JP2009236177A - Sealing structure - Google Patents

Sealing structure Download PDF

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JP2009236177A
JP2009236177A JP2008081156A JP2008081156A JP2009236177A JP 2009236177 A JP2009236177 A JP 2009236177A JP 2008081156 A JP2008081156 A JP 2008081156A JP 2008081156 A JP2008081156 A JP 2008081156A JP 2009236177 A JP2009236177 A JP 2009236177A
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sealing device
shaft
annular groove
sealing
housing
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Kazunori Jinbo
一憲 神保
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Nok Corp
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Nok Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a sealing structure which keeps a stable sealing performance, and plans to suppress mechanical loss. <P>SOLUTION: The sealing structure is characterized in that on one side surface of an annular groove 61, a projection 62 including a slant surface 62a inclining from a groove bottom side to a surface of a shaft 50 as it goes from the one side surface side to the other side surface side, is arranged, a sealing device 10 extends from the one side surface side to the other side surface side, and provides a seal lip 12 slidably contacting the surface of the shaft 50, and near a lip root of the seal lip 12, a slant surface 12b closely contacting the slant surface 62a in the projection 62 at fluid pressure application is formed. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、軸とハウジングに設けられた軸孔との間の環状隙間を密封する密封構造に関するものである。   The present invention relates to a sealing structure that seals an annular gap between a shaft and a shaft hole provided in a housing.

自動車，建設機械及び産業機械などにおいては、各種油圧・空圧機器が用いられている。油圧・空圧機器においては、軸とハウジングに設けられた軸孔との間の環状隙間を密封する密封装置が設けられる。   Various hydraulic and pneumatic devices are used in automobiles, construction machinery, industrial machinery, and the like. In a hydraulic / pneumatic device, a sealing device is provided for sealing an annular gap between a shaft and a shaft hole provided in the housing.

図７〜図９を参照して、かかる密封装置の一例を説明する。図７は従来例に係る密封装置の模式的断面図である。図８は従来例に係る密封装置を装着した状態（密封流体の圧力による負荷がない場合）を示す模式的断面図である。図９は従来例に係る密封装置を装着した状態（密封流体の圧力による負荷がある場合）を示す模式的断面図である。なお、図示の密封装置１００は、油圧・空圧機器に好適に用いられる往復動用のＵ型パッキンである。   An example of such a sealing device will be described with reference to FIGS. FIG. 7 is a schematic cross-sectional view of a conventional sealing device. FIG. 8 is a schematic cross-sectional view showing a state in which a sealing device according to a conventional example is mounted (when there is no load due to the pressure of the sealing fluid). FIG. 9 is a schematic cross-sectional view showing a state in which a sealing device according to a conventional example is mounted (when there is a load due to the pressure of the sealing fluid). The illustrated sealing device 100 is a reciprocating U-shaped packing that is preferably used in hydraulic and pneumatic equipment.

ここで、図７においては、密封装置１００には外力が作用していない場合の状態を示しており、軸１５０とハウジング１６０との寸法関係が分かるように、軸１５０とハウジング１６０については点線で示している。   Here, FIG. 7 shows a state where no external force is applied to the sealing device 100, and the shaft 150 and the housing 160 are indicated by dotted lines so that the dimensional relationship between the shaft 150 and the housing 160 can be understood. Show.

図示の例においては、密封装置１００は、ハウジング１６０の軸孔内周面に形成された環状溝１６１に装着される。そして、密封装置１００は、環状溝１６１の溝底面に密着する外周シール部（第１シール部）１１０と、軸１５０の表面に摺動自在に接触するシールリップ（第２シール部）１２０とを備えている。   In the illustrated example, the sealing device 100 is mounted in an annular groove 161 formed on the inner peripheral surface of the shaft hole of the housing 160. The sealing device 100 includes an outer peripheral seal portion (first seal portion) 110 that is in close contact with the groove bottom surface of the annular groove 161, and a seal lip (second seal portion) 120 that is slidably in contact with the surface of the shaft 150. I have.

密封装置１００における外周側は、その全域にわたって、外径が環状溝１６１の溝底面の内径よりも大きくなるように設定されている（図７参照）。従って、密封装置１００が環状溝１６１に装着された状態では、密封装置１００の外周側の全面が、環状溝１６１の溝底面に密着する（図８参照）。一方、密封装置１００における内周側は、シールリップ１２０のリップ先端付近のみ、内径が軸１５０の径よりも小さくなるように設定されている（図７参照）。従って、密封装置１００を環状溝１６１に装着した状態であって、流体圧力による負荷がない場合には、シールリップ１２０の先端付近のみが、軸１５０の表面に密着する（図８参照）。   The outer peripheral side of the sealing device 100 is set so that the outer diameter is larger than the inner diameter of the groove bottom surface of the annular groove 161 over the entire region (see FIG. 7). Therefore, in a state where the sealing device 100 is mounted in the annular groove 161, the entire outer surface of the sealing device 100 is in close contact with the groove bottom surface of the annular groove 161 (see FIG. 8). On the other hand, the inner peripheral side of the sealing device 100 is set so that the inner diameter is smaller than the diameter of the shaft 150 only in the vicinity of the lip tip of the seal lip 120 (see FIG. 7). Accordingly, when the sealing device 100 is mounted in the annular groove 161 and there is no load due to fluid pressure, only the vicinity of the end of the seal lip 120 is in close contact with the surface of the shaft 150 (see FIG. 8).

図示の従来例では、使用状態においては、図中左側の圧力が、流体圧力（油圧や空圧）によって高くなるように構成されている。すなわち、使用状態においては、図９に示すように、密封装置１００を介して左側が高圧（Ｈ）となり、右側が低圧（Ｌ）となる。   In the illustrated conventional example, the pressure on the left side in the figure is configured to be increased by the fluid pressure (hydraulic pressure or pneumatic pressure) in the use state. That is, in the use state, as shown in FIG. 9, the left side becomes high pressure (H) and the right side becomes low pressure (L) through the sealing device 100.

従って、使用状態においては、密封装置１００は流体圧力によって環状溝１６１内において、低圧（Ｌ）側に押し付けられる。これにより、密封装置１００の低圧（Ｌ）側の端面は、環状溝１６１の低圧（Ｌ）側側面に密着する。また、流体圧力によって、外周シール部１１０は環状溝１６１の溝底面側に押し付けられ、シールリップ１２０は軸１５０の表面側に押し付けられる。   Therefore, in a use state, the sealing device 100 is pressed to the low pressure (L) side in the annular groove 161 by the fluid pressure. Thereby, the low pressure (L) side end surface of the sealing device 100 is in close contact with the low pressure (L) side surface of the annular groove 161. Further, the outer peripheral seal portion 110 is pressed against the groove bottom surface side of the annular groove 161 by the fluid pressure, and the seal lip 120 is pressed against the surface side of the shaft 150.

