JPH048918A - Sliding bearing - Google Patents
Sliding bearingInfo
- Publication number
- JPH048918A JPH048918A JP2107350A JP10735090A JPH048918A JP H048918 A JPH048918 A JP H048918A JP 2107350 A JP2107350 A JP 2107350A JP 10735090 A JP10735090 A JP 10735090A JP H048918 A JPH048918 A JP H048918A
- Authority
- JP
- Japan
- Prior art keywords
- shaft member
- lubricating oil
- gap
- receiving member
- sliding bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000010687 lubricating oil Substances 0.000 claims description 40
- 239000003921 oil Substances 0.000 claims description 17
- 238000007789 sealing Methods 0.000 claims description 8
- 239000000314 lubricant Substances 0.000 claims description 3
- 238000005461 lubrication Methods 0.000 abstract description 3
- 230000007423 decrease Effects 0.000 description 5
- 239000000428 dust Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 230000000452 restraining effect Effects 0.000 description 1
Landscapes
- Sealing Of Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明はすべり軸受に関し、特に、軸部材より僅かに大
径の穴を有する受部材に軸部材を挿入し、受部材又は軸
部材に設けた給油孔を介して軸邪材と受部材との隙間部
分に潤滑油を供給するようにしたすべり軸受に関する。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a plain bearing, and in particular, a shaft member is inserted into a receiving member having a hole slightly larger in diameter than the shaft member, and an oil supply provided in the receiving member or the shaft member is used. The present invention relates to a sliding bearing in which lubricating oil is supplied to a gap between a shaft member and a receiving member through a hole.
従来の技術
第４図は従来のすべり軸受の構成を示す断面図、第５図
は第４図の■−■線に沿った断面図である。BACKGROUND OF THE INVENTION FIG. 4 is a sectional view showing the structure of a conventional sliding bearing, and FIG. 5 is a sectional view taken along the line ■--■ in FIG. 4.
１はピン（軸部材）であり、ピン１はビン支持体２にそ
の両端部近傍が支持されているとともに、その一端部に
は拘束プレート３が一体的に固着され、ピン支持体２か
らの抜けと回転が防止されている。４はブツシュ（受部
材） ５はブツシュ支持体であり、ブツシュ４はピン１
の外径よりも僅かに大径の内径を有するリング状の部材
で、ブツシュ支持体５に対して一体的な動作をなすよう
に嵌合・接着されている。ブツシュ４の内側面には一対
の環状溝が形成され、これら環状溝に環状のダストシー
ル６．６が挿入されるかたちで設けられている。ダスト
シール６．６の内面はピン１の外周に当接しており、ダ
ストシール６．６は軸受外部から内部にゴミ等の侵入を
防止するものである。また、ブツシュ４には外側から内
側に貫通する給油孔７が形成され、ブツシュ支持体５に
はこれに連続するかたちで給油孔８が形成され、これら
の孔７，８を介して潤滑油が供給され、ピン１とブツシ
ュ４の摩擦抵抗を低下せしめるようにしている。1 is a pin (shaft member), and the pin 1 is supported near both ends by the bottle support 2, and a restraint plate 3 is integrally fixed to one end of the pin 1, so that the pin 1 is supported by the bottle support 2. Prevents it from coming off and rotating. 4 is a bushing (receiving member), 5 is a bushing support body, bushing 4 is a pin 1
It is a ring-shaped member having an inner diameter slightly larger than the outer diameter of the bushing support body 5, and is fitted and bonded to the bushing support body 5 so as to operate integrally with the bushing support body 5. A pair of annular grooves are formed on the inner surface of the bushing 4, and an annular dust seal 6.6 is inserted into these annular grooves. The inner surface of the dust seal 6.6 is in contact with the outer periphery of the pin 1, and the dust seal 6.6 prevents dirt and the like from entering the bearing from the outside. Further, the bushing 4 is formed with an oil supply hole 7 penetrating from the outside to the inside, and the bush support 5 is formed with an oil supply hole 8 continuous thereto, and lubricating oil is supplied through these holes 7 and 8. The frictional resistance between the pin 1 and the bushing 4 is reduced.
