JPH11210747A - Journal bearing - Google Patents
Journal bearingInfo
- Publication number
- JPH11210747A JPH11210747A JP1446598A JP1446598A JPH11210747A JP H11210747 A JPH11210747 A JP H11210747A JP 1446598 A JP1446598 A JP 1446598A JP 1446598 A JP1446598 A JP 1446598A JP H11210747 A JPH11210747 A JP H11210747A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- inner ring
- rotating shaft
- ring
- journal 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.)
- Withdrawn
Links
Landscapes
- Sliding-Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、蒸気タービン・発
電機など大型回転機械の回転軸を支承するジャーナル軸
受に係わり、特に調心機能および振動抑制効果を与える
ようにしたジャーナル軸受に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a journal bearing for supporting a rotating shaft of a large rotating machine such as a steam turbine and a generator, and more particularly to a journal bearing having an aligning function and a vibration suppressing effect.
【０００２】[0002]
【従来の技術】図２０（ａ）および（ｂ）は一般的なジ
ャーナル軸受の正面断面図および側面断面図であって、
ジャーナル軸受は内周面に回転軸１を支承する軸受面２
ａを設けた上下２分割された内輪２と、その内輪２の外
周に内輪２と同心状に配設され、上記内輪２を支持する
上下２分割された外輪３から構成されている。2. Description of the Related Art FIGS. 20A and 20B are a front sectional view and a side sectional view of a general journal bearing.
The journal bearing has a bearing surface 2 for supporting the rotating shaft 1 on the inner peripheral surface.
The inner ring 2 is divided into upper and lower parts, and an outer ring 3 is provided on the outer periphery of the inner ring 2 concentrically with the inner ring 2 and supports the inner ring 2.
【０００３】外輪３は図示しない基礎台或はケーシング
に固定されており、内輪２の内周面には潤滑特性を良く
するためにホワイトメタル等の軸受合金が接着されてい
る。また、内輪２および外輪３には、回転軸１と内輪２
の軸受面２ａとの間の環状間隙内に潤滑油を給排する潤
滑油供給孔４および潤滑油排油孔５が穿設されており、
潤滑油供給孔４から供給された潤滑油が回転軸１と軸受
面２ａとの間の間隙を流れ、潤滑油排油孔５から軸受外
へ排出され、軸受面の潤滑が行なわれる。すなわち、回
転軸１が回転すると軸受面２ａとの間隙を流れている潤
滑油がクサビ油膜を形成し油膜圧力を発生し、この油膜
を介して回転軸が支承される。The outer ring 3 is fixed to a base or casing (not shown), and a bearing alloy such as white metal is adhered to the inner peripheral surface of the inner ring 2 to improve lubrication characteristics. The inner ring 2 and the outer ring 3 have a rotating shaft 1 and an inner ring 2.
A lubricating oil supply hole 4 for supplying and discharging lubricating oil and a lubricating oil discharging oil hole 5 are formed in an annular gap between the lubricating oil and the bearing surface 2a.
The lubricating oil supplied from the lubricating oil supply hole 4 flows through the gap between the rotating shaft 1 and the bearing surface 2a, and is discharged out of the bearing through the lubricating oil drain hole 5 to lubricate the bearing surface. That is, when the rotating shaft 1 rotates, the lubricating oil flowing in the gap with the bearing surface 2a forms a wedge oil film to generate an oil film pressure, and the rotating shaft is supported via the oil film.
【０００４】ところで、上記内輪２の外周面は球面加工
されており、この球面部が外輪３の球面座３ａに係合支
持されている。内輪２の外周球面の曲率と外輪３の球面
座３ａの曲率は同一寸法であるが、通常若干の隙間がで
きるように加工されいる。したがって、この球面によっ
て内輪２は球面の中心の回りに揺動可能であり、回転軸
の組立の際に予め軸のアライメント量を考慮した上で、
回転軸１と軸受面２ａとが平行になるように内輪２を傾
けることができる。また、回転中において、回転軸のア
ライメントが変化した場合でも、回転軸１の傾きに対応
してこれに追従して内輪２が傾斜して調心機能を奏し、
軸受機能が損なわれることを防止することができる。The outer peripheral surface of the inner ring 2 is formed into a spherical surface, and this spherical portion is engaged with and supported by the spherical seat 3 a of the outer ring 3. The curvature of the outer spherical surface of the inner ring 2 and the curvature of the spherical seat 3a of the outer ring 3 are the same, but are usually worked so as to have a slight gap. Therefore, the inner ring 2 can swing around the center of the spherical surface by this spherical surface, and in consideration of the amount of shaft alignment in advance when assembling the rotating shaft,
The inner ring 2 can be inclined so that the rotating shaft 1 and the bearing surface 2a are parallel. In addition, even during the rotation, even if the alignment of the rotating shaft changes, the inner ring 2 inclines according to the inclination of the rotating shaft 1 according to the inclination of the rotating shaft 1 to perform the centering function,
It is possible to prevent the bearing function from being impaired.