以上のように、従来例に係る密封装置１００においては、流体圧力によって、シールリップ１２０が軸１５０の表面に押し付けられる。そのため、シールリップ１２０における軸１５０への接触面積が大きくなり、緊迫力（接触圧力）が高くなる。そして、これに伴
って、摺動抵抗が高くなり、機械的損失が大きくなってしまう。 As described above, in the sealing device 100 according to the conventional example, the seal lip 120 is pressed against the surface of the shaft 150 by the fluid pressure. For this reason, the contact area of the seal lip 120 with the shaft 150 increases, and the tightening force (contact pressure) increases. Along with this, the sliding resistance increases and the mechanical loss increases.

また、流体圧力によって、密封装置１００が環状溝１６１の低圧（Ｌ）側に押し付けられることで、その一部（ヒール部Ｘ）が、軸１５０とハウジング１６０の軸孔との間の隙間にはみ出してしまう現象が生じる。このようなはみ出し現象が生じた場合には、軸１５０との摺動時において、特に軸偏心が生じた場合などに、ヒール部Ｘが破損してしまうことがある。そのため、破損した部分が異物となって漏れの原因となったり、面圧分布の変化に伴って密封性能を低下させる原因となったりしてしまう。   Further, when the sealing device 100 is pressed against the low pressure (L) side of the annular groove 161 by the fluid pressure, a part (heel portion X) thereof protrudes into the gap between the shaft 150 and the shaft hole of the housing 160. Phenomenon occurs. When such a protrusion phenomenon occurs, the heel portion X may be damaged when the shaft 150 is slid, particularly when shaft eccentricity occurs. For this reason, the damaged portion becomes a foreign matter and causes leakage, or causes a decrease in sealing performance with changes in the surface pressure distribution.

なお、関連する技術としては、特許文献１〜３に開示されたものがある。
実公昭５８−１４２７３号公報 実開平５−３７３８号公報 特開２００２−１３６４４号公報 In addition, as a related technique, there exists what was disclosed by patent documents 1-3.
Japanese Utility Model Publication No. 58-14273 Japanese Utility Model Publication No. 5-3738 JP 2002-13644 A

本発明の目的は、安定した密封性能を維持しつつ、機械的損失の抑制を図った密封構造を提供することにある。   The objective of this invention is providing the sealing structure which aimed at suppression of mechanical loss, maintaining the stable sealing performance.

本発明は、上記課題を解決するために以下の手段を採用した。   The present invention employs the following means in order to solve the above problems.

すなわち、本発明の密封構造は、
軸と、
該軸が挿通される軸孔を有するハウジングと、
前記軸及びハウジングのうちの一方の部材に形成された環状溝に装着され、これら軸とハウジングに設けられた軸孔との間に形成される環状隙間を密封する密封装置と、
を備える密封構造において、
前記環状溝における一方の側面には、一方の側面側から他方の側面側に向かうにつれて、溝底側から前記軸及びハウジングのうちの他方の部材表面に向かって傾斜する傾斜面を有する突起部が設けられており、
前記密封装置は、
前記環状溝の溝底面に密着する第１シール部と、
前記一方の側面側から他方の側面側に向かって伸びて、前記他方の部材表面に摺動自在に接触するリップ状の第２シール部と、
を備えており、
第２シール部におけるリップの根本付近には、前記他方の側面側から流体圧力を受けた際に、前記突起部における前記傾斜面に密着する傾斜面が形成されていることを特徴とする。 That is, the sealing structure of the present invention is
The axis,
A housing having a shaft hole through which the shaft is inserted;
A sealing device mounted in an annular groove formed in one member of the shaft and the housing and sealing an annular gap formed between the shaft and a shaft hole provided in the housing;
In a sealing structure comprising:
On one side surface of the annular groove, there is a protrusion having an inclined surface that is inclined from the groove bottom side toward the other member surface of the shaft and the housing from one side surface side to the other side surface side. Provided,
The sealing device includes:
A first seal portion closely contacting the groove bottom surface of the annular groove;
A lip-shaped second seal portion extending from the one side surface to the other side surface and slidably contacting the other member surface;
With
In the vicinity of the base of the lip in the second seal portion, an inclined surface is formed that is in close contact with the inclined surface of the projection when receiving fluid pressure from the other side surface side.

本発明の密封構造によれば、密封装置が流体圧力を受けた際には、第２シール部におけるリップの根本付近の傾斜面が、環状溝に設けられた突起部の傾斜面に密着する。そのため、リップ状の第２シール部は、流体圧力を受けている際に、リップの根本が環状溝に設けられた突起部によって支えられた状態となる。従って、第２シール部は、その姿勢が安定され、リップ先端付近のみが他方の部材表面に摺動自在な状態で接触することになる。これにより、摺動抵抗の増加を抑制できる。   According to the sealing structure of the present invention, when the sealing device receives fluid pressure, the inclined surface near the base of the lip in the second seal portion is in close contact with the inclined surface of the protrusion provided in the annular groove. Therefore, the lip-shaped second seal portion is in a state where the root of the lip is supported by the protrusion provided in the annular groove when receiving fluid pressure. Accordingly, the posture of the second seal portion is stabilized, and only the vicinity of the lip tip comes into contact with the other member surface in a slidable state. Thereby, the increase in sliding resistance can be suppressed.