このすべり軸受はラジアル方向（軸方向に対して直角方
向）の荷重を負担するものであり、第５図中のＡ点は、
軸受が外部から荷重を受けてピン１とプツシ５４とが接
触している位置を示している。This sliding bearing bears a load in the radial direction (direction perpendicular to the axial direction), and point A in Fig. 5 is
It shows the position where the pin 1 and the pusher 54 are in contact with each other when the bearing receives an external load.
発明が解決しようとする課題
しかし、上述したような従来のすべり軸受は、軸部材（
ピン）と受部材（ブツシュ）との接触部分（第５図にお
けるＡ点りに、潤滑油の粘性によってのみ潤滑油を送る
ようにしたものであり、該接触部分における接触面圧が
高い場合には、潤滑が不十分となり、軸部材と受部材が
その接触部分で焼き付けを起こすことがあるという問題
があった。Problems to be Solved by the Invention However, in the conventional sliding bearing as described above, the shaft member (
The lubricant is designed to send lubricating oil only by the viscosity of the lubricating oil to the contact area (point A in Fig. 5) between the pin) and the receiving member (bush), and when the contact surface pressure at the contact area is high, However, there was a problem in that lubrication was insufficient and seizing could occur at the contact area between the shaft member and the receiving member.
本発明はこのような点に鑑みてなされたものであり、そ
の目的とするところは、潤滑特性が良好で、焼き付は等
の発生が少ないすべり軸受を提供することである。The present invention has been made in view of these points, and its purpose is to provide a sliding bearing that has good lubrication properties and is less prone to seizure and the like.
課題を解決するための手段
従来のすべり軸受における焼き付は等の不具合は、軸部
材と受部材との隙間内で潤滑油が自由に流動するため、
軸部材と受部材の接触部分で潤滑油による被膜が形成で
きない場合があることが原因であるから、以下のような
構造を採用することにより上記問題を解決する。Means to Solve the Problem Problems such as seizure in conventional plain bearings occur because lubricating oil flows freely within the gap between the shaft member and the receiving member.
This problem is caused by the fact that a coating of lubricating oil may not be formed at the contact portion between the shaft member and the receiving member, and the above problem is solved by adopting the following structure.
即ち、軸部材より僅かに大径の穴を有する受部材に軸部
材を挿入し、受部材又は軸部材に設けた給油孔を介して
軸部材と受部材との隙間に潤滑油を供給するようにする
とともに、該軸部材及び受部材に供給した潤滑油の漏れ
を防止するための環状のシール部材を該隙間の少なくと
も二箇所に介装してなるすべり軸受において、前記環状
シール部材間に渡って前記軸部材表面に当接する棒状の
シール部材を、前記受部材と一体的に回動するように設
ける。That is, the shaft member is inserted into a receiving member having a hole with a slightly larger diameter than the shaft member, and lubricating oil is supplied to the gap between the shaft member and the receiving member through the receiving member or an oil supply hole provided in the shaft member. and an annular seal member interposed in at least two places in the gap to prevent leakage of lubricating oil supplied to the shaft member and the receiving member, wherein the annular seal member is interposed between the annular seal members. A rod-shaped sealing member that comes into contact with the surface of the shaft member is provided so as to rotate integrally with the receiving member.
また、前記棒状シール部材は、前記環状シール部材間に
渡って前記受部材内面に当接するように、前記軸部材と
一体的に回動するように設けることもできる。Further, the rod-shaped seal member may be provided so as to rotate integrally with the shaft member so as to come into contact with the inner surface of the receiving member across the annular seal member.
作 用
本発明によれば、軸部材、受部材、環状シール部材によ
り囲まれた隙間部分を、この軸受がラジアル方向に荷重
を受けたときに、棒状シール部材により２つの室に分割
するようにしており、軸部材と受部材の一方が回動（揺
動）したときに、該棒状シール部材により画成された２
つの室の一方においては、圧力が上昇するから、軸部材
と受部材の接触部分に潤滑油が強制的に供給され、潤滑
油による被膜の形成が促進され、他方の室においては、
圧力が低下するから、この部分に潤滑油を供給するよう
に給油孔の位置を適宜設定することにより、潤滑油の吸
入が促進される。According to the present invention, the gap portion surrounded by the shaft member, the receiving member, and the annular seal member is divided into two chambers by the rod-shaped seal member when the bearing receives a load in the radial direction. When one of the shaft member and the receiving member rotates (swings), the two parts defined by the rod-shaped seal member
In one of the two chambers, as the pressure increases, lubricating oil is forcibly supplied to the contact area between the shaft member and the receiving member, promoting the formation of a film of lubricating oil, and in the other chamber,
Since the pressure decreases, suction of the lubricating oil is promoted by appropriately setting the position of the oil supply hole so that the lubricating oil is supplied to this area.
