接触面圧が、上記直角状角部とその近傍を除いた部位の接触面圧よりも、高目になるように構成したものである。 Further, the present invention provides a vane seal that is mounted in a portal-type concave groove of a shoe on the casing side of a rotary actuator; the groove bottom of the concave groove is a gate-type having right-angle corners at both ends; A seal body made of a portal elastic rubber as a whole; and the outer surface on the anti-groove bottom side of the seal body so as to be in contact with the outer peripheral surface of the rotary main shaft of the rotary body and both inner end surfaces of the casing. A friction material covering material, and the shape of both corners of the inner surface on the groove bottom side of the portal-shaped seal body as a whole is a shape that is built up at a virtual right-angled corner, and a rotary In a state where the main body is assembled inside the casing, the right-angled corner portion elastically compresses and deforms the build-up of the seal main body, and generates a resilient biasing force toward the right-angled corner portion of the portal-type covering material. The contact surface pressure in the vicinity of the right angle corner and its vicinity is Than the contact surface pressure of the portion excluding the vicinity of the aforementioned right-angled corners, which is constituted such that the relatively high value.

本発明によれば、弾性ゴムのシール本体から生ずる弾発付勢力を低摩擦性樹脂が受けつ
つ、ケーシング内周面や両内端面等の摺接相手面に対し、均等かつ十分な面圧にて接触し
、内部漏洩を低減できる。しかも、溝底面及び溝側面に対しては弾性ゴムのシール本体自
体が密に弾発的に圧接して、一層、内部漏洩を低減可能である。 According to the present invention, the low friction resin receives the elastic biasing force generated from the elastic rubber seal body, and the surface pressure is equal and sufficient against the sliding contact surface such as the inner peripheral surface of the casing or both inner end surfaces. To reduce internal leakage. In addition, the elastic rubber seal body itself is tightly and elastically pressed against the groove bottom surface and the groove side surface, thereby further reducing internal leakage.

さらに、門型のシール本体の両隅部に肉盛りすることによって、従来から至難と考えら
れていたところの、門型の角部と相手部材の直角隅部との相対的摺接部には、十分な接触
面圧が発生して、内部漏洩の著しい低減が達成可能となる。 Furthermore, by burying at both corners of the portal-type seal body, the relative sliding contact between the portal-shaped corner and the right-angled corner of the mating member has been considered difficult until now. Sufficient contact surface pressure is generated, and a significant reduction in internal leakage can be achieved.

本発明の実施の一形態を示す簡略断面図である。It is a simplified sectional view showing an embodiment of the present invention. ベーンシールの一例を示す正面図である。It is a front view which shows an example of a vane seal. 図２の（III−III）拡大断面図である。It is (III-III) expanded sectional drawing of FIG. 斜視図である。It is a perspective view. 一部破断にて示した分解状態の要部説明図である。It is principal part explanatory drawing of the decomposition | disassembly state shown by the partial fracture | rupture. 本発明の作用を説明するための要部拡大断面説明図である。It is principal part expanded sectional explanatory drawing for demonstrating the effect | action of this invention. 他の実施の形態を示す要部説明図である。It is principal part explanatory drawing which shows other embodiment. 図７の要部拡大斜視説明図である。It is principal part expansion perspective explanatory drawing of FIG. 本発明の作用を説明するための要部拡大断面説明図である。It is principal part expanded sectional explanatory drawing for demonstrating the effect | action of this invention.

以下、図示の実施の形態に基づき本発明を詳説する。
図１の簡略図に示すように、ロータリアクチュエータＲは、ケーシング１とロータリ本
体２とを備え、ケーシング１は、円筒壁部１Ａと（両端を閉塞する）左右の側壁部１Ｂ，
１Ｂとを有し、さらに、円筒壁部１Ａの内周面１０には、１８０°対称位置に門型凹溝３
を有するシュー４，４がラジアル内方向へ突設され、かつ、ロータリ本体２は、１８０°
対称位置にベーン６，６が突設された回転主軸７を備え、このベーン６には門型凹溝８が
形成されている。 Hereinafter, the present invention will be described in detail based on the illustrated embodiment.
As shown in the simplified diagram of FIG. 1, the rotary actuator R includes a casing 1 and a rotary body 2, and the casing 1 includes a cylindrical wall portion 1 </ b> A and left and right side wall portions 1 </ b> B (closing both ends).
1B, and the inner circumferential surface 10 of the cylindrical wall portion 1A has a portal groove 3 at a 180 ° symmetrical position.
Shoes 4 and 4 projecting radially inward, and the rotary body 2 is 180 °
A rotation main shaft 7 is provided with vanes 6 and 6 projecting at symmetrical positions, and a portal groove 8 is formed in the vane 6.