また、環状溝に設けられた突起部の傾斜面は、環状溝における一方の側面側（低圧側）から他方の側面側（高圧側）に向かうにつれて、溝底側から軸及びハウジングのうちの他方の部材表面に向かって傾斜している。そのため、第２シール部が、突起部の傾斜面から
受ける抗力は、一方の側面側から他方の側面側に向かう方向の分力と、他方の部材表面から環状溝の溝底面に向かう方向の分力との合力となる。従って、第２シール部自体が一方の側面側から他方の側面側に向かって伸びた構成であることと相俟って、第２シール部の他方の部材に対する接触面積の増加を好適に抑制すると共に、第２シール部の一部が、軸とハウジングの軸孔との間の隙間にはみ出してしまうことを好適に抑制できる。 In addition, the inclined surface of the protrusion provided in the annular groove has the other side of the shaft and the housing from the groove bottom side toward the other side surface (high pressure side) from one side surface (low pressure side) of the annular groove. It inclines toward the member surface. Therefore, the drag force that the second seal portion receives from the inclined surface of the projection is a component force in a direction from one side surface to the other side surface and a component in a direction from the other member surface to the groove bottom surface of the annular groove. It becomes a combined force with power. Accordingly, in combination with the configuration in which the second seal portion itself extends from one side surface to the other side surface, an increase in the contact area of the second seal portion with the other member is suitably suppressed. At the same time, it is possible to suitably suppress a part of the second seal portion from protruding into the gap between the shaft and the shaft hole of the housing.

また、前記突起先端は湾曲面によって構成されており、
第２シール部には、前記他方の側面側から流体圧力を受けた際に、前記突起部先端の湾曲面に密着する湾曲面が形成されているとよい。 In addition, the protrusion tip is configured by a curved surface,
The second seal portion may be formed with a curved surface that comes into close contact with the curved surface at the tip of the protrusion when receiving fluid pressure from the other side surface.

これにより、突起部先端付近においても、第２シール部の姿勢を安定させることができると共に、突起部先端から受ける応力集中は緩和されるので、突起部先端によって第２シール部が破損してしまうことを抑制できる。   As a result, the posture of the second seal portion can be stabilized even in the vicinity of the tip of the projection, and the stress concentration received from the tip of the projection is alleviated, so that the second seal portion is damaged by the tip of the projection. This can be suppressed.

また、前記密封装置は、その断面形状が略Ｕ字形状のＵ型パッキンであり、
該Ｕ型パッキンのＵ溝部分における肉厚と、前記突起部の高さが略等しくなるように設定されているとよい。 The sealing device is a U-shaped packing having a substantially U-shaped cross section,
The thickness of the U groove portion of the U-shaped packing and the height of the protruding portion may be set to be substantially equal.

このように設定することで、第２シール部の姿勢を好適に安定させることができる。   By setting in this way, the posture of the second seal portion can be suitably stabilized.

以上説明したように、本発明によれば、安定した密封性能を維持しつつ、機械的損失の抑制を図ることができる。   As described above, according to the present invention, it is possible to suppress mechanical loss while maintaining stable sealing performance.

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１）
図１〜図４を参照して、本発明の実施例１に係る密封構造について説明する。 Example 1
With reference to FIGS. 1-4, the sealing structure which concerns on Example 1 of this invention is demonstrated.

＜密封装置＞
図１を参照して、本発明の実施例１に係る密封構造に用いられる密封装置について説明する。図１は本発明の実施例１に係る密封装置の模式的断面図である。本実施例に係る密封装置１０は、油圧・空圧機器に好適に用いられる往復動用のＵ型パッキンである。また、密封装置１０の素材としては、ウレタン樹脂やゴム材などを好適に適用できる。なお、図１においては、密封装置１０には外力が作用していない場合の状態を示しており、軸５０とハウジング６０との寸法関係（中心軸を一致させた状態における寸法関係）が分かるように、軸５０とハウジング６０については点線で示している。 <Sealing device>
With reference to FIG. 1, the sealing device used for the sealing structure which concerns on Example 1 of this invention is demonstrated. 1 is a schematic cross-sectional view of a sealing device according to Embodiment 1 of the present invention. The sealing device 10 according to the present embodiment is a reciprocating U-shaped packing that is preferably used in hydraulic and pneumatic equipment. Moreover, as a raw material of the sealing device 10, a urethane resin, a rubber material, etc. can be applied suitably. FIG. 1 shows a state where no external force is applied to the sealing device 10, so that the dimensional relationship between the shaft 50 and the housing 60 (the dimensional relationship when the central axes are matched) can be seen. The shaft 50 and the housing 60 are indicated by dotted lines.

本実施例に係る密封装置１０は、外周側に外周シール部（第１シール部）１１を備え、内周側にシールリップ（第２シール部）１２を備えている。シールリップ１２のリップ先端１２ａは、先端が尖った形状で構成されている。また、シールリップ１２の根本付近は、リップ先端１２ａに向かって縮径する傾斜面１２ｂが形成されており、その先端に環状凸部１２ｃが設けられている。この傾斜面１２ｂと環状凸部１２ｃは湾曲面１２ｄによって滑らかに接続されている。   The sealing device 10 according to the present embodiment includes an outer peripheral seal portion (first seal portion) 11 on the outer peripheral side, and a seal lip (second seal portion) 12 on the inner peripheral side. The lip tip 12a of the seal lip 12 is configured with a sharp tip. In addition, an inclined surface 12b whose diameter decreases toward the lip tip 12a is formed near the base of the seal lip 12, and an annular convex portion 12c is provided at the tip. The inclined surface 12b and the annular convex portion 12c are smoothly connected by a curved surface 12d.

＜密封装置を装着した状態＞
特に、図２を参照して、本発明の実施例１に係る密封装置１０を装着した状態について説明する。図２は本発明の実施例１に係る密封装置を装着した状態（密封流体の圧力による負荷がない場合）を示す模式的断面図である。 <State with sealing device>
In particular, with reference to FIG. 2, a state in which the sealing device 10 according to the first embodiment of the present invention is mounted will be described. FIG. 2 is a schematic cross-sectional view showing a state in which the sealing device according to Embodiment 1 of the present invention is mounted (when there is no load due to the pressure of the sealing fluid).

本実施例に係る密封装置１０は、軸５０とハウジング６０に設けられた軸孔（軸５０が挿通される孔）との間の環状隙間を密封するために用いられる。なお、本実施例においては、軸５０とハウジング６０は相対的に往復移動するように構成されており、密封装置１０と軸５０との間で摺動するように構成されている。   The sealing device 10 according to the present embodiment is used for sealing an annular gap between a shaft 50 and a shaft hole provided in the housing 60 (a hole through which the shaft 50 is inserted). In this embodiment, the shaft 50 and the housing 60 are configured to reciprocate relative to each other, and are configured to slide between the sealing device 10 and the shaft 50.