実 施 例 以下、本発明の実施例を図面に基づいて詳述する。Example Hereinafter, embodiments of the present invention will be described in detail based on the drawings.
第１図は本発明を適用したすべり軸受の構成を示す一実
施例断面図、第２図は第１図の■−■線に沿った断面及
び油圧回路を示す図、第３図は一実施例に採用したシー
ル部材を示す斜視図である。Fig. 1 is a cross-sectional view of one embodiment showing the structure of a sliding bearing to which the present invention is applied, Fig. 2 is a cross-sectional view along the line ■-■ of Fig. 1 and a diagram showing a hydraulic circuit, and Fig. 3 is an embodiment of the slide bearing. FIG. 3 is a perspective view showing a sealing member adopted as an example.
１１はピン（軸部材）であり、ピン１１はピン支持体１
２にその両端部近傍が支持されているとともに、その一
端部には拘束プレート１３が一体的に固着され、ビン支
持体１２からの抜けと回転が防止されている。１４はブ
ツシュ（受部材）１５はブツシュ支持体であり、ブツシ
ュ１４はピン１１の外径よりも僅かに大径の内径を有す
るリング状の部材で、ブツシュ支持体１５に対して一体
的な動作をなすように嵌合・接着されている。11 is a pin (shaft member), and the pin 11 is the pin support 1
The vicinity of both ends thereof is supported by the bottle support member 2, and a restraining plate 13 is integrally fixed to one end thereof to prevent the bottle support member 12 from coming off and rotating. Reference numeral 14 denotes a bushing (receiving member); 15 is a bushing support; the bushing 14 is a ring-shaped member having an inner diameter slightly larger than the outer diameter of the pin 11; They are fitted and bonded to form a
ブツシュ１４の内側面には一対の環状溝が形成されてい
るとともに、この環状溝に渡って軸方向に直線状の溝が
形成されている。これらの環状溝及び直線溝には、第３
図に示されるような、棒状シール部１６ａ及びその両端
部に環状シール部１６ｂ、１６ｂを一体的に設けてなる
シールＳ材１６が挿入されるかたちで設けられている。A pair of annular grooves are formed on the inner surface of the bush 14, and a linear groove is formed in the axial direction across the annular grooves. These annular grooves and straight grooves have a third
As shown in the figure, a seal S material 16, which is formed by integrally providing a rod-shaped seal portion 16a and annular seal portions 16b, 16b at both ends thereof, is provided in an inserted manner.
シール部材１６の環状シール部１６ｂ、１６ｂの内面は
ピン１１の外周に当接しており、ピン１１とブツシュ１
４との隙間部分を軸受外部から隔離している。The inner surfaces of the annular seal portions 16b, 16b of the seal member 16 are in contact with the outer periphery of the pin 11, and the pin 11 and the bush 1 are in contact with each other.
4 is isolated from the outside of the bearing.
プツシ：Ｌ１４には、第２図に示されているように、外
側から内側に貫通する一対の給油孔１７ａ。As shown in FIG. 2, pusher L14 has a pair of oil supply holes 17a penetrating from the outside to the inside.
１７ｂが互いに対向するように形成され、ブツシュ支持
体１５にはこれらに連続するかたちで、給油孔１８ａ、
１８ｂが形成され、これらの孔１７ａ、１７ｂ、１８ａ
、１８ｂを介してピン１１とブツシュ１４との隙間部分
に潤滑油が供給されるようになっている。17b are formed to face each other, and the bush support 15 has oil supply holes 18a,
18b is formed, and these holes 17a, 17b, 18a
, 18b, lubricating oil is supplied to the gap between the pin 11 and the bush 14.
このすべり軸受に対する潤滑油は、第２図に示されるよ
うな油圧回路により供給される。第２図において、１９
ａ、１９ｂはブツシュ支持体１５の給油孔ｘｇａ、１８
ｂに接続された潤滑油導管、２０はアキュムレータ、２
１はアキュムレータ圧保持用逆止弁、２２は管内の圧力
が上昇した場合の安全機構としてのリリーフ弁である。Lubricating oil for this sliding bearing is supplied by a hydraulic circuit as shown in FIG. In Figure 2, 19
a, 19b are oil supply holes xga, 18 of the bush support 15
a lubricating oil conduit connected to b, 20 an accumulator, 2
1 is a check valve for maintaining the accumulator pressure, and 22 is a relief valve as a safety mechanism when the pressure inside the pipe increases.
