JP5194647B2 - Seal ring - Google Patents

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JP5194647B2
JP5194647B2 JP2007225235A JP2007225235A JP5194647B2 JP 5194647 B2 JP5194647 B2 JP 5194647B2 JP 2007225235 A JP2007225235 A JP 2007225235A JP 2007225235 A JP2007225235 A JP 2007225235A JP 5194647 B2 JP5194647 B2 JP 5194647B2
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peripheral surface
sealing target
shaft hole
seal ring
target fluid
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JP2009058028A (en
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弘明 門馬
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Nok Corp
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Description

本発明は、２部材間の環状隙間をシールするためのシールリングに関するものである。   The present invention relates to a seal ring for sealing an annular gap between two members.

図４に示すのは、断面矩形のシールリングであり、図５に示すような回転継ぎ手における軸シールとして、あるいは、特許文献に示すようなパワーステアリングにおけるコントロールバルブ用シールとして用いられている。図４は、従来技術に係るシールリングの模式的断面図である。図５は、回転継ぎ手の一部切り欠き模式的斜視断面図である。   FIG. 4 shows a seal ring having a rectangular cross section, which is used as a shaft seal in a rotary joint as shown in FIG. 5 or as a control valve seal in a power steering as shown in Patent Literature. FIG. 4 is a schematic cross-sectional view of a seal ring according to the prior art. FIG. 5 is a schematic perspective cross-sectional view of a rotary joint partially cut away.

シールリング１００は、ハウジング２００の軸孔２０１と、該軸孔２０１に挿入され、ハウジング２００に対して回転・揺動運動をする軸３００と、の間の環状隙間をシールするものである。   The seal ring 100 seals an annular gap between the shaft hole 201 of the housing 200 and the shaft 300 that is inserted into the shaft hole 201 and rotates and swings relative to the housing 200.

図４（ａ）に示すように、シールリング１００は、軸３００の外周面に設けられた環状溝３０１に装着され、密封対象流体側Ｏから受ける圧力Ｐにより、その外周面１０１がハウジング２００の軸孔２０１内周面に密着し、非密封対象流体側Ａの側面１０２が環状溝３０１の側壁面３１０に密着する。これにより、密封対象流体の非密封対象流体側Ａへの漏れを防止している。   As shown in FIG. 4A, the seal ring 100 is mounted in an annular groove 301 provided on the outer peripheral surface of the shaft 300, and the outer peripheral surface 101 of the housing 200 is caused by the pressure P received from the fluid to be sealed O. The side surface 102 on the non-sealing target fluid side A is in close contact with the side wall surface 310 of the annular groove 301. Thereby, the leakage to the non-sealing target fluid side A of the sealing target fluid is prevented.

また、軸３００の回転・揺動運動時においては、シールリング１００は、基本的に外周面１０１がハウジング２００の軸孔２０１内周面に密着して軸３００に対して静止した状態となり、側面１０２が軸３００の環状溝３０１の側壁面３１０に対して摺動する構成となっている。すなわち、ハウジング２００と軸３００との相対回転においては、シールリング１００は、ハウジング２００と供回りするように構成されている。
実開平４−１１０６７３号公報 Further, during the rotation / oscillation movement of the shaft 300, the seal ring 100 is basically in a state where the outer peripheral surface 101 is in close contact with the inner peripheral surface of the shaft hole 201 of the housing 200 and is stationary with respect to the shaft 300. 102 is configured to slide with respect to the side wall surface 310 of the annular groove 301 of the shaft 300. That is, the seal ring 100 is configured to rotate with the housing 200 in the relative rotation between the housing 200 and the shaft 300.
Japanese Utility Model Laid-Open No. 4-110673

油圧が作用する前の状態においては、シールリング１００は、環状溝３０１に対して自由な状態で装着されているため、必ずしも非密封対象流体側Ａに押し込まれた状態となっているわけではない。すなわち、側面１０２が必ずしも環状溝３０１の側壁面３１０に密着しているわけではない。したがって、装着時においてシールリング１００が密封対象流体側Ｏに位置している場合には、油圧を受けてシールリング１００が非密封対象流体側Ａに向かって軸方向に移動し、側面１０２が環状溝３０１の側壁面３１０に密着する状態となる。   In a state before the hydraulic pressure is applied, the seal ring 100 is mounted in a free state with respect to the annular groove 301 and is not necessarily pushed into the non-sealing target fluid side A. . That is, the side surface 102 is not necessarily in close contact with the side wall surface 310 of the annular groove 301. Therefore, when the seal ring 100 is positioned on the sealing target fluid side O at the time of mounting, the seal ring 100 moves in the axial direction toward the non-sealing target fluid side A by receiving hydraulic pressure, and the side surface 102 is annular. The groove 301 is in close contact with the side wall surface 310.

