JP2010084819A

JP2010084819A - Sealing device

Info

Publication number: JP2010084819A
Application number: JP2008252703A
Authority: JP
Inventors: 渉 ▲徳▼永; Wataru Tokunaga; Nozomi Suzuki; 望鈴木
Original assignee: Nok Corp
Current assignee: Nok Corp
Priority date: 2008-09-30
Filing date: 2008-09-30
Publication date: 2010-04-15

Abstract

<P>PROBLEM TO BE SOLVED: To reduce torque based on fluid lubrication by increasing the thickness of a fluid film in a lip sliding part, in a sealing device (bidirectional seal) in which a sliding mate member such as a rotary shaft is rotated in a normal direction and a reverse direction. <P>SOLUTION: A normal screw part 10 and a reverse screw part 11 for pumping are provided in an inclined surface of a seal lip 6 on a side opposite to a sealed fluid side. A recessed part 12 is provided in an intermediate surface 9 of the seal lip 6, and a contact part 15 continued on the circumference is provided in a part of the recessed part 12 of the intermediate surface 9 on a side opposite to the sealed fluid side. When a mate member among the edges of the recessed part 12 is normally rotated, at least one part of a part positioning in front in the rotating direction is set in a direction inclined forward in the rotating direction at this point from a sealed fluid side to the side opposite to the sealed fluid. When the mate member among the edges of the recessed part 12 is rotated reversely, at least one part of the part positioning in front in the rotating direction is set in a direction inclined forward in the rotating direction at this point from the sealed fluid side to the side opposite to the sealed fluid side. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、密封装置に係り、更に詳しくは、シールリップを有する密封装置に関するものである。本発明の密封装置は例えば、自動車関連の分野において用いられ、あるいは汎用機械等の分野において用いられる。 The present invention relates to a sealing device, and more particularly to a sealing device having a sealing lip. The sealing device of the present invention is used, for example, in the field of automobiles or in the field of general-purpose machines.

シールリップを有する密封装置においては一般に、シールリップの摺動摩耗を抑制すべく低トルク化が求められている。低トルク化の手法としては、シールリップの小断面化などによる緊迫力の低減、材料の変更や表面の改質（例えばフッ素樹脂コーティング）などの低摩擦係数化が検討されているが、更なる低トルク化を実現するため、摺動部における流体膜（油膜）を厚くすることで流体潤滑にもとづく低トルク化を実現することが考えられる。 Generally, a sealing device having a seal lip is required to have a low torque so as to suppress sliding wear of the seal lip. As methods for reducing torque, reduction of the frictional force, such as reducing the tension by reducing the cross-section of the seal lip, changing the material, and modifying the surface (for example, fluororesin coating) has been studied. In order to realize a reduction in torque, it is conceivable to realize a reduction in torque based on fluid lubrication by increasing the thickness of the fluid film (oil film) in the sliding portion.

また、シールリップを有する密封装置としては従来から、回転軸等の摺動相手部材が一方向のみに回転するもの（一方向回転シール）と、正逆両方向に回転するもの（両方向回転シール）とが知られており、前者の一方向回転シールのみならず後者の両方向回転シールにおいても上記流体潤滑にもとづく低トルク化が求められている。 Moreover, as a sealing device having a seal lip, conventionally, a sliding partner such as a rotating shaft rotates in only one direction (one-way rotating seal), and a device that rotates in both forward and reverse directions (two-way rotating seal) Therefore, not only the former one-way rotating seal but also the latter two-way rotating seal is required to reduce the torque based on the fluid lubrication.

両方向回転シールの従来技術としては図１０に示すように、密封性能を向上させるべくシールリップ５１の反密封流体側斜面５２に、相手部材５３が正方向に回転するときにポンピング作用によって密封流体を押し戻す作用を奏する正ネジ部５４と、相手部材５３が逆方向に回転するときにポンピング作用によって密封流体を押し戻す作用を奏する逆ネジ部５５とを設けたものが知られているが、この従来技術においても上記流体潤滑にもとづく低トルク化は実現されていない（特許文献１参照）。
特開平１−３１２２７４号公報特開２００３−１８５０２８号公報特開２００６−１２５４５４号公報 As shown in FIG. 10, as a prior art of the bi-directional rotating seal, the sealing fluid is pumped to the anti-sealing fluid side inclined surface 52 of the seal lip 51 so as to improve the sealing performance by the pumping action when the mating member 53 rotates in the forward direction. There is known one provided with a normal screw portion 54 that exerts an action of pushing back and a reverse screw portion 55 that exerts an action of pushing back the sealing fluid by a pumping action when the counterpart member 53 rotates in the reverse direction. However, torque reduction based on the fluid lubrication is not realized (see Patent Document 1).
Japanese Unexamined Patent Publication No. 1-312274 JP 2003-185028 A JP 2006-125454 A

本発明は以上の点に鑑みて、回転軸等の摺動相手部材が正逆両方向に回転する密封装置（両方向シール）において、上記したようにリップ摺動部における流体膜を厚くすることで流体潤滑にもとづく低トルク化を実現することを目的とする。 In view of the above, the present invention provides a sealing device (bidirectional seal) in which a sliding counterpart member such as a rotating shaft rotates in both forward and reverse directions by increasing the thickness of the fluid film in the lip sliding portion as described above. The purpose is to achieve low torque based on lubrication.

上記目的を達成するため、本発明の請求項１による密封装置は、回転軸等の相手部材が正逆両方向に相対回転する密封装置であって、前記相手部材の周面に摺動自在に密接するシールリップを有し、前記シールリップは、密封流体側斜面および反密封流体側斜面ならびに前記両斜面の間に設けられた中間面を有し、前記相手部材が正方向に回転するときにポンピング作用によって密封流体を押し戻す作用を奏する正ネジ部と、前記相手部材が逆方向に回転するときにポンピング作用によって密封流体を押し戻す作用を奏する逆ネジ部とが前記反密封流体側斜面に設けられ、前記中間面に凹部が設けられ、前記凹部は前記中間面および反密封流体側斜面の境界部に達しないように設けられて前記中間面における前記凹部の反密封流体側の部位に円周上連続する前記相手部材に対する接触部が設けられ、前記凹部の縁辺のうち前記相手部材が正方向に回転するときに回転方向の前方となる部位は少なくともその一部が密封流体側から反密封流体側へかけてこのときの回転方向の前方へ傾斜する向きに設定され、前記凹部の縁辺のうち前記相手部材が逆方向に回転するときに回転方向の前方となる部位は少なくともその一部が密封流体側から反密封流体側へかけてこのときの回転方向の前方へ傾斜する向きに設定されていることを特徴とするものである。 In order to achieve the above object, a sealing device according to claim 1 of the present invention is a sealing device in which a mating member such as a rotating shaft rotates relative to both forward and reverse directions, and is slidably in close contact with the peripheral surface of the mating member. The sealing lip has a sealing fluid side slope and an anti-sealing fluid side slope and an intermediate surface provided between the both slopes, and is pumped when the mating member rotates in the forward direction. A positive screw portion that exerts an action of pushing back the sealing fluid by an action, and a reverse screw portion that exerts an action of pushing back the sealing fluid by a pumping action when the counterpart member rotates in the reverse direction, are provided on the anti-sealing fluid side inclined surface, A concave portion is provided on the intermediate surface, and the concave portion is provided so as not to reach a boundary portion between the intermediate surface and the anti-sealing fluid side slope, and is provided at a portion of the intermediate surface on the anti-sealing fluid side. A contact portion for the circumferentially continuous member is provided, and at least a part of the edge of the recess that is forward in the rotational direction when the partner member rotates in the forward direction is anti-sealed from the sealed fluid side. It is set to the direction which inclines forward of the rotation direction at this time toward the fluid side, and at least a part of the portion which is the front of the rotation direction when the counterpart member rotates in the reverse direction among the edges of the recesses It is characterized in that it is set to be inclined in the forward direction of the rotation direction from the sealing fluid side to the anti-sealing fluid side.

また、本発明の請求項２による密封装置は、回転軸等の相手部材が正逆両方向に相対回転する密封装置であって、前記相手部材の周面に摺動自在に密接するシールリップを有し、前記シールリップは、密封流体側斜面および反密封流体側斜面ならびに前記両斜面の間に設けられた中間面を有し、前記相手部材が正方向に回転するときにポンピング作用によって密封流体を押し戻す作用を奏する正ネジ部と、前記相手部材が逆方向に回転するときにポンピング作用によって密封流体を押し戻す作用を奏する逆ネジ部とが前記反密封流体側斜面に設けられ、前記中間面に凹部が設けられ、前記凹部は前記中間面および反密封流体側斜面の境界部に達しないように設けられて前記中間面における前記凹部の反密封流体側の部位に円周上連続する前記相手部材に対する接触部が設けられ、前記凹部の底面のうち前記相手部材が正方向に回転するときに回転方向の前方となる部位は少なくともその一部がこのときの回転方向の前方へ向けて深さが徐々に浅くなる傾斜面状に設定され、前記凹部の縁辺のうち前記相手部材が逆方向に回転するときに回転方向の前方となる部位は少なくともその一部がこのときの回転方向の前方へ向けて深さが徐々に浅くなる傾斜面状に設定されていることを特徴とするものである。 The sealing device according to claim 2 of the present invention is a sealing device in which a mating member such as a rotating shaft relatively rotates in both forward and reverse directions, and has a seal lip that is slidably in contact with the peripheral surface of the mating member. The sealing lip has a sealing fluid side inclined surface and an anti-sealing fluid side inclined surface and an intermediate surface provided between the both inclined surfaces, and when the counterpart member rotates in the forward direction, the sealing fluid is pumped by a pumping action. A forward screw portion that exerts an action of pushing back and a reverse screw portion that acts to push back the sealing fluid by a pumping action when the counterpart member rotates in the reverse direction are provided on the inclined surface on the anti-sealing fluid side, and a recess is formed in the intermediate surface The concave portion is provided so as not to reach a boundary portion between the intermediate surface and the anti-sealing fluid side inclined surface, and is continuous on the circumference to a portion of the intermediate surface on the anti-sealing fluid side of the concave portion. A contact portion for the hand member is provided, and at least a part of the bottom surface of the recess that is forward in the rotation direction when the counterpart member rotates in the forward direction is deeper toward the front in the rotation direction at this time. The portion of the edge of the recess that is forward in the rotational direction when the mating member rotates in the reverse direction is at least part of the front in the rotational direction at this time. It is characterized by being set to an inclined surface shape in which the depth gradually decreases toward.