２３は潤滑油供給用のポンプ、２４は潤滑油タンク、２
５ａ、２５ｂは軸受内の圧力が異常に上昇した場合の安
全機構としてのリリーフ弁、２６ａ、２６ｂは潤滑油供
給用逆止弁である。このような油圧回路により、ピン１
１とブツシュ１４との隙間部分に対して潤滑油を二箇所
から給油するようになっている。23 is a lubricating oil supply pump, 24 is a lubricating oil tank, 2
5a and 25b are relief valves as a safety mechanism in case the pressure inside the bearing increases abnormally, and 26a and 26b are check valves for lubricating oil supply. With this hydraulic circuit, pin 1
Lubricating oil is supplied to the gap between the bushing 1 and the bushing 14 from two locations.
このすべり軸受はラジアル方向（軸方向に対して直角方
向）の荷重を負担するものであり、第２図中のＡ点は、
このすべり軸受が外部から荷重を受けてピン１１とブツ
シュ１４とが接触している位置を示している。以下、説
明の便宜上、ピン１１は回動（揺動）せず、ブツシュ１
４を含むブツシュ支持体１５が回動（揺動）するものと
し、ピン１１とブツシュ１４の接触位置（Ａ点）は回動
によって移動しないものとする。This sliding bearing bears the load in the radial direction (direction perpendicular to the axial direction), and point A in Fig. 2 is
This slide bearing is shown at a position where the pin 11 and the bush 14 are in contact with each other when they receive a load from the outside. Hereinafter, for convenience of explanation, the pin 11 does not rotate (swing) and the bush 1
It is assumed that the bushing support body 15 including the bushing 4 rotates (swings), and the contact position (point A) between the pin 11 and the bushing 14 does not move due to the rotation.
いま、ブツシュ１４、ブツシュ支持体１５が時計方向に
回転する場合を考える。このとき、比較的下側に位置す
るシール部材１６の棒状シール部１６ａは、ブツシュ１
４の回動に伴って、左上方向に移動しながらＡ点に接近
する。これにより、ピン１１、ブツシュ１４、シール部
材１６の棒状シール部１６ ａ、 ２ツ（Ｄ３Ｘ状シー
ル部１６ｂ、１６ｂ、及びＡ点で囲まれる図示左側の室
Ｂの体積は減少する。この室已にはもともと潤滑油が充
満しているので、この体積の減少に伴い潤滑油圧力が高
圧となり、潤滑油がＡ点に強制的に押し込まれ、潤滑油
被膜が保持されることになる。尚、給油孔１７ａの部分
においては油圧回路による潤滑油により加圧状態にある
から、通常は潤滑油が逆流することはない。室Ｂ内の圧
力が過大となった場合には、す９−）弁２５ａが作動し
、この圧力を解放するようになっている。Now, consider the case where the bushing 14 and the bushing support 15 rotate clockwise. At this time, the rod-shaped seal portion 16a of the seal member 16 located relatively below the bush 1
Along with the rotation of 4, it approaches point A while moving toward the upper left. As a result, the volume of the chamber B on the left side in the figure, which is surrounded by the pin 11, the bush 14, the rod-shaped seal portions 16a and 2 (D3X-shaped seal portions 16b, 16b, and point A) of the seal member 16, decreases. is originally filled with lubricating oil, so as this volume decreases, the lubricating oil pressure increases, forcing the lubricating oil to point A, and maintaining the lubricating oil film. Since the oil supply hole 17a is pressurized by lubricating oil from the hydraulic circuit, normally the lubricating oil will not flow backwards.If the pressure in chamber B becomes excessive, the valve 9-) 25a is activated to relieve this pressure.
ピン１１、ブツシュ１４、シール部材１６の棒状シール
部１６ａ、２つの環状シール部１６ｂ。The pin 11, the bush 14, the rod-shaped seal portion 16a of the seal member 16, and the two annular seal portions 16b.