しかしながら、シールリング１００の外周面１０１とハウジング２００の軸孔２０１内周面との間の摺動抵抗の度合によっては、油圧が作用してもシールリング１００が完全に非密封対象流体側Ａに押し込められずに環状溝３０１の側壁面３１０との間に隙間が生じ、図４（ｂ）に矢印で示すような漏れ経路が形成されることがある。   However, depending on the degree of sliding resistance between the outer peripheral surface 101 of the seal ring 100 and the inner peripheral surface of the shaft hole 201 of the housing 200, the seal ring 100 is completely moved to the non-sealing target fluid side A even when hydraulic pressure is applied. A gap may be formed between the annular groove 301 and the side wall surface 310 without being pushed in, and a leakage path as indicated by an arrow in FIG. 4B may be formed.

例えば、図５に示す回転継ぎ手においては、図中の矢印で示す流路に加わる圧力をシールリング１００によって密封することで油の流路を確保しているが、上述のような漏れ経路が形成されてしまうと、油の流路を確保することが困難となってしまう。   For example, in the rotary joint shown in FIG. 5, the oil flow path is secured by sealing the pressure applied to the flow path indicated by the arrow in the figure with the seal ring 100, but the above-described leakage path is formed. If it does, it will become difficult to ensure the flow path of oil.

また、軸回転時における動圧の発生やハウジング２００及び軸３００の偏心等による環状隙間の変化等が生じた場合でも、ハウジング２００及び軸３００に対するシールリング
１００の密着状態は維持されなければならない（ハウジング及び軸に対する追随性）。 Further, even when a dynamic pressure is generated during shaft rotation or a change in the annular gap due to eccentricity of the housing 200 and the shaft 300 occurs, the close contact state of the seal ring 100 with respect to the housing 200 and the shaft 300 must be maintained ( Followability to housing and shaft).

従来においては、シールリングの外径寸法や厚さ（外周面の半径寸法と内周面の半径寸法との差）を調整することによって、油圧応答性の向上（油圧が作用してからシールリングが漏れ経路を遮断するまでに要する時間を短くすること）や追随性の向上を図ってきたが、さらなる向上が望まれている。   Conventionally, by adjusting the outer diameter and thickness of the seal ring (difference between the radial dimension of the outer peripheral surface and the radial dimension of the inner peripheral surface), the hydraulic response is improved (the seal ring after the hydraulic pressure is applied). Has shortened the time required to block the leakage path) and improved followability, but further improvements are desired.

本発明は上記の従来技術の課題を解決するためになされたもので、その目的とするところは、相手部材に対する追随性及び油圧応答性の高いシールリングを提供することにある。   The present invention has been made in order to solve the above-described problems of the prior art, and an object of the present invention is to provide a seal ring having high followability to a mating member and high hydraulic response.

上記目的を達成するために、本発明におけるシールリングは、
軸孔を有するハウジングと前記軸孔に挿入される軸のうち軸の外周面に設けられた環状溝に軸方向に移動可能に装着され、
密封対象流体から受ける圧力によって、前記軸孔の内周面に密着するとともに、前記環状溝の非密封対象流体側の側壁面に摺動接触することにより、前記軸とハウジング間の環状隙間をシールするシールリングにおいて、
密封対象流体から非密封対象流体側かつ前記軸孔の内周面側の方向の圧力を受けるように構成された受圧凹部を有し、
シールリングの非密封対象流体側の側面は、前記環状溝の溝底側が前記軸孔の内周面側に対して非密封対象流体側に突出したテーパ状の傾斜面であることを特徴とする。
In order to achieve the above object, the seal ring in the present invention comprises:
A housing having a shaft hole and a shaft inserted into the shaft hole are attached to an annular groove provided on the outer peripheral surface of the shaft so as to be movable in the axial direction.
The annular gap between the shaft and the housing is sealed by being in close contact with the inner peripheral surface of the shaft hole by the pressure received from the fluid to be sealed and slidingly contacting the side wall surface of the annular groove on the non-sealing target fluid side. In the seal ring to
A pressure receiving recess configured to receive a pressure in the direction of the non-sealing target fluid side and the inner peripheral surface side of the shaft hole from the sealing target fluid;
The side surface on the non-sealing target fluid side of the seal ring is a tapered inclined surface in which the groove bottom side of the annular groove protrudes toward the non-sealing target fluid side with respect to the inner peripheral surface side of the shaft hole. .

このように、シールリングが受圧凹部で密封対象流体から非密封対象流体側かつ他方の部材側方向に圧力を受けることより、シールリングの軸及びハウジングに対する追随性が向上されるとともに、油圧作動時におけるシールリングの軸方向の移動がスムーズとなって漏れ経路の形成が抑制される。   Thus, the seal ring receives pressure from the fluid to be sealed toward the non-sealing fluid side and the other member in the pressure receiving recess, thereby improving the followability of the seal ring to the shaft and the housing, and at the time of hydraulic operation. The movement of the seal ring in the axial direction is smooth and the formation of a leakage path is suppressed.