上記構成を有する本発明の請求項１による密封装置においては、シールリップの密封流体側斜面および反密封流体側斜面の間に中間面が設けられ、中間面に凹部が設けられ、凹部は中間面および反密封流体側斜面の境界部に達しないように設けられて中間面における凹部の反密封流体側の部位に円周上連続する相手部材に対する接触部が設けられている。 In the sealing device according to claim 1 of the present invention having the above-described configuration, an intermediate surface is provided between the sealing fluid-side inclined surface and the anti-sealing fluid-side inclined surface of the seal lip, a concave portion is provided in the intermediate surface, and the concave portion is the intermediate surface. In addition, a contact portion is provided so as not to reach the boundary portion of the anti-sealing fluid-side inclined surface, and a contact portion with respect to the opposite member that is circumferentially continuous at a portion of the intermediate surface on the anti-sealing fluid side of the recess.

また、凹部の縁辺のうち相手部材が正方向に回転するときに回転方向の前方となる部位は少なくともその一部が密封流体側から反密封流体側へかけてこのときの回転方向の前方へ傾斜する向きに設定されている。したがって相手部材が正方向に回転するとき、シールリップの摺動部に導入される密封流体すなわちシールリップの中間面に導入される密封流体はその一部が凹部に取り込まれ、取り込まれた密封流体は相手部材の回転に引き摺られ、凹部縁辺の傾斜に沿って流れて集束し、このように集束した状態で凹部から中間面へ溢出し、中間面で厚い流体膜を形成する。圧力としては中間面を相手部材から浮かす動圧が発生する。 Further, at least a part of the edge of the recess that is forward in the rotational direction when the counterpart member rotates in the forward direction is inclined forward in the rotational direction from the sealed fluid side to the anti-sealed fluid side. The orientation is set. Accordingly, when the mating member rotates in the forward direction, a part of the sealing fluid introduced into the sliding portion of the seal lip, that is, the sealing fluid introduced into the intermediate surface of the seal lip, is taken into the recess, and the taken-in sealing fluid Is dragged by the rotation of the mating member, flows and converges along the inclination of the edge of the recess, overflows from the recess to the intermediate surface in such a focused state, and forms a thick fluid film on the intermediate surface. As the pressure, a dynamic pressure that floats the intermediate surface from the counterpart member is generated.

また、凹部の縁辺のうち相手部材が逆方向に回転するときに回転方向の前方となる部位は少なくともその一部が密封流体側から反密封流体側へかけてこのときの回転方向の前方へ傾斜する向きに設定されている。したがって相手部材が逆方向に回転するとき、シールリップの摺動部に導入される密封流体すなわちシールリップの中間面に導入される密封流体はその一部が凹部に取り込まれ、取り込まれた密封流体は相手部材の回転に引き摺られ、凹部縁辺の傾斜に沿って流れて集束し、このように集束した状態で凹部から中間面へ溢出し、中間面で厚い流体膜を形成する。圧力としては中間面を相手部材から浮かす動圧が発生する。 Further, at least a part of the edge of the recess that is forward in the rotational direction when the counterpart member rotates in the reverse direction is inclined forward from the sealed fluid side to the anti-sealed fluid side. The orientation is set. Therefore, when the mating member rotates in the reverse direction, a part of the sealing fluid introduced into the sliding portion of the seal lip, that is, the sealing fluid introduced into the intermediate surface of the seal lip, is taken into the recess, and the taken-in sealing fluid Is dragged by the rotation of the mating member, flows and converges along the inclination of the edge of the recess, overflows from the recess to the intermediate surface in such a focused state, and forms a thick fluid film on the intermediate surface. As the pressure, a dynamic pressure that floats the intermediate surface from the counterpart member is generated.

したがって、以上のように相手部材が正方向に回転するときも逆方向に回転するときも中間面に厚い流体膜が形成され動圧が発生するので、何れの場合も流体潤滑にもとづく低トルク化が実現される。 Therefore, as described above, even when the mating member rotates in the forward direction or in the reverse direction, a thick fluid film is formed on the intermediate surface and dynamic pressure is generated. Therefore, in any case, the torque can be reduced based on fluid lubrication. Is realized.

中間面に設けられる接触部は円周上連続したものであるので、いわゆる静止漏れを抑制する作用もある。 Since the contact portion provided on the intermediate surface is continuous on the circumference, there is also an action of suppressing so-called stationary leakage.

上記構成を有する本発明の請求項２による密封装置においては、シールリップの密封流体側斜面および反密封流体側斜面の間に中間面が設けられ、中間面に凹部が設けられ、凹部は中間面および反密封流体側斜面の境界部に達しないように設けられて中間面における凹部の反密封流体側の部位に円周上連続する相手部材に対する接触部が設けられている。 In the sealing device according to claim 2 of the present invention having the above-described configuration, an intermediate surface is provided between the sealing fluid side inclined surface and the anti-sealing fluid side inclined surface of the seal lip, a concave portion is provided in the intermediate surface, and the concave portion is the intermediate surface. In addition, a contact portion is provided so as not to reach the boundary portion of the anti-sealing fluid-side inclined surface, and a contact portion with respect to the opposite member that is circumferentially continuous at a portion of the intermediate surface on the anti-sealing fluid side of the concave portion.

また、凹部の底面のうち相手部材が正方向に回転するときに回転方向の前方となる部位は少なくともその一部がこのときの回転方向の前方へ向けて深さが徐々に浅くなる傾斜面状に設定されている。したがって相手部材が正方向に回転するとき、シールリップの摺動部に導入される密封流体すなわちシールリップの中間面に導入される密封流体はその一部が凹部に取り込まれ、取り込まれた密封流体は相手部材の回転に引き摺られ、凹部底面の傾斜に沿って流れて集束し、このように集束した状態で凹部から中間面へ溢出し、中間面で厚い流体膜を形成する。圧力としては中間面を相手部材から浮かす動圧が発生する。 Further, at least a part of the bottom surface of the concave portion that is forward in the rotational direction when the counterpart member rotates in the forward direction is an inclined surface whose depth gradually decreases toward the forward in the rotational direction at this time. Is set to Accordingly, when the mating member rotates in the forward direction, a part of the sealing fluid introduced into the sliding portion of the seal lip, that is, the sealing fluid introduced into the intermediate surface of the seal lip, is taken into the recess, and the taken-in sealing fluid Is dragged by the rotation of the mating member, flows and converges along the slope of the bottom surface of the recess, overflows from the recess to the intermediate surface in such a focused state, and forms a thick fluid film on the intermediate surface. As the pressure, a dynamic pressure that floats the intermediate surface from the counterpart member is generated.

また、凹部の底面のうち相手部材が逆方向に回転するときに回転方向の前方となる部位は少なくともその一部がこのときの回転方向の前方へ向けて深さが徐々に浅くなる傾斜面状に設定されている。したがって相手部材が逆方向に回転するとき、シールリップの摺動部に導入される密封流体すなわちシールリップの中間面に導入される密封流体はその一部が凹部に取り込まれ、取り込まれた密封流体は相手部材の回転に引き摺られ、凹部底面の傾斜に沿って流れて集束し、このように集束した状態で凹部から中間面へ溢出し、中間面で厚い流体膜を形成する。圧力としては中間面を相手部材から浮かす動圧が発生する。 Further, at least a part of the bottom surface of the concave portion that is forward in the rotation direction when the counterpart member rotates in the reverse direction is inclined so that the depth gradually decreases toward the front in the rotation direction at this time. Is set to Therefore, when the mating member rotates in the reverse direction, a part of the sealing fluid introduced into the sliding portion of the seal lip, that is, the sealing fluid introduced into the intermediate surface of the seal lip, is taken into the recess, and the taken-in sealing fluid Is dragged by the rotation of the mating member, flows and converges along the slope of the bottom surface of the recess, overflows from the recess to the intermediate surface in such a focused state, and forms a thick fluid film on the intermediate surface. As the pressure, a dynamic pressure that floats the intermediate surface from the counterpart member is generated.

また、中間面に設けられる接触部は円周上連続したものであるので、いわゆる静止漏れを抑制する作用もある。 Further, since the contact portion provided on the intermediate surface is continuous on the circumference, there is also an action of suppressing so-called stationary leakage.

本発明は、以下の効果を奏する。 The present invention has the following effects.