１６ｂ１及びＡ点て囲まれる図示右側の室Ｃはこれと逆
に、その体積が増大するので負圧となり、アキュムレー
タ２０に蓄圧された潤滑油は逆止弁２６ｂ、潤滑油導管
１９ｂ、ブツシュ１４及びブツシュ支持体１５の給油孔
１７ｂ、１８ｂを経て、この室Ｃ内に吸入される。これ
により供給される潤滑油は、シール部材１６の環状シー
ル部１６ｂ等から漏れ出た潤滑油を補填するためのもの
である。漏出油量よりも多く潤滑油が供給される等によ
り室Ｃ内の潤滑油圧力が過大となった場合には、リリー
フ弁２５ｂが作動してこの圧力を解放する。On the contrary, the chamber C on the right side of the figure surrounded by 16b1 and point A becomes negative pressure as its volume increases, and the lubricating oil accumulated in the accumulator 20 flows through the check valve 26b, the lubricating oil conduit 19b, the bush 14 and The oil is sucked into this chamber C through the oil supply holes 17b and 18b of the bush support 15. The lubricating oil thus supplied is for replenishing the lubricating oil leaking from the annular seal portion 16b of the seal member 16 and the like. When the lubricating oil pressure in the chamber C becomes excessive due to, for example, lubricating oil being supplied in an amount larger than the amount of leaked oil, the relief valve 25b operates to release this pressure.
上述したように、シール部材１６の棒状シール部１６ａ
が移動することで、室Ｂ及び室Ｃの体積が変化すること
による圧力の増減により、ビン１１とブツシュ１４との
接触部分くＡ点）における潤滑油切れを防止するととも
に、ビン１１とブツシュ１４との隙間部分に潤滑油を吸
入するようにしており、非常に効率的である。As described above, the rod-shaped seal portion 16a of the seal member 16
By moving, the pressure increases and decreases due to changes in the volumes of chambers B and C, which prevents lubricating oil from running out at the contact point A between the bottle 11 and the bushing 14. The lubricating oil is sucked into the gap between the two and is extremely efficient.
また、上記一実施例においては、シール部材１６はブツ
シュ１４に形成された溝に挿入されるかたちで設けられ
、ブツシュ１４の回動に追動するようにしているが、本
発明性の実施例として、以下のように構成しても良い。Furthermore, in the embodiment described above, the sealing member 16 is provided to be inserted into a groove formed in the bushing 14 and follows the rotation of the bushing 14, but in the embodiment of the present invention It may be configured as follows.
即ち、シール部材１６の棒状シール部１６ａ及び２つの
環状ンール部１６ｂ、１６ｂが嵌合する溝を、ビン１１
に形成し、ビン１１の回動に追動するようにシール部材
１６を装着して構成する。That is, the groove in which the rod-shaped seal portion 16a and the two annular ring portions 16b, 16b of the seal member 16 fit is formed on the bottle 11.
A seal member 16 is attached to follow the rotation of the bottle 11.
上記一実施例に示した構成であると、ブツシュ１４の回
動に同期して、ビン１１とブツシュ１４の接触点Ａが移
動した場合には結果としてシール部材１６の棒状シール
部１６ａと該接触点へとの相対位置が変化しないことに
なり、室Ｂ及び室Ｃの体積変化が起こらずその効果を生
じない。このような場合には、ピンｌｌ側にシール部材
１６を装着して構成することにより、該接触点Ａとシー
ル部材１６の棒状シール部１６ａとの相対位置が変化し
、本発明による効果を享受することができる。いずれの
すべり軸受を使用するかは実際の用途に応じて適宜選定
すればよい。With the configuration shown in the above embodiment, when the contact point A between the bottle 11 and the bush 14 moves in synchronization with the rotation of the bush 14, as a result, the rod-shaped seal portion 16a of the seal member 16 and the contact point A move. Since the relative position to the point does not change, the volume of chambers B and C does not change and the effect does not occur. In such a case, by attaching the seal member 16 to the pin 11 side, the relative position between the contact point A and the rod-shaped seal portion 16a of the seal member 16 changes, and the effects of the present invention can be enjoyed. can do. Which sliding bearing to use may be appropriately selected depending on the actual application.
