JP2004308684A - Sintered oil retaining bearing - Google Patents

Sintered oil retaining bearing Download PDF

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Publication number
JP2004308684A
JP2004308684A JP2003099061A JP2003099061A JP2004308684A JP 2004308684 A JP2004308684 A JP 2004308684A JP 2003099061 A JP2003099061 A JP 2003099061A JP 2003099061 A JP2003099061 A JP 2003099061A JP 2004308684 A JP2004308684 A JP 2004308684A
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JP
Japan
Prior art keywords
bearing
rotating shaft
diameter
enlarged diameter
sintered oil
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Pending
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JP2003099061A
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Japanese (ja)
Inventor
Tsuneo Maruyama
恒夫 丸山
Teruo Shimizu
輝夫 清水
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Mitsubishi Materials Corp
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Mitsubishi Materials Corp
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Application filed by Mitsubishi Materials Corp filed Critical Mitsubishi Materials Corp
Priority to JP2003099061A priority Critical patent/JP2004308684A/en
Priority to KR1020057018238A priority patent/KR20050116395A/en
Priority to EP04725193.9A priority patent/EP1610011B1/en
Priority to US10/551,739 priority patent/US8360648B2/en
Priority to PCT/JP2004/004814 priority patent/WO2004090360A1/en
Priority to CNB2004800086331A priority patent/CN100395460C/en
Priority to EP12152069.6A priority patent/EP2447555B1/en
Publication of JP2004308684A publication Critical patent/JP2004308684A/en
Priority to US13/676,757 priority patent/US8726515B2/en
Pending legal-status Critical Current

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Abstract

<P>PROBLEM TO BE SOLVED: To provide a sintered oil retaining bearing capable of obtaining high durability without damaging a rotary shaft and the bearing itself even though the rotary shaft is inclined inside the bearing by receiving large shearing load. <P>SOLUTION: The sintered oil retaining bearing has a bearing hole 3 with a circular cross section supporting the rotary shaft 2 on a bearing body 1 made of sintered metal. The bearing hole 3 is provided with a shaft supporting portion 3a with a uniform diameter having the inside of the bearing hole 3 functioning as a frictional surface and tapered enlarged diameter portions 3b and 3c formed continuously with the shaft supporting portion 3a and arranged on both sides of the