すなわち、本発明の請求項１による密封装置においては上記したように、凹部の縁辺のうち相手部材が正方向に回転するときに回転方向の前方となる部位が密封流体側から反密封流体側へかけてこのときの回転方向の前方へ傾斜する向きに設定されているため、相手部材が正方向に回転するとき、凹部に取り込まれ集束する密封流体によって中間面に厚い流体膜が形成され動圧が発生する。また凹部の縁辺のうち相手部材が逆方向に回転するときに回転方向の前方となる部位が密封流体側から反密封流体側へかけてこのときの回転方向の前方へ傾斜する向きに設定されているため、相手部材が逆方向に回転するとき、凹部に取り込まれ集束する密封流体によって中間面に厚い流体膜が形成され動圧が発生する。したがって相手部材が正方向に回転するときも逆方向に回転するときも中間面に厚い流体膜が形成され動圧が発生するので、何れの場合も流体潤滑にもとづく低トルク化を実現することができる。円周上連続する接触部はいわゆる静止漏れを抑制することができる。 That is, in the sealing device according to claim 1 of the present invention, as described above, the portion of the edge of the recess that is forward in the rotational direction when the counterpart member rotates in the forward direction is from the sealed fluid side to the anti-sealed fluid side. Therefore, when the counterpart member rotates in the forward direction, a thick fluid film is formed on the intermediate surface by the sealing fluid that is taken in and converged when the counterpart member rotates in the forward direction. Will occur. In addition, the part of the edge of the recess that is forward in the rotational direction when the counterpart member rotates in the opposite direction is set to be inclined in the forward direction in the rotational direction from the sealed fluid side to the anti-sealed fluid side. Therefore, when the mating member rotates in the reverse direction, a thick fluid film is formed on the intermediate surface by the sealing fluid that is taken in and converged in the recess, and dynamic pressure is generated. Therefore, even when the mating member rotates in the forward direction or in the reverse direction, a thick fluid film is formed on the intermediate surface and dynamic pressure is generated. Therefore, in any case, it is possible to realize a low torque based on fluid lubrication. it can. The circumferentially continuous contact portion can suppress so-called stationary leakage.

また、本発明の請求項２による密封装置においては上記したように、凹部の底面のうち相手部材が正方向に回転するときに回転方向の前方となる部位がこのときの回転方向の前方へ向けて深さが徐々に浅くなる傾斜面状に設定されているため、相手部材が正方向に回転するとき、凹部に取り込まれ集束する密封流体によって中間面に厚い流体膜が形成され動圧が発生する。また凹部の底面のうち相手部材が逆方向に回転するときに回転方向の前方となる部位がこのときの回転方向の前方へ向けて負荷さが徐々に浅くなる傾斜面状に設定されているため、相手部材が逆方向に回転するとき、凹部に取り込まれ集束する密封流体によって中間面に厚い流体膜が形成され動圧が発生する。したがって相手部材が正方向に回転するときも逆方向に回転するときも中間面に厚い流体膜が形成され動圧が発生するので、何れの場合も流体潤滑にもとづく低トルク化を実現することができる。円周上連続する接触部はいわゆる静止漏れを抑制することができる。 Moreover, in the sealing device according to claim 2 of the present invention, as described above, the portion of the bottom surface of the recess that is forward in the rotational direction when the counterpart member rotates in the forward direction is directed forward in the rotational direction at this time. As the mating member rotates in the forward direction, a thick fluid film is formed on the intermediate surface by the sealed fluid that is taken in and converged in the concavity and generates dynamic pressure. To do. Moreover, since the part which becomes the front of a rotation direction when the other member rotates in a reverse direction among the bottom surfaces of a recessed part is set to the inclined surface shape where load becomes shallow gradually toward the front of the rotation direction at this time When the mating member rotates in the reverse direction, a thick fluid film is formed on the intermediate surface by the sealing fluid that is taken in and converged in the recess, and dynamic pressure is generated. Therefore, even when the mating member rotates in the forward direction or in the reverse direction, a thick fluid film is formed on the intermediate surface and dynamic pressure is generated. Therefore, in any case, it is possible to realize a low torque based on fluid lubrication. it can. The circumferentially continuous contact portion can suppress so-called stationary leakage.

本発明には、以下の実施形態が含まれる。 The present invention includes the following embodiments.

請求項１関連・・・
（１）本発明は、油側傾斜のフラット部（中間面）とそこに設けられた油側からの吸込み逆向きネジを有するオイルシールの改良発明であり、両回転シールへの応用を図ったものである。
（２）中間面に、中間面と密封流体側斜面との境界部に達し、中間面と反密封流体側斜面との境界部に達しないように凹部を設け、中間面の反密封流体側には、連続した接触部が確保される。
（３）摺動方向（回転方向）の前方の凹部と中間面の境界線（凹部縁辺）は、摺動方向に直交、または密封流体側から反密封流体側へかけて摺動方向の前方へ傾斜する向きに設定する。
（４）凹部は、両回転に対応するため、軸方向に線対称な形が望ましいが、凹部円周方向両側の傾斜の角度は異なってもよい。
（５）摺動方向の前方の凹部と中間面の境界線は、曲線形状でもよく、密封流体側から反密封流体側へかけて、一部を摺動方向の前方へ傾斜する向きに設定する。
（６）この構成により、凹部に取り込まれた潤滑油は、軸の回転により、軸摺動方向に引き寄せられ、さらに凹部の形状により反密封流体側へと送り込まれる。
（７）反密封流体側斜面にまで到達した潤滑油は、反密封流体側斜面ネジによって密封流体側に戻される。
（８）これにより、中間面を浮かす圧力を発生させ、中間面の油膜厚さを増加させることで、流体潤滑にもとづく低トルク化を実現する。
（９）下記実施例に示すような凹部を設けることで、上記（６）（７）（８）の効果を両回転に対応可能とする。 Claim 1 related ...
(1) The present invention is an improved invention of an oil seal having a flat portion (intermediate surface) inclined on the oil side and a suction reverse screw provided from the oil side, and is applied to both rotary seals. Is.
(2) A concave portion is provided on the intermediate surface so as to reach the boundary between the intermediate surface and the sealed fluid side inclined surface, and not to reach the boundary between the intermediate surface and the anti-sealed fluid side inclined surface. A continuous contact portion is secured.
(3) The boundary between the recess and the intermediate surface in the sliding direction (rotation direction) and the boundary surface (the recess edge) are orthogonal to the sliding direction or forward from the sealing fluid side to the anti-sealing fluid side. Set to tilt direction.
(4) Since the concave portion corresponds to both rotations, a shape that is line-symmetric in the axial direction is desirable, but the inclination angles on both sides in the circumferential direction of the concave portion may be different.
(5) The boundary line between the concave portion in the front of the sliding direction and the intermediate surface may be a curved shape, and is set so that a part thereof is inclined forward in the sliding direction from the sealing fluid side to the anti-sealing fluid side. .
(6) With this configuration, the lubricating oil taken into the recess is drawn in the shaft sliding direction by the rotation of the shaft, and further fed to the anti-sealing fluid side by the shape of the recess.
(7) The lubricating oil that has reached the anti-sealing fluid side inclined surface is returned to the sealing fluid side by the anti-sealing fluid side inclined screw.
(8) Thereby, the pressure which floats an intermediate surface is generated, and the oil film thickness of the intermediate surface is increased, thereby realizing a reduction in torque based on fluid lubrication.
(9) By providing a recess as shown in the following embodiment, the effects (6), (7), and (8) can be applied to both rotations.

請求項２関連・・・
（１０）本発明は、油側傾斜のフラット部（中間面）とそこに設けられた油側からの吸込み逆向きネジを有するオイルシールの改良発明であり、両回転シールへの応用を図ったものである。
（１１）中間面に、軸の両回転方向に徐々に深さが浅くなる傾斜面を持つ凹部を設ける。
（１２）この凹部は、密封流体側斜面まで通じているが、反密封流体側斜面とは通じていない。中間面の反密封流体側には連続した接触部が確保される。
（１３）凹部は傾斜面以外に底面を設けてもよい。
（１４）また、軸方向に対称な凹部を交互に設けてもよい。
（１５）傾斜面と中間面の境界線（凹部縁辺）は、摺動方向（回転方向）に直交する形が望ましいが、反密封流体側から密封流体側へかけて摺動方向の前方へ傾斜する向きに設定してもよい。
（１６）反密封流体側斜面ネジを設けてもよい。
（１７）この構成により、凹部に取り込まれた潤滑油は軸の摺動により傾斜面に引き摺られていくことで、くさび効果により中間面を浮かす圧力が発生し、中間面の油膜厚さを増加させることで、流体潤滑にもとづく低トルク化を実現する。
（１８）中間面の反密封流体側の連続した接触部も油膜により持ち上げられるため、潤滑油は中間面の反密封流体側まで移動するが、反密封流体側斜面にまで到達した油は反密封流体側斜面ネジによって密封流体側に戻される。
（１９）下記実施例に示すような凹部を設けることで、上記（１７）（１８）の効果を両回転に対応可能とする。
（２０）また、この構成は、傾斜面はその軸摺動方向の後流部の油膜厚さを増加させるように作用するだけで、積極的に潤滑油を大気側に送り込む作用は生じないので、万が一、大気側のネジのポンピング力が低下することがあっても、潤滑油の漏れは生じない。 Claim 2 related ...
(10) The present invention is an improved invention of an oil seal having a flat part (intermediate surface) inclined on the oil side and a suction reverse screw provided from the oil side, and is applied to both rotary seals. Is.
(11) A concave portion having an inclined surface whose depth gradually decreases in both rotation directions of the shaft is provided on the intermediate surface.
(12) The recess communicates with the sealed fluid side slope, but does not communicate with the anti-sealed fluid side slope. A continuous contact portion is secured on the anti-sealing fluid side of the intermediate surface.
(13) The recess may have a bottom surface other than the inclined surface.
(14) Moreover, you may provide the recessed part symmetrical to an axial direction alternately.
(15) The boundary line (concave edge) between the inclined surface and the intermediate surface is preferably perpendicular to the sliding direction (rotational direction), but inclined forward from the anti-sealing fluid side to the sealing fluid side. You may set to the direction to do.
(16) An anti-sealing fluid side bevel screw may be provided.
(17) With this configuration, the lubricating oil taken into the recess is dragged to the inclined surface by sliding the shaft, generating a pressure to lift the intermediate surface due to the wedge effect, and increasing the oil film thickness of the intermediate surface As a result, low torque is achieved based on fluid lubrication.
(18) Since the continuous contact portion on the anti-sealing fluid side of the intermediate surface is also lifted by the oil film, the lubricating oil moves to the anti-sealing fluid side of the intermediate surface, but the oil that has reached the anti-sealing fluid side slope is anti-sealing It is returned to the sealed fluid side by a fluid side bevel screw.
(19) By providing a recess as shown in the following embodiment, the effects (17) and (18) can be applied to both rotations.
(20) Further, in this configuration, since the inclined surface only acts to increase the oil film thickness of the wake portion in the axial sliding direction, there is no effect of positively feeding the lubricating oil to the atmosphere side. In the unlikely event that the pumping force of the screw on the atmosphere side may be reduced, the lubricating oil does not leak.

