WO2011108298A1 - 密封装置 - Google Patents
密封装置 Download PDFInfo
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- WO2011108298A1 WO2011108298A1 PCT/JP2011/050724 JP2011050724W WO2011108298A1 WO 2011108298 A1 WO2011108298 A1 WO 2011108298A1 JP 2011050724 W JP2011050724 W JP 2011050724W WO 2011108298 A1 WO2011108298 A1 WO 2011108298A1
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- ring
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- seal ring
- annular groove
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
- F16J15/3208—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip provided with tension elements, e.g. elastic rings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
Definitions
- the present invention relates to a sealing device provided in a rotating part of various machines such as a machine tool and a construction machine, and more particularly to a sealing device excellent in sealing performance of a rotating part that is subjected to high fluid pressure and rotates at a low torque.
- a first member (outer member) 11 is used to seal an annular gap S formed between the inner and outer two members 11 and 12 that rotate relative to each other coaxially.
- An O-ring (back ring) 14 and a seal ring 15 fitted to the inside of the annular groove 13 for sealing are formed in the inner surface of the shaft hole 11a along the circumferential direction.
- inclined surfaces 15a and 15b are formed on both sides in the axial direction (direction in which fluid pressure P is applied) of the sliding surface with the second member (inner member) 12.
- the fluid pressure P when the fluid pressure P is applied, the fluid is placed between the inclined surface 15a on the side that contacts the working fluid (the counter pressure side) and the second member 12.
- the conventional sealing device described above uses an O-ring as the back ring 14, the contact between the back ring 14 and the bottom surface 13a of the sealing annular groove 13 is incomplete.
- a high fluid pressure P is applied, the space between the back ring 14 and the bottom surface 13a of the annular ring groove 13 on the side in contact with the working fluid expands, so that the contact between the two becomes incomplete.
- the elastic restoring force of the back ring 14 does not effectively act as a pressing force for urging the seal ring 15 toward the second member 12 and the sealing performance becomes unstable.
- the problem to be solved by the present invention is to provide a sealing device capable of realizing a low torque of a rotating part while always exhibiting a stable and high sealing performance even when a high fluid pressure is acting.
- a sealing device is a sealing device that seals an annular gap formed between two inner and outer members that rotate relative to each other coaxially.
- a buckling provided in contact with the bottom surface of the annular groove for sealing having a rectangular cross section formed along the circumferential direction on one member;
- the contact surface with the bottom surface of the buckling is a cylindrical surface, and the contact surface with the seal ring is an annular convex curved surface having a constant curvature in the axial direction,
- the contact surface of the seal ring with the back ring is a cylindrical surface, and the contact surface with the other member is an annular convex curved surface having a certain curvature in the axial direction. is there.
- a typical example of two inner and outer members that rotate relative to each other coaxially is a shaft and a housing.
- the seal ring is mounted on the inner peripheral side of the buckling and slides on the shaft (outer peripheral surface) under the radial inward pressing force of the buckling To do.
- the seal ring is mounted on the outer peripheral side of the buckling, and receives the pressing force radially outward by the buckling (the inner peripheral surface). To slide.
- the back ring and the seal ring are pressed against the counter pressure side of the sealing annular groove formed in one member, that is, the side surface that does not contact the working fluid. .
- the buckling receives elastic compression by the working fluid pressure, and presses the seal ring toward the other member side by the elastic restoring force. Since the contact surface with the back ring is a cylindrical surface and the contact surface with the other member is an annular convex curved surface having a certain curvature in the axial direction, the seal ring has a working fluid pressure and a back surface.
- the end surface on the counter pressure side is brought into surface contact with the side surface on the counter pressure side of the annular groove for sealing, and the counter pressure side portion of the inner peripheral surface is brought into surface contact with the other member Stabilizes with a good posture. Then, when the working fluid pressure acts on the portion of the inner peripheral surface of the seal ring that is in contact with the working fluid, the space between that portion and the other member is expanded, and the seal ring and the other member The contact area is reduced.