bearing hole 3 at an axial direction by enlarging its diameter outwardly. The distance between a straight line L1a extending an inclined surface of one enlarged diameter portion 3b and a straight line L1b extending an inclined surface of the other enlarged diameter portion 3c being opposite with the inclined surface of one enlarged diameter portion 3b while sandwiching the center of the bearing body 1 is roughly equal to the diameter D of the rotary shaft 2. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】
本発明は、焼結含油軸受に関する。
【０００２】
【従来の技術】
焼結体の内部にあらかじめ潤滑油を含侵させておき、軸の回転によるポンプ作用と摩擦熱による熱膨張で油をしみ出させて摩擦面を潤滑する焼結含油軸受は、無給油で長期間使用できることから、自動車や家電製品、音響機器等の回転軸の軸受として広く採用されている。
【０００３】
上記従来の焼結含油軸受においては、軸受孔に挿通された回転軸を心出し（軸受の中心軸線と回転軸の軸線とを一致させること）するために、軸受孔の一部分を他の部分より小径にし、この部分だけを回転軸に接触させる構造を採用している。
【０００４】
ところで、上記のように軸受孔の一部分を他の部分より小径にすると、軸受全体の長さに対して実際に回転軸に接触する部分の長さが短くなるために軸支持の状態が不安定になり易く、回転軸が心ずれし易いという問題がある。
【０００５】
そこで、従来の焼結含油軸受の中には、軸受孔を、回転軸を支持する軸支部と、軸支部に連なって外方に向かって径が拡大する拡径部とからなる形状とし、さらに拡径部の焼結密度を軸支部より密に形成して回転軸の心ずれを抑制するものがある（例えば下記の特許文献１）。
【０００６】
この構造を採用した軸受においては、回転軸にせん断荷重が作用すると、回転軸に振れが生じることで回転軸と軸支部との間を潤滑していた潤滑油が拡径部側に押し出され、回転軸と拡径部との間に充たされる。回転軸と拡径部との間に充たされた潤滑油は、回転軸が振れることで拡径部に押し付けられるように加圧されるが、拡径部が密に形成されていることから、軸受本体の内部には押し込まれず、回転軸と拡径部との間に残って回転軸に対し反力を作用させる。この反力により回転軸の振れが抑制され、軸受に対する回転軸の心ずれが防止される。
【０００７】
【特許文献１】
特公平８−１９９４１号公報
【０００８】
【発明が解決しようとする課題】
上記のような構造は回転軸の心ずれを抑制するうえで非常に有効である。しかしながら、回転軸に振れを生じさせるせん断荷重が非常に大きく、回転軸と拡径部との間に残った潤滑油による押し返し作用が十分に機能しなかった場合は、回転軸が軸受本体の内部で軸線を傾斜させたまま支持されることになる。このとき、回転軸の表面が軸支部と拡径部との境界に押し付けられ、軸受本体に対して点で接する。ここでは、回転軸があたかもてこのように作用して軸支部の両端を抉る（こじる）動きをし、接点において回転軸と軸受本体との間に力の集中が起こる。このような力の集中が起こると、この点を中心として過度の摩耗や過熱が起こることが考えられる。こういった現象は、回転軸と拡径部との間に充ちた潤滑油による押し返し作用が機能する限りは起こり得ないが、突発的に予期せぬ大きなせん断荷重が作用したとすれば、回転軸や軸受の耐久性が損なわれる可能性がある。
【０００９】
本発明は上記の事情に鑑みてなされたものであり、回転軸が大きなせん断荷重を受けて軸受内部で傾斜しても、回転軸や自らを傷めることがなく高い耐久性が得られる焼結含油軸受を提供することを目的としている。
【００１０】
【課題を解決するための手段】
上記の課題を解決するための手段として、次のような構成の焼結含油軸受を採用する。すなわち本発明に係る請求項１記載の焼結含油軸受は、焼結金属により形成された軸受本体に、回転軸を支持する断面円形の軸受孔が形成された焼結含油軸受において、
前記軸受孔が、内側を摩擦面として径の大きさが一定の軸支部と、
該軸支部に連なって軸方向の両側にそれぞれ設けられ、外方に向かって径が拡大してテーパ状をなす拡径部とを備え、
前記軸支部の一側方に設けられた一方の拡径部の前記長手方向に対するテーパ角と、前記軸支部の他側方に設けられた他方の拡径部の前記長手方向に対するテーパ角とが等しく、
かつ前記一方の拡径部の傾斜面を傾斜方向に延長した直線と、前記他方の拡径部の傾斜面を傾斜方向に延長した直線とが平行配置されるとともに両直線の間隔が前記回転軸の径にほぼ等しいことを特徴とする。
【００１１】
請求項２記載の焼結含油軸受は、請求項１記載の焼結含油軸受において、前記双方の拡径部の前記長手方向に対するテーパ角がいずれも３°以下であることを特徴とする。
【００１２】
請求項３記載の焼結含油軸受は、焼結金属により形成された軸受本体に、回転軸を支持する断面円形の軸受孔が形成された焼結含油軸受において、
前記軸受孔が、内側を摩擦面として前記回転軸よりも大径でかつ径の大きさが一定の軸支部と、
該軸支部に連なって設けられ、外方に向かって径が拡大してテーパ状をなす拡径部とを備え、