つぎに本発明の実施例を図面にしたがって説明する。 Next, embodiments of the present invention will be described with reference to the drawings.

第一実施例・・・
図１は、本発明の第一実施例に係る密封装置（オイルシール）１の要部断面を示している。図２（Ａ）は図１の要部を拡大して示している。当該実施例に係る密封装置１は両回転シールであって、以下のように構成されている。 First embodiment ...
FIG. 1 shows a cross section of a main part of a sealing device (oil seal) 1 according to a first embodiment of the present invention. FIG. 2A shows an enlarged view of the main part of FIG. The sealing device 1 according to the embodiment is a double-rotating seal and is configured as follows.

すなわち先ず図１に示すように、金属環２に被着（加硫接着）されたゴム状弾性体３によって外周シール部４およびダストリップ５などとともに軸（相手部材、図示せず）の周面に摺動自在に密接するシールリップ６が設けられており、このシールリップ６の先端摺動部に密封流体側斜面７および反密封流体側斜面８が設けられ、両斜面７，８の間に中間面（フラット面）９が設けられている。中間面９は円筒面状に形成され、軸挿入時、軸の周面と全面に亙って接触するが、図２（Ａ）に示すようにその初期状態（軸挿入前の自由状態）において密封流体側Ｃに傾斜角度θ_１をもつ傾斜面状（円錐面状）のものであっても良い。傾斜角度θ_１の大きさとしては、０〜２０度が好適であり、０．１〜１０度が一層好適である。これにより中間面９はその反密封流体側Ｄの部位（後記する円周上連続する接触部１５）で軸の周面に強く接触する。 That is, first, as shown in FIG. 1, a peripheral surface of a shaft (a mating member, not shown) together with an outer peripheral seal portion 4 and a dust strip 5 by a rubber-like elastic body 3 adhered (vulcanized and bonded) to a metal ring 2. A seal lip 6 that is slidably in contact with the seal lip 6 is provided, and a sealing fluid side inclined surface 7 and an anti-sealing fluid side inclined surface 8 are provided at the tip sliding portion of the seal lip 6. An intermediate surface (flat surface) 9 is provided. The intermediate surface 9 is formed in a cylindrical shape and contacts the entire surface of the shaft when the shaft is inserted, but in its initial state (free state before shaft insertion) as shown in FIG. inclined surface shape at the sealed fluid side C having an inclination angle theta ₁ may be of (conical shape). As a magnitude | size of inclination | tilt angle (theta) ₁ , 0-20 degree is suitable and 0.1-10 degree is still more suitable. As a result, the intermediate surface 9 strongly contacts the peripheral surface of the shaft at a portion on the anti-sealing fluid side D (a contact portion 15 that continues on the circumference described later).

反密封流体側斜面８に、軸が正方向に回転（正回転、図２（Ａ）における矢印Ｅ）するときにポンピング作用によって密封流体を密封流体側Ｃへ押し戻す作用を奏する正ネジ部１０が設けられ、また軸が逆方向に回転（逆回転、図２（Ａ）における矢印Ｆ）するときにポンピング作用によって密封流体を密封流体側Ｃへ押し戻す作用を奏する逆ネジ部１１が設けられている。 On the anti-sealing fluid side inclined surface 8, there is a positive screw portion 10 that acts to push the sealing fluid back to the sealing fluid side C by a pumping action when the shaft rotates in the positive direction (forward rotation, arrow E in FIG. 2A). There is also provided a reverse screw portion 11 that acts to push the sealing fluid back to the sealing fluid side C by a pumping action when the shaft rotates in the reverse direction (reverse rotation, arrow F in FIG. 2A). .

正ネジ部１０は、円周上多数設けられた螺旋状の突起群よりなり、図では断面三角形状の突起を想定して描いているが、その形状は特に限定されるものではない。螺旋の向きはその反密封流体側端部１０ａから密封流体側端部１０ｂへかけて軸の正回転方向Ｅの前方へ向けて傾斜する向きに設定されている。逆ネジ部１１はこれも円周上多数設けられた螺旋状の突起群よりなり、図では断面三角形状の突起を想定して描いているが、その形状は特に限定されるものではない。螺旋の向きはその反密封流体側端部１１ａから密封流体側端部１１ｂへかけて軸の逆回転方向Ｆの前方へ向けて傾斜する向きに設定されている。正ネジ部１０および逆ネジ部１１は円周上１本ずつ交互に設けられているが、多条ネジのように複数本ずつ交互に設けられるものであっても良い。この場合、ネジの長さは異なるものであっても良い。 The regular screw portion 10 is composed of a group of spiral projections provided on the circumference, and is drawn assuming projections having a triangular cross section in the figure, but the shape is not particularly limited. The direction of the spiral is set so as to incline forward in the positive rotation direction E of the shaft from the anti-sealing fluid side end 10a to the sealing fluid side end 10b. The reverse screw portion 11 is also composed of a spiral projection group provided in a large number on the circumference, and is drawn assuming projections having a triangular cross section in the figure, but the shape is not particularly limited. The direction of the spiral is set so as to incline toward the front in the reverse rotation direction F of the shaft from the anti-sealing fluid side end portion 11a to the sealing fluid side end portion 11b. Although the normal screw portion 10 and the reverse screw portion 11 are alternately provided one by one on the circumference, a plurality of the normal screw portions 10 and the reverse screw portions 11 may be alternately provided like a multiple thread screw. In this case, the screw length may be different.

中間面９に凹部１２が設けられている。この凹部１２は中間面９および密封流体側斜面７の境界部１３に達し、中間面９および反密封流体側斜面８の境界部１４には達しないように設けられ、これにより中間面９における凹部１２の反密封流体側Ｄの部位には、円周上連続する所定の軸方向幅ｇを有する軸に対する接触部１５が設けられている。またこの凹部１２はネジ部１０，１１と同様、同じ形状のものが多数、円周方向に一定の間隔をあけて並んで設けられている。 A recess 12 is provided in the intermediate surface 9. The concave portion 12 is provided so as to reach the boundary portion 13 between the intermediate surface 9 and the sealed fluid side inclined surface 7 and not reach the boundary portion 14 between the intermediate surface 9 and the anti-sealed fluid side inclined surface 8. A contact portion 15 for a shaft having a predetermined axial width g that is continuous on the circumference is provided at a portion of the twelve anti-sealing fluid side D. In addition, like the screw portions 10 and 11, many of the concave portions 12 have the same shape, and are provided side by side with a constant interval in the circumferential direction.