また、環状溝の側壁面に対しては、テーパ状に構成された非密封対象流体側の傾斜側面における環状溝の溝底側の縁部が摺動する構成となる。したがって、シールリングの環状溝に対する摺動抵抗が低減され、回転トルクの低減、摺動時における発熱や摩耗の低減を図ることができる。   Moreover, it becomes the structure which the edge part by the side of the groove | channel of the annular groove in the inclined side surface by the side of the non-sealing object fluid comprised in the taper shape slides with respect to the side wall surface of an annular groove. Therefore, sliding resistance with respect to the annular groove of the seal ring is reduced, and it is possible to reduce rotational torque and heat generation and wear during sliding.

前記受圧凹部は、
シールリングにおける密封対象流体側であって前記環状溝の溝底側の部分に設けられ、非密封対象流体側かつ前記軸孔の内周面側の方向に向かって凹んだ凹部であり、
前記軸孔の内周面に密着する周面の反対側に設けられ、軸方向に沿って延びる受圧周面と、
前記非密封対象流体側の側面の反対側に設けられ、該側面に沿ってテーパ状に延びる受圧傾斜面と、を有するとよい。
The pressure receiving recess is
A recessed portion that is provided on a portion of the seal groove on the fluid bottom side of the annular groove on the groove bottom side, and is recessed toward the non-sealing target fluid side and the inner peripheral surface of the shaft hole ;
A pressure receiving peripheral surface provided on the opposite side of the peripheral surface closely contacting the inner peripheral surface of the shaft hole, and extending along the axial direction;
It is good to have a pressure receiving inclined surface provided on the opposite side of the side surface on the non-sealing target fluid side and extending in a tapered shape along the side surface.

かかる構成によれば、密封対象流体から、受圧周面によって径方向に他方の部材側の方向の圧力を受け、受圧傾斜面によって軸方向に対して他方の部材側に傾いた方向、すなわち、非密封対象流体側かつ他方の部材側の方向の圧力を受ける。したがって、これらの圧力の合力により、シールリングには非密封対象流体側かつ他方の部材側の方向の力が作用し、軸及びハウジングに対する追随性が向上される。   According to this configuration, the pressure in the radial direction from the fluid to be sealed is received by the pressure receiving circumferential surface in the direction of the other member, and the direction inclined by the pressure receiving inclined surface toward the other member side with respect to the axial direction, It receives pressure in the direction of the fluid to be sealed and the direction of the other member. Therefore, due to the resultant force of these pressures, a force in the direction of the non-sealing target fluid side and the other member side acts on the seal ring, and the followability to the shaft and the housing is improved.

上記目的を達成するために、本発明におけるシールリングは、
軸孔を有するハウジングと前記軸孔に挿入される軸のうち軸の外周面に設けられた環状溝に軸方向に移動可能に装着され、
密封対象流体側から受ける圧力によって、前記軸孔の内周面に密着するとともに、前記環状溝の非密封対象流体側の側壁面に摺動接触することにより、前記軸とハウジング間の環状隙間をシールするシールリングにおいて、
前記軸孔の内周面に密着するシール周面と、該シール周面の反対側に設けられ密封対象
流体から前記軸孔の内周面側の方向の圧力を受ける受圧周面と、有する筒状部と、
前記筒状部の非密封対象流体側の端部から前記環状溝の溝底側に向かって、径方向に対して非密封対象流体側に斜めの方向に突出し、密封対象流体側及び非密封対象流体側の両側面がテーパ状の傾斜面に構成された突出部と、を備え、
前記突出部の非密封対象流体側の側面における前記環状溝の溝底側の縁部が、前記環状溝の側壁面に摺動接触し、
前記突出部の密封対象流体側の側面が、密封対象流体から非密封対象流体側かつ前記軸孔の内周面側の方向の圧力を受けることを特徴とする。 In order to achieve the above object, the seal ring in the present invention comprises:
A housing having a shaft hole and a shaft inserted into the shaft hole are attached to an annular groove provided on the outer peripheral surface of the shaft so as to be movable in the axial direction.
Due to the pressure received from the sealing target fluid side, the annular clearance between the shaft and the housing is reduced by closely contacting the inner peripheral surface of the shaft hole and slidingly contacting the side wall surface of the annular groove on the non-sealing target fluid side. In the seal ring to seal,
A cylinder having a seal peripheral surface that is in close contact with the inner peripheral surface of the shaft hole , and a pressure receiving peripheral surface that is provided on the opposite side of the seal peripheral surface and receives pressure in a direction toward the inner peripheral surface side of the shaft hole from a fluid to be sealed And
From the end of the cylindrical portion on the non-sealing target fluid side toward the groove bottom side of the annular groove, the cylindrical portion protrudes obliquely toward the non-sealing target fluid side with respect to the radial direction, and the sealing target fluid side and the non-sealing target A projecting portion in which both side surfaces on the fluid side are configured as tapered inclined surfaces;
The groove bottom side edge of the annular groove on the non-sealing target fluid side surface of the protrusion is in sliding contact with the side wall surface of the annular groove,
The side surface of the projecting portion on the side of the fluid to be sealed receives pressure from the fluid to be sealed in the direction toward the fluid to be sealed and on the inner peripheral surface side of the shaft hole .