可動側の全体門型のべーンシール９は、回転主軸７のべーン６の門型凹溝８に装着され
ている。固定側の全体門型のべーンシール５は、ケーシング１側のシュー４の門型凹溝３
に装着されている。 The movable-side whole portal vane seal 9 is mounted in the portal groove 8 of the vane 6 of the rotary spindle 7. The fixed portal vane seal 5 is formed by a portal groove 3 of the shoe 4 on the casing 1 side.
It is attached to.

図２〜図６に示した実施の一形態に於て、可動側ベーンシール９は、全体が門型で、か
つ、横断面形状が矩形の弾性ゴムから成るシール本体１１と、ケーシング１の内周面１０
と（側壁部１Ｂの）両内端面１２，１２に摺接するように上記シール本体１１の反溝底側
の外面１３に被覆される（門型の）低摩擦性樹脂の被覆材１４と、から構成される。 In the embodiment shown in FIGS. 2 to 6, the movable-side vane seal 9 includes a seal body 11 made of elastic rubber having a portal shape and a rectangular cross section, and an inner periphery of the casing 1. Surface 10
And (a portal-type) low-friction resin coating 14 that is coated on the outer surface 13 on the side opposite to the groove of the seal body 11 so as to be in sliding contact with both inner end surfaces 12 and 12 (of the side wall 1B). Composed.

上記シール本体１１は、ＥＰＤＭやその他のゴム材質のものが用いられ、他方、被覆材
１４は、ＰＴＦＥ等の合成樹脂であって、上述した低摩擦性を備え、さらに、（好ましく
は）耐摩耗性を備えた材質のものとする。また、この被覆材１４の横断面形状は、一文字
型とすると共に、横断面矩形のシール本体１１の外面１３に、接着し、又は、単に重ね合
わせている。 The seal body 11 is made of EPDM or other rubber material, while the covering material 14 is a synthetic resin such as PTFE and has the above-mentioned low friction property, and (preferably) wear resistance. It shall be of a material with properties. Further, the cross-sectional shape of the covering material 14 is a single character type, and is adhered or simply overlapped to the outer surface 13 of the seal body 11 having a rectangular cross-section.

そして、全体が門型とされているシール本体１１が、図５の矢印Ｃの方向からベーン６
の門型凹溝８に装着されるのであるが、この凹溝８の溝底８Ａに対応するシール本体内面
１６の両隅部Ｇ，Ｇの形状が、（仮想直角隅部Ｈを基本形状と想定した場合、）仮想直角
隅部Ｈに直角三角形の肉盛り２０を行った形状とする。つまり、小さな勾配面を形成する
。 Then, the seal main body 11 having a gate shape as a whole is formed from the vane 6 in the direction of the arrow C in FIG.
The shape of both corners G, G of the seal body inner surface 16 corresponding to the groove bottom 8A of the groove 8 is (the virtual right-angled corner H is a basic shape). Assuming that :) a virtual right corner portion H is formed with a right triangle build-up 20. That is, a small gradient surface is formed.

図５の矢印Ｃ方向から（上述の）ベーンシール９を凹溝８に装着して、ロータリ本体２
をケーシング１の内部に組付けた状態の要部を、図６に示す。この図６から明らかとなる
ように、ベーン６の凹溝８の溝底（面）８Ａは、直角状角部１５を有し、この角部１５が
ベーンシール９の肉盛り２０を弾性圧縮させて、直角隅部の形状まで変形させる。 The vane seal 9 (described above) is attached to the concave groove 8 from the direction of arrow C in FIG.
The principal part of the state which assembled | attached inside the casing 1 is shown in FIG. As apparent from FIG. 6, the groove bottom (surface) 8 </ b> A of the concave groove 8 of the vane 6 has a right-angled corner 15, and the corner 15 elastically compresses the build-up 20 of the vane seal 9. Deform to right corner shape.