凹部１２の縁辺（凹部１２および中間面９の境界線）のうち軸が正回転Ｅするときに回転方向の前方となる部位１２ａは、密封流体側Ｃから反密封流体側Ｄへかけてこのときの回転方向Ｅの前方へ傾斜する向きに設定されている（以下、「一方の傾斜縁辺１２ａ」とも称する）。すなわち凹部１２の縁辺のうち軸が正回転Ｅするときに回転方向の前方となる部位には、密封流体側Ｃから反密封流体側Ｄへかけてこのときの回転方向Ｅの前方へ傾斜する向きの一方の傾斜縁辺１２ａが形成されている。また凹部１２の縁辺のうち軸が逆回転Ｆするときに回転方向の前方となる部位１２ｂは、密封流体側Ｃから反密封流体側Ｄへかけてこのときの回転方向Ｆの前方へ傾斜する向きに設定されている（以下、「他方の傾斜縁辺１２ｂ」とも称する）。すなわち凹部１２の縁辺のうち軸が逆回転Ｆするときに回転方向の前方となる部位には、密封流体側Ｃから反密封流体側Ｄへかけてこのときの回転方向Ｆの前方へ傾斜する向きの他方の傾斜縁辺１２ｂが形成されている。したがって凹部１２は円周方向両端に互いに反対向きの傾斜縁辺１２ａ，１２ｂを有しているので、全体として図示するように平面台形状に形成され、この台形状のうち左右の斜辺（傾斜縁辺１２ａ，１２ｂ）および長底辺（反密封流体側縁辺）はそれぞれ底面からの立ち上がり面とされ、短底辺（密封流体側縁辺）は密封流体側Ｃへ向けての開口部とされている。凹部１２の深さは凹部１２の全面に亙って一定とされ、立ち上がり面は中間面９に対して直角面をなしているが、流体が流れやすいように傾斜を付けても良い。一方の傾斜縁辺１２ａの傾斜角度θ_２と他方の傾斜縁辺１２ｂの傾斜角度θ_３とは互いに同じに設定されているが（θ_２＝θ_３）、図２（Ｂ）に示すように互いに異なるように設定されても良い（θ_２≠θ_３，すなわちθ_２＞θ_３またはθ_２＜θ_３）。 Of the edge of the recess 12 (boundary line between the recess 12 and the intermediate surface 9), the portion 12a that is forward in the rotation direction when the shaft rotates forward E is from the sealed fluid side C to the anti-sealed fluid side D at this time. Is set to be inclined forward in the rotational direction E (hereinafter also referred to as “one inclined edge 12a”). That is, the portion of the edge of the recess 12 that is forward in the rotational direction when the shaft rotates forward E is inclined in the forward direction of the rotational direction E from the sealed fluid side C to the anti-sealed fluid side D. One inclined edge 12a is formed. Further, a portion 12b which is the front in the rotation direction when the shaft rotates in the reverse direction F on the edge of the recess 12 is inclined in the forward direction in the rotation direction F from the sealed fluid side C to the anti-sealed fluid side D. (Hereinafter also referred to as “the other inclined edge 12b”). In other words, the portion of the edge of the recess 12 that is forward in the rotational direction when the shaft rotates in the reverse direction F is inclined forward from the sealed fluid side C to the anti-sealed fluid side D in this rotational direction F. The other inclined edge 12b is formed. Accordingly, since the recess 12 has inclined edges 12a and 12b opposite to each other at both ends in the circumferential direction, it is formed in a flat trapezoidal shape as shown in the figure as a whole. 12b) and the long bottom side (anti-sealing fluid side edge) are rising surfaces from the bottom surface, and the short bottom side (sealing fluid side edge) is an opening toward the sealing fluid side C. The depth of the concave portion 12 is constant over the entire surface of the concave portion 12, and the rising surface is a plane perpendicular to the intermediate surface 9, but may be inclined so that the fluid can easily flow. Although the inclination angle theta ₃ inclination angle theta ₂ and other inclined edge 12b of the one inclined edge 12a is set to be equal to each other (θ _{2 =} θ _3), different from each other as shown in FIG. 2 (B) (Θ ₂ ≠ θ ₃ , that is, θ ₂ > θ ₃ or θ ₂ <θ ₃ ).

上記構成の密封装置１は、ハウジングの軸孔内周に装着され、前記軸孔に挿通した回転軸の周面に摺動自在に密接することにより機内の密封流体（油）が機外へ漏洩しないようこれをシールするものであって、両回転シールであり、上記構成により以下の作用効果を発揮する点に特徴を有している。 The sealing device 1 having the above-described configuration is mounted on the inner periphery of the shaft hole of the housing, and the sealing fluid (oil) in the machine leaks out of the machine by being slidably in close contact with the peripheral surface of the rotating shaft inserted through the shaft hole. This is a double-rotating seal, and is characterized in that the following effects are exhibited by the above configuration.

すなわち上記密封装置１が装着されると一部の密封流体が境界部１３に開口する開口部から凹部１２に取り込まれ、図３に示すように軸が正回転Ｅすると凹部１２に取り込まれた密封流体はその粘性によって軸の正回転Ｅに引き摺られ、凹部１２縁辺に設けた一方の傾斜縁辺１２ａに沿って流れて集束し（凹部１２の断面積が徐々に小さくなるため）、集束しつつ凹部１２から中間面９ないし接触部１５へ溢出し（矢印Ｈ）、中間面９とくに円周上連続する接触部１５上で厚い流体膜を形成する。圧力としては中間面９ないし接触部１５を軸から浮かす動圧が発生する。また軸が逆回転Ｆ（図２）すると凹部１２に取り込まれた密封流体はその粘性によって軸の逆回転Ｆに引き摺られ、凹部１２縁辺に設けた他方の傾斜縁辺１２ｂに沿って流れて集束し（凹部１２の断面積が徐々に小さくなるため）、集束しつつ凹部１２から中間面９ないし接触部１５へ溢出し、中間面９とくに円周上連続する接触部１５上で厚い流体膜を形成する。圧力としては中間面９ないし接触部１５を軸から浮かす動圧が発生する。したがって軸が正回転Ｅするときも逆回転Ｆするときも中間面９ないし接触部１５上に厚い流体膜が形成され動圧が発生するので、何れの場合も流体潤滑にもとづく低トルク化を実現し、シールリップ６が早期に摺動摩耗するのを抑制することができる。中間面９に設けられた接触部１５は円周上連続したものであって軸の周面に全周に亙って密接するので、軸回転静止時の漏洩（いわゆる静止漏れ）を抑制することもできる。 That is, when the sealing device 1 is mounted, a part of the sealing fluid is taken into the concave portion 12 from the opening portion that opens to the boundary portion 13, and the sealing portion taken into the concave portion 12 when the shaft rotates forward E as shown in FIG. The fluid is dragged by the positive rotation E of the shaft due to its viscosity, flows and converges along one inclined edge 12a provided on the edge of the recess 12 (because the cross-sectional area of the recess 12 gradually decreases). 12 overflows from the intermediate surface 9 to the contact portion 15 (arrow H), and a thick fluid film is formed on the intermediate surface 9, particularly on the contact portion 15 continuous on the circumference. As the pressure, a dynamic pressure for floating the intermediate surface 9 or the contact portion 15 from the shaft is generated. When the shaft rotates in the reverse direction F (FIG. 2), the sealing fluid taken into the recess 12 is dragged by the reverse rotation F of the shaft due to its viscosity, and flows along the other inclined edge 12b provided on the edge of the recess 12 and converges. (Because the cross-sectional area of the concave portion 12 gradually decreases), the condensing portion 12 overflows from the concave portion 12 to the intermediate surface 9 or the contact portion 15, and forms a thick fluid film on the intermediate surface 9, particularly on the contact portion 15 continuous on the circumference. To do. As the pressure, a dynamic pressure for floating the intermediate surface 9 or the contact portion 15 from the shaft is generated. Therefore, a thick fluid film is formed on the intermediate surface 9 or the contact portion 15 when the shaft rotates in the forward direction E or in the reverse direction F, so that dynamic pressure is generated. In any case, a reduction in torque based on fluid lubrication is realized. In addition, it is possible to suppress the sliding lip 6 from sliding and wearing at an early stage. The contact portion 15 provided on the intermediate surface 9 is continuous on the circumference and is in close contact with the circumferential surface of the shaft over the entire circumference, so that leakage at the time of stationary shaft rotation (so-called stationary leakage) is suppressed. You can also.

尚、中間面９ないし接触部１５から反密封流体側斜面８のほうへ流出する密封流体は正ネジ部１０（正回転時）または逆ネジ部１１（逆回転時）のポンピング作用によって密封流体側Ｃへ押し戻されるが、正回転時、一方の傾斜縁辺１２ａから接触部１５を介して反密封流体側斜面８へ流出する密封流体を正ネジ部１０が押し戻しやすいように凹部１２および正ネジ部１０の円周方向位置関係を規定すると、正ネジ部１０による押し戻し量の増加が期待されるので、ポンピング効率が向上する。また同様に逆回転時、他方の傾斜縁辺１２ｂから接触部１５を介して反密封流体側斜面８へ流出する密封流体を逆ネジ部１１が押し戻しやすいように凹部１２および逆ネジ部１１の円周方向位置関係を規定すると、逆ネジ部１１による押し戻し量の増加が期待されるので、ポンピング効率が向上する。これらを実現するには具体的には、凹部１２および両ネジ部１０，１１の円周方向位置関係として、正ネジ部１０（例えば図２（Ａ）における２つの正ネジ部１０のうち左側の正ネジ部１０）とその正回転方向Ｅの後方側に配置された逆ネジ部１１（例えば図２（Ａ）における２つの逆ネジ部１１のうち右側の逆ネジ部１１）との間に凹部１２を配置するのが好適である。 In addition, the sealing fluid that flows out from the intermediate surface 9 or the contact portion 15 toward the anti-sealing fluid side inclined surface 8 is the sealing fluid side by the pumping action of the forward screw portion 10 (forward rotation) or the reverse screw portion 11 (reverse rotation). The concave portion 12 and the positive screw portion 10 are pushed back to C so that the positive screw portion 10 can easily push back the sealing fluid flowing out from the one inclined edge 12a to the anti-sealing fluid side inclined surface 8 through the contact portion 15 during forward rotation. If the positional relationship in the circumferential direction is defined, an increase in the amount of pushing back by the positive screw portion 10 is expected, so that the pumping efficiency is improved. Similarly, during reverse rotation, the circumference of the concave portion 12 and the reverse screw portion 11 is such that the reverse screw portion 11 can easily push back the sealing fluid flowing out from the other inclined edge 12b to the anti-sealing fluid side inclined surface 8 through the contact portion 15. If the directional position relationship is defined, an increase in the amount of pushback by the reverse screw portion 11 is expected, so that the pumping efficiency is improved. Specifically, in order to realize these, as the circumferential positional relationship between the concave portion 12 and the both screw portions 10 and 11, the positive screw portion 10 (for example, the left of the two positive screw portions 10 in FIG. A concave portion between the normal screw portion 10) and the reverse screw portion 11 (for example, the right reverse screw portion 11 of the two reverse screw portions 11 in FIG. 2A) disposed on the rear side in the normal rotation direction E. 12 is preferably arranged.