- the contact surface with the bottom surface of the ring groove for sealing of the buckling is a cylindrical surface, so that the working fluid can flow between the buckling and the bottom surface of the annular groove for sealing even when high working fluid pressure is applied. There is no room for entry, and the entire contact surface of the buckling with the bottom surface of the sealing annular groove is always kept in contact with the bottom surface of the sealing annular groove.
- the buckling is a rubber D-ring
- the seal ring is preferably a resin ring made of polyethylene or polyamide.
- a rubber D-ring as the back ring, the seal ring can be tilted while an appropriate pressing force due to rubber elasticity is applied to the seal ring.
- a resin ring made of polyethylene or polyamide as the seal ring, the wear of the rubber D-ring due to friction between both rings is minimized, and the durability of the seal ring against high fluid pressure and the other member Can be secured.
- the end surface of the seal ring may have a tapered surface that is inclined so that the distance from the side surface of the sealing annular groove increases as it approaches the bottom surface of the sealing annular groove. desirable. According to this configuration, when the seal ring is tilted by receiving the working fluid pressure and the pressing force by the buckling, the end surface on the counter pressure side of the seal ring is well faced to the side surface on the counter pressure side of the seal annular groove. Because of contact, more stable sealing performance can be realized.
- the sealing device of the present invention even when a high working fluid pressure is applied, the elastic restoring force of the buckling is always effectively applied as a pressing force for urging the seal ring, thereby realizing a stable sealing performance at all times.
- FIG. 1 It is a fragmentary sectional view which illustrates an embodiment of a sealing device of the present invention, (A) shows the state of a buckling and a seal ring when fluid pressure is not acting, and (B) is where fluid pressure is acting. The state of the buckling and the seal ring at the time is shown. It is a fragmentary sectional view which illustrates the conventional sealing device, (A) is the state of the buckling and seal ring when fluid pressure does not act, and (B) is the buckling when fluid pressure is acting. And the state of the seal ring.
- the sealing device of this embodiment is applied to a rotating part such as a hydraulic machine tool, and is inserted through a housing (one member) 1 and a shaft hole 1a of the housing 1 as shown in FIG.
- An annular gap S formed between the cylindrical shaft (the other member) 2 is sealed while allowing relative rotation of the members 1 and 2.
- This sealing device has a D-ring (back ring) 3 and a seal ring 4. Both the rings 3 and 4 are mounted in a sealing annular groove 5 having a rectangular cross section formed along the circumferential direction on the inner surface of the shaft hole 1a.
- the D ring 3 is provided in contact with the bottom surface 5a of the annular groove 5 for sealing.
- the D ring 3 has an outer peripheral surface 3a that is a cylindrical surface similar to the bottom surface 5a of the sealing annular groove 5, and an inner peripheral surface 3b that is an annular convex curved surface having a constant curvature in the axial direction. It is a rubber sealing member having a letter-shaped cross-sectional shape.
- the seal ring 4 is a resin sealing member made of polyethylene or polyamide whose outer peripheral surface 4a is a cylindrical surface and whose inner peripheral surface 4b is an annular convex curved surface having a certain curvature in the axial direction. is there.
- the axial curvature of the inner peripheral surface 4 b of the seal ring 4 is selected to be smaller than the axial curvature of the inner peripheral surface 3 b of the D ring 3.
- the seal ring 4 is provided in close contact with the inner peripheral surface 3b of the back ring 3 over the entire circumference, and relatively rotates and slides while being in close pressure contact with the entire outer periphery of the shaft 2.
- the inner diameter dimension of the D ring 3 and the outer diameter dimension of the seal ring 4 are substantially equal, and the D ring 3 and the seal ring 4 are mounted in the seal annular groove 5 in close contact with each other.
- the D-ring 3 is sandwiched between the seal ring 4 and the bottom surface 5 a of the sealing annular groove 5 and is compressed radially.
- the elastic restoring force of the D-ring 3 works as a pressing force that urges the seal ring 4 toward the shaft 2 side.
- tapered surfaces 4c and 4d are formed at both end surface portions of the seal ring 4 so as to increase the distance from the side surface 5b of the groove 5 toward the bottom surface 5a of the annular groove 5 for sealing.