該拡径部の傾斜面を傾斜方向に延長した直線と、前記軸受本体の中央を挟んで前記拡径部の傾斜面と対向する前記軸支部との間隔が、前記回転軸の径にほぼ等しいことを特徴とする。
【００１３】
請求項４記載の焼結含油軸受は、請求項３記載の焼結含油軸受において、前記回転軸の前記長手方向に対する前記拡径部のテーパ角が３°以下であることを特徴とする。
【００１４】
回転軸に振れを生じさせるせん断荷重が非常に大きく、回転軸と拡径部との間に残った潤滑油による押し返し作用が十分に機能しなかった場合、回転軸が軸受本体の内部で軸線を傾斜させたまま支持されることになる。このような場合、本発明においては、回転軸が軸支部の両端を抉（こじ）たりせず、拡径部に押し付けられて線で接するため、この部分において回転軸と軸受本体との間に力の集中が起こらない。したがって、過度の摩耗や過熱も起こらない。
【００１５】
【発明の実施の形態】
本発明に係る焼結含油軸受の第１の実施形態を図１および図２に示して説明する。
図１に示す焼結含油軸受（以下では単に軸受とする）は、焼結金属により形成された軸受本体１の内部に、回転軸２が挿通される軸受孔３が形成されている。軸受孔３は、回転軸２の長手方向の軸線Ｏに直交する面内における断面形状が円形をなしており、軸受本体１のほぼ中央にあって回転軸２の直径よりも径が若干大きく、かつ長手方向のいずれの位置においても径の大きさが一定の軸支部３ａと、軸支部３ａに連なって長手方向の両側にそれぞれ設けられ、外方に向かって単調に径が拡大してテーパ状をなす拡径部３ｂ，３ｃとを備えている。いずれの拡径部３ｂ，３ｃも、その傾斜面と軸受本体１の軸方向に平行な直孔部３ａの内面（または回転軸２の軸線Ｏ）とがなす角（テーパ角）θ１は、３°以下に設定されている。なお、図１ではθ１を明確にするために誇張して図示してある。
【００１６】
軸受本体１を回転軸２の軸線Ｏに沿う断面で見るとき（図１参照）、軸支部３ａを挟んで存在する２つの拡径部３ｂ，３ｃについては、一方の拡径部３ｂの傾斜面を軸受本体１の中央に向けて傾斜方向に延長した直線Ｌ１ａと、対角に位置する他方の拡径部３ｃの傾斜面を軸受本体１の中央に向けて傾斜方向に延長した直線Ｌ１ｂとが平行配置されるとともに、両直線Ｌ１ａ，Ｌ１ｂの間隔ｄ１が、回転軸２の直径Ｄよりも若干大きく、かつ軸支部３ａの内径にほぼ等しくなっている。
【００１７】
拡径部３ｂ，３ｃをなす軸受本体１の内壁部４は、軸支部３ａをなす内壁部５よりも焼結密度が高い、すなわち内壁部４の表面および内部に残る気孔が、内壁部５の表面および内部に残る気孔よりも小さく、数も少なくなっている。このような軸受本体１の各部における粗密の違いは、焼結工程の後に行う矯正（再加圧）工程において、該当する部分に対する加圧力を加減することによって実現されている。
【００１８】
上記構成の軸受は、軸受本体１に潤滑油を含侵させたうえで、軸受孔３に回転軸２を挿通されて使用される。軸受に支持された回転軸２を回転させるために比較的小さなトルクが伝達されたときには、回転軸２に作用するせん断荷重も小さく、回転軸２に振れはほとんど生じないので、回転軸２の表面が軸支部３ａに接し、この部分を摩擦面として支持される。軸支部３ａでは、回転軸２の回転によるポンプ作用と摩擦熱による熱膨張とによって軸受本体１の内部から潤滑油がしみ出し、摩擦面を潤滑する。
【００１９】
回転軸２を回転させるために大きなトルクが伝達されたときには、回転軸２に作用するせん断荷重が大きく、回転軸２に強い振れが生じて心ずれを起こそうとする。このとき、回転軸２に振れが生じたことで、回転軸２と軸支部３ａとの間を潤滑していた潤滑油が一方の拡径部３ｂ側、および他方の拡径部３ｃ側に押し出され、回転軸２と拡径部３ｂとの間、および回転軸２と拡径部３ｃとの間に充たされる。回転軸２と拡径部３ｂ，３ｃとの間に充たされた潤滑油は、回転軸２が振れることで拡径部３ｂ，３ｃに押し付けられるように加圧されるが、拡径部３ｂ，３ｃが密に形成されていることから、軸受本体１の内部には押し込まれず、回転軸２と拡径部３ｂ，３ｃとの間に残って回転軸２に対し反力を作用させる。この反力により回転軸２の振れが抑制され、軸受に対する回転軸２の心ずれが防止される。
【００２０】
しかしながら、回転軸２に作用するせん断荷重が非常に大きく、回転軸２と拡径部３ｂ，３ｃとの間に残った潤滑油による押し返し作用が十分に機能しなかった場合は、回転軸２が軸受本体１の内部で軸線を傾斜させたまま軸支持されることになる。このとき、回転軸２の表面は、図２に示すように拡径部３ｂ，３ｃにそれぞれ点ではなく線で接するため、この部分においては回転軸２と軸受本体１との間に力の集中が起こらず、過度の摩耗や過熱が起こらない。
【００２１】
次に、本発明に係る焼結含油軸受の第２の実施形態を図３に示して説明する。なお、上記第１の実施形態において既に説明した構成要素には同一符号を付して説明は省略する。
本実施形態の軸受には、拡径部３ｂは軸支部３ａの一側方にのみ設けられており、軸支部３ａの他側方には面取り部３ｄが設けられている。この面取り部３ｄは、主に軸受孔３に回転軸２を通し易くするために設けられたもので、回転軸２が軸受本体１に対してどのように変位しようとも回転軸２に接することはない。
【００２２】
さらに、軸受本体１を回転軸２の軸線Ｏに沿う断面で見るとき（図３参照）、軸支部３ａと拡径部３ｂとについては、拡径部３ｂの傾斜面を軸受本体１の中央に向けて傾斜方向に延長した直線Ｌ１ａと、軸受本体１の中央を挟んで拡径部３ｂの傾斜面と対向する軸支部３ａの内壁面との間隔（拡径部３ｂから最も遠い軸支部３ａの終端部分に、直線Ｌ１ａから下ろした垂線の長さに相当する）ｄ２が、回転軸２の直径Ｄよりも若干大きく、かつ軸支部３ａの内径にほぼ等しくなっている。
また、本実施形態においても、拡径部３ｂの傾斜面と軸受本体１の軸方向に平行な直孔部３ａの内面（または回転軸２の軸線Ｏ）とがなす角（テーパ角）θ１は３°以下に設定されている。