【０００５】図２１は、軸受が回転軸１の傾きに追随し
ていく様子を示す図であり、回転軸１と軸受面２ａとの
間に相対的な傾斜が生じると、回転軸１と軸受面２ａと
の隙間に形成されている油膜の厚さが軸方向に不均一と
なり、一方の軸受端での油膜厚さが極度に薄くなり、軸
受油膜圧力分布も実線で示すように油膜厚さが薄いとこ
ろでピークとなる。この時内輪２には、軸受油膜圧力分
布が軸受中心に対して非対称になりモーメントＭが発生
する。したがって、球面座３ａに生じている摩擦抵抗が
モーメントＭより小さいと内輪２は球面座に沿って点線
で示した位置まで移動する。そして、軸方向の軸受油膜
圧力分布は軸受中心に対して対称になり、モーメントＭ
はなくなり、この位置でバランスし、軸受と回転軸が平
行に保たれる。FIG. 21 is a view showing how the bearing follows the inclination of the rotating shaft 1. When a relative inclination occurs between the rotating shaft 1 and the bearing surface 2a, the rotating shaft 1 and the bearing are moved. The thickness of the oil film formed in the gap with the surface 2a becomes non-uniform in the axial direction, the oil film thickness at one bearing end becomes extremely thin, and the oil film pressure distribution as shown by the solid line also shows the oil film thickness distribution. Peaks where the lightening is thin. At this time, in the inner ring 2, the bearing oil film pressure distribution becomes asymmetric with respect to the bearing center, and a moment M is generated. Therefore, when the frictional resistance generated in the spherical seat 3a is smaller than the moment M, the inner race 2 moves along the spherical seat to the position shown by the dotted line. Then, the bearing oil film pressure distribution in the axial direction becomes symmetric with respect to the bearing center, and the moment M
And the balance is maintained at this position, and the bearing and the rotating shaft are kept parallel.
【０００６】[0006]
【発明が解決しようとする課題】最近の蒸気タービン・
発電機、ガスタービン・発電機は大容量化される傾向に
ある。その結果、それぞれの軸も長大化されるため、軸
はたわみ易くなり、アライメント変化量も大きく、さら
には軸受荷重も増大する。また、タービンは運転中にお
いても、負荷や外気温などの運転条件によって、タービ
ン車室内の温度や真空度が変化し、その影響で軸受台が
変形するため、軸のアライメントや傾きが大きく変化す
ることになる。この回転軸の変化に対し、軸受は回転軸
との平行を保つように球面により追従して動作すること
が理想である。最近のタービン・発電機の大型化によ
り、軸のアライメントや傾きの変化は大きくなるため、
球面座の調心機能、球面座が滑ることにより軸受の内輪
が回転軸に追随し、軸受と回転軸を平行に保つ機能は、
ますます重要になりつつある。SUMMARY OF THE INVENTION Recent steam turbines
Generators, gas turbines, and generators tend to have larger capacities. As a result, each shaft is also lengthened, so that the shaft is easily bent, the amount of alignment change is large, and the bearing load is also increased. Further, even during operation of the turbine, the temperature and the degree of vacuum in the turbine cabin change depending on operating conditions such as a load and an outside air temperature. Will be. Ideally, the bearing follows the change of the rotating shaft and operates by following the spherical surface so as to keep the bearing parallel to the rotating shaft. With the recent increase in the size of turbines and generators, changes in shaft alignment and tilt have increased.
The centering function of the spherical seat, the inner ring of the bearing follows the rotating shaft by sliding the spherical seat, the function to keep the bearing and the rotating shaft parallel,
Increasingly important.
【０００７】しかし、球面座は乾燥摩擦であるためその
時の摩擦係数は非常に大きく、最大０．７に達する場合
もある。また、軸受の内輪外周面や外輪内周面を完全な
球面に加工するのは不可能で、加工粗さによる凹凸や加
工時の表面のうねりにより、両表面には、微少な凹凸が
多数存在するため、実際には、内輪と外輪は面でなく、
いくつかの点で接している。その接し方によっては、両
表面の凸部が引っかかるなどして、発生する摩擦力が更
に大きくなる場合がある。また、軸回転中は、軸受面と
回転軸間の摩擦損失が熱に変わるため、内輪は外輪より
温度が高くなるので、熱膨張量は内輪の方が外輪よりも
大きく、内輪と外輪の間隙は小さくなる。そのため、上
述の摩擦力が大きくなる傾向は顕著になる。However, since the spherical seat has dry friction, the coefficient of friction at that time is very large, sometimes reaching a maximum of 0.7. In addition, it is impossible to machine the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring into a perfect spherical surface, and there are many fine irregularities on both surfaces due to irregularities due to machining roughness and undulation of the surface during machining. In practice, the inner and outer rings are not planes,
We are touched in several ways. Depending on the manner of contact, the generated frictional force may be further increased due to the projections on both surfaces being caught. Also, during shaft rotation, the friction loss between the bearing surface and the rotating shaft changes into heat, so the temperature of the inner ring is higher than that of the outer ring, so the thermal expansion of the inner ring is larger than that of the outer ring, and the gap between the inner ring and the outer ring is larger. Becomes smaller. Therefore, the tendency that the frictional force described above becomes large becomes remarkable.