本実施例に係る密封装置１０は、ハウジング６０の軸孔内周面に形成された環状溝６１に装着される。そして、密封装置１０がこの環状溝６１に装着された状態においては、外周シール部１１が環状溝６１の溝底面に密着し、シールリップ１２が軸５０の表面に摺動自在な状態で接触した状態となる。   The sealing device 10 according to this embodiment is mounted in an annular groove 61 formed on the inner peripheral surface of the shaft hole of the housing 60. When the sealing device 10 is mounted in the annular groove 61, the outer peripheral seal portion 11 is in close contact with the groove bottom surface of the annular groove 61, and the seal lip 12 is in contact with the surface of the shaft 50 in a slidable state. It becomes a state.

ここで、本実施例に係る密封装置１０においては、その外周側は、その全域にわたって、外径が環状溝６１の溝底面の内径よりも大きくなるように設定されている（図１参照）。従って、密封装置１０が環状溝６１に装着された状態では、密封装置１０の外周側の全面が、環状溝６１の溝底面に密着する（図２参照）。一方、密封装置１０における内周側は、シールリップ１２のリップ先端付近のみ、内径が軸５０の径よりも小さくなるように設定されている（図１参照）。従って、密封装置１０が環状溝６１に装着された状態であって、流体圧力による負荷がない場合には、シールリップ１２の先端付近のみが、軸５０の表面に密着する（図２参照）。   Here, in the sealing device 10 according to the present embodiment, the outer peripheral side is set such that the outer diameter is larger than the inner diameter of the groove bottom surface of the annular groove 61 over the entire region (see FIG. 1). Therefore, in a state where the sealing device 10 is mounted in the annular groove 61, the entire outer surface of the sealing device 10 is in close contact with the groove bottom surface of the annular groove 61 (see FIG. 2). On the other hand, the inner peripheral side of the sealing device 10 is set so that the inner diameter is smaller than the diameter of the shaft 50 only in the vicinity of the lip tip of the seal lip 12 (see FIG. 1). Therefore, when the sealing device 10 is mounted in the annular groove 61 and there is no load due to fluid pressure, only the vicinity of the end of the seal lip 12 is in close contact with the surface of the shaft 50 (see FIG. 2).

また、本実施例においては、環状溝６１における一方の側面（使用時においては、低圧となる側の側面）には、一方の側面側から他方の側面側に向かって突き出た突起部６２が設けられている。   In the present embodiment, one side surface of the annular groove 61 (the side surface on the low pressure side in use) is provided with a protrusion 62 that protrudes from one side surface toward the other side surface. It has been.

この突起部６２は、一方の側面側から他方の側面側に向かうにつれて、環状溝６１の溝底側から軸５０の表面に向かって傾斜する傾斜面６２ａを有している。また、突起部６２の先端６２ｂは湾曲面によって構成されている。   The protrusion 62 has an inclined surface 62 a that is inclined from the groove bottom side of the annular groove 61 toward the surface of the shaft 50 as it goes from one side surface side to the other side surface side. Moreover, the front-end | tip 62b of the projection part 62 is comprised by the curved surface.

＜密封装置が流体圧力を受けた状態＞
特に、図３を参照して、本発明の実施例１に係る密封装置１０が流体圧力を受けた際の動作（各部の働き）について説明する。図３は本発明の実施例１に係る密封装置を装着した状態（密封流体の圧力による負荷がある場合）を示す模式的断面図である。 <The state where the sealing device is subjected to fluid pressure>
In particular, with reference to FIG. 3, the operation (function of each part) when the sealing device 10 according to the first embodiment of the present invention receives fluid pressure will be described. FIG. 3 is a schematic cross-sectional view showing a state in which the sealing device according to Embodiment 1 of the present invention is mounted (when there is a load due to the pressure of the sealing fluid).

本実施例では、使用状態においては、図中左側の圧力が、流体圧力（油圧や空圧）によって高くなるように構成されている。すなわち、使用状態においては、図３に示すように、密封装置１０を介して左側が高圧（Ｈ）となり、右側が低圧（Ｌ）となる。なお、高圧側には密封対象となる流体が密封される。低圧側においては、適用される油圧・空圧機器に応じて、高圧側と同様に密封対象流体による流体圧力が作用する場合もあるし、大気圧となる場合もある。また、適用される油圧・空圧機器に応じて、左側が常時高圧となる場合もあるし、間欠的に高圧となる場合もある。   In the present embodiment, in use, the pressure on the left side in the figure is configured to be increased by the fluid pressure (hydraulic pressure or pneumatic pressure). That is, in the use state, as shown in FIG. 3, the left side becomes high pressure (H) and the right side becomes low pressure (L) through the sealing device 10. Note that a fluid to be sealed is sealed on the high pressure side. On the low pressure side, depending on the applied hydraulic / pneumatic equipment, the fluid pressure by the fluid to be sealed may act as in the high pressure side, or it may become atmospheric pressure. Further, depending on the applied hydraulic / pneumatic equipment, the left side may be constantly at a high pressure or may be intermittently at a high pressure.

以上のような構成により、使用状態では、密封装置１０は流体圧力によって環状溝６１内において、低圧（Ｌ）側に押し付けられる。これにより、密封装置１０の低圧（Ｌ）側の端面は、環状溝６１の低圧（Ｌ）側側面に密着する。また、流体圧力によって、外周シール部１１は環状溝６１の溝底面側に押し付けられ、シールリップ１２は軸５０の表面側に向かって押し付けられる。   With the above configuration, the sealing device 10 is pressed against the low pressure (L) side in the annular groove 61 by the fluid pressure in the use state. Thereby, the low pressure (L) side end surface of the sealing device 10 is in close contact with the low pressure (L) side side surface of the annular groove 61. Further, the outer peripheral seal portion 11 is pressed against the groove bottom surface side of the annular groove 61 by the fluid pressure, and the seal lip 12 is pressed toward the surface side of the shaft 50.

そして、本実施例においては、流体圧力を受けて、密封装置１０が低圧（Ｌ）側に押し付けられると、シールリップ１２の根本付近に形成された傾斜面１２ｂが、環状溝６１に設けられた突起部６２の傾斜面６２ａに対して全面的に密着するように構成されている。また、このとき、シールリップ１２における、傾斜面１２ｂと環状凸部１２ｃとの間の湾曲面１２ｄも、湾曲面で構成された、突起部６２の先端６２ｂに密着するように構成されている。   In this embodiment, when the sealing device 10 is pressed against the low pressure (L) side under the fluid pressure, the annular groove 61 is provided with an inclined surface 12 b formed near the root of the seal lip 12. The protrusion 62 is configured to be in close contact with the inclined surface 62a. At this time, the curved surface 12d between the inclined surface 12b and the annular convex portion 12c in the seal lip 12 is also configured to be in close contact with the tip 62b of the protruding portion 62, which is configured by a curved surface.