このように、筒状部の受圧周面が、密封対象流体から他方の部材側の方向の圧力を受け、突出部の密封対象流体側の傾斜側面が、密封対象流体から非密封対象流体側かつ他方の部材側の方向、すなわち、軸方向に対して他方の部材側に傾いた方向の圧力を受けることにより、シールリングには、これらの圧力の合力による非密封対象流体側かつ他方の部材側の方向の力が作用する。これにより、シールリングの軸及びハウジングに対する追随性及び油圧応答性が向上される。   Thus, the pressure-receiving peripheral surface of the cylindrical portion receives pressure in the direction of the other member from the fluid to be sealed, and the inclined side surface of the protrusion on the side of the fluid to be sealed is from the fluid to be sealed to the non-sealing target fluid side and By receiving the pressure in the direction of the other member, that is, in the direction inclined to the other member with respect to the axial direction, the seal ring has a non-sealed fluid side and the other member side due to the resultant force of these pressures. The force in the direction of Thereby, the followability and hydraulic response to the shaft and housing of the seal ring are improved.

また、環状溝の側壁面に対しては、テーパ状に構成された非密封対象流体側の傾斜側面における環状溝の溝底側の縁部が摺動する構成となり、シールリングの環状溝に対する摺動抵抗が低減される。したがって、回転トルクの低減、摺動時の発熱や摩耗の低減が図られる。   In addition, with respect to the side wall surface of the annular groove, the edge portion on the groove bottom side of the annular groove on the inclined side surface on the non-sealing target fluid side formed in a tapered shape slides, and the seal ring slides with respect to the annular groove. Dynamic resistance is reduced. Therefore, it is possible to reduce rotational torque and heat generation and wear during sliding.

以上説明したように、本発明により、相手部材に対する追随性及び油圧応答性が向上する。   As described above, according to the present invention, the followability to the counterpart member and the hydraulic response are improved.

以下に図面を参照して、この発明を実施するための最良の形態を、実施例に基づいて例示的に詳しく説明する。ただし、この実施例に記載されている構成部品の寸法、材質、形状、その相対配置などは、特に特定的な記載がない限りは、この発明の範囲をそれらのみに限定する趣旨のものではない。   The best mode for carrying out the present invention will be exemplarily described in detail below with reference to the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention only to those unless otherwise specified. .

（実施例）
図１〜図３を参照して、本発明の実施例に係るシールリング１について説明する。図１は、本実施例に係るシールリング１の構成を示す模式図であり、（ａ）がシールリング１を軸方向からみた様子を示し、（ｂ）が（ａ）のＡ−Ａ断面を示している。図２は、本実施例に係るシールリング１の装着状態を示す模式的断面図である。図３は、本実施例に係るシールリング１の寸法形状を説明する模式的断面図である。 (Example)
With reference to FIGS. 1-3, the seal ring 1 which concerns on the Example of this invention is demonstrated. 1A and 1B are schematic views showing the configuration of a seal ring 1 according to the present embodiment, in which FIG. 1A shows a state of the seal ring 1 viewed from the axial direction, and FIG. 1B shows an AA cross section of FIG. Show. FIG. 2 is a schematic cross-sectional view showing a mounted state of the seal ring 1 according to the present embodiment. FIG. 3 is a schematic cross-sectional view illustrating the dimensional shape of the seal ring 1 according to the present embodiment.

図１に示すように、シールリング１は、断面略Ｌ字形の樹脂材料からなる環状部材である。シールリング１の材料としては、例えば、充填剤入りＰＴＦＥやＰＡ（ポリアミド）等を挙げることができる。   As shown in FIG. 1, the seal ring 1 is an annular member made of a resin material having a substantially L-shaped cross section. Examples of the material of the seal ring 1 include PTFE containing filler and PA (polyamide).

図２に示すように、シールリング１は、ハウジング２と、ハウジング２の軸孔２０に挿入された軸３との間の環状隙間４をシールするためのものであり、軸３の外周面に設けられた環状溝３０に装着されて使用される。本実施例に係るシールリング１は、例えば、図５に示すような回転継ぎ手の軸シールや、パワーステアリングのコントロールバルブ用シ
ール等の回転・揺動用シールとして用いることができる。 As shown in FIG. 2, the seal ring 1 is for sealing an annular gap 4 between the housing 2 and the shaft 3 inserted into the shaft hole 20 of the housing 2. It is used by being attached to the annular groove 30 provided. The seal ring 1 according to this embodiment can be used as a rotation / swing seal such as a shaft seal of a rotary joint as shown in FIG. 5 or a control valve seal of a power steering.