【０００８】球面座に発生する摩擦力が、内輪を滑らそ
うとする力よりも大きい場合には、内輪が滑らず球面座
が正常に機能しない。この場合、図２１の実線のよう
に、回転軸１と軸受面２ａに傾きが生じたまま運転され
ることになる。この時、軸受油膜圧力分布は、一方の軸
受端での油膜厚さが極度に薄くなるため、その部分で局
所的に軸受油膜圧力が上昇し、発生する最大油膜圧力も
球面座が正常に機能したときに比べると大きくなる。ま
た、軸受表面の温度も最大油膜圧力発生点で１２０度を
越える場合があることが、実験により確かめられてお
り、軸受表面の融点及び耐力の低いホワイトメタルが、
溶融または焼付きを起こす、いわゆる片当り現象により
軸受の損傷を発生する可能性が高くなる。また、接触に
よって回転軸に不安定振動を引き起こし、更には回転軸
系全体に悪影響を与えかねない状態となる。また、図２
２は、回転軸と軸受とが相対的に傾いている場合と回転
軸と軸受とが平行な場合の、回転数に対する回転軸の軸
支部の振動振幅をそれぞれＡおよびＢに示している。回
転軸と軸受とが相対的に平行な場合の方が振動振幅は全
体的に小さくなっているが、これは、回転軸と軸受とが
相対的に傾いていると軸受の減衰効果が小さくなるため
振動が大きくなり、危険速度上でラビング等の振動問題
を引き起こす可能性もあることを示している。If the friction force generated in the spherical seat is larger than the force for sliding the inner ring, the inner ring does not slip and the spherical seat does not function normally. In this case, as shown by the solid line in FIG. 21, the operation is performed with the rotating shaft 1 and the bearing surface 2a inclined. At this time, the bearing oil film pressure distribution is such that the oil film thickness at one end of the bearing is extremely thin, so the bearing oil film pressure locally increases at that point, and the maximum oil film pressure that occurs also causes the spherical seat to function normally. It is larger than when you do. Experiments have also confirmed that the temperature of the bearing surface may exceed 120 degrees at the point where the maximum oil film pressure is generated.
The possibility of damage to the bearing is increased due to the so-called one-side contact phenomenon that causes melting or seizure. In addition, the contact causes unstable vibration on the rotating shaft, and furthermore, the rotating shaft system may be adversely affected. FIG.
A and B show vibration amplitudes of the shaft support portion of the rotating shaft with respect to the number of rotations when the rotating shaft and the bearing are relatively inclined and when the rotating shaft and the bearing are parallel, respectively. The vibration amplitude is smaller overall when the rotating shaft and the bearing are relatively parallel, but this reduces the damping effect of the bearing when the rotating shaft and the bearing are relatively inclined. Therefore, the vibration becomes large, and there is a possibility that a vibration problem such as rubbing may be caused on a critical speed.
【０００９】また、大容量化によってタービン単体が大
型化すると当然軸受も大型となり、また、軸受の負荷能
力を保つために軸受幅も大きくなる。軸受が大型化し、
軸受幅が大きくなると、回転軸の傾きが同じでも、軸受
両端部における軸受面と回転軸の間隙は小さくなる。ま
た、大型化によって、軸受荷重も大きくなるため、軸受
球面座の動作は悪くなる傾向があり、軸受球面座が動作
しない場合もある。そうなると先に述べたような片当り
現象が起こりやすくなり、更には軸受損傷の可能性が高
くなることになる。Also, if the turbine unit becomes large due to the large capacity, the bearing naturally becomes large, and the bearing width also becomes large in order to maintain the load capacity of the bearing. Larger bearings
When the bearing width increases, the gap between the bearing surface and the rotating shaft at both ends of the bearing decreases even if the inclination of the rotating shaft is the same. In addition, since the bearing load increases as the size increases, the operation of the bearing spherical seat tends to deteriorate, and the bearing spherical seat may not operate. In this case, the above-described one-side contact phenomenon easily occurs, and the possibility of bearing damage increases.
【００１０】そこで、球面座に発生する摩擦力を低減す
るため、図２３および図２４に示すように外輪３の内周
または内輪２の外周面に周方向に延びる油溝６を設け、
その油溝６に潤滑油を供給することも提案されている。
しかし、この場合、潤滑油が油溝６内を流れるため潤滑
油が内輪と外輪間の隙間に十分浸透できなかったり、或
は潤滑油供給路等の構造が複雑になるなどの問題があっ
た。Therefore, in order to reduce the frictional force generated in the spherical seat, an oil groove 6 extending in the circumferential direction is provided on the inner circumference of the outer race 3 or the outer circumference of the inner race 2 as shown in FIGS.
It has also been proposed to supply lubricating oil to the oil groove 6.
However, in this case, there is a problem that the lubricating oil cannot sufficiently penetrate into the gap between the inner ring and the outer ring because the lubricating oil flows in the oil groove 6, or the structure of the lubricating oil supply path and the like becomes complicated. .
【００１１】本発明は、上記の問題点を解決することを
目的としたもので、回転軸のアライメント変化に対し、
それに追従して軸との平行を保つように動作する調心機
能を持つことで片当りによる損傷を防止し、また、軸振
動を抑制し得るジャーナル軸受を提供することにある。SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and has been made in consideration of a change in alignment of a rotating shaft.
It is another object of the present invention to provide a journal bearing that has a centering function that operates so as to keep it parallel to the shaft following it, thereby preventing damage due to one-side contact and suppressing shaft vibration.
【００１２】[0012]
【課題を解決するための手段】第１の発明は、内周面に
回転軸を支承する軸受面を設けた内輪とその内輪の外周
に設けられた外輪との間に球面座を具えたジャーナル軸
受において、上記外輪の内周面または外輪の外周面に潤
滑油用の少なくとも１個の油溝を設けるとともに、その
油溝内に多孔質体を装着したことを特徴とする。しかし
て、潤滑油は多孔質体の中をゆっくりと流れ、少ない潤
滑油量で球面座を十分潤滑し、球面座で発生する摩擦力
が小さくなり、内輪と外輪が滑りやすくなり、内輪が回
転軸に追随し軸受と回転軸を平行に保つことができる。According to a first aspect of the present invention, there is provided a journal having a spherical seat between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on the outer periphery of the inner ring. In the bearing, at least one oil groove for lubricating oil is provided on the inner peripheral surface of the outer ring or the outer peripheral surface of the outer ring, and a porous body is mounted in the oil groove. Therefore, the lubricating oil flows slowly through the porous body, lubricates the spherical seat sufficiently with a small amount of lubricating oil, the frictional force generated at the spherical seat decreases, the inner and outer rings become slippery, and the inner ring rotates. The bearing and the rotating shaft can be kept parallel to the shaft.