このように、角張った角部１５によって、ベーンシール９の肉盛り２０が弾性圧縮変形
し、図６に於てベクトルＦにて示す如く、門型べーンシール９の被覆材１４の直角状角部
１７へ向かって弾発的付勢力が作用し、これによって、ベーンシール９の被覆材１４と、
ケーシング１の円筒壁部１Ａ・側壁部１Ｂの内面との接触面圧力Ｐは、（図６のように）
直角状角部１７及びその近傍域で、十分に大となる。即ち、角部１７，１７とその近傍を
除いた部位の接触面圧よりも、角部１７とその近傍の接触面圧が高目になることにより、
従来、内部漏洩を発生して、シール性の確保が困難と考えられてきた、角部１７とその近
傍から、内部漏洩を著しく減少できる。なお、図６に於て、ケーシング１については、断
面を示す斜線を省略して図示した。 In this way, the build-up 20 of the vane seal 9 is elastically compressed and deformed by the angular corners 15, and as shown by the vector F in FIG. 6, the right-angled corners 17 of the covering 14 of the portal vane seal 9. A resilient biasing force acts toward the cover 14, whereby the covering 14 of the vane seal 9,
The contact surface pressure P with the inner surface of the cylindrical wall portion 1A / side wall portion 1B of the casing 1 is as shown in FIG.
It becomes sufficiently large in the right-angled corner portion 17 and its vicinity. That is, the contact surface pressure at the corner 17 and the vicinity thereof is higher than the contact surface pressure at the portion excluding the corners 17 and 17 and the vicinity thereof.
Conventionally, internal leakage can be remarkably reduced from the corner portion 17 and its vicinity, where internal leakage has occurred and it has been considered difficult to ensure sealing performance. In FIG. 6, the casing 1 is illustrated with the oblique lines indicating the cross section omitted.

なお、図６に於て、直角状角部１５に微小なアール面取りや勾配面取りを設けても良い
（図示省略）。 In FIG. 6, the right-angle corner 15 may be provided with a minute round chamfer or a gradient chamfer (not shown).

次に、図１に示したシュー４に用いられるベーンシール５に関しても、図２，図３，図
４，図６によって説明可能であり、図５におけるロータリ本体２の代りに、門型凹溝３を
有するシュー４を置き換えれば良い（図示省略）。即ち、図２，図３，図４，図６に於て
、ロータリアクチュエータＲのケーシング１の内周面１０からラジアル内方向へ突設され
たシュー４の門型凹溝３に装着されるベーンシール５は、全体が門型の弾性ゴムのシール
本体１１と、ロータリ本体２の回転主軸７の外周面７Ａ、及び、ケーシング内端面１２に
接触（圧接）するように、シール本体１１の反溝底側の外面１３に被覆される（接着又は
重ね合わさった）低摩擦性樹脂の被覆材１４と、から構成される。
シール本体１１と被覆材１４の材質及び形状は、既述の可動側のべーン６用のベーンシ
ール９と同様の構成とする。 Next, the vane seal 5 used in the shoe 4 shown in FIG. 1 can also be explained with reference to FIGS. 2, 3, 4, and 6. In place of the rotary body 2 in FIG. It is sufficient to replace the shoe 4 having (not shown). That is, in FIG. 2, FIG. 3, FIG. 4, and FIG. 6, the vane seal mounted in the portal groove 3 of the shoe 4 projecting radially inward from the inner peripheral surface 10 of the casing 1 of the rotary actuator R. 5 is an anti-groove bottom of the seal body 11 so as to come into contact (pressure contact) with the seal body 11 made of a portal elastic rubber as a whole, the outer peripheral surface 7A of the rotary main shaft 7 of the rotary body 2 and the inner end face 12 of the casing. And a low-friction resin coating 14 that is coated (adhered or superposed) on the outer surface 13 on the side.
The material and shape of the seal body 11 and the covering material 14 are the same as those of the vane seal 9 for the movable vane 6 described above.