【００２３】
上記構成の軸受において、回転軸２に作用するせん断荷重が非常に大きく、回転軸２と拡径部３ｂとの間に残った潤滑油による押し返し作用が十分に機能しなかった場合は、回転軸２が軸受本体１の内部で軸線を傾斜させたまま軸支持されることになるが、回転軸２の表面は拡径部３ｂに点ではなく線で接するため、この部分において回転軸２と軸受本体１との間に力の集中が起こらず、過度の摩耗や過熱が起こらない。
【００２４】
ところで、上記第１、第２の実施形態の軸受はいずれも、軸受本体１の各部に粗密の違いを設けて回転軸の心ずれを防止する構造を備えているが、本発明はこのような構造を備える焼結含油軸受にのみ適用されるものではなく、軸受本体の焼結密度が均一な焼結含油軸受にも適用可能であることはいうまでもない。
【００２５】
【発明の効果】
以上説明したように、本発明によれば、回転軸が大きなせん断荷重を受け、軸受内部で軸線を傾斜させても、回転軸の表面がテーパ状に形成された拡径部に線で接するため、この部分において回転軸と軸受本体との間に力の集中が起こらず、過度の摩耗や過熱が起こらない。したがって、回転軸や軸受自らが傷つくことがなく、高い耐久性が得られる。
【図面の簡単な説明】
【図１】本発明の第１の実施形態を示す図であって、回転軸の軸線方向に沿う平面で断面視した焼結含油軸受である。
【図２】軸受内部で傾斜した回転軸を示す全体概要図である。
【図３】本発明の第２の実施形態を示す図であって、回転軸の軸線方向に沿う平面で断面視した焼結含油軸受である。
【符号の説明】
１ 軸受本体
２ 回転軸
３ 軸受孔
３ａ 軸支部
３ｂ，３ｃ 拡径部
３ｄ 面取り部
Ｏ 軸線[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a sintered oil-impregnated bearing.
[0002]
[Prior art]
Lubricating oil is impregnated in the sintered body in advance, and the oil is extruded by the pump action due to the rotation of the shaft and the thermal expansion due to frictional heat to lubricate the friction surface. Because it can be used for a period, it is widely used as a bearing for rotating shafts of automobiles, home appliances, audio equipment, and the like.
[0003]
In the above-mentioned conventional sintered oil-impregnated bearing, in order to center the rotating shaft inserted in the bearing hole (to make the center axis of the bearing coincide with the axis of the rotating shaft), a part of the bearing hole is separated from other parts. A structure is adopted in which the diameter is reduced and only this portion is brought into contact with the rotating shaft.
[0004]
By the way, if one part of the bearing hole is made smaller in diameter than the other part as described above, the length of the part that actually contacts the rotating shaft becomes shorter than the entire length of the bearing, and the shaft support state becomes unstable. And there is a problem that the axis of rotation tends to be misaligned.
[0005]
Therefore, in conventional sintered oil-impregnated bearings, the bearing hole is formed of a shaft supporting portion that supports the rotating shaft, and a diameter-enlarging portion that is connected to the shaft supporting portion and whose diameter increases outward. There is one in which the sintering density of the enlarged diameter portion is formed more densely than that of the shaft support portion to suppress misalignment of the rotating shaft (for example, Patent Document 1 below).