【００１３】第２の発明は、内輪を支持する外輪全体ま
たはその一部、或は内輪外周面が多孔質材によって形成
されている。しかして、この場合も第１の発明と同様な
作用効果を奏する。In the second invention, the entire outer ring supporting the inner ring or a part thereof, or the outer peripheral surface of the inner ring is formed of a porous material. Thus, in this case, the same operation and effect as those of the first invention can be obtained.
【００１４】また、第３の発明は、球面座へ供給される
潤滑油が、軸受外輪外周部から内輪内周面に向って穿設
された軸受用潤滑油供給孔から分岐導出されることを特
徴とする。According to a third aspect of the present invention, the lubricating oil supplied to the spherical seat is branched and led out from a lubricating oil supply hole for a bearing drilled from the outer peripheral portion of the bearing outer ring toward the inner peripheral surface of the inner ring. Features.
【００１５】さらに、第４の発明は、内輪と外輪間の球
面座に潤滑油を供給するための潤滑油供給路を、定格運
転時に油膜の圧力が高圧となる軸受面に連通したことを
特徴とする。したがって、第３および第４の発明におい
ては球面座用の潤滑油として軸受用潤滑油を利用するこ
とができる。Further, the fourth invention is characterized in that a lubricating oil supply passage for supplying lubricating oil to a spherical seat between the inner ring and the outer ring communicates with a bearing surface where the oil film pressure becomes high during rated operation. And Therefore, in the third and fourth inventions, the lubricating oil for bearings can be used as the lubricating oil for the spherical seat.
【００１６】第５の発明は、内周面に回転軸を支承する
軸受面を設けた内輪とその内輪の外周に設けられた外輪
との間に球面座を具えたジャーナル軸受において、回転
軸と軸受面との相対的な傾きを検出する検出装置と、そ
の検出装置と同じ円周方向位置もしくはそれと径方向に
対向する位置或はその両位置に設けられ、外輪と内輪の
間に軸受幅方向の力を発生し、内輪を外輪に対して傾動
させるアクチュエータと、上記検出装置で検出された傾
きが許容値以内になるように上記アクチュエータを制御
する信号を出力する制御装置とを有することを特徴とす
る。したがって、この場合検出された回転軸と軸受面と
の相対的な傾きが許容値を超えている場合にはアクチュ
エータが上記傾きを修正するように作動し、傾きが許容
値内におさえられる。According to a fifth aspect of the present invention, there is provided a journal bearing having a spherical seat between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on the outer periphery of the inner ring. A detecting device for detecting a relative inclination with respect to the bearing surface, and a detecting device provided at the same circumferential position as the detecting device or at a position radially opposed to the detecting device, or at both positions, and a bearing width direction between the outer ring and the inner ring; And a control device for outputting a signal for controlling the actuator such that the inclination detected by the detection device is within an allowable value. And Therefore, in this case, when the detected relative inclination between the rotating shaft and the bearing surface exceeds the allowable value, the actuator operates to correct the inclination, and the inclination is kept within the allowable value.
【００１７】また、第６の発明は、内周面に回転軸を支
承する軸受面を設けた内輪とその内輪の外周に設けられ
た外輪との間に球面座を具えたジャーナル軸受におい
て、軸受幅方向中央を通る鉛直面に対して対称の位置
に、内輪に対してそれぞれ逆の方向の力を作用させる２
つの油圧アクチュエータを設けるとともに、その油圧ア
クチュエータと同じ周方向位置で軸受両側面付近の軸受
面上に２つの開口を設け、各開口を対応する油圧アクチ
ュエータに連通させ、上記開口付近の軸受潤滑油を用
い、回転軸が傾いた時の非対称油膜圧力分布により内輪
を回転軸の傾きに追随させるようにしたことを特徴とす
る。しかして、この場合も軸受面における非対称油膜圧
力の作用によってアクチュエータが作動され回転軸と軸
受面との相対的な傾きが解消される。According to a sixth aspect of the present invention, there is provided a journal bearing having a spherical seat between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on the outer periphery of the inner ring. Apply a force in the opposite direction to the inner ring at a position symmetrical to the vertical plane passing through the center in the width direction.
Two hydraulic actuators are provided, and two openings are provided on the bearing surface near the both sides of the bearing at the same circumferential position as the hydraulic actuators, and each opening is communicated with the corresponding hydraulic actuator, and the bearing lubricating oil near the opening is provided. The inner ring is adapted to follow the inclination of the rotating shaft by an asymmetric oil film pressure distribution when the rotating shaft is inclined. Thus, also in this case, the actuator is operated by the action of the asymmetric oil film pressure on the bearing surface, and the relative inclination between the rotating shaft and the bearing surface is eliminated.