シールリング１は、軸方向に円筒状に延びる筒状部１０と、筒状部１０の非密封対象流体側Ａの端部から軸中心に向かって、径方向に対して非密封対象流体側Ａ（筒状部１０とは反対側）に傾いた方向に突出する突出部１１と、から構成されている。そして、筒状部１０と突出部１１とが劣角を形成する部分に、非密封対象流体側Ａかつハウジング２側の方向に向かって凹んだ受圧凹部１２が形成されている。   The seal ring 1 includes a cylindrical portion 10 that extends in a cylindrical shape in the axial direction, and a non-sealing target fluid side A with respect to the radial direction from the end of the cylindrical portion 10 on the non-sealing target fluid side A toward the axial center. And a projecting portion 11 projecting in a direction inclined to the side opposite to the cylindrical portion 10. And the pressure-receiving recessed part 12 dented toward the direction of the non-sealing object fluid side A and the housing 2 side is formed in the part in which the cylindrical part 10 and the protrusion part 11 form an inferior angle.

シールリング１は、密封対象流体側Ｏ（図中下側）から作用する油圧（図中矢印Ｐ）により、非密封対象流体側Ａ（図中上側）に押される。そして、筒状部１０の外周面１３が、軸孔２０の内周面２１に密着し、突出部１１の非密封対象流体側Ａの傾斜側面（テーパ面）１４の内径側の縁部１５が環状溝３０の側壁面３１に密着する。これにより、密封対象流体の非密封対象流体側Ａへの漏れが抑制される。   The seal ring 1 is pushed to the non-sealing target fluid side A (upper side in the figure) by hydraulic pressure (arrow P in the figure) acting from the sealing target fluid side O (lower side in the figure). And the outer peripheral surface 13 of the cylindrical part 10 closely_contact | adheres to the inner peripheral surface 21 of the shaft hole 20, and the edge part 15 by the side of the inner diameter side of the inclination side surface (taper surface) 14 of the non-sealing target fluid side A of the protrusion part 11 exists. It closely contacts the side wall surface 31 of the annular groove 30. Thereby, the leakage to the non-sealing target fluid side A of the sealing target fluid is suppressed.

また、軸３の回転・揺動運動時においては、シールリング１は、外周面１３がハウジング２の軸孔内周面２１に密着し、傾斜側面１４の縁部１５が軸３の環状溝３０の側壁面３１に対して摺動する。すなわち、ハウジング２と軸３との相対回転においては、シールリング１は基本的にハウジング２と供回りするように構成されている。   Further, when the shaft 3 rotates or swings, the outer peripheral surface 13 of the seal ring 1 is in close contact with the inner peripheral surface 21 of the shaft hole of the housing 2, and the edge 15 of the inclined side surface 14 is the annular groove 30 of the shaft 3. It slides with respect to the side wall surface 31. That is, the seal ring 1 is basically configured to rotate with the housing 2 in the relative rotation between the housing 2 and the shaft 3.

受圧凹部１２は、筒状部１０の内周面１６と、突出部１１の密封対象流体側の傾斜側面（テーパ面）１７と、から構成されている。図２に示すように、内周面１６は、密封対象流体から外径方向、すなわち、ハウジング２の軸孔内周面２１側に向かう方向の圧力を受け、テーパ面１７は、概ね軸方向であって、若干軸方向に対して外径側に傾いた方向の圧力を受ける。したがって、シールリング１には、図２において矢印Ｑで示すように、内周面１６、テーパ面１７で受ける圧力の合力によって、ハウジング２の軸孔内周面２１側かつ非密封対象流体側Ａの方向に作用する力が発生する。   The pressure receiving recess 12 includes an inner peripheral surface 16 of the tubular portion 10 and an inclined side surface (tapered surface) 17 of the protruding portion 11 on the fluid to be sealed side. As shown in FIG. 2, the inner peripheral surface 16 receives pressure in the outer diameter direction from the fluid to be sealed, that is, in the direction toward the shaft hole inner peripheral surface 21 side of the housing 2, and the tapered surface 17 is substantially in the axial direction. Therefore, it receives a pressure in a direction slightly inclined toward the outer diameter side with respect to the axial direction. Therefore, as shown by an arrow Q in FIG. 2, the seal ring 1 has a shaft hole inner peripheral surface 21 side of the housing 2 and a non-sealing target fluid side A by the resultant force of the pressure received by the inner peripheral surface 16 and the tapered surface 17. A force acting in the direction of is generated.

この合力の作用によって、シールリング１のハウジング２及び軸３に対する追随性が向上される。また、油圧作動時におけるシールリング１の軸方向の移動がスムーズとなり、シールリング１と環状溝３０の側壁面３１との接触状態をより確実に形成することができる。したがって、漏れ経路の形成を防止することができ、また、油圧応答性が向上されることにより、油圧が作用する前の密封対象流体側Ｏと非密封対象流体側Ａとが連通した状態から、油圧が作用してシールリング１と環状溝３０の側壁面３１とが接触する密封状態となるまでの時間が短縮される。すなわち、漏れ経路が形成された状態を迅速に解消することができる。したがって、漏れ経路を介しての吹き抜け漏れを低減することができ、また、例えば、図５に示す回転継ぎ手においては、油の流路の確保をより確実に行うことができる。   By the action of this resultant force, the followability of the seal ring 1 to the housing 2 and the shaft 3 is improved. Moreover, the axial movement of the seal ring 1 during the hydraulic operation becomes smooth, and the contact state between the seal ring 1 and the side wall surface 31 of the annular groove 30 can be more reliably formed. Therefore, it is possible to prevent the formation of a leakage path, and by improving the hydraulic pressure response, from the state where the sealing target fluid side O and the non-sealing target fluid side A before the hydraulic pressure is communicated with each other, The time until the sealing state in which the seal ring 1 and the side wall surface 31 of the annular groove 30 come into contact with each other by the hydraulic pressure is reduced. That is, the state where the leakage path is formed can be quickly eliminated. Therefore, blow-through leakage through the leakage path can be reduced, and, for example, in the rotary joint shown in FIG. 5, the oil flow path can be more reliably secured.