また、本実施例においては、Ｕ型パッキンである密封装置１０におけるＵ溝部分における肉厚Ｗと、突起部６２の高さｈが略等しくなるように設定されている（図３参照）。そのため、流体圧力が作用している状態においては、シールリップ１２は、Ｕ溝部分よりも先端側のみが、軸５０の表面に向かって撓むように変形することになる。   In the present embodiment, the thickness W of the U groove portion of the sealing device 10 that is a U-shaped packing and the height h of the protrusion 62 are set to be substantially equal (see FIG. 3). Therefore, in a state where the fluid pressure is acting, the seal lip 12 is deformed so that only the distal end side of the U groove portion is bent toward the surface of the shaft 50.

＜本実施例の優れた点＞
本実施例に係る密封構造によれば、密封装置１０が流体圧力を受けた際には、シールリップ１２におけるリップの根本付近の傾斜面１２ｂが、環状溝６１に設けられた突起部６２の傾斜面６２ａに密着する。そのため、シールリップ１２は、流体圧力を受けている際に、リップの根本が環状溝６１に設けられた突起部６２によって支えられた状態となる。従って、シールリップ１２は、その姿勢が安定され、リップ先端１２ａ付近のみが軸５０の表面に摺動自在な状態で接触することになる。これにより、摺動抵抗の増加を抑制できる。 <Excellent points of this embodiment>
According to the sealing structure according to the present embodiment, when the sealing device 10 receives fluid pressure, the inclined surface 12b near the base of the lip in the seal lip 12 is inclined by the protrusion 62 provided in the annular groove 61. Adheres to the surface 62a. Therefore, the seal lip 12 is in a state where the root of the lip is supported by the projection 62 provided in the annular groove 61 when receiving the fluid pressure. Therefore, the posture of the seal lip 12 is stabilized, and only the vicinity of the lip tip 12a comes into contact with the surface of the shaft 50 in a slidable state. Thereby, the increase in sliding resistance can be suppressed.

また、環状溝６１に設けられた突起部６２の傾斜面６２ａは、環状溝６１における一方の側面側（使用時において低圧（Ｌ）側）から他方の側面側（使用時において高圧（Ｈ）側）に向かうにつれて、環状溝６１の溝底側から軸５０の表面に向かって傾斜している。そのため、シールリップ１２が、突起部６２の傾斜面６２ａから受ける抗力（図３中、矢印Ｆ）は、一方の側面側から他方の側面側に向かう方向の分力と、軸５０の表面から環状溝６１の溝底面に向かう方向の分力との合力となる。   Further, the inclined surface 62a of the protrusion 62 provided in the annular groove 61 is changed from one side surface side (low pressure (L) side in use) to the other side surface side (high pressure (H) side in use). ) Toward the surface of the shaft 50 from the groove bottom side of the annular groove 61. Therefore, the drag force (arrow F in FIG. 3) that the seal lip 12 receives from the inclined surface 62a of the protrusion 62 is a component force in a direction from one side surface to the other side surface, and an annular shape from the surface of the shaft 50. This is the resultant force with the component force in the direction toward the groove bottom surface of the groove 61.

従って、シールリップ１２自体が一方の側面側から他方の側面側に向かって伸びた構成であることと相俟って、シールリップ１２の軸５０の表面に対する接触面積の増加を好適に抑制すると共に、シールリップ１２の一部が、軸５０とハウジング６０の軸孔との間の隙間にはみ出してしまうことを好適に抑制できる。   Accordingly, coupled with the configuration in which the seal lip 12 itself extends from one side surface to the other side surface, it is possible to suitably suppress an increase in the contact area of the seal lip 12 with the surface of the shaft 50. Further, it is possible to suitably suppress a part of the seal lip 12 from protruding into the gap between the shaft 50 and the shaft hole of the housing 60.

また、本実施例においては、流体圧力を受けて、密封装置１０が低圧（Ｌ）側に押し付けられた際に、シールリップ１２における、傾斜面１２ｂと環状凸部１２ｃとの間の湾曲面１２ｄも、湾曲面で構成された、突起部６２の先端６２ｂに密着するように構成されている。   Further, in this embodiment, when the sealing device 10 is pressed to the low pressure (L) side under the fluid pressure, the curved surface 12d between the inclined surface 12b and the annular convex portion 12c in the seal lip 12 is obtained. Is also configured to be in close contact with the tip 62b of the protrusion 62, which is formed of a curved surface.

従って、突起部６２の先端６２ｂ付近においても、シールリップ１２の姿勢を安定させることができると共に、突起部６２の先端６２ｂから受ける応力集中は緩和されるので、突起部６２の先端６２ｂによってシールリップ１２が破損してしまうことを抑制できる。   Accordingly, the posture of the seal lip 12 can be stabilized even in the vicinity of the tip 62b of the projection 62, and the stress concentration received from the tip 62b of the projection 62 is alleviated. It can suppress that 12 is damaged.

また、本実施例においては、密封装置１０におけるＵ溝部分における肉厚Ｗと、突起部６２の高さｈが略等しくなるように設定されているので、流体圧力が作用している状態においては、シールリップ１２は、Ｕ溝部分よりも先端側のみが、軸５０の表面に向かって撓むように変形する。従って、シールリップ１２の姿勢を好適に安定させることができる。   In the present embodiment, the thickness W of the U-groove portion of the sealing device 10 and the height h of the protrusion 62 are set to be substantially equal. Therefore, in a state where fluid pressure is acting. The seal lip 12 is deformed so that only the front end side of the U-groove portion is bent toward the surface of the shaft 50. Accordingly, the posture of the seal lip 12 can be preferably stabilized.

以上のように、本実施例に係る密封構造によれば、シールリップ１２のリップ先端１２ａの軸５０の表面に対する摺動抵抗の増加を抑制できるので、機械的損失を抑制すること
ができる。また、シールリップ１２の一部が、軸５０とハウジング６０の軸孔との間の隙間にはみ出してしまうことを抑制できるので、安定した密封性能を維持させることができる。なお、本実施例においては、いわゆるバックアップリングを必要とすることなく、シールリップ１２の一部のはみ出しを防止することができる。従って、部品点数が増加してしまうこともなく、バックアップリングを設けることに伴う各種不具合対策も必要ない。 As described above, according to the sealing structure according to the present embodiment, an increase in sliding resistance with respect to the surface of the shaft 50 of the lip tip 12a of the seal lip 12 can be suppressed, so that mechanical loss can be suppressed. Moreover, since it can suppress that a part of seal lip 12 protrudes into the clearance gap between the axis | shaft 50 and the shaft hole of the housing 60, the stable sealing performance can be maintained. In this embodiment, it is possible to prevent a part of the seal lip 12 from protruding without requiring a so-called backup ring. Therefore, the number of parts does not increase, and various countermeasures for providing a backup ring are not necessary.