そして、図２，図３，図４に示したように、可動側ベーンシール９と同じ構成のベーン
シール５を、シュー４の門型凹溝３に装着すると、この凹溝３の溝底３Ａに対応するシー
ル本体内面１６の両隅部Ｇ，Ｇの形状が、仮想直角隅部Ｈに直角三角形の肉盛り２０を行
っている。ロータリ本体２をケーシング１の内部へ組付けると、図６に示すように、肉盛
り２０が弾性圧縮変形して、ベクトルＦのような弾発的付勢力がゴム内部に発生して、ベ
ーンシール５の被覆材１４は、ケーシング１の側壁部１Ｂの内端面１２、及び、回転主軸
７の外周面７Ａに対して、直角状角部１７及びその近傍域では、それを除いた部位に比較
して、図６のように大きな接触面圧をもって、接触する。これによって、門型ベーンシール５のシール性能は十分に改善され、特に、角部１７とその近傍の内部漏洩は、著しく低減できる。 As shown in FIGS. 2, 3, and 4, when the vane seal 5 having the same configuration as the movable vane seal 9 is attached to the portal groove 3 of the shoe 4, it corresponds to the groove bottom 3 </ b> A of the groove 3. The shape of both corners G, G of the seal body inner surface 16 to be formed is a right-angled triangular overlay 20 at the virtual right-angled corner H. When the rotary main body 2 is assembled into the casing 1, as shown in FIG. 6, the build-up 20 is elastically compressed and deformed, and a resilient urging force such as the vector F is generated inside the rubber, so that the vane seal 5 The covering material 14 is compared with the portion except the right-angled corner portion 17 and the vicinity thereof with respect to the inner end surface 12 of the side wall portion 1B of the casing 1 and the outer peripheral surface 7A of the rotating main shaft 7. , with a large contact surface pressure as in FIG. 6, to come in contact. Thereby, the sealing performance of the portal vane seal 5 is sufficiently improved, and in particular, the internal leakage in the corner portion 17 and the vicinity thereof can be remarkably reduced.

次に、図７〜図９に示した別の実施の形態では、ロータリ本体２のべーン６の個数を、
中心角度（１２０°）として、３個とした場合を例示し、かつ、各ベーン６に２個の門型
凹溝８，８を形成し、２本のベーンシール９，９を各ベーン６に装着している（図７参照
）。
なお、図７では、上方の１個のべーン６にのみベーンシール９，９を装着した状態を示
し、残りの２個のべーン６ではベーンシール９を図示省略している。そして、図９に示す
ように、既述の図２〜図６と同様に、肉盛り２０を仮想直角隅部Ｈに（付加）形成した構
成であるが、さらに、加圧油導入孔２２を、各ベーン６の軸心方向両端部に貫設している
。 Next, in another embodiment shown in FIGS. 7 to 9, the number of vanes 6 of the rotary body 2 is set as follows.
The center angle (120 °) is exemplified as three, and two vane grooves 8 and 8 are formed in each vane 6, and two vane seals 9 and 9 are attached to each vane 6. (See FIG. 7).
FIG. 7 shows a state in which the vane seals 9 and 9 are attached only to the upper one vane 6, and the vane seals 9 are omitted from the remaining two vanes 6. And as shown in FIG. 9, it is the structure which formed the build-up 20 in the virtual right-angled corner part H like the above-mentioned FIGS. 2-6, Furthermore, pressurization oil introduction hole 22 is further provided. The vanes 6 are provided at both ends in the axial direction.