また、環状溝３０の側壁面３１に対しては、テーパ状に構成された非密封対象流体側の傾斜側面１４の縁部１５が摺動する構成となるので、シールリング１の環状溝３０に対する摺動抵抗が低減され、回転トルクの低減、摺動時における発熱や摩耗の低減を図ることができる。   In addition, since the edge 15 of the inclined side surface 14 on the non-sealing target fluid side configured in a tapered shape slides on the side wall surface 31 of the annular groove 30, The sliding resistance is reduced, and it is possible to reduce rotational torque and heat generation and wear during sliding.

また、突出部１１の先端側の縁部１５を環状溝３０の側壁面３１に摺動接触させる構成とすることで、従来技術に係るシールリップの先端が摺動面と接触する構成と同じような効果を得ることができ、ハウジング２及び軸３の偏心時等における摺動相手部材の挙動による影響が低減され、良好なシール性の維持が可能となる。   Further, by adopting a configuration in which the edge portion 15 on the distal end side of the projecting portion 11 is in sliding contact with the side wall surface 31 of the annular groove 30, it is the same as the configuration in which the distal end of the seal lip according to the prior art contacts the sliding surface. Thus, the influence of the behavior of the sliding mating member when the housing 2 and the shaft 3 are eccentric is reduced, and good sealing performance can be maintained.

また、受圧凹部１２（傾斜側面１７）で受ける圧力によって縁部１５を支点として生じるモーメント等の影響により、縁部１５における環状溝３０の側壁面３１に対する密着性
が向上される。したがって、縁部１５によって構成される摺動シール部のシール性が向上される。 Moreover, the adhesiveness with respect to the side wall surface 31 of the annular groove 30 in the edge part 15 improves by the influence of the moment etc. which produce the edge part 15 as a fulcrum by the pressure received in the pressure receiving recessed part 12 (inclined side surface 17). Therefore, the sealing performance of the sliding seal portion constituted by the edge portion 15 is improved.

また、シールリング１の非密封対象流体側Ａの側面１４のうち環状溝３０の開口部側の領域は、環状溝３０の開口部の縁部から離れた構成となっているため、シールリング１の一部が軸孔２０の表面２１と軸３の表面との間に噛み込み等を生じるのが防止される。   Further, the region on the opening side of the annular groove 30 in the side surface 14 on the non-sealing target fluid side A of the seal ring 1 is configured to be separated from the edge of the opening portion of the annular groove 30. Is prevented from being caught between the surface 21 of the shaft hole 20 and the surface of the shaft 3.

次に、図３を参照して、本実施例に係るシールリング１の寸法形状について詳しく説明する。ここでは、シールリング１が装着される環状溝３０が従来と同じ仕様である場合における、シールリング１の寸法形状の好ましい一例を示す。したがって、相手部材の仕様等が異なる場合にはシールリングの寸法形状も当然変更されるものであり、その場合は以下に示すものに限られるものではない。   Next, with reference to FIG. 3, the dimension shape of the seal ring 1 which concerns on a present Example is demonstrated in detail. Here, a preferable example of the dimensional shape of the seal ring 1 in the case where the annular groove 30 in which the seal ring 1 is mounted has the same specifications as the conventional one is shown. Therefore, when the specifications of the mating member are different, the dimensions and shape of the seal ring are naturally changed. In that case, the shape is not limited to the following.

まず、シールリング１の全体の高さ（軸方向の幅）Ｈ１及び肉厚（最も外側の外周面の半径寸法と最も内側の内周面の半径寸法との差）Ｔ１はそれぞれ１．９５ｍｍ、１．７ｍｍである。これは、従来の矩形断面のシールリングと同じ設定である。   First, the overall height (axial width) H1 and thickness (difference between the radial dimension of the outermost outer peripheral surface and the radial dimension of the innermost inner peripheral surface) T1 of the seal ring 1 are 1.95 mm, 1.7 mm. This is the same setting as a conventional seal ring having a rectangular cross section.