ここで、図４は流体圧力（ここでは油圧）とシールリップの軸に対する緊迫力（接触圧力）との関係について、従来例（上述した図７〜図９に示したもの）と本実施例とを比較した結果を示すグラフである。なお、従来例と本実施例においては、構成（形状）以外の条件（密封装置等の各種部材の素材や基本的構成部の寸法（密封装置の最小径，最大径及び幅寸法や軸径や環状溝の最大幅や深さ））については同一条件としている。このグラフからも、本実施例の場合の方が、緊迫力を低減することができ、摺動抵抗の増加を抑制できることが分かる。例えば、油圧が１０ＭＰａの場合において、本実施例のものは従来例のものに比べて緊迫力を約４０％低減させることができた。また、最大発生主歪を、油圧が１０ＭＰａの場合に、約１０％低減させることができることも確認できた。   Here, FIG. 4 shows the relationship between the fluid pressure (here, hydraulic pressure) and the pressing force (contact pressure) against the shaft of the seal lip with the conventional example (shown in FIGS. 7 to 9 described above) and the present embodiment. It is a graph which shows the result of having compared. In the conventional example and the present embodiment, conditions other than the configuration (shape) (materials of various members such as a sealing device and dimensions of basic components (minimum diameter, maximum diameter and width dimensions of the sealing device, shaft diameter, The maximum width and depth of the annular groove)) are the same. Also from this graph, it can be seen that in the case of the present embodiment, the tightening force can be reduced and the increase in sliding resistance can be suppressed. For example, when the hydraulic pressure is 10 MPa, the present example can reduce the tension force by about 40% compared to the conventional example. It was also confirmed that the maximum generated main strain can be reduced by about 10% when the hydraulic pressure is 10 MPa.

（実施例２）
図５及び図６には、本発明の実施例２が示されている。上記実施例１では、ハウジングの軸孔内周に設けられた環状溝に密封装置が装着される場合を示したが、本実施例では、軸の外周に設けられた環状溝に密封装置が装着される場合を示す。 (Example 2)
5 and 6 show a second embodiment of the present invention. In the first embodiment, the case where the sealing device is attached to the annular groove provided in the inner periphery of the shaft hole of the housing is shown. In this embodiment, the sealing device is attached to the annular groove provided in the outer periphery of the shaft. The case where it is done is shown.

図５は本発明の実施例２に係る密封装置の模式的断面図である。図６は本発明の実施例２に係る密封装置を装着した状態（密封流体の圧力による負荷がある場合）を示す模式的断面図である。本実施例に係る密封装置２０は、油圧・空圧機器に好適に用いられる往復動用のＵ型パッキンである。また、密封装置２０の素材としては、ウレタン樹脂やゴム材などを好適に適用できる。なお、図５においては、密封装置２０には外力が作用していない場合の状態を示しており、軸５５とハウジング６５との寸法関係（中心軸を一致させた状態における寸法関係）が分かるように、軸５５とハウジング６５については点線で示している。   FIG. 5 is a schematic cross-sectional view of a sealing device according to Embodiment 2 of the present invention. FIG. 6 is a schematic cross-sectional view showing a state in which the sealing device according to Embodiment 2 of the present invention is mounted (when there is a load due to the pressure of the sealing fluid). The sealing device 20 according to the present embodiment is a reciprocating U-shaped packing that is suitably used for hydraulic and pneumatic equipment. Moreover, as a raw material of the sealing device 20, a urethane resin, a rubber material, etc. can be applied suitably. FIG. 5 shows a state where no external force is applied to the sealing device 20, so that the dimensional relationship between the shaft 55 and the housing 65 (the dimensional relationship when the central axes are matched) can be seen. The shaft 55 and the housing 65 are indicated by dotted lines.

本実施例に係る密封装置２０は、内周側に内周シール部（第１シール部）２１を備え、外周側にシールリップ（第２シール部）２２を備えている。シールリップ２２のリップ先端２２ａは、先端が尖った形状で構成されている。また、シールリップ２２の根本付近は、リップ先端２２ａに向かって拡径する傾斜面２２ｂが形成されており、その先端に環状凸部２２ｃが設けられている。この傾斜面２２ｂと環状凸部２２ｃは湾曲面２２ｄによって滑らかに接続されている。   The sealing device 20 according to this embodiment includes an inner peripheral seal portion (first seal portion) 21 on the inner peripheral side and a seal lip (second seal portion) 22 on the outer peripheral side. The lip tip 22a of the seal lip 22 is configured to have a sharp tip. In addition, an inclined surface 22b whose diameter increases toward the lip tip 22a is formed near the base of the seal lip 22, and an annular convex portion 22c is provided at the tip. The inclined surface 22b and the annular convex portion 22c are smoothly connected by a curved surface 22d.

本実施例に係る密封装置２０においても、軸５５とハウジング６５に設けられた軸孔（軸５５が挿通される孔）との間の環状隙間を密封するために用いられる。なお、本実施例においては、軸５５とハウジング６５は相対的に往復移動するように構成されており、密封装置２０とハウジング６５との間で摺動するように構成されている。   Also in the sealing device 20 according to the present embodiment, it is used for sealing an annular gap between the shaft 55 and a shaft hole provided in the housing 65 (a hole through which the shaft 55 is inserted). In this embodiment, the shaft 55 and the housing 65 are configured to reciprocate relatively, and are configured to slide between the sealing device 20 and the housing 65.

本実施例に係る密封装置２０は、軸５５の外周に形成された環状溝５６に装着される。そして、密封装置２０がこの環状溝５６に装着された状態においては、内周シール部２１が環状溝５６の溝底面に密着し、シールリップ２２がハウジング６５の軸孔内周面に摺動自在な状態で接触した状態となる。   The sealing device 20 according to this embodiment is mounted in an annular groove 56 formed on the outer periphery of the shaft 55. When the sealing device 20 is mounted in the annular groove 56, the inner peripheral seal portion 21 is in close contact with the groove bottom surface of the annular groove 56, and the seal lip 22 is slidable on the inner peripheral surface of the shaft hole of the housing 65. It will be in the state which touched in the state.