【００１８】第７の発明は、内周面に回転軸を支承する
軸受面を設けた内輪とその内輪の外周に設けられた外輪
との間に球面座を具えたジャーナル軸受において、内輪
と外輪との熱膨張量の差を小さくしたことを特徴とす
る。これにより内輪と外輪の間隙が小さくなって内輪と
外輪とが滑りにくくなることが防止される。According to a seventh aspect of the present invention, there is provided a journal bearing having a spherical seat between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on the outer periphery of the inner ring. Is characterized in that the difference in the amount of thermal expansion between them is reduced. This prevents the gap between the inner ring and the outer ring from becoming smaller and the inner ring and the outer ring from becoming less slippery.
【００１９】さらに第８の発明は、内周面に回転軸を支
承する軸受面を設けた内輪とその内輪の外周に設けられ
た外輪との間に球面座を具えたジャーナル軸受におい
て、外輪内側球面の曲率半径を内輪外側球面の曲率半径
より大きくしたことを特徴とする。したがって、この場
合には内輪が外輪の内側で転がるように作動し、内輪の
移動をスムーズに行うことができる。According to an eighth aspect of the present invention, there is provided a journal bearing having a spherical seat between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on the outer periphery of the inner ring. The radius of curvature of the spherical surface is larger than the radius of curvature of the outer spherical surface of the inner ring. Therefore, in this case, the inner ring operates so as to roll inside the outer ring, and the inner ring can be moved smoothly.
【００２０】また、第９の発明は、内周面に回転軸を支
承する軸受面を設けた内輪とその内輪の外周に設けられ
た外輪との間に球面座を具えたジャーナル軸受におい
て、軸受外周部に同じ高さで互いに相反する方向に突出
する２本の腕を設け、その各腕と軸受台間に介装された
球体を介して軸受を軸受台上に支持するようにしたこと
を特徴とする。しかして、この場合球体が軸受台の上を
転がることができ、軸受が球体と軸受台が接触している
点を中心に回転することにより、軸受が回転軸に容易に
追随することができる。A ninth invention provides a journal bearing having a spherical seat between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on the outer periphery of the inner ring. Two arms protruding in opposite directions at the same height are provided on the outer peripheral portion, and the bearing is supported on the bearing base via a sphere interposed between each arm and the bearing base. Features. Thus, in this case, the sphere can roll on the bearing pedestal, and the bearing can easily follow the rotary shaft by rotating around the point where the sphere and the pedestal are in contact.
【００２１】さらに第１０の発明は、内周面に回転軸を
支承する軸受面を設けた内輪とその内輪の外周に設けら
れた外輪との間に球面座を具えたジャーナル軸受におい
て、内輪を支持する外輪部の外側にさらに第２の外輪を
設け、両外輪間にも球面座を設けたことを特徴とする。
この場合には、球面座を２つ具えていることとなり、ど
ちらかの球面座が固着を起こし、摩擦力が大きくなって
滑りが悪くなり球面座として機能しなくなった場合で
も、他方の球面座が滑ることにより軸受が回転軸に容易
に追随できる。Further, a tenth invention provides a journal bearing having a spherical seat between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on the outer periphery of the inner ring. A second outer ring is further provided outside the outer ring portion to be supported, and a spherical seat is provided between both outer rings.
In this case, two spherical seats are provided, and even if one of the spherical seats is fixed and the friction force is increased and slippage is deteriorated and the spherical seat does not function, the other spherical seat does not function. By sliding, the bearing can easily follow the rotating shaft.
【００２２】[0022]
【発明の実施の形態】以下、添付図面を参照して本発明
の実施の形態について説明する。なお、図中図２０乃至
図２４と同一部分については同一符号を付し、その詳細
な説明は省略する。Embodiments of the present invention will be described below with reference to the accompanying drawings. In the drawings, the same parts as those in FIGS. 20 to 24 are denoted by the same reference numerals, and detailed description thereof will be omitted.
【００２３】図１は本発明のジャーナル軸受の一実施の
形態を示す図であり、図１は軸受中心軸線を含む鉛直面
で切断した側面断面図である。内輪２の外周にこれと同
心状に配設された外輪３の内周面には、周方向に延びる
少なくとも１個（図においては２個）の油溝１０が形成
されており、その油溝１０の頂部位置に潤滑油供給路１
１が連通され、上記油溝１０の下部位置に潤滑油排油路
１２が連通されている。そして上記油溝１０にはその油
溝１０と同一形状の多孔質体１３が挿入されている。FIG. 1 is a view showing an embodiment of a journal bearing according to the present invention, and FIG. 1 is a side sectional view cut along a vertical plane including a central axis of the bearing. At least one (two in the figure) oil grooves 10 extending in the circumferential direction are formed on the inner peripheral surface of the outer ring 3 arranged concentrically on the outer periphery of the inner ring 2, and the oil grooves 10 at the top position
1 is communicated, and a lubricating oil discharge passage 12 is communicated with a lower position of the oil groove 10. A porous body 13 having the same shape as the oil groove 10 is inserted into the oil groove 10.