次に、筒状部１０の外周面１３の高さ（軸方向の幅）Ｈ２は、１．６５ｍｍ、筒状部１０の肉厚Ｔ２は、０．８ｍｍ、突出部１１の軸方向の幅Ｈ３は、０．８ｍｍである。また、筒状部１０の内周面１６と突出部１１のテーパ面１７とがなす角度αは、１００°、テーパ面１４が径方向に対してなす角度βは、１０°となっている。このテーパ面１４の角度βは、角度βによって形成される高さ（Ｈ１−Ｈ２）がシールリング高さ（Ｈ１）に対して１０〜２０％の範囲となるように設定するのが好ましい。なお、上記各寸法の寸法公差は±０．０５ｍｍとする。   Next, the height (axial width) H2 of the outer peripheral surface 13 of the cylindrical portion 10 is 1.65 mm, the thickness T2 of the cylindrical portion 10 is 0.8 mm, and the axial width H3 of the protruding portion 11. Is 0.8 mm. Further, the angle α formed by the inner peripheral surface 16 of the cylindrical portion 10 and the tapered surface 17 of the protruding portion 11 is 100 °, and the angle β formed by the tapered surface 14 with respect to the radial direction is 10 °. The angle β of the tapered surface 14 is preferably set so that the height (H1-H2) formed by the angle β is in the range of 10 to 20% with respect to the seal ring height (H1). The dimensional tolerance of each of the above dimensions is ± 0.05 mm.

このように、本実施例に係るシールリング１は、受圧凹部１２を設けることにより、従来の矩形断面のシールリングと比べてボリュームが小さくなっており、ボリュームに対する受圧面の面積の比率が従来と比べて増加している。したがって、従来のシールリングに比して相手部材に対する追随性及び油圧応答性が向上される。   As described above, the seal ring 1 according to the present embodiment is provided with the pressure receiving recess 12 so that the volume is smaller than that of the conventional seal ring having a rectangular cross section. Compared to the increase. Therefore, the followability to the counterpart member and the hydraulic response are improved as compared with the conventional seal ring.

本実施例に係るシールリングの構成を示す模式図。The schematic diagram which shows the structure of the seal ring which concerns on a present Example. 本実施例に係るシールリングの装着状態を示す模式的断面図。The typical sectional view showing the wearing state of the seal ring concerning this example. 本実施例に係るシールリングの模式的断面図。The typical sectional view of the seal ring concerning this example. 従来技術に係るシールリングの模式的断面図。The typical sectional view of the seal ring concerning a prior art. 回転継ぎ手の一部切り欠き模式的斜視断面図。FIG. 3 is a schematic perspective cross-sectional view of a rotary joint partially cut away.

符号の説明Explanation of symbols

１ シールリング
１０ 筒状部
１１ 突出部
１２ 受圧凹部
１３ 外周面
１４ 傾斜側面
１５ 縁部
１６ 内周面
１７ 傾斜側面
２ ハウジング
２０ 軸孔
２１ 内周面
３ 軸
３０ 環状溝
３１ 側壁面
４ 環状隙間 DESCRIPTION OF SYMBOLS 1 Seal ring 10 Cylindrical part 11 Protrusion part 12 Pressure receiving recessed part 13 Outer peripheral surface 14 Inclined side surface 15 Edge part 16 Inner peripheral surface 17 Inclined side surface 2 Housing 20 Shaft hole 21 Inner peripheral surface 3 Shaft 30 Annular groove 31 Side wall surface 4 Annular gap

Claims (3)