- the inner peripheral surface 4b is an annular convex curved surface having a constant curvature in the axial direction. Inclination is received in response to the pressing force generated by the pressure, and the entire tapered surface 4c on the counter pressure side is stabilized in a posture in which it is in surface contact with the side surface 5b on the counter pressure side of the sealing annular groove 5.
- the inner peripheral surface 4b of the seal ring 4 in contact with the shaft 2 is an annular convex curved surface having a certain curvature in the axial direction, and the curvature is smaller than the axial curvature of the inner peripheral surface 3b of the D ring 3.
- the tilting of the seal ring 4 to the stable posture performed in response to the hydraulic pressure P and the pressing force by the D ring 3 is smoothly performed in a stepless manner. Then, when the hydraulic pressure P acts on the portion 4b1 of the inner peripheral surface 4b of the seal ring 4 that comes into contact with the hydraulic oil, the space between the portion 4b1 and the shaft 2 expands, and the seal ring 4 and the shaft 2 The contact area is reduced. As a result, the pressing force of the D-ring 3 acts intensively on the portion 4b2 in contact with the shaft 2 of the seal ring 4, so that high sealing performance is secured, and the frictional resistance between the seal ring 4 and the shaft 2 is reduced. Therefore, the torque of the rotating part can be reduced.
- the outer peripheral surface 3a of the D ring 3 is a cylindrical surface, there is no room for hydraulic oil to enter between the D ring 3 and the bottom surface 5a of the annular groove 5 for sealing even when the hydraulic pressure P is applied. In other words, the entire outer peripheral surface 3a of the D-ring 3 is always kept in contact with the bottom surface 5a of the sealing annular groove 5. Therefore, the elastic restoring force of the D ring 3 is always effectively applied as a pressing force for urging the seal ring 4 toward the shaft 2 side, so that a stable sealing performance can always be realized.
- both end surfaces of the seal ring 4 are tapered surfaces 4c and 4d, the above-described operational effects can be achieved regardless of the hydraulic pressure P acting from either side in the axial direction. Therefore, this sealing device can be suitably used even for a rotating part of a hydraulic machine in which the direction in which the hydraulic pressure P acts during operation is switched.
- the tapered surfaces 4c and 4d are formed on both end surface portions of the seal ring 4, but the tapered surfaces may be provided only on the end surface portion on the counter pressure side.
- the D-ring 3 and the seal ring 4 are attached to the seal annular groove 5 provided in the shaft hole 1 a of the housing (one member) 1, and the seal ring 4 is attached to the shaft (the other member).