図９に於て、溝底３Ａ，８Ａの形状は、角部１５Ａが小面取り１５Ｃを有し、この小面
取り１５Ｃの傾斜方向寸法は、好ましくは、図２〜図４に示した自由状態下の肉盛り２０
の傾斜方向寸法Ｋよりも僅かに小さく設定する。図６で述べたゴム圧縮に伴う弾発力（ベ
クトル）Ｆよりも小さ目の弾発力を発生させると共に、小面取り１５Ｃに開口した上記導
入孔２２から流入する（圧力室側の）作動油圧力Ｐ_０をプラスさせて、十分に大きいベク
トルＦ（図６参照）を作用させ、図６で述べたように、ベーンシール９の被覆材１４は、
ケーシング１の内端面１２と内周面１０に、適切な大きい接触面圧力Ｐをもって、接触し
て、シール性能を発揮する。なお、図９に於て、ケーシング１については、断面を示す斜
線を省略して図示した。また、（図示省略するが）シュー側の固定側ベーンシール５につ
いては、２本凹溝８，８を有する図９と同様の構成とし、あるいは、図２〜図６にて述べ
たような１本凹溝８の構成とする。 9, the shape of the groove bottoms 3A and 8A is such that the corner portion 15A has a small chamfer 15C, and the inclination direction dimension of the small chamfer 15C is preferably in the free state shown in FIGS. 20 fillet of meat
Is set to be slightly smaller than the inclination direction dimension K. A hydraulic force smaller than the elastic force (vector) F accompanying the rubber compression described in FIG. 6 is generated, and the hydraulic oil pressure (on the pressure chamber side) flows from the introduction hole 22 opened to the small chamfer 15C. By adding P ₀ and applying a sufficiently large vector F (see FIG. 6), as described in FIG. 6, the covering 14 of the vane seal 9 is
The inner end surface 12 and the inner peripheral surface 10 of the casing 1 are brought into contact with an appropriate large contact surface pressure P to exhibit sealing performance. In FIG. 9, the casing 1 is illustrated by omitting oblique lines indicating a cross section. Further, the stationary vane seal 5 on the shoe side (not shown) has the same configuration as that of FIG. 9 having two concave grooves 8, 8, or one as described in FIGS. The configuration of the concave groove 8 is adopted.

なお、図７と図８から判るように、導入孔２２は、２個の隣設するベーンシール９，９
が近い側の油収容室へ開口しており、近い側の油収容室が高圧となった状態下で、対応す
るベーンシール９が図９にて述べたように圧力Ｐ_０を受けて十分な密封作用をなすと共に
、他のべーンシール９は小さな接触面圧のままであり、このようにして交互に揺動方向が
切換わる往復動ロータリアクチュエータＲに於て、隣設する２個のべーンシール９，９は
交互に密封作用をなすものである。 As can be seen from FIGS. 7 and 8, the introduction hole 22 has two adjacent vane seals 9, 9.
Is open to the oil storage chamber on the near side, and the corresponding vane seal 9 receives the pressure P ₀ as shown in FIG. In addition, the other vane seals 9 remain at a small contact surface pressure. Thus, in the reciprocating rotary actuator R in which the swing directions are alternately switched in this way, the two adjacent vane seals 9 are provided. , 9 alternately perform a sealing action.

本発明は上述の実施の形態以外にも設計変更自由であって、例えば、ベーン６の数を単
数としたり、４個以上とすることも自由である。 In addition to the above-described embodiment, the present invention is free to change the design. For example, the number of vanes 6 may be singular or may be four or more.

本発明は、上述したように、全体が門型の弾性ゴムのシール本体１１と、ロータリアク
チュエータＲのケーシング１の内周面１０及び両内端面１２，１２に摺接するようにシー
ル本体１１の反溝底側の外面１３に被覆される低摩擦性樹脂の被覆材１４と、から構成さ
れているので、門型の角部に於ける面圧が安定し、ロータリアクチュエータの内部漏洩が
極めて少なくなって、著しくシール性能が向上できる。また、被覆材１４によって、内方
のゴム（シール本体１１）のはみ出しが防止され、耐久性も優れている。さらに、門型凹
溝８の溝底８Ａ及び溝側面に対しては、（従来の樹脂のみから成るベーンシールに比べて
）弾性ゴムのシール本体１１によって、密封性能が改善され、一層優れたシール性が発揮
される。特に、全体が門型の上記シール本体１１の溝底側の内面１６の両隅部Ｇ，Ｇの形状が、仮想直角隅部Ｈに肉盛り２０した形状であって、かつ、ケーシング１の内部に組付けた状態で、上記直角状角部１５が上記シール本体１１の肉盛り２０を弾性圧縮変形させて、上記門型被覆材１４の直角状角部１７へ向かって弾発的付勢力を作用させ、上記直角状角部１７とその近傍の接触面圧が、上記直角状角部１７とその近傍を除いた部位の接触面圧よりも、高目になるように構成した（図６参照）ので、角部１７とその近傍からの内部漏洩を著しく減少でき、従来は少々の内部リークはやむを得ないと考えられていたところのロータリアクチュエータ用ベーンシールのシール性能が飛躍的に向上できる。 In the present invention, as described above, the seal body 11 made of a portal elastic rubber as a whole, and the inner surface 10 of the casing 1 of the rotary actuator R and the inner ends 12 and 12 of the rotary actuator R are slidably contacted. Since the outer surface 13 on the groove bottom side is covered with the low friction resin coating material 14, the surface pressure at the corner of the gate is stabilized, and the internal leakage of the rotary actuator is extremely reduced. Thus, the sealing performance can be remarkably improved. Further, the covering material 14 prevents the inner rubber (seal main body 11) from protruding and has excellent durability. Furthermore, the sealing performance is improved with respect to the groove bottom 8A and the groove side surface of the gate-shaped recessed groove 8 by an elastic rubber seal body 11 (compared to a conventional vane seal made of only resin), and further excellent sealing performance. Is demonstrated. In particular, the shape of both corners G, G of the inner surface 16 on the groove bottom side of the seal body 11 having a portal shape as a whole is a shape in which the imaginary right-angled corner H is overlaid, and the inside of the casing 1 In the assembled state, the right-angled corner portion 15 elastically compresses and deforms the build-up 20 of the seal body 11 to generate a resilient urging force toward the right-angled corner portion 17 of the portal type covering material 14. The contact surface pressure in the vicinity of the right-angled corner 17 and the vicinity thereof is configured to be higher than the contact surface pressure in the portion excluding the right-angled corner 17 and the vicinity thereof (see FIG. 6). Therefore, the internal leakage from the corner portion 17 and the vicinity thereof can be remarkably reduced, and the sealing performance of the vane seal for a rotary actuator, which has been conventionally considered to be unavoidable, can be greatly improved.