軸孔を有するハウジングと前記軸孔に挿入される軸のうち軸の外周面に設けられた環状溝に軸方向に移動可能に装着され、
密封対象流体から受ける圧力によって、前記軸孔の内周面に密着するとともに、前記環状溝の非密封対象流体側の側壁面に摺動接触することにより、前記軸とハウジング間の環状隙間をシールするシールリングにおいて、
密封対象流体から非密封対象流体側かつ前記軸孔の内周面側の方向の圧力を受けるように構成された受圧凹部を有し、
シールリングの非密封対象流体側の側面は、前記環状溝の溝底側が前記軸孔の内周面側に対して非密封対象流体側に突出したテーパ状の傾斜面であることを特徴とするシールリング。 A housing having a shaft hole and a shaft inserted into the shaft hole are attached to an annular groove provided on the outer peripheral surface of the shaft so as to be movable in the axial direction.
The annular gap between the shaft and the housing is sealed by being in close contact with the inner peripheral surface of the shaft hole by the pressure received from the fluid to be sealed and slidingly contacting the side wall surface of the annular groove on the non-sealing target fluid side. In the seal ring to
A pressure receiving recess configured to receive a pressure in the direction of the non-sealing target fluid side and the inner peripheral surface side of the shaft hole from the sealing target fluid;
The side surface on the non-sealing target fluid side of the seal ring is a tapered inclined surface in which the groove bottom side of the annular groove protrudes toward the non-sealing target fluid side with respect to the inner peripheral surface side of the shaft hole. Seal ring. 前記受圧凹部は、
シールリングにおける密封対象流体側であって前記環状溝の溝底側の部分に設けられ、非密封対象流体側かつ前記軸孔の内周面側の方向に向かって凹んだ凹部であり、
前記軸孔の内周面に密着する周面の反対側に設けられ、軸方向に沿って延びる受圧周面と、
前記非密封対象流体側の側面の反対側に設けられ、該側面に沿ってテーパ状に延びる受圧傾斜面と、を有することを特徴とする請求項１に記載のシールリング。 The pressure receiving recess is
A recessed portion that is provided on a portion of the seal groove on the fluid bottom side of the annular groove on the groove bottom side, and is recessed toward the non-sealing target fluid side and the inner peripheral surface of the shaft hole ;
A pressure receiving peripheral surface provided on the opposite side of the peripheral surface closely contacting the inner peripheral surface of the shaft hole, and extending along the axial direction;
2. The seal ring according to claim 1, further comprising: a pressure-receiving inclined surface that is provided on a side opposite to the side surface on the non-sealing target fluid side and extends in a tapered shape along the side surface. 軸孔を有するハウジングと前記軸孔に挿入される軸のうち軸の外周面に設けられた環状溝に軸方向に移動可能に装着され、
密封対象流体側から受ける圧力によって、前記軸孔の内周面に密着するとともに、前記環状溝の非密封対象流体側の側壁面に摺動接触することにより、前記軸とハウジング間の環状隙間をシールするシールリングにおいて、
前記軸孔の内周面に密着するシール周面と、該シール周面の反対側に設けられ密封対象流体から前記軸孔の内周面側の方向の圧力を受ける受圧周面と、有する筒状部と、
前記筒状部の非密封対象流体側の端部から前記環状溝の溝底側に向かって、径方向に対して非密封対象流体側に斜めの方向に突出し、密封対象流体側及び非密封対象流体側の両側面がテーパ状の傾斜面に構成された突出部と、を備え、
前記突出部の非密封対象流体側の側面における前記環状溝の溝底側の縁部が、前記環状
溝の側壁面に摺動接触し、
前記突出部の密封対象流体側の側面が、密封対象流体から非密封対象流体側かつ前記軸孔の内周面側の方向の圧力を受けることを特徴とするシールリング。 A housing having a shaft hole and a shaft inserted into the shaft hole are attached to an annular groove provided on the outer peripheral surface of the shaft so as to be movable in the axial direction.
Due to the pressure received from the sealing target fluid side, the annular clearance between the shaft and the housing is reduced by closely contacting the inner peripheral surface of the shaft hole and slidingly contacting the side wall surface of the annular groove on the non-sealing target fluid side. In the seal ring to seal,
A cylinder having a seal peripheral surface that is in close contact with the inner peripheral surface of the shaft hole , and a pressure receiving peripheral surface that is provided on the opposite side of the seal peripheral surface and receives pressure in a direction toward the inner peripheral surface side of the shaft hole from a fluid to be sealed And
From the end of the cylindrical portion on the non-sealing target fluid side toward the groove bottom side of the annular groove, the cylindrical portion protrudes obliquely toward the non-sealing target fluid side with respect to the radial direction, and the sealing target fluid side and the non-sealing target A projecting portion in which both side surfaces on the fluid side are configured as tapered inclined surfaces;
The groove bottom side edge of the annular groove on the non-sealing target fluid side surface of the protrusion is in sliding contact with the side wall surface of the annular groove,
The seal ring, wherein a side surface of the projecting portion on the side of the fluid to be sealed receives pressure from the fluid to be sealed in the direction of the fluid to be sealed and on the inner peripheral surface side of the shaft hole .
JP2007225235A 2007-08-31 2007-08-31 Seal ring Expired - Fee Related JP5194647B2 (en)

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KR101749955B1 (en) * 2015-08-31 2017-06-26 비전네이처(주) Direct receiving type water purifier
KR20190124968A (en) * 2018-04-27 2019-11-06 권오선 Direct receiving type water purifier

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JP7307474B2 (en) * 2019-11-20 2023-07-12 有限会社飯田製作所 Sealing member, manufacturing method thereof, and airtight sliding mechanism
CN113236781B (en) * 2021-04-15 2022-04-15 大连理工大学 Sealing ring with antifriction and heat dissipation structure on end face and machining method thereof

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JPS5817936Y2 (en) * 1979-03-20 1983-04-12 三菱重工業株式会社 bearing device
JPS5822564U (en) * 1981-08-05 1983-02-12 三菱重工業株式会社 Sealing device
JP2001090843A (en) * 1999-09-24 2001-04-03 Eagle Ind Co Ltd Shaft sealing device
JP4736394B2 (en) * 2004-10-15 2011-07-27 Ｎｏｋ株式会社 Seal ring
JP4952179B2 (en) * 2005-10-03 2012-06-13 Ｎｏｋ株式会社 Seal structure

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KR101749955B1 (en) * 2015-08-31 2017-06-26 비전네이처(주) Direct receiving type water purifier
KR20190124968A (en) * 2018-04-27 2019-11-06 권오선 Direct receiving type water purifier
KR102069803B1 (en) 2018-04-27 2020-01-28 권오선 Direct receiving type water purifier

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