[0006]
In a bearing employing this structure, when a shear load is applied to the rotating shaft, a run-out occurs in the rotating shaft, so that the lubricating oil that has lubricated between the rotating shaft and the shaft support portion is pushed out to the enlarged diameter portion side, It is filled between the rotating shaft and the enlarged diameter portion. The lubricating oil filled between the rotating shaft and the enlarged diameter portion is pressurized so as to be pressed against the enlarged diameter portion by swinging the rotating shaft, but because the enlarged diameter portion is formed densely. However, it is not pushed into the inside of the bearing main body, but remains between the rotating shaft and the enlarged diameter portion to exert a reaction force on the rotating shaft. Due to this reaction force, run-out of the rotary shaft is suppressed, and misalignment of the rotary shaft with respect to the bearing is prevented.
[0007]
[Patent Document 1]
Japanese Patent Publication No. 8-19941
[Problems to be solved by the invention]
The above structure is very effective in suppressing the misalignment of the rotating shaft. However, if the shearing load that causes runout on the rotating shaft is very large and the pushing back action by the lubricating oil remaining between the rotating shaft and the enlarged diameter portion does not function sufficiently, the rotating shaft will And is supported with the axis inclined. At this time, the surface of the rotating shaft is pressed against the boundary between the shaft support portion and the enlarged diameter portion and comes into contact with the bearing body at a point. In this case, the rotating shaft acts as if it were like this, and makes a movement of scooping (prying) both ends of the shaft support portion, and a concentration of force occurs between the rotating shaft and the bearing body at the contact point. If such a concentration of force occurs, excessive wear or overheating may occur around this point. These phenomena cannot occur as long as the push-back action of the lubricating oil filled between the rotating shaft and the enlarged diameter part functions, but if unexpected large shear loads are applied suddenly, The durability of shafts and bearings may be impaired.
[0009]
The present invention has been made in view of the above circumstances, and even when the rotating shaft receives a large shear load and tilts inside the bearing, a sintered oil-impregnated product that can obtain high durability without damaging the rotating shaft or itself. The purpose is to provide bearings.
[0010]
[Means for Solving the Problems]
As means for solving the above problems, a sintered oil-impregnated bearing having the following configuration is employed. That is, the sintered oil-impregnated bearing according to claim 1 according to the present invention is a sintered oil-impregnated bearing in which a bearing body having a circular cross section for supporting a rotating shaft is formed in a bearing body formed of a sintered metal,
The bearing hole, a shaft support portion having a constant diameter with the inside being a friction surface,
A diameter-enlarging portion which is provided on each side in the axial direction in connection with the shaft support portion, and has a diameter which increases outward and forms a tapered shape;
The taper angle with respect to the longitudinal direction of one enlarged diameter portion provided on one side of the shaft support portion, and the taper angle with respect to the longitudinal direction of the other enlarged diameter portion provided on the other side of the shaft support portion. equally,
In addition, a straight line extending the inclined surface of the one enlarged portion in the inclined direction and a straight line extending the inclined surface of the other enlarged portion in the inclined direction are arranged in parallel, and the interval between the two straight lines is the rotation axis. Is substantially equal to the diameter of
[0011]
The sintered oil-impregnated bearing according to claim 2 is characterized in that, in the sintered oil-impregnated bearing according to claim 1, both of the tapered angles of the two enlarged diameter portions with respect to the longitudinal direction are 3 ° or less.
[0012]
The sintered oil-impregnated bearing according to claim 3, wherein the bearing body formed of a sintered metal is provided with a bearing hole having a circular cross section for supporting a rotating shaft,
The bearing hole has a larger diameter than the rotating shaft with the inner side as a friction surface and a fixed diameter support portion,
A diameter-enlarging portion that is provided in continuation with the shaft support portion, and has a diameter that increases outward and forms a tapered shape;
An interval between a straight line that extends the inclined surface of the enlarged diameter portion in the inclination direction and the shaft support that faces the inclined surface of the enlarged diameter portion across the center of the bearing body is substantially equal to the diameter of the rotating shaft. It is characterized by the following.
[0013]
A sintered oil-impregnated bearing according to a fourth aspect is characterized in that in the sintered oil-impregnated bearing according to the third aspect, a taper angle of the enlarged diameter portion with respect to the longitudinal direction of the rotating shaft is 3 ° or less.