また、凹部１２の形状については、その機能（正回転および逆回転の双方につきそれぞれ流体を集束して動圧を発生させること）を果たすかぎり、様々なものが考えられる。 Various shapes of the concave portion 12 are conceivable as long as the function (concentrates fluids for both forward rotation and reverse rotation to generate dynamic pressure) is achieved.

すなわち、上記第一実施例では凹部１２の平面形状を台形状としたが、その機能を発揮するのは円周方向両端の傾斜縁辺１２ａ，１２ｂであるので、このような傾斜縁辺１２ａ，１２ｂを有するかぎり凹部１２の形状は限定されない。例えば図４の例では、台形状が円周方向に２分割されたような形状とされ、すなわち一方の傾斜縁辺１２ａを有する一定幅の溝状凹部１２Ａと他方の傾斜縁辺１２ｂを有する一定幅の溝状凹部１２Ｂとが円周方向に並んで設けられている。尚、図４（Ａ）はθ_２＝θ_３の場合、図４（Ｂ）はθ_２≠θ_３の場合をそれぞれ示している。 That is, in the first embodiment, the planar shape of the recess 12 is a trapezoidal shape. However, since it is the inclined edges 12a and 12b at both ends in the circumferential direction that perform the function, such inclined edges 12a and 12b are provided. As long as it has, the shape of the recess 12 is not limited. For example, in the example of FIG. 4, the trapezoidal shape is divided into two in the circumferential direction, that is, the groove-shaped recess 12A having a certain width having one inclined edge 12a and the width having a certain width having the other inclined edge 12b. A groove-like recess 12B is provided side by side in the circumferential direction. 4A shows the case where θ ₂ = θ ₃ , and FIG. 4B shows the case where θ ₂ ≠ θ ₃ .

また、凹部１２の縁辺のうち軸が正回転するときに回転方向の前方となる部位１２ａおよび凹部１２の縁辺のうち軸が逆回転するときに回転方向の前方となる部位１２ｂはそれぞれ、その一部が密封流体側Ｃから反密封流体側Ｄへかけてこのときの回転方向の前方へ傾斜する向きに設定されていれば（一部に傾斜縁辺１２ａ，１２ｂが設けられていれば）、流体を集束して動圧を発生させると考えられる。したがって傾斜する向きに設定されるのは各部位の少なくとも一部であれば良い。例えば図５の例では、凹部１２は平面円弧形状（楕円の一部が切り欠かれて切欠部が開口部とされたもの）とされ、中間面９および密封流体側斜面７の境界部１３から楕円の中心線０に至る部位が上記条件に合致する傾斜縁辺１２ａ，１２ｂとされている。尚、このように傾斜縁辺１２ａ，１２ｂは曲線状であっても良い。 Further, a portion 12a that is forward in the rotational direction when the shaft rotates forward in the edge of the concave portion 12 and a portion 12b that is forward in the rotational direction when the shaft is reversely rotated in the edge of the concave portion 12 are respectively one of them. If the portion is set to be inclined in the forward direction of the rotation direction from the sealed fluid side C to the anti-sealed fluid side D (if the inclined edges 12a and 12b are provided in part), the fluid It is thought that the dynamic pressure is generated by converging. Therefore, it is only necessary that at least a part of each part is set to the inclined direction. For example, in the example of FIG. 5, the concave portion 12 has a planar arc shape (a part of the ellipse is cut out and the cutout portion is an opening), and from the boundary portion 13 of the intermediate surface 9 and the sealed fluid side inclined surface 7. The parts reaching the center line 0 of the ellipse are inclined edges 12a and 12b that meet the above conditions. In this way, the inclined edges 12a and 12b may be curved.

また、凹部１２の形状は、凹部１２縁辺の少なくとも一部に傾斜を付けることにより、正回転方向Ｅについてはその前方へ向けて凹部１２の断面積（密封装置１の中心軸線を含む各平面で裁断したときの断面積）が徐々に縮小する形状であれば良く、逆回転方向Ｆについてもその前方へ向けて凹部１２の断面積（密封装置１の中心軸線を含む各平面で裁断したときの断面積）が徐々に縮小する形状であれば良い。 In addition, the shape of the recess 12 is formed by inclining at least a part of the edge of the recess 12, so that the forward rotation direction E is directed forward in the cross-sectional area of the recess 12 (on each plane including the central axis of the sealing device 1). The cross-sectional area at the time of cutting may be a shape that gradually decreases, and the cross-sectional area of the concave portion 12 (when cutting in each plane including the central axis of the sealing device 1) is also directed forward in the reverse rotation direction F. Any shape that gradually reduces the cross-sectional area) may be used.

第二実施例・・・
図６は、本発明の第二実施例に係る密封装置（オイルシール）１の要部断面を示している。図７（Ａ）は図６の要部を拡大して示している。図７（Ｂ）は図７（Ａ）のＩ方向矢視図であってかつ環状の中間面９を平面状に展開して示している。当該実施例に係る密封装置１は両回転シールであって、以下のように構成されている。 Second embodiment ...
FIG. 6 shows a cross section of the main part of a sealing device (oil seal) 1 according to the second embodiment of the present invention. FIG. 7A shows an enlarged view of the main part of FIG. FIG. 7 (B) is a view in the direction of the arrow I in FIG. 7 (A), and shows an annular intermediate surface 9 developed in a planar shape. The sealing device 1 according to the embodiment is a double-rotating seal and is configured as follows.

すなわち先ず図６に示すように、金属環２に被着（加硫接着）されたゴム状弾性体３によって外周シール部４およびダストリップ５などとともに軸（相手部材、図示せず）の周面に摺動自在に密接するシールリップ６が設けられており、このシールリップ６の先端摺動部に密封流体側斜面７および反密封流体側斜面８が設けられ、両斜面７，８の間に中間面（フラット面）９が設けられている。中間面９は円筒面状に形成され、軸挿入時、軸の周面と全面に亙って接触するが、図７（Ａ）に示すようにその初期状態（軸挿入前の自由状態）において密封流体側Ｃに傾斜角度θ_１をもつ傾斜面状（円錐面状）のものであっても良い。傾斜角度θ_１の大きさとしては、０〜２０度が好適であり、０．１〜１０度が一層好適である。これにより中間面９はその反密封流体側Ｄの部位（後記する円周上連続する接触部１５）で軸の周面に強く接触する。 That is, first, as shown in FIG. 6, a peripheral surface of a shaft (a mating member, not shown) together with an outer peripheral seal portion 4 and a dust lip 5 by a rubber-like elastic body 3 adhered (vulcanized and bonded) to a metal ring 2. A seal lip 6 that is slidably in contact with the seal lip 6 is provided, and a sealing fluid side inclined surface 7 and an anti-sealing fluid side inclined surface 8 are provided at the tip sliding portion of the seal lip 6. An intermediate surface (flat surface) 9 is provided. The intermediate surface 9 is formed in a cylindrical surface shape and contacts the entire surface of the shaft when the shaft is inserted, but in its initial state (free state before shaft insertion) as shown in FIG. inclined surface shape at the sealed fluid side C having an inclination angle theta ₁ may be of (conical shape). As a magnitude | size of inclination | tilt angle (theta) ₁ , 0-20 degree is suitable and 0.1-10 degree is still more suitable. As a result, the intermediate surface 9 strongly contacts the peripheral surface of the shaft at a portion on the anti-sealing fluid side D (a contact portion 15 that continues on the circumference described later).

反密封流体側斜面８に、軸が正方向に回転（正回転、図７（Ａ）における矢印Ｅ）するときにポンピング作用によって密封流体を密封流体側Ｃへ押し戻す作用を奏する正ネジ部１０が設けられ、また軸が逆方向に回転（逆回転、図７（Ａ）における矢印Ｆ）するときにポンピング作用によって密封流体を密封流体側Ｃへ押し戻す作用を奏する逆ネジ部１１が設けられている。 On the anti-sealing fluid side inclined surface 8, there is a positive screw portion 10 that acts to push the sealing fluid back to the sealing fluid side C by a pumping action when the shaft rotates in the positive direction (forward rotation, arrow E in FIG. 7A). Also provided is a reverse screw portion 11 that acts to push the sealing fluid back to the sealing fluid side C by a pumping action when the shaft rotates in the reverse direction (reverse rotation, arrow F in FIG. 7A). .