また、ロータリアクチュエータＲのケーシング１側のシュー４の門型凹溝３に装着され
るベーンシールに於て；全体が門型の弾性ゴムのシール本体１１と；ロータリ本体２の回
転主軸７の外周面７Ａ、及び、ケーシング１の両内端面１２，１２に接触するように、シ
ール本体１１の反溝底側の外面１３に被覆される低摩擦性樹脂の被覆材１４と；から構成
されたことによって、門型の角部に於ける面圧が安定し、ロータリアクチュエータの内部
漏洩が極めて少なくなって、著しくシール性能が向上できる。また、被覆材１４によって
、内方のゴム（シール本体１１）のはみ出しが防止され、耐久性も優れている。さらに、
門型凹溝３の溝底３Ａ及び溝側面に対しては、（従来の樹脂のみから成るベーンシールに
比べて）弾性ゴムのシール本体１１によって、密封性能が改善され、一層優れたシール性
が発揮される。特に、全体が門型の上記シール本体１１の溝底側の内面１６の両隅部Ｇ，Ｇの形状が、仮想直角隅部Ｈに肉盛り２０した形状であって、かつ、ロータリ本体２をケーシング１の内部に組付けた状態で、上記直角状角部１５が上記シール本体１１の肉盛り２０を弾性圧縮変形させて、上記門型被覆材１４の直角状角部１７へ向かって弾発的付勢力を作用させ、上記直角状角部１７とその近傍の接触面圧が、上記直角状角部１７とその近傍を除いた部位の接触面圧よりも、高目になるように構成した（図６参照）ので、直角状角部１７とその近傍からの内部漏洩を著しく減少でき、従来は少々の内部リークはやむを得ないと考えられていたところのロータリアクチュエータ用ベーンシールのシール性能が飛躍的に向上する。 Further, in the vane seal mounted in the portal concave groove 3 of the shoe 4 on the casing 1 side of the rotary actuator R; the entire seal body 11 made of a portal elastic rubber; and the outer peripheral surface of the rotary main shaft 7 of the rotary body 2 7A, and a low-friction resin coating material 14 coated on the outer surface 13 on the side opposite to the groove of the seal body 11 so as to be in contact with both inner end surfaces 12, 12 of the casing 1. The surface pressure at the gate-shaped corner is stabilized, the internal leakage of the rotary actuator is extremely reduced, and the sealing performance can be remarkably improved. Further, the covering material 14 prevents the inner rubber (seal main body 11) from protruding and has excellent durability. further,
For the groove bottom 3A and the groove side surface of the gate-shaped recessed groove 3, the sealing performance is improved by the elastic rubber seal body 11 (compared to the conventional vane seal made only of resin), and more excellent sealing performance is exhibited. Is done. In particular, the shape of both corners G and G of the inner surface 16 on the groove bottom side of the seal body 11 having a gate shape as a whole is a shape in which an imaginary right-angled corner H is overlaid, and the rotary body 2 is In the state assembled in the casing 1, the right-angled corner 15 elastically compresses and deforms the build-up 20 of the seal body 11, and elastically moves toward the right-angled corner 17 of the portal cover 14. The contact surface pressure in the vicinity of the right-angled corner 17 and the vicinity thereof is configured to be higher than the contact surface pressure in the portion excluding the right-angled corner 17 and the vicinity thereof. (Refer to FIG. 6) Therefore, the internal leakage from the right-angled corner 17 and the vicinity thereof can be remarkably reduced, and the sealing performance of the vane seal for the rotary actuator, which has been considered to be unavoidable in the past, is drastically improved. To improve.