尚、上記性の実施例において、棒状シール部１６ａのブ
ツシュ１４の給油孔１７ａ、１８ｂに対する干渉が問題
となる場合には、給油孔はブツシュ１４にではなくビン
１１に設けて対応することができる。In the embodiment described above, if interference of the rod-shaped seal portion 16a with the oil supply holes 17a, 18b of the bush 14 becomes a problem, the oil supply hole can be provided in the bottle 11 instead of in the bush 14. .
また、上記２つの実施例において、棒状シール部１６ａ
及び環状シール部１６ｂ、１６ｂがビン１１又はブツシ
ュ１４に十分に密着するようにするため、シール部材１
６はビン１１又はブツシュ１４に十分なつぶし代をもっ
て装着する必要がある。さらに、シール部材１６の棒状
シール部１６ａと環状シール部１６ｂ、１６ｂとは一体
的に形成しているが、本発明はこれに限定されず、これ
らの接合部での密閉性が保たれれば分離していてもかま
わない。Furthermore, in the above two embodiments, the rod-shaped seal portion 16a
In order to ensure that the annular seal portions 16b and 16b are in close contact with the bottle 11 or the bush 14, the seal member 1 is
6 needs to be attached to the bottle 11 or bush 14 with sufficient crushing allowance. Further, although the rod-shaped seal portion 16a and the annular seal portions 16b, 16b of the seal member 16 are integrally formed, the present invention is not limited to this, and as long as the sealing performance at these joints is maintained. It doesn't matter if they are separated.
発明の効果
本発明は以上詳述したように、軸部材と受部材の隙間に
軸方向に渡る棒状シール部材を設け、ラジアル方向の荷
重が作用した際に、軸部材と受部材の接触部及びこの棒
状シール部材により画成される前記隙間の各室の体積が
、軸受の回動又は揺動によりそれぞれ増減し、これによ
り、各室内に圧力変化を生じせしめ、高圧力の室側から
潤滑油を強制的に該接触部に供給することができるから
、該接触部に潤滑油被膜を形成することができ、焼き付
は等の障害発生を減少することができるという効果を奏
する。Effects of the Invention As described in detail above, the present invention provides a rod-shaped seal member extending in the axial direction in the gap between the shaft member and the receiving member, and when a load in the radial direction is applied, the contact portion between the shaft member and the receiving member and The volume of each chamber in the gap defined by this rod-shaped seal member increases or decreases due to the rotation or rocking of the bearing, which causes a pressure change in each chamber, causing lubricating oil to flow from the high-pressure chamber side. Since the lubricating oil can be forcibly supplied to the contact portion, a lubricant film can be formed on the contact portion, and the occurrence of troubles such as seizure can be reduced.
第１図は本発明一実施例の構成を示す断面図、第２図は
第１図の■−■線に沿った断面及び油圧回路の構成を示
す図、
第３図は本発明一実施例におけるシール部材の斜視図、
′Ｍ４図は従来技術を示す断面図、
第５１！Ｉは第４図の■−ｖ線に沿った断面図である。
１１・・・ビン（軸部材）、
１４・・・ブツシュ（受託材）、
１６・・・シール部材、
１６ａ・・・棒状シール部（棒状シール部材）、ｂ・・
・環状シール部。Fig. 1 is a cross-sectional view showing the configuration of an embodiment of the present invention, Fig. 2 is a cross-sectional view taken along the line ■-■ in Fig. 1 and a diagram showing the configuration of a hydraulic circuit, and Fig. 3 is an embodiment of the present invention. Figure 51 is a perspective view of the sealing member in Figure 51. 'M4 is a sectional view showing the prior art. I is a cross-sectional view taken along the line ■-v in FIG. 4. 11... Bottle (shaft member), 14... Bush (contracted material), 16... Seal member, 16a... Rod-shaped seal part (rod-shaped seal member), b...
・Annular seal part.