凹部１２の底面のうち軸が正回転Ｅするときに回転方向の前方となる部位１２ｃは、このときの回転方向Ｅの前方へ向けて深さが徐々に浅くなる傾斜面状に設定されている（以下、「一方の傾斜底面１２ｃ」とも称する）。すなわち凹部１２の底面のうち軸が正回転Ｅするときに回転方向の前方となる部位には、このときの回転方向Ｅの前方へ向けて深さが徐々に浅くなる傾斜面状の一方の傾斜底面１２ｃが形成されている。また凹部１２の底面のうち軸が逆回転Ｆするときに回転方向の前方となる部位１２ｄは、このときの回転方向Ｆの前方へ向けて深さが徐々に浅くなる傾斜面状に設定されている（以下、「他方の傾斜底面１２ｄ」とも称する）。すなわち凹部１２の底面のうち軸が逆回転Ｆするときに回転方向の前方となる部位には、このときの回転方向Ｆの前方へ向けて深さが徐々に浅くなる傾斜面状の他方の傾斜底面１２ｄが形成されている。したがって凹部１２は円周方向両端に互いに反対向きの傾斜底面１２ｃ，１２ｄを有しているので、全体として図７（Ｂ）に示すように断面三角形状に形成され、この三角形状の左右の斜辺（傾斜底面１２ｃ，１２ｄ）がそれぞれ端部で中間面９に連なっている。また凹部１２の平面形状は長方形状とされ、その反密封流体側縁辺は底面からの立ち上がり面とされ、密封流体側縁辺は密封流体側Ｃへ向けての開口部とされている。凹部１２の底面は両傾斜底面１２ｃ，１２ｄ二面の組み合わせよりなるが、図７（Ｃ）に示すように中間面９と平行な平行面１２ｅが両傾斜底面１２ｃ，１２ｄの間に第三面として設けられても良い。また一方の傾斜底面１２ｃの傾斜角度θ_４と他方の傾斜底面１２ｄの傾斜角度θ_５とは互いに同じに設定されているが（θ_４＝θ_５）、図７（Ｄ）に示すように互いに異なるように設定されても良い（θ_４≠θ_５，すなわちθ_４＞θ_５またはθ_４＜θ_５）。この図７（Ｄ）の例では、θ_４＞θ_５に設定された凹部１２Ｃと、θ_４＜θ_５に設定された凹部１２Ｄとが円周上交互に設けられている。 Of the bottom surface of the recess 12, the portion 12 c that is forward in the rotational direction when the shaft rotates forward E is set to have an inclined surface that gradually decreases in depth toward the front in the rotational direction E at this time. (Hereinafter also referred to as “one inclined bottom surface 12c”). That is, in the bottom surface of the recess 12, one of the inclined surface-shaped slopes whose depth gradually decreases toward the front in the rotational direction E at the front portion in the rotational direction when the shaft rotates forward E. A bottom surface 12c is formed. Further, a portion 12d which is the front in the rotation direction when the shaft rotates in the reverse direction F on the bottom surface of the recess 12 is set to have an inclined surface shape whose depth gradually decreases toward the front in the rotation direction F at this time. (Hereinafter also referred to as “the other inclined bottom surface 12d”). That is, in the bottom surface of the concave portion 12, the portion that becomes the front in the rotation direction when the shaft rotates in the reverse direction F, the other inclination of the inclined surface shape whose depth gradually decreases toward the front in the rotation direction F at this time. A bottom surface 12d is formed. Accordingly, since the recess 12 has inclined bottom surfaces 12c and 12d opposite to each other at both ends in the circumferential direction, the recess 12 is formed in a triangular shape as shown in FIG. 7B as a whole. (Inclined bottom surfaces 12c and 12d) are connected to the intermediate surface 9 at their respective ends. The planar shape of the recess 12 is a rectangular shape, its anti-sealing fluid side edge is a rising surface from the bottom surface, and the sealing fluid side edge is an opening toward the sealing fluid side C. The bottom surface of the recess 12 is a combination of two inclined bottom surfaces 12c and 12d. As shown in FIG. 7C, a parallel surface 12e parallel to the intermediate surface 9 is a third surface between the inclined bottom surfaces 12c and 12d. It may be provided as. Although the inclination angle theta ₅ of the inclination angle theta ₄ and the other inclined bottom surface 12d of one of the inclined bottom surface 12c is set to be equal to each other (θ _{4 =} θ _5), to each other as shown in FIG. 7 (D) They may be set differently (θ ₄ ≠ θ ₅ , that is, θ ₄ > θ ₅ or θ ₄ <θ ₅ ). In the example of FIG. 7D, the recesses 12C set to θ ₄ > θ ₅ and the recesses 12D set to θ ₄ <θ ₅ are alternately provided on the circumference.

すなわち上記密封装置１が装着されると一部の密封流体が境界部１３に開口する開口部から凹部１２に取り込まれ、軸が正回転Ｅすると凹部１２に取り込まれた密封流体はその粘性によって軸の正回転Ｅに引き摺られ、凹部１２底面に設けた一方の傾斜底面１２ｃに沿って流れて集束し（凹部１２の断面積が徐々に小さくなるため）、集束しつつ凹部１２から中間面９ないし接触部１５へ溢出し、中間面９ないし接触部１５上で厚い流体膜を形成する。圧力としては中間面９ないし接触部１５を軸から浮かす動圧が発生する。また、図８に示すように軸が逆回転Ｆすると凹部１２に取り込まれた密封流体はその粘性によって軸の逆回転Ｆに引き摺られ、凹部１２底面に設けた他方の傾斜底面１２ｄに沿って流れて集束し（凹部１２の断面積が徐々に小さくなるため、矢印Ｋ）、集束しつつ凹部１２から中間面９ないし接触部１５へ溢出し、中間面９ないし接触部１５上で厚い流体膜を形成する。圧力としては中間面９ないし接触部１５を軸から浮かす動圧が発生する。したがって軸が正回転Ｅするときも逆回転Ｆするときも中間面９ないし接触部１５上に厚い流体膜が形成され動圧が発生するので、何れの場合も流体潤滑にもとづく低トルク化を実現し、シールリップ６が早期に摺動摩耗するのを抑制することができる。中間面９に設けられた接触部１５は円周上連続したものであって軸の周面に全周に亙って密接するので、軸回転静止時の漏洩（いわゆる静止漏れ）を抑制することもできる。 That is, when the sealing device 1 is mounted, a part of the sealing fluid is taken into the concave portion 12 from the opening portion that opens to the boundary portion 13, and when the shaft rotates in the forward direction E, the sealing fluid taken into the concave portion 12 has a shaft due to its viscosity. Of the recess 12 and flows along one inclined bottom surface 12c provided on the bottom surface of the recess 12 (because the cross-sectional area of the recess 12 is gradually reduced). Overflowing to the contact portion 15, a thick fluid film is formed on the intermediate surface 9 or the contact portion 15. As the pressure, a dynamic pressure for floating the intermediate surface 9 or the contact portion 15 from the shaft is generated. Further, as shown in FIG. 8, when the shaft rotates in the reverse direction F, the sealing fluid taken into the recess 12 is dragged by the viscosity of the shaft in the reverse rotation F and flows along the other inclined bottom surface 12d provided on the bottom surface of the recess 12. (The arrow K) because the cross-sectional area of the concave portion 12 gradually decreases, overflows from the concave portion 12 to the intermediate surface 9 through the contact portion 15 while converging, and a thick fluid film is formed on the intermediate surface 9 through the contact portion 15. Form. As the pressure, a dynamic pressure for floating the intermediate surface 9 or the contact portion 15 from the shaft is generated. Therefore, a thick fluid film is formed on the intermediate surface 9 or the contact portion 15 when the shaft rotates in the forward direction E or in the reverse direction F, so that dynamic pressure is generated. In any case, a reduction in torque based on fluid lubrication is realized. In addition, it is possible to suppress the sliding lip 6 from sliding and wearing at an early stage. The contact portion 15 provided on the intermediate surface 9 is continuous on the circumference and is in close contact with the circumferential surface of the shaft over the entire circumference, so that leakage at the time of stationary shaft rotation (so-called stationary leakage) is suppressed. You can also.

尚、凹部１２の形状については、その機能（正回転および逆回転の双方につきそれぞれ流体を集束して動圧を発生させること）を果たすかぎり、様々なものが考えられる。 Various shapes of the concave portion 12 are conceivable as long as they fulfill their functions (concentrate fluids for both forward rotation and reverse rotation to generate dynamic pressure).

すなわち、上記第二実施例では凹部１２の平面形状を長方形状としたが、その機能を発揮するのは一対の傾斜底面１２ｃ，１２ｄであるので、このような傾斜底面１２ｃ，１２ｄを有するかぎり凹部１２の形状は限定されない。例えば図９の例では、凹部１２の平面形状は長方形状に代えて台形状とされ、この台形状において、凹部１２の縁辺（凹部１２および中間面９の境界線）のうち軸が正回転Ｅするときに回転方向の前方となる部位１２ａは、反密封流体側Ｄから密封流体側Ｃへかけてこのときの回転方向Ｅの前方へ傾斜する向きに設定されている。また凹部１２の縁辺のうち軸が逆回転Ｆするときに回転方向の前方となる部位１２ｂは、反密封流体側Ｄから密封流体側Ｃへかけてこのときの回転方向Ｆの前方へ傾斜する向きに設定されている。 That is, in the second embodiment, the concave portion 12 has a rectangular planar shape. However, since the function is performed by the pair of inclined bottom surfaces 12c and 12d, the concave portion 12 has the inclined bottom surfaces 12c and 12d. The shape of 12 is not limited. For example, in the example of FIG. 9, the planar shape of the recess 12 is a trapezoid instead of a rectangle, and in this trapezoidal shape, the axis of the edge of the recess 12 (the boundary line between the recess 12 and the intermediate surface 9) is rotated forward E. In this case, the portion 12a that is forward in the rotational direction is set to be inclined in the forward direction in the rotational direction E from the anti-sealing fluid side D to the sealing fluid side C. Further, a portion 12b which is the front in the rotational direction when the shaft rotates in the reverse direction F on the edge of the recess 12 is inclined in the forward direction in the rotational direction F from the anti-sealing fluid side D to the sealing fluid side C. Is set to