１ケーシング
２ロータリ本体
３門型凹溝
３Ａ溝底
４シュー
５ベーンシール
６ベーン
７回転主軸
７Ａ外周面
８門型凹溝
８Ａ溝底
９ベーンシール
１０内周面
１１シール本体
１２内端面
１３外面
１４被覆材
１５直角状角部
１６内面
１７直角状角部
２０肉盛り
Ｇ両隅部
Ｒロータリアクチュエータ
Ｈ仮想直角隅部 DESCRIPTION OF SYMBOLS 1 Casing 2 Rotary main body 3 Portal groove 3A Groove bottom 4 Shoe 5 Vane seal
6 Vane 7 Rotating spindle 7A Outer peripheral surface 8 Portal groove
8A Groove bottom 9 Vane seal 10 Inner peripheral surface 11 Seal body 12 Inner end surface 13 Outer surface 14 Coating material
15 Right angle corner 16 Inner surface
17 Right angle corner 20 Overlay G Both corners R Rotary actuator H Virtual right angle corner

Claims

In the vane seal mounted in the portal groove (8) of the vane (6) of the rotary actuator (R),
The groove bottom (8A) of the concave groove (8) is a gate type having right-angled corners (15) (15) at both ends,
Further, the sealing body (11) of the portal elastic rubber as a whole and the inner peripheral surface (10) and the inner end surfaces (12) (12) of the casing (1) of the rotary actuator (R) are slidably contacted with each other. The entire low-friction resin coated on the outer surface (13) on the anti-groove bottom side of the seal body (11) is composed of a gate-shaped coating material (14) ,
The shape of both corners (G) and (G) of the inner surface (16) on the groove bottom side of the seal body (11) that is entirely gate-shaped is a shape in which the virtual right-angled corner (H) is overlaid (20). In addition, in the state assembled in the casing (1), the right-angled corner (15) elastically compresses and deforms the build-up (20) of the seal body (11), and the portal cover A resilient urging force is applied to the right-angled corner (17) of the material (14), and the contact surface pressure in the vicinity of the right-angled corner (17) and the vicinity thereof is the same as that of the right-angled corner (17). A vane seal for a rotary actuator, characterized in that it is configured to be higher than the contact surface pressure of a portion excluding its vicinity .

Portal groove (3) of shoe (4) on casing (1) side of rotary actuator (R)
In the vane seal attached to
The groove bottom (3A) of the concave groove (3) is a gate type having right-angled corners (15) (15) at both ends,
Furthermore, the seal body (11) of the entire gate-shaped elastic rubber,
The outer peripheral surface (7A) of the rotary main shaft (7) of the rotary body (2), and the casing (1)
A coating material (14) of a low friction resin coated on the outer surface (13) of the bottom side of the groove of the seal body (11) so as to be in contact with both inner end surfaces (12) and (12).
Consisting of
The shape of both corners (G) and (G) of the inner surface (16) on the groove bottom side of the seal body (11) that is entirely gate-shaped is a shape in which the virtual right-angled corner (H) is overlaid (20). In addition, with the rotary main body (2) assembled in the casing (1), the right-angled corner (15) elastically compresses and deforms the build-up (20) of the seal main body (11). Then, a resilient urging force is applied to the right-angled corner (17) of the portal type covering material (14), and the contact surface pressure in the vicinity of the right-angled corner (17) and the vicinity thereof is the right-angled shape. corners (17) and than the contact surface pressure of the portion excluding the vicinity Benshi Le rotary actuator characterized by being configured such that the relatively high value.