【００２４】しかして、潤滑油供給路１１から供給され
た潤滑油は油溝１０内に流入し、その油溝１０内を下方
に流れ、潤滑油排油路１２から排出される。この間潤滑
油は多孔質体１３の中をゆっくりと流れ、その間に内輪
２と外輪３の間の微少な隙間に浸透していき少ない潤滑
油量で十分な油膜が形成される。したがって、球面座部
分の摩擦係数が小さくなり、作用する摩擦力も小さくな
って球面座が滑りやすくなり、内輪２が回転軸の傾きに
確実に追随し、軸受の内輪を回転軸と平行に保つことが
できる。Thus, the lubricating oil supplied from the lubricating oil supply passage 11 flows into the oil groove 10, flows downward in the oil groove 10, and is discharged from the lubricating oil discharge passage 12. During this time, the lubricating oil slowly flows through the porous body 13, and in the meantime, penetrates into the minute gap between the inner ring 2 and the outer ring 3 to form a sufficient oil film with a small amount of lubricating oil. Therefore, the friction coefficient of the spherical seat portion is reduced, the acting frictional force is also reduced, the spherical seat becomes slippery, the inner ring 2 reliably follows the inclination of the rotating shaft, and the inner ring of the bearing is kept parallel to the rotating shaft. Can be.
【００２５】ところで、図１においては外輪３の内周面
に油溝１０を形成したものを示したが、内輪２の外周面
に周方向に延びる油溝１０を形成してもよい。この場合
も図１に示すものと全く同一の作用効果を奏する。Although FIG. 1 shows the case where the oil groove 10 is formed on the inner peripheral surface of the outer ring 3, the oil groove 10 extending in the circumferential direction may be formed on the outer peripheral surface of the inner ring 2. In this case, the same operation and effect as those shown in FIG. 1 are obtained.
【００２６】図２は、球面座部分に潤滑油を供給するよ
うにした他の実施例を示す図であり、軸受の外輪３が多
孔質体によって形成されている。しかして、油溝１０内
に流入した潤滑油は油溝１０内を流れる間に外輪３の多
孔質体内に浸透し、内輪と外輪が接触している球面座全
体に行きわたり、これにより球面座に作用する摩擦力を
小さくすることができる。FIG. 2 is a view showing another embodiment in which lubricating oil is supplied to the spherical seat portion. The outer ring 3 of the bearing is formed of a porous body. Thus, the lubricating oil flowing into the oil groove 10 penetrates into the porous body of the outer ring 3 while flowing through the oil groove 10, and reaches the entire spherical seat where the inner ring and the outer ring are in contact with each other. Can be reduced.
【００２７】なお、上記実施例では外輪全体を多孔質体
によって形成したものを示したが、内輪２と対向する一
部分のみを多孔質体によって形成してもよい。また、図
１０に示すように、内輪２の外周面部に多孔質部２０を
設けても同様の作用効果を奏せしめることができる。Although the entire outer ring is formed of a porous material in the above embodiment, only a part of the outer ring opposed to the inner ring 2 may be formed of a porous material. Further, as shown in FIG. 10, even when the porous portion 20 is provided on the outer peripheral surface portion of the inner ring 2, the same function and effect can be obtained.
【００２８】ところで、図１および図３には、油溝１０
に球面座用潤滑油を直接供給するようにしたものを示し
たが、図４（ａ），（ｂ）に示すように、軸受用潤滑油
の一部を分岐して油溝１０に導入するようにしてもよ
い。すなわち、外輪３および内輪２に穿設されている軸
受用の潤滑油供給孔４および潤滑油排油孔５が、その途
中で前記油溝１０に連通されている。FIGS. 1 and 3 show an oil groove 10.
The lubricating oil for the spherical seat is supplied directly to the lubricating oil. However, as shown in FIGS. 4A and 4B, a part of the lubricating oil for the bearing is branched and introduced into the oil groove 10. You may do so. That is, the lubricating oil supply hole 4 and the lubricating oil drain hole 5 for the bearing formed in the outer ring 3 and the inner ring 2 communicate with the oil groove 10 in the middle thereof.
【００２９】したがって、潤滑油供給孔４から供給され
た潤滑油はその一部が分岐されて油溝１０内に流入し、
その後潤滑油排油孔５から排出される。このため、球面
座に潤滑油を供給するために別の潤滑油供給用の配管等
を設ける必要がなく、また油溝１０に流れ込む潤滑油の
量は、潤滑油供給孔４と油溝１０とが連通している部分
の断面積を変えることによって調整することができる。Therefore, the lubricating oil supplied from the lubricating oil supply hole 4 is partially branched and flows into the oil groove 10,
Thereafter, it is discharged from the lubricating oil drain hole 5. Therefore, it is not necessary to provide another lubricating oil supply pipe or the like to supply the lubricating oil to the spherical seat, and the amount of the lubricating oil flowing into the oil groove 10 depends on the amount of the lubricating oil supply hole 4 and the oil groove 10. It can be adjusted by changing the cross-sectional area of the portion communicating with.
【００３０】図５および図６は、それぞれ油溝１０への
潤滑油供給手段の他の例を示す図であって、球面座への
潤滑油を内輪２と回転軸１との間に形成されている油膜
により供給するようにしてある。すなわち、内輪２と回
転軸１との間に形成される油膜の圧力は、回転軸１の回
転に対応してその周方向位置で異なっている。図中符号
２１は軸受面上の周方向の潤滑油圧力分布を示す。そこ
で、定格回転数時に軸受面上で油膜圧力が最大となる部
分と油溝１０との間にこれらを連通する潤滑油供給路２
２が穿設されている。FIGS. 5 and 6 are views showing other examples of the lubricating oil supply means to the oil groove 10, respectively, in which the lubricating oil to the spherical seat is formed between the inner ring 2 and the rotating shaft 1. FIG. It is made to supply by the oil film which is. That is, the pressure of the oil film formed between the inner ring 2 and the rotating shaft 1 is different at the circumferential position corresponding to the rotation of the rotating shaft 1. In the drawing, reference numeral 21 indicates a circumferential lubricating oil pressure distribution on the bearing surface. Therefore, the lubricating oil supply passage 2 communicating between the portion where the oil film pressure is maximum on the bearing surface and the oil groove 10 at the rated rotation speed is provided.