凹部１２の形状としては、凹部１２底面の少なくとも一部に傾斜を付けることにより、正回転方向Ｅについてはその前方へ向けて凹部１２の断面積（密封装置１の中心軸線を含む各平面で裁断したときの断面積）が徐々に縮小する形状であれば良く、逆回転方向Ｆについてもその前方へ向けて凹部１２の断面積（密封装置１の中心軸線を含む各平面で裁断したときの断面積）が徐々に縮小する形状であれば良い。また凹部１２および両ネジ部１０，１１の円周方向位置関係としては上記したように、正ネジ部１０（例えば図７（Ａ）における３つの正ネジ部１０のうち左側の正ネジ部１０）とその正回転方向Ｅの後方側に配置された逆ネジ部１１（例えば図７（Ａ）における３つの逆ネジ部１１のうち右側の逆ネジ部１１）との間に凹部１２（例えば図７（Ａ）における３つの凹部１２のうち中央の凹部１２）を配置するのが好適である。 As the shape of the recess 12, at least a part of the bottom surface of the recess 12 is inclined so that the forward rotation direction E is cut forward in the cross-sectional area of the recess 12 (each plane including the central axis of the sealing device 1). The cross-sectional area at the time of cutting may be a shape that gradually decreases, and the cross-sectional area of the recess 12 in the reverse rotation direction F (cutting when cut in each plane including the central axis of the sealing device 1) Any shape can be used as long as the area is gradually reduced. Further, as described above, the circumferential positional relationship between the concave portion 12 and the screw portions 10 and 11 is the positive screw portion 10 (for example, the left positive screw portion 10 of the three positive screw portions 10 in FIG. 7A). And a concave portion 12 (for example, FIG. 7) between the reverse screw portion 11 (for example, the right reverse screw portion 11 of the three reverse screw portions 11 in FIG. 7A) arranged on the rear side in the forward rotation direction E. It is preferable to arrange the central recess 12) among the three recesses 12 in (A).

本発明の第一実施例に係る密封装置の要部断面図Sectional drawing of the principal part of the sealing device which concerns on 1st Example of this invention. （Ａ）は図１の要部拡大図、（Ｂ）は凹部の他の形状例を示す図(A) is an enlarged view of the main part of FIG. 1, (B) is a diagram showing another example of the concave shape 同密封装置の作動説明図Operation explanatory diagram of the sealing device （Ａ）および（Ｂ）とも凹部の他の形状例を示す図The figure which shows the other example of a shape of a recessed part with (A) and (B) 凹部の他の形状例を示す図The figure which shows the other example of a recessed part shape 本発明の第二実施例に係る密封装置の要部断面図Sectional drawing of the principal part of the sealing device which concerns on 2nd Example of this invention. （Ａ）は図６の要部拡大図、（Ｂ）は図７（Ａ）におけるＩ方向矢視図、（Ｃ）および（Ｄ）はそれぞれ凹部の他の形状例を示す図6A is an enlarged view of the main part of FIG. 6, FIG. 7B is a view taken in the direction of the arrow I in FIG. 7A, and FIGS. （Ａ）は同密封装置の作動説明図、（Ｂ）は図８（Ａ）におけるＪ方向矢視図(A) is an operation explanatory view of the sealing device, (B) is a view in the direction of arrow J in FIG. 8 (A). 凹部の他の形状例を示す図The figure which shows the other example of a recessed part shape 従来例に係る密封装置の要部断面図Sectional drawing of the principal part of the sealing device which concerns on a prior art example

符号の説明Explanation of symbols

１密封装置
２金属環
３ゴム状弾性体
４外周シール部
５ダストリップ
６シールリップ
７密封流体側斜面
８反密封流体側斜面
９中間面
１０正ネジ部
１０ａ，１１ａ反密封流体側端部
１０ｂ，１１ｂ密封流体側端部
１１逆ネジ部
１２凹部
１２ａ，１２ｂ傾斜縁辺
１２ｃ，１２ｄ傾斜底面
１２ｅ平行面
１３，１４境界部
１５接触部 DESCRIPTION OF SYMBOLS 1 Sealing device 2 Metal ring 3 Rubber-like elastic body 4 Peripheral seal part 5 Dustrip 6 Seal lip 7 Sealed fluid side inclined surface 8 Anti-sealed fluid side inclined surface 9 Middle surface 10 Positive thread part 10a, 11a Anti-sealed fluid side end part 10b, 11b Sealed fluid side end portion 11 Reverse screw portion 12 Recessed portion 12a, 12b Inclined edge 12c, 12d Inclined bottom surface 12e Parallel surface 13, 14 Boundary portion 15 Contact portion

Claims

回転軸等の相手部材が正逆両方向に相対回転する密封装置であって、
前記相手部材の周面に摺動自在に密接するシールリップを有し、
前記シールリップは、密封流体側斜面および反密封流体側斜面ならびに前記両斜面の間に設けられた中間面を有し、
前記相手部材が正方向に回転するときにポンピング作用によって密封流体を押し戻す作用を奏する正ネジ部と、前記相手部材が逆方向に回転するときにポンピング作用によって密封流体を押し戻す作用を奏する逆ネジ部とが前記反密封流体側斜面に設けられ、
前記中間面に凹部が設けられ、前記凹部は前記中間面および反密封流体側斜面の境界部に達しないように設けられて前記中間面における前記凹部の反密封流体側の部位に円周上連続する前記相手部材に対する接触部が設けられ、
前記凹部の縁辺のうち前記相手部材が正方向に回転するときに回転方向の前方となる部位は少なくともその一部が密封流体側から反密封流体側へかけてこのときの回転方向の前方へ傾斜する向きに設定され、
前記凹部の縁辺のうち前記相手部材が逆方向に回転するときに回転方向の前方となる部位は少なくともその一部が密封流体側から反密封流体側へかけてこのときの回転方向の前方へ傾斜する向きに設定されていることを特徴とする密封装置。 A sealing device in which a mating member such as a rotating shaft relatively rotates in both forward and reverse directions,
Having a seal lip slidably in contact with the peripheral surface of the mating member;
The sealing lip has a sealing fluid side slope and an anti-sealing fluid side slope and an intermediate surface provided between the slopes,
A normal screw portion that acts to push back the sealing fluid by a pumping action when the counterpart member rotates in the forward direction, and a reverse screw portion that acts to push back the sealing fluid by a pumping action when the counterpart member rotates in the reverse direction Are provided on the anti-seal fluid side slope,
A concave portion is provided on the intermediate surface, and the concave portion is provided so as not to reach a boundary portion between the intermediate surface and the anti-seal fluid side inclined surface, and is continuous on the circumference at a portion of the intermediate surface on the anti-seal fluid side of the recess. A contact portion for the mating member is provided,
Of the edge of the recess, at least a part of the portion that is forward in the rotational direction when the counterpart member rotates in the forward direction is inclined forward in the rotational direction from the sealed fluid side to the anti-sealed fluid side. Is set to the orientation
At least a part of the edge of the recess that is forward in the rotational direction when the counterpart member rotates in the reverse direction is inclined forward from the sealed fluid side to the anti-sealed fluid side. A sealing device characterized in that the sealing device is set in an orientation.

回転軸等の相手部材が正逆両方向に相対回転する密封装置であって、
前記相手部材の周面に摺動自在に密接するシールリップを有し、
前記シールリップは、密封流体側斜面および反密封流体側斜面ならびに前記両斜面の間に設けられた中間面を有し、
前記相手部材が正方向に回転するときにポンピング作用によって密封流体を押し戻す作用を奏する正ネジ部と、前記相手部材が逆方向に回転するときにポンピング作用によって密封流体を押し戻す作用を奏する逆ネジ部とが前記反密封流体側斜面に設けられ、
前記中間面に凹部が設けられ、前記凹部は前記中間面および反密封流体側斜面の境界部に達しないように設けられて前記中間面における前記凹部の反密封流体側の部位に円周上連続する前記相手部材に対する接触部が設けられ、
前記凹部の底面のうち前記相手部材が正方向に回転するときに回転方向の前方となる部位は少なくともその一部がこのときの回転方向の前方へ向けて深さが徐々に浅くなる傾斜面状に設定され、
前記凹部の縁辺のうち前記相手部材が逆方向に回転するときに回転方向の前方となる部位は少なくともその一部がこのときの回転方向の前方へ向けて深さが徐々に浅くなる傾斜面状に設定されていることを特徴とする密封装置。 A sealing device in which a mating member such as a rotating shaft relatively rotates in both forward and reverse directions,
Having a seal lip slidably in contact with the peripheral surface of the mating member;
The sealing lip has a sealing fluid side slope and an anti-sealing fluid side slope and an intermediate surface provided between the slopes,
A normal screw portion that acts to push back the sealing fluid by a pumping action when the counterpart member rotates in the forward direction, and a reverse screw portion that acts to push back the sealing fluid by a pumping action when the counterpart member rotates in the reverse direction Are provided on the anti-seal fluid side slope,
A concave portion is provided on the intermediate surface, and the concave portion is provided so as not to reach a boundary portion between the intermediate surface and the anti-seal fluid side inclined surface, and is continuous on the circumference at a portion of the intermediate surface on the anti-seal fluid side of the recess. A contact portion for the mating member is provided,
Of the bottom surface of the recess, at least a part of the bottom portion of the concave portion that is forward in the rotational direction when the counterpart member rotates in the forward direction is inclined so that the depth gradually decreases toward the front in the rotational direction at this time. Set to
Of the edge of the recess, at least part of the part that is forward in the rotational direction when the counterpart member rotates in the reverse direction is an inclined surface whose depth gradually decreases toward the forward in the rotational direction at this time. The sealing device characterized by being set to.