- a D-ring and a seal ring are attached to an annular groove for sealing provided on the shaft (one member) 2, and the seal ring is attached to the housing (the other member).
- It can also be suitably used for a configuration in which it is brought into contact with one shaft hole 1a.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sealing Devices (AREA)
Abstract
Description
このような事情の下、高い流体圧がかかり且つ低トルクで回転する回転部の密封性を向上させた密封装置が各種提案されている。
その一例として、図2(A)に示すように、互いに同軸的に相対回転する内外二部材11、12間に形成される環状の隙間Sを密封するべく、第1部材(外側の部材)11の軸孔11aの内面部に周方向に沿って形成されたシール用環状溝13に、Oリング(バックリング)14とその内側に嵌合したシールリング15とを装着するとともに、シールリング15の第2部材(内側の部材)12との摺動面の軸方向(流体圧Pがかかる方向)両側に傾斜面15a、15bを形成したものがある。この密封装置は、図2(B)に示すように、流体圧Pが加えられたときに作動流体と接触する側(反圧力側)の傾斜面15aと第2部材12との間に流体が入り込むことによりシールリング15の第2部材12との接触面積が減少し、シールリング15と第2部材12との摩擦抵抗が小さくなることにより、高い密封性能と回転部の低トルク化を同時に実現する。(たとえば、特許文献1参照)
一方の部材に周方向に沿って形成された断面矩形状のシール用環状溝の底面に接触させて設けられたバックリングと、
前記シール用環状溝の開口側に設けられ、前記バックリングにより押圧されて他方の部材に全周に亘って摺接して相対的に回転摺動するシールリングと、を有し、
前記バックリングの前記底面との接触面は円筒形状の面であり且つ前記シールリングとの接触面は軸方向に一定の曲率を有する円環状の凸曲面であり、
前記シールリングの前記バックリングとの接触面は円筒形状の面であり且つ前記他方の部材との接触面は軸方向に一定の曲率を有する円環状の凸曲面であることを特徴とするものである。
シールリングは、バックリングとの接触面が円筒形状の面であり且つ他方の部材との接触面が軸方向に一定の曲率を有する円環状の凸曲面になっているため、作動流体圧とバックリングによる押圧力とを受けて傾き、その反圧力側の端面をシール用環状溝の反圧力側の側面に面接触させるとともに、その内周面の反圧力側部分を他方の部材に面接触させた姿勢で安定する。そして、シールリングの内周面の作動流体が接触している部分に作動流体圧が作用することにより、その部分と他方の部材との間の空間が拡大し、シールリングと他方の部材との接触面積が小さくなる。その結果、シールリングの他方の部材と接触している部分にバックリングの押圧力が集中的に作用するため高い密封性能が確保され、シールリングと他方の部材との摩擦抵抗が小さくなるため回転部の低トルク化が実現される。
バックリングのシール用環状溝の底面との接触面が円筒形状の面であることにより、高い作動流体圧が作用しているときでもバックリングとシール用環状溝の底面との間に作動流体が入り込む余地はなく、バックリングのシール用環状溝の底面との接触面全体がシール用環状溝の底面に常に接触した状態に保たれる。すなわち、シール用環状溝の底面もバックリングの当該底面との接触面も共に円筒形状の面であるので、両面間に隙間が発生しない。したがって、バックリングの弾性復元力をシールリングを他方の部材側に付勢する押圧力として常に有効に作用させて、常に安定した密封性能を実現できる。
前記シールリングは、ポリエチレン又はポリアミドからなる樹脂製リングであることが望ましい。
バックリングとして、ゴム製のDリングを使用することにより、シールリングに対しゴム弾性による適度な押圧力を作用させつつ、シールリングを傾動させることができる。シールリングとして、ポリエチレン又はポリアミドからなる樹脂製リングを使用することにより、両リング間の摩擦によるゴム製のDリングの摩耗を極力少なくするとともに、高い流体圧に対するシールリングの耐久性及び他方の部材との摺動性を確保できる。
この構成によれば、シールリングが作動流体圧とバックリングによる押圧力とを受けて傾いたときに、シールリングの反圧力側の端面がシール用環状溝の反圧力側の側面に良好に面接触するので、より安定した密封性能を実現できる。
この実施形態の密封装置は、油圧工作機械などの回転部に適用されるものであり、図1(A)に示すように、ハウジング(一方の部材)1とハウジング1の軸孔1aに挿通された円柱状の軸(他方の部材)2との間に形成される環状の隙間Sを両部材1、2の相対回転を許容しつつ密封するものである。
たとえば、上記実施形態では、シールリング4の両端面部にテーパ面4c、4dが形成されているが、反圧力側の端面部のみにテーパ面を設けてもよい。
また、上記実施形態では、ハウジング(一方の部材)1の軸孔1aに設けられたシール用環状溝5にDリング3とシールリング4とを装着して、シールリング4を軸(他方の部材)2に接触させる構成を例示したが、本発明は、軸(一方の部材)2に設けられたシール用環状溝にDリングとシールリングとを装着して、シールリングをハウジング(他方の部材)1の軸孔1aに接触させる構成にも好適に用いることができる。
1a 軸孔
2 軸
3 バックリング
3a 外周面(シール用環状溝の底面との接触面)
3b 内周面(シールリングとの接触面)
4 シールリング
4a 外周面(バックリングとの接触面)
4b 内周面(軸との接触面)
4c、4d テーパ面
5 シール用環状溝
5a 底面
S 隙間
Claims (3)
- 互いに同軸的に相対回転する内外二部材間に形成される環状の隙間を密封する密封装置であって、