Claims (1)
を挿入し、受部材又は軸部材に設けた給油孔を介して軸
部材と受部材との隙間部分に潤滑油を供給するようにす
るとともに、該隙間部分に供給した潤滑油の漏れを防止
するための環状のシール部材を該隙間部分の少なくとも
二箇所に介装してなるすべり軸受において、 前記環状シール部材間に渡って前記軸部材表面に当接す
る棒状のシール部材を、前記受部材と一体的に回動する
ように設けたことを特徴とするすべり軸受。 ２、軸部材より僅かに大径の穴を有する受部材に軸部材
を挿入し、受部材又は軸部材に設けた給油孔を介して軸
部材と受部材との隙間部分に潤滑油を供給するようにす
るとともに、該隙間部分に供給した潤滑油の漏れを防止
するための環状のシール部材を該隙間部分の少なくとも
二箇所に介装してなるすべり軸受において、 前記環状シール部材間に渡って前記受部材内面に当接す
る棒状のシール部材を、前記軸部材と一体的に回動する
ように設けたことを特徴とするすべり軸受。 ３、前記受部材又は軸部材に設ける潤滑油供給のための
給油孔を互いに対向するように二箇所に設け、前記棒状
シール部材の移動による前記軸部材と受部材との隙間部
分内の圧力変化により、潤滑油が吸入されるようにした
ことを特徴とする請求項１又は２記載のすべり軸受。[Scope of Claims] 1. The shaft member is inserted into a receiving member having a hole with a slightly larger diameter than the shaft member, and the gap between the shaft member and the receiving member is inserted through the receiving member or the oil supply hole provided in the shaft member. A sliding bearing comprising annular sealing members interposed at at least two locations in the gap for supplying lubricating oil to the gap and preventing leakage of the lubricant supplied to the gap, wherein the annular A sliding bearing characterized in that a rod-shaped sealing member that abuts the surface of the shaft member across between the sealing members is provided so as to rotate integrally with the receiving member. 2. Insert the shaft member into a receiving member that has a hole with a slightly larger diameter than the shaft member, and supply lubricating oil to the gap between the shaft member and the receiving member through the receiving member or the oil supply hole provided in the shaft member. In a sliding bearing comprising annular seal members interposed at at least two locations in the gap portion to prevent leakage of lubricating oil supplied to the gap portion, the slide bearing has the following features: A sliding bearing characterized in that a rod-shaped seal member that abuts the inner surface of the receiving member is provided so as to rotate integrally with the shaft member. 3. Oil supply holes for supplying lubricating oil provided in the receiving member or the shaft member are provided at two locations facing each other, and pressure changes in the gap between the shaft member and the receiving member due to movement of the rod-shaped seal member. 3. The sliding bearing according to claim 1, wherein lubricating oil is sucked into the sliding bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2107350A JP2634478B2 (en) | 1990-04-25 | 1990-04-25 | Plain bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2107350A JP2634478B2 (en) | 1990-04-25 | 1990-04-25 | Plain bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH048918A true JPH048918A (en) | 1992-01-13 |
| JP2634478B2 JP2634478B2 (en) | 1997-07-23 |
Family
ID=14456831
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2107350A Expired - Fee Related JP2634478B2 (en) | 1990-04-25 | 1990-04-25 | Plain bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2634478B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5599327A (en) * | 1993-12-16 | 1997-02-04 | Terumo Kabushiki Kaisha | Connector |
| WO2012169130A1 (en) * | 2011-06-09 | 2012-12-13 | オイレス工業株式会社 | Synthetic-resin plain bearing |
| JP2017137972A (en) * | 2016-02-05 | 2017-08-10 | 株式会社牧野フライス製作所 | Lubricant supply device |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61136019A (en) * | 1984-11-30 | 1986-06-23 | Hitachi Ltd | Axle bearing device |
-
1990
- 1990-04-25 JP JP2107350A patent/JP2634478B2/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61136019A (en) * | 1984-11-30 | 1986-06-23 | Hitachi Ltd | Axle bearing device |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5599327A (en) * | 1993-12-16 | 1997-02-04 | Terumo Kabushiki Kaisha | Connector |
| WO2012169130A1 (en) * | 2011-06-09 | 2012-12-13 | オイレス工業株式会社 | Synthetic-resin plain bearing |
| KR101496906B1 (en) * | 2011-06-09 | 2015-02-27 | 오일레스고교 가부시키가이샤 | Synthetic resin-made sliding bearing |
| US9091297B2 (en) | 2011-06-09 | 2015-07-28 | Oiles Corporation | Synthetic resin-made sliding bearing |
| US9618035B2 (en) | 2011-06-09 | 2017-04-11 | Oiles Corporation | Synthetic resin-made sliding bearing |
| JP2017137972A (en) * | 2016-02-05 | 2017-08-10 | 株式会社牧野フライス製作所 | Lubricant supply device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2634478B2 (en) | 1997-07-23 |
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