ここで、本実施例に係る密封装置２０においては、その内周側は、その全域にわたって、内径が環状溝５６の溝底面の内径よりも小さくなるように設定されている（図１参照）。従って、密封装置２０が環状溝５６に装着された状態では、密封装置２０の内周側の全
面が、環状溝５６の溝底面に密着する。一方、密封装置２０における外周側は、シールリップ２２のリップ先端付近のみ、外径がハウジング６５の軸孔内径よりも大きくなるように設定されている（図５参照）。従って、密封装置２０が環状溝５６に装着された状態であって、流体圧力による負荷がない場合には、シールリップ２２の先端付近のみが、ハウジング６５の軸孔内周面に密着する。 Here, in the sealing device 20 according to the present embodiment, the inner peripheral side is set so that the inner diameter is smaller than the inner diameter of the groove bottom surface of the annular groove 56 over the entire area (see FIG. 1). Therefore, when the sealing device 20 is mounted in the annular groove 56, the entire inner peripheral side of the sealing device 20 is in close contact with the bottom surface of the annular groove 56. On the other hand, the outer peripheral side of the sealing device 20 is set so that the outer diameter is larger than the inner diameter of the shaft hole of the housing 65 only in the vicinity of the tip of the seal lip 22 (see FIG. 5). Therefore, when the sealing device 20 is mounted in the annular groove 56 and there is no load due to fluid pressure, only the vicinity of the end of the seal lip 22 is in close contact with the inner peripheral surface of the shaft hole of the housing 65.

そして、本実施例においては、環状溝５６における一方の側面（使用時においては、低圧となる側の側面）には、一方の側面側から他方の側面側に向かって突き出た突起部５７が設けられている。   In the present embodiment, one side surface of the annular groove 56 (the side surface on which the pressure is low when in use) is provided with a protrusion 57 protruding from one side surface to the other side surface. It has been.

この突起部５７は、一方の側面側から他方の側面側に向かうにつれて、環状溝５６の溝底側からハウジング６５の軸孔内周表面に向かって傾斜する傾斜面５７ａを有している。また、突起部５７の先端５７ｂは湾曲面によって構成されている。   The projecting portion 57 has an inclined surface 57 a that is inclined from the groove bottom side of the annular groove 56 toward the inner peripheral surface of the shaft hole of the housing 65 from one side surface side to the other side surface side. Moreover, the front-end | tip 57b of the projection part 57 is comprised by the curved surface.

そして、本実施例では、使用状態において、図中左側の圧力が、流体圧力（油圧や空圧）によって高くなるように構成されている。すなわち、使用状態においては、図６に示すように、密封装置２０を介して左側が高圧（Ｈ）となり、右側が低圧（Ｌ）となる。なお、高圧側には密封対象となる流体が密封される。低圧側においては、適用される油圧・空圧機器に応じて、高圧側と同様に密封対象流体による流体圧力が作用する場合もあるし、大気圧となる場合もある。また、適用される油圧・空圧機器に応じて、左側が常時高圧となる場合もあるし、間欠的に高圧となる場合もある。   In this embodiment, the pressure on the left side in the figure is configured to be increased by the fluid pressure (hydraulic pressure or pneumatic pressure) in the usage state. That is, in the use state, as shown in FIG. 6, the left side becomes high pressure (H) and the right side becomes low pressure (L) through the sealing device 20. Note that a fluid to be sealed is sealed on the high pressure side. On the low pressure side, depending on the applied hydraulic / pneumatic equipment, the fluid pressure by the fluid to be sealed may act as in the high pressure side, or it may become atmospheric pressure. Further, depending on the applied hydraulic / pneumatic equipment, the left side may be constantly at a high pressure or may be intermittently at a high pressure.

以上のような構成により、使用状態では、密封装置２０は流体圧力によって環状溝５６内において、低圧（Ｌ）側に押し付けられる。これにより、密封装置２０の低圧（Ｌ）側の端面は、環状溝５６の低圧（Ｌ）側側面に密着する。また、流体圧力によって、内周シール部２１は環状溝５６の溝底面側に押し付けられ、シールリップ２２はハウジング６５の軸孔内周表面側に向かって押し付けられる。   With the above-described configuration, in a use state, the sealing device 20 is pressed against the low pressure (L) side in the annular groove 56 by fluid pressure. Thereby, the low pressure (L) side end surface of the sealing device 20 is in close contact with the low pressure (L) side surface of the annular groove 56. Further, the inner peripheral seal portion 21 is pressed against the groove bottom surface side of the annular groove 56 by the fluid pressure, and the seal lip 22 is pressed toward the inner peripheral surface side of the shaft hole of the housing 65.

そして、本実施例においては、流体圧力を受けて、密封装置２０が低圧（Ｌ）側に押し付けられると、シールリップ２２の根本付近に形成された傾斜面２２ｂが、環状溝５６に設けられた突起部５７の傾斜面５７ａに対して全面的に密着するように構成されている。また、このとき、シールリップ２２における、傾斜面２２ｂと環状凸部２２ｃとの間の湾曲面２２ｄも、湾曲面で構成された、突起部５７の先端５７ｂに密着するように構成されている。   In this embodiment, when the sealing device 20 is pressed to the low pressure (L) side under the fluid pressure, the annular groove 56 is provided with an inclined surface 22 b formed near the root of the seal lip 22. The protrusion 57 is configured to be in close contact with the inclined surface 57a. At this time, the curved surface 22d between the inclined surface 22b and the annular convex portion 22c in the seal lip 22 is also configured to be in close contact with the tip 57b of the protruding portion 57 that is configured by a curved surface.

また、本実施例においては、Ｕ型パッキンである密封装置２０におけるＵ溝部分における肉厚Ｗと、突起部５７の高さｈが略等しくなるように設定されている（図６参照）。そのため、流体圧力が作用している状態においては、シールリップ２２は、Ｕ溝部分よりも先端側のみが、ハウジング６５の軸孔内周表面に向かって撓むように変形することになる。   In the present embodiment, the thickness W of the U groove portion of the sealing device 20 that is a U-shaped packing and the height h of the protrusion 57 are set to be substantially equal (see FIG. 6). Therefore, in a state where fluid pressure is acting, the seal lip 22 is deformed so that only the distal end side of the U groove portion is bent toward the inner peripheral surface of the shaft hole of the housing 65.