[0014]
If the shear load that causes runout on the rotating shaft is very large and the push-back action of the lubricating oil remaining between the rotating shaft and the enlarged diameter portion does not function sufficiently, the rotating shaft will It will be supported while inclined. In such a case, in the present invention, since the rotating shaft is pressed against the enlarged diameter portion and comes into contact with the line without making the ends of the shaft supporting portion gouge, the portion between the rotating shaft and the bearing body at this portion There is no concentration of power. Therefore, neither excessive wear nor overheating occurs.
[0015]
BEST MODE FOR CARRYING OUT THE INVENTION
A first embodiment of a sintered oil-impregnated bearing according to the present invention will be described with reference to FIGS.
In the sintered oil-impregnated bearing shown in FIG. 1 (hereinafter simply referred to as a bearing), a bearing hole 3 through which a rotating shaft 2 is inserted is formed inside a bearing body 1 formed of a sintered metal. The bearing hole 3 has a circular cross section in a plane perpendicular to the longitudinal axis O of the rotating shaft 2, is substantially at the center of the bearing body 1, and has a diameter slightly larger than the diameter of the rotating shaft 2. In addition, a shaft supporting portion 3a having a constant diameter at any position in the longitudinal direction and provided on both sides in the longitudinal direction so as to be continuous with the shaft supporting portion 3a. And enlarged diameter portions 3b and 3c. The angle (taper angle) θ1 between the inclined surface of each of the enlarged diameter portions 3b and 3c and the inner surface of the straight hole portion 3a (or the axis O of the rotating shaft 2) parallel to the axial direction of the bearing body 1 is 3 ° is set below. Note that FIG. 1 is exaggerated in order to clarify θ1.
[0016]
When the bearing body 1 is viewed in a cross section along the axis O of the rotating shaft 2 (see FIG. 1), the two enlarged diameter portions 3b and 3c sandwiching the shaft support 3a are inclined surfaces of one enlarged diameter portion 3b. A straight line L1a extending in the inclined direction toward the center of the bearing main body 1 and a straight line L1b extending in the inclined direction toward the center of the bearing main body 1 by extending the diagonally inclined surface of the other enlarged diameter portion 3c toward the center of the bearing main body 1. In addition to being arranged in parallel, the distance d1 between the straight lines L1a and L1b is slightly larger than the diameter D of the rotating shaft 2 and substantially equal to the inner diameter of the shaft support 3a.
[0017]
The inner wall portion 4 of the bearing body 1 forming the enlarged diameter portions 3b and 3c has a higher sintering density than the inner wall portion 5 forming the shaft support portion 3a, that is, pores remaining on the surface and inside of the inner wall portion 4 are formed. It is smaller and smaller in number than the pores remaining on the surface and inside. Such a difference in density in each part of the bearing body 1 is realized by increasing or decreasing the pressure applied to the corresponding part in a correction (re-pressurization) step performed after the sintering step.
[0018]
The bearing having the above configuration is used after the bearing body 1 is impregnated with lubricating oil and the rotating shaft 2 is inserted through the bearing hole 3. When a relatively small torque is transmitted to rotate the rotating shaft 2 supported by the bearing, the shear load acting on the rotating shaft 2 is small, and the rotating shaft 2 hardly oscillates. Is in contact with the shaft support 3a, and this portion is supported as a friction surface. In the shaft support 3a, the lubricating oil exudes from the inside of the bearing main body 1 due to the pumping action due to the rotation of the rotating shaft 2 and the thermal expansion due to frictional heat, and lubricates the friction surface.
[0019]
When a large torque is transmitted to rotate the rotating shaft 2, the shear load acting on the rotating shaft 2 is large, and a strong run-out occurs on the rotating shaft 2 to cause misalignment. At this time, due to the run-out of the rotating shaft 2, the lubricating oil that has lubricated between the rotating shaft 2 and the shaft support 3a is pushed out to the one enlarged diameter portion 3b side and the other enlarged diameter portion 3c side. The space between the rotating shaft 2 and the enlarged diameter portion 3b and the space between the rotating shaft 2 and the enlarged diameter portion 3c are filled. The lubricating oil filled between the rotating shaft 2 and the enlarged diameter portions 3b, 3c is pressurized so as to be pressed against the enlarged diameter portions 3b, 3c as the rotating shaft 2 swings. , 3c are densely formed, so that they are not pushed into the inside of the bearing main body 1 and remain between the rotating shaft 2 and the enlarged diameter portions 3b, 3c to exert a reaction force on the rotating shaft 2. The deflection of the rotating shaft 2 is suppressed by this reaction force, and the misalignment of the rotating shaft 2 with respect to the bearing is prevented.