2 are drilled.
【００３１】したがって、回転軸１の回転中には油膜圧
力が高い部分から潤滑油が潤滑油供給路２２を通って油
溝１０に導入される。この軸受油膜圧力は高い部分では
４０〜６０ｋｇｆ／ｃｍ2 と非常に高圧となるので、そ
の部分を油溝１０と連通させることによって複雑な形状
で管路抵抗の大きい油溝にも潤滑油を供給することがで
きる。Therefore, during the rotation of the rotary shaft 1, the lubricating oil is introduced into the oil groove 10 through the lubricating oil supply passage 22 from the portion where the oil film pressure is high. Since the bearing oil film pressure is as high as 40 to 60 kgf / cm 2 in a high part, lubricating oil is supplied to an oil groove having a complicated shape and a large pipe resistance by connecting the part with the oil groove 10. can do.
【００３２】さらに、図６に示すように、軸受面上の油
膜圧力が負となる部分を油溝１０と潤滑油排油路２３を
介して連通させることによって、球面座からの潤滑油を
排出させることができる。これによって、球面座への潤
滑油の供給と排出の圧力差を大きくすることができ、球
面座への潤滑油の供給を容易に行うことができる。Further, as shown in FIG. 6, the portion where the oil film pressure on the bearing surface becomes negative communicates with the oil groove 10 through the lubricating oil discharge passage 23, thereby discharging the lubricating oil from the spherical seat. Can be done. As a result, the pressure difference between the supply and discharge of the lubricating oil to the spherical seat can be increased, and the lubricating oil can be easily supplied to the spherical seat.
【００３３】図７は本発明の他の実施の形態を示す図で
あり、内輪２の両側には周方向同一位置に回転軸１の外
周面と対向する左右一対の変位センサ２５ａ，２５ｂが
取り付けられている。また、内輪２の外周左右部には周
方向に延びる突条２６ａ，２６ｂが突設されており、両
突条２６ａ，２６ｂの内側面と外輪３の両外側面との間
には、上記変位センサ２５ａ，２５ｂと同じ周方向位置
もしくは１８０°反対位置（図には１８０°反対位置の
ものを示す）に、それぞれ油圧アクチュエータ２７ａ，
２７ｂが介装されている。両油圧アクチュエータ２７
ａ，２７ｂは互いに正反対の向きの力を発生し、外輪３
と内輪２の間に軸受幅方向の力を発生し球面座を滑らせ
得るようにしてある。FIG. 7 is a view showing another embodiment of the present invention. A pair of left and right displacement sensors 25a and 25b facing the outer peripheral surface of the rotary shaft 1 are mounted on both sides of the inner race 2 at the same position in the circumferential direction. Have been. Protrusions 26a, 26b extending in the circumferential direction protrude from left and right portions of the outer periphery of the inner ring 2, and the displacement between the inner surfaces of the two protrusions 26a, 26b and the outer surfaces of the outer ring 3 is provided. The hydraulic actuators 27a, 27b are located at the same circumferential position as the sensors 25a, 25b or at a position 180 ° opposite to that of the sensors 25a (25b).
27b is interposed. Double hydraulic actuator 27
a and 27b generate forces in opposite directions to each other, and
A force in the bearing width direction is generated between the inner ring 2 and the inner ring 2 so that the spherical seat can slide.
【００３４】しかして、変位センサ２５ａ，２５ｂによ
って計測された回転軸１と内輪２間の相対的な変位がア
ンプ２８、Ａ／Ｄ変換器２９を介して計算機３０に入力
され、その計算機３０で軸受両側面における回転軸１と
内輪２との変位から軸受内輪２と回転軸１との相対的な
傾きが算出される。回転軸１の回転中は回転軸が振動し
ているため、計測される回転軸変位には振動成分も含ま
れるので、計測値の直流成分をもって回転軸の静的な変
位とする。The relative displacement between the rotating shaft 1 and the inner ring 2 measured by the displacement sensors 25a and 25b is input to the computer 30 via the amplifier 28 and the A / D converter 29. The relative inclination between the bearing inner ring 2 and the rotating shaft 1 is calculated from the displacement between the rotating shaft 1 and the inner ring 2 on both side surfaces of the bearing. Since the rotating shaft is vibrating while the rotating shaft 1 is rotating, the measured displacement of the rotating shaft includes a vibration component. Therefore, the DC component of the measured value is used as the static displacement of the rotating shaft.
【００３５】そこで、算出された傾きが許容値を超えて
いる場合には、計算機３０から油圧アクチュエータ２７
ａ，２７ｂを動作させる制御信号が出され、これがＡ／
Ｄ変換器３１、アンプ３２を介して油圧アクチュエータ
２７ａ，２７ｂに送られ油圧源３３から制御油が給排さ
れる。すなわち、例えば変位センサ２５ａと回転軸１間
がより多く離間している場合には油圧アクチュエータ２
７ａ，２７ｂによって内輪２が図において左方向に傾動
され、軸受面が回転軸１に追随される。このようにして
常に回転軸１と軸受面とが平行になるように容易に制御
される。If the calculated inclination exceeds the allowable value, the computer 30 sends the hydraulic actuator 27
a, and a control signal for operating 27b is issued.