以上のような構成により、本実施例においても、上述した実施例１の場合と同様の作用効果を有することは言うまでもない。   Needless to say, with the above-described configuration, this embodiment also has the same operational effects as those of the first embodiment described above.

図１は本発明の実施例１に係る密封装置の模式的断面図である。1 is a schematic cross-sectional view of a sealing device according to Embodiment 1 of the present invention. 図２は本発明の実施例１に係る密封装置を装着した状態（密封流体の圧力による負荷がない場合）を示す模式的断面図である。FIG. 2 is a schematic cross-sectional view showing a state in which the sealing device according to Embodiment 1 of the present invention is mounted (when there is no load due to the pressure of the sealing fluid). 図３は本発明の実施例１に係る密封装置を装着した状態（密封流体の圧力による負荷がある場合）を示す模式的断面図である。FIG. 3 is a schematic cross-sectional view showing a state in which the sealing device according to Embodiment 1 of the present invention is mounted (when there is a load due to the pressure of the sealing fluid). 図４は流体圧力と緊迫力との関係を示すグラフである。FIG. 4 is a graph showing the relationship between fluid pressure and tension. 図５は本発明の実施例２に係る密封装置の模式的断面図である。FIG. 5 is a schematic cross-sectional view of a sealing device according to Embodiment 2 of the present invention. 図６は本発明の実施例２に係る密封装置を装着した状態（密封流体の圧力による負荷がある場合）を示す模式的断面図である。FIG. 6 is a schematic cross-sectional view showing a state in which the sealing device according to Embodiment 2 of the present invention is mounted (when there is a load due to the pressure of the sealing fluid). 図７は従来例に係る密封装置の模式的断面図である。FIG. 7 is a schematic cross-sectional view of a conventional sealing device. 図８は従来例に係る密封装置を装着した状態（密封流体の圧力による負荷がない場合）を示す模式的断面図である。FIG. 8 is a schematic cross-sectional view showing a state in which a sealing device according to a conventional example is mounted (when there is no load due to the pressure of the sealing fluid). 図９は従来例に係る密封装置を装着した状態（密封流体の圧力による負荷がある場合）を示す模式的断面図である。FIG. 9 is a schematic cross-sectional view showing a state in which a sealing device according to a conventional example is mounted (when there is a load due to the pressure of the sealing fluid).

符号の説明Explanation of symbols

１０ 密封装置
１１ 外周シール部
１２ シールリップ
１２ａ リップ先端
１２ｂ 傾斜面
１２ｃ 環状凸部
１２ｄ 湾曲面
２０ 密封装置
２１ 内周シール部
２２ シールリップ
２２ａ リップ先端
２２ｂ 傾斜面
２２ｃ 環状凸部
２２ｄ 湾曲面
５０，５５ 軸
５６ 環状溝
５７ 突起部
５７ａ 傾斜面
５７ｂ 先端
６０ ハウジング
６１ 環状溝
６２ 突起部
６２ａ 傾斜面
６２ｂ 先端
６５ ハウジング DESCRIPTION OF SYMBOLS 10 Sealing device 11 Outer peripheral seal part 12 Seal lip 12a Lip front end 12b Inclined surface 12c Annular convex part 12d Curved surface 20 Sealing device 21 Inner peripheral seal part 22 Seal lip 22a Lip front end 22b Inclined surface 22c Annular convex part 22d Curved surface 50, 55 Shaft 56 Annular groove 57 Projection 57a Inclined surface 57b Tip 60 Housing 61 Annular groove 62 Projection 62a Inclined surface 62b Tip 65 Housing

Claims (3)

軸と、
該軸が挿通される軸孔を有するハウジングと、
前記軸及びハウジングのうちの一方の部材に形成された環状溝に装着され、これら軸とハウジングに設けられた軸孔との間に形成される環状隙間を密封する密封装置と、
を備える密封構造において、
前記環状溝における一方の側面には、一方の側面側から他方の側面側に向かうにつれて、溝底側から前記軸及びハウジングのうちの他方の部材表面に向かって傾斜する傾斜面を有する突起部が設けられており、
前記密封装置は、
前記環状溝の溝底面に密着する第１シール部と、
前記一方の側面側から他方の側面側に向かって伸びて、前記他方の部材表面に摺動自在に接触するリップ状の第２シール部と、
を備えており、
第２シール部におけるリップの根本付近には、前記他方の側面側から流体圧力を受けた際に、前記突起部における前記傾斜面に密着する傾斜面が形成されていることを特徴とする密封構造。 The axis,
A housing having a shaft hole through which the shaft is inserted;
A sealing device mounted in an annular groove formed in one member of the shaft and the housing and sealing an annular gap formed between the shaft and a shaft hole provided in the housing;
In a sealing structure comprising:
On one side surface of the annular groove, there is a protrusion having an inclined surface that is inclined from the groove bottom side toward the other member surface of the shaft and the housing from one side surface side to the other side surface side. Provided,
The sealing device includes:
A first seal portion closely contacting the groove bottom surface of the annular groove;
A lip-shaped second seal portion extending from the one side surface to the other side surface and slidably contacting the other member surface;
With
In the vicinity of the base of the lip in the second seal portion, an inclined surface is formed that is in close contact with the inclined surface of the projection when receiving fluid pressure from the other side surface side. . 前記突起部先端は湾曲面によって構成されており、
第２シール部には、前記他方の側面側から流体圧力を受けた際に、前記突起部先端の湾曲面に密着する湾曲面が形成されていることを特徴とする請求項１に記載の密封構造。 The protrusion tip is configured by a curved surface,
2. The sealing according to claim 1, wherein the second seal portion is formed with a curved surface that is in close contact with the curved surface at the tip of the protruding portion when fluid pressure is received from the other side surface side. Construction. 前記密封装置は、その断面形状が略Ｕ字形状のＵ型パッキンであり、
該Ｕ型パッキンのＵ溝部分における肉厚と、前記突起部の高さが略等しくなるように設定されていることを特徴とする請求項１または２に記載の密封構造。 The sealing device is a U-shaped packing having a substantially U-shaped cross section,
3. The sealing structure according to claim 1, wherein a thickness of the U-shaped portion of the U-shaped packing is set to be substantially equal to a height of the protruding portion.
JP2008081156A 2008-03-26 2008-03-26 Sealing structure Pending JP2009236177A (en)

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