[0020]
However, when the shearing load acting on the rotating shaft 2 is very large and the pushing back action by the lubricating oil remaining between the rotating shaft 2 and the enlarged diameter portions 3b, 3c does not function sufficiently, the rotating shaft 2 is The shaft is supported inside the bearing body 1 while keeping the axis inclined. At this time, since the surface of the rotating shaft 2 contacts the enlarged diameter portions 3b and 3c not by points but by lines as shown in FIG. 2, the concentration of force between the rotating shaft 2 and the bearing main body 1 in this portion. No excessive wear and overheating occur.
[0021]
Next, a second embodiment of the sintered oil-impregnated bearing according to the present invention will be described with reference to FIG. Note that the same reference numerals are given to the components already described in the first embodiment, and description thereof will be omitted.
In the bearing of this embodiment, the enlarged diameter portion 3b is provided only on one side of the shaft support 3a, and a chamfered portion 3d is provided on the other side of the shaft support 3a. The chamfered portion 3d is provided mainly for facilitating the passage of the rotating shaft 2 through the bearing hole 3, so that the rotating shaft 2 is in contact with the rotating shaft 2 regardless of how the rotating shaft 2 is displaced with respect to the bearing body 1. Absent.
[0022]
Further, when the bearing main body 1 is viewed in a cross section along the axis O of the rotating shaft 2 (see FIG. 3), with respect to the shaft support 3a and the enlarged diameter portion 3b, the inclined surface of the enlarged diameter portion 3b is located at the center of the bearing main body 1. Between the straight line L1a extending in the direction of inclination toward the inner wall surface of the shaft support portion 3a opposed to the inclined surface of the enlarged diameter portion 3b with the center of the bearing body 1 interposed therebetween (of the shaft support portion 3a furthest from the enlarged diameter portion 3b). D2) is slightly larger than the diameter D of the rotating shaft 2 and substantially equal to the inner diameter of the shaft support 3a.
Also in the present embodiment, the angle (taper angle) θ1 formed between the inclined surface of the enlarged diameter portion 3b and the inner surface of the straight hole portion 3a (or the axis O of the rotating shaft 2) parallel to the axial direction of the bearing body 1 is It is set to 3 ° or less.
[0023]
In the bearing having the above configuration, when the shear load acting on the rotating shaft 2 is very large and the pushing back action by the lubricating oil remaining between the rotating shaft 2 and the enlarged diameter portion 3b does not function sufficiently, The shaft 2 is supported inside the bearing body 1 while keeping its axis inclined. However, the surface of the rotating shaft 2 contacts the enlarged diameter portion 3b not by a point but by a line. There is no concentration of force between the main body 1 and excessive wear or overheating.
[0024]
By the way, the bearings of the first and second embodiments are both provided with a structure for preventing the misalignment of the rotating shaft by providing a difference in density between each part of the bearing body 1. It goes without saying that the present invention is not only applied to a sintered oil-impregnated bearing having a structure, but is also applicable to a sintered oil-impregnated bearing having a uniform sintered density of the bearing body.
[0025]
【The invention's effect】
As described above, according to the present invention, even if the rotating shaft receives a large shear load and the axis is inclined inside the bearing, the surface of the rotating shaft comes into contact with the tapered enlarged portion by a line. In this part, no concentration of force occurs between the rotating shaft and the bearing main body, so that excessive wear and overheating do not occur. Therefore, the rotating shaft and the bearings themselves are not damaged, and high durability can be obtained.
[Brief description of the drawings]
FIG. 1 is a view showing a first embodiment of the present invention, and is a sintered oil-impregnated bearing viewed in cross section along a plane along the axial direction of a rotating shaft.
FIG. 2 is an overall schematic diagram showing a rotating shaft inclined inside a bearing.