The control oil is sent to the hydraulic actuators 27 a and 27 b via the D converter 31 and the amplifier 32, and the control oil is supplied and discharged from the hydraulic source 33. That is, for example, when the displacement sensor 25a and the rotating shaft 1 are farther apart from each other, the hydraulic actuator 2
The inner ring 2 is tilted leftward in the figure by 7a and 27b, and the bearing surface follows the rotating shaft 1. In this way, it is easily controlled so that the rotating shaft 1 and the bearing surface are always parallel.
【００３６】図８は、傾き計測の手段として温度センサ
を用いた例を示したものである。すなわち、２つの温度
センサ３４ａ，３４ｂが同じ周方向位置で軸受の内輪２
の両側面付近に取り付けられており、軸受潤滑油温度ま
たは軸受金温度を計測し、２点の温度差から回転軸の傾
きを算出する。予め試験もしくはシミュレーション計算
によって、回転軸が傾いたときの軸受潤滑油温度または
軸受金温度の分布を求めておき、傾きと温度の関係を計
算機に入力しておくことにより、測定された温度から回
転軸と軸受の傾きを求めることができる。したがって、
この場合も油圧アクチュエータ２７ａ，２７ｂによっ
て、回転軸１と軸受面とを常に平行に維持させることが
できる。FIG. 8 shows an example in which a temperature sensor is used as a means for measuring the inclination. That is, when the two temperature sensors 34a and 34b are in the same circumferential position,
It measures the temperature of the bearing lubricating oil or the temperature of the bearing metal, and calculates the inclination of the rotating shaft from the temperature difference between the two points. The distribution of the bearing lubricating oil temperature or bearing metal temperature when the rotating shaft is tilted is determined in advance by a test or simulation calculation, and the relationship between the tilt and the temperature is input to a computer. The inclination between the shaft and the bearing can be determined. Therefore,
Also in this case, the rotary shaft 1 and the bearing surface can be always maintained in parallel by the hydraulic actuators 27a and 27b.
【００３７】ところで、図７および図８においては油圧
アクチュエータを使用したものを示したが、図９に示す
ように電磁アクチュエータ３５ａ，３５ｂを使用しても
よく、また空気圧アクチュエータ或は圧電アクチュエー
タを使用してもよい。FIGS. 7 and 8 show the case using a hydraulic actuator. However, as shown in FIG. 9, electromagnetic actuators 35a and 35b may be used, or a pneumatic actuator or a piezoelectric actuator may be used. May be.
【００３８】図１０は、センサーおよびアクチュエータ
を円周方向位置の差が９０度となるように２組取り付け
た例を示したものであり、２個の変位センサー２５ａが
内輪２の端部に９０度の間隔で取り付けられている。ま
た、アクチュエータはそれぞれ変位センサーと同じ周方
向位置または１８０度反対の位置に取り付けられてい
る。しかして、全ての方向の傾きが２つの方向の合成で
表わされるので、内輪と回転軸が如何なる方向に傾いて
もその傾きを検出、修正することができる。FIG. 10 shows an example in which two sets of sensors and actuators are mounted so that the difference between the positions in the circumferential direction is 90 degrees, and two displacement sensors 25a are attached to the end of the inner ring 2 by 90 degrees. Installed at intervals of degrees. Further, the actuators are respectively mounted at the same circumferential position as the displacement sensor or at a position opposite by 180 degrees. Thus, since the inclination in all directions is represented by the combination of the two directions, the inclination can be detected and corrected regardless of the direction in which the inner ring and the rotation axis are inclined.
【００３９】図１１は本発明の他の実施の形態を示す図
であり、回転軸１が傾いた時に軸方向の軸受油膜圧力分
布Ｐが軸受の中心線に対して非対称になることを利用し
て、油圧アクチュエータにより球面座を滑らせようとす
るものである。FIG. 11 is a view showing another embodiment of the present invention, which utilizes the fact that the axial bearing oil film pressure distribution P becomes asymmetric with respect to the center line of the bearing when the rotating shaft 1 is inclined. Thus, the spherical seat is slid by a hydraulic actuator.
【００４０】すなわち、２つの油圧アクチュエータ２７
ａ，２７ｂが軸受幅方向中央を通る鉛直面に対して対称
の位置に内輪２と外輪３の間の球面座を滑らせるように
取り付けられており、発生する力の向きはそれぞれ正反
対となっている。また、内輪２の両側面付近の軸受面上
には、油圧アクチュエータと同じ周方向位置に２つの油
供給口３６ａ，３６ｂが設けられている。上記油供給口
３６ａ，３６ｂはそれぞれ反対側の油圧アクチュエータ
２７ａ，２７ｂに接続されている。すなわち、左側の油
圧アクチュエータ２７ａは右の油供給口３６ｂと、右側
の油圧アクチュエータ２７ｂは左の油供給口３６ａと接
続されている。That is, the two hydraulic actuators 27
a and 27b are mounted so as to slide on a spherical seat between the inner ring 2 and the outer ring 3 at positions symmetrical with respect to a vertical plane passing through the center in the bearing width direction, and the directions of generated forces are opposite to each other. I have. Two oil supply ports 36a and 36b are provided on the bearing surface near both side surfaces of the inner race 2 at the same circumferential position as the hydraulic actuator. The oil supply ports 36a and 36b are connected to hydraulic actuators 27a and 27b on opposite sides, respectively. That is, the left hydraulic actuator 27a is connected to the right oil supply port 36b, and the right hydraulic actuator 27b is