一方の部材に周方向に沿って形成された断面矩形状のシール用環状溝の底面に接触させて設けられたバックリングと、
前記シール用環状溝の開口側に設けられ、前記バックリングにより押圧されて他方の部材に全周に亘って摺接して相対的に回転摺動するシールリングと、を有し、
前記バックリングの前記底面との接触面は円筒形状の面であり且つ前記シールリングとの接触面は軸方向に一定の曲率を有する円環状の凸曲面であり、
前記シールリングの前記バックリングとの接触面は円筒形状の面であり且つ前記他方の部材との接触面は軸方向に一定の曲率を有する円環状の凸曲面であることを特徴とする密封装置。 - 前記バックリングは、ゴム製のDリングであり、
前記シールリングは、ポリエチレン又はポリアミドからなる樹脂製リングである、請求項1に記載の密封装置。 - 前記シールリングの端面は、前記シール用環状溝の底面に近づくほど前記シール用環状溝の側面との間隔が拡大するように傾斜したテーパ面を有している、請求項1又は2に記載の密封装置。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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US13/582,713 US8985591B2 (en) | 2010-03-04 | 2011-01-18 | Sealing apparatus |
CN201180007831.6A CN102782376B (zh) | 2010-03-04 | 2011-01-18 | 密封装置 |
EP11750411.8A EP2543912B1 (en) | 2010-03-04 | 2011-01-18 | Sealing device |
JP2011538777A JP5765670B2 (ja) | 2010-03-04 | 2011-01-18 | 密封装置 |
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JP2010047352 | 2010-03-04 | ||
JP2010-047352 | 2010-03-04 |
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US (1) | US8985591B2 (ja) |
EP (1) | EP2543912B1 (ja) |
JP (1) | JP5765670B2 (ja) |
CN (1) | CN102782376B (ja) |
WO (1) | WO2011108298A1 (ja) |
Cited By (2)
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CN117913690A (zh) * | 2024-03-20 | 2024-04-19 | 四川电器集团中低压智能配电有限公司 | 一种新能源用开关设备 |
CN117913690B (zh) * | 2024-03-20 | 2024-05-24 | 四川电器集团中低压智能配电有限公司 | 一种新能源用开关设备 |
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- 2011-01-18 EP EP11750411.8A patent/EP2543912B1/en active Active
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- 2011-01-18 WO PCT/JP2011/050724 patent/WO2011108298A1/ja active Application Filing
- 2011-01-18 JP JP2011538777A patent/JP5765670B2/ja active Active
- 2011-01-18 CN CN201180007831.6A patent/CN102782376B/zh active Active
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JPH03104564U (ja) * | 1990-02-09 | 1991-10-30 | ||
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JP2005504237A (ja) | 2001-09-18 | 2005-02-10 | ブザック + シャンバン ゲー エム ベー ハー | 高圧封止装置 |
JP2005054827A (ja) * | 2003-08-07 | 2005-03-03 | Nok Corp | 密封装置 |
JP2007092791A (ja) * | 2005-09-27 | 2007-04-12 | Nok Corp | シールリング |
JP2006342972A (ja) * | 2006-08-10 | 2006-12-21 | Ntn Corp | シール部材 |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN117913690A (zh) * | 2024-03-20 | 2024-04-19 | 四川电器集团中低压智能配电有限公司 | 一种新能源用开关设备 |
CN117913690B (zh) * | 2024-03-20 | 2024-05-24 | 四川电器集团中低压智能配电有限公司 | 一种新能源用开关设备 |
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EP2543912A4 (en) | 2016-10-12 |
US20120319359A1 (en) | 2012-12-20 |
EP2543912A1 (en) | 2013-01-09 |
JPWO2011108298A1 (ja) | 2013-06-24 |
CN102782376B (zh) | 2015-09-02 |
CN102782376A (zh) | 2012-11-14 |
US8985591B2 (en) | 2015-03-24 |
JP5765670B2 (ja) | 2015-08-19 |
EP2543912B1 (en) | 2018-03-07 |
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