FIG. 3 is a view showing a second embodiment of the present invention, and is a sintered oil-impregnated bearing viewed in cross section along a plane along the axial direction of a rotating shaft.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Bearing main body 2 Rotating shaft 3 Bearing hole 3a Shaft support part 3b, 3c Large diameter part 3d Chamfer part O Axis line

Claims (4)

焼結金属により形成された軸受本体に、回転軸を支持する断面円形の軸受孔が形成された焼結含油軸受において、
前記軸受孔が、内側を摩擦面として径の大きさが一定の軸支部と、
該軸支部に連なって軸方向の両側にそれぞれ設けられ、外方に向かって径が拡大してテーパ状をなす拡径部とを備え、
前記軸支部の一側方に設けられた一方の拡径部の前記長手方向に対するテーパ角と、前記軸支部の他側方に設けられた他方の拡径部の前記長手方向に対するテーパ角とが等しく、
かつ前記一方の拡径部の傾斜面を傾斜方向に延長した直線と、前記他方の拡径部の傾斜面を傾斜方向に延長した直線とが平行配置されるとともに両直線の間隔が前記回転軸の径にほぼ等しいことを特徴とする焼結含油軸受。In a sintered oil-impregnated bearing in which a bearing body having a circular cross section for supporting a rotating shaft is formed in a bearing body formed of sintered metal,
The bearing hole, a shaft support portion having a constant diameter with the inside being a friction surface,
A diameter-enlarging portion which is provided on each side in the axial direction so as to be continuous with the shaft support portion, and has a diameter which increases outward and forms a tapered shape;
The taper angle with respect to the longitudinal direction of one enlarged diameter portion provided on one side of the shaft support portion, and the taper angle with respect to the longitudinal direction of the other enlarged diameter portion provided on the other side of the shaft support portion. equally,
In addition, a straight line extending the inclined surface of the one enlarged portion in the inclined direction and a straight line extending the inclined surface of the other enlarged portion in the inclined direction are arranged in parallel, and the interval between the two straight lines is the rotation axis. A sintered oil-impregnated bearing characterized by having a diameter substantially equal to the diameter of the oil-impregnated bearing. 前記双方の拡径部の前記長手方向に対するテーパ角がいずれも３°以下であることを特徴とする請求項１記載の焼結含油軸受。2. The sintered oil-impregnated bearing according to claim 1, wherein a taper angle of each of the enlarged diameter portions with respect to the longitudinal direction is 3 ° or less. 3. 焼結金属により形成された軸受本体に、回転軸を支持する断面円形の軸受孔が形成された焼結含油軸受において、
前記軸受孔が、内側を摩擦面として径の大きさが一定の軸支部と、
該軸支部に連なって設けられ、外方に向かって径が拡大してテーパ状をなす拡径部とを備え、
該拡径部の傾斜面を傾斜方向に延長した直線と、前記軸受本体の中央を挟んで前記拡径部の傾斜面と対向する前記軸支部との間隔が、前記回転軸の径にほぼ等しいことを特徴とする焼結含油軸受。In a sintered oil-impregnated bearing in which a bearing body having a circular cross section for supporting a rotating shaft is formed in a bearing body formed of sintered metal,
The bearing hole, a shaft support portion having a constant diameter with the inside being a friction surface,
A diameter-enlarging portion that is provided in continuation with the shaft support portion and has a diameter that increases outward and forms a tapered shape;
An interval between a straight line that extends the inclined surface of the enlarged diameter portion in the inclination direction and the shaft support that faces the inclined surface of the enlarged diameter portion across the center of the bearing body is substantially equal to the diameter of the rotating shaft. A sintered oil-impregnated bearing characterized in that: 前記回転軸の前記長手方向に対する前記拡径部のテーパ角が３°以下であることを特徴とする請求項３記載の焼結含油軸受。The sintered oil-impregnated bearing according to claim 3, wherein a taper angle of the enlarged diameter portion with respect to the longitudinal direction of the rotating shaft is 3 ° or less.
JP2003099061A 2003-04-02 2003-04-02 Sintered oil retaining bearing Pending JP2004308684A (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
JP2003099061A JP2004308684A (en) 2003-04-02 2003-04-02 Sintered oil retaining bearing
KR1020057018238A KR20050116395A (en) 2003-04-02 2004-04-01 Oil-impregnated sintered bearing and method of producing the same
EP04725193.9A EP1610011B1 (en) 2003-04-02 2004-04-01 Oil-impregnated sintered bearing and method of producing the same
US10/551,739 US8360648B2 (en) 2003-04-02 2004-04-01 Oil-impregnated sintered bearing and method of producing the same
PCT/JP2004/004814 WO2004090360A1 (en) 2003-04-02 2004-04-01 Oil-impregnated sintered bearing and method of producing the same
CNB2004800086331A CN100395460C (en) 2003-04-02 2004-04-01 Oil-impregnated sintered bearing and method of producing the same
EP12152069.6A EP2447555B1 (en) 2003-04-02 2004-04-01 Oil-impregnated sintered bearing and method of manufacturing the same
US13/676,757 US8726515B2 (en) 2003-04-02 2012-11-14 Oil-impregnated sintered bearing and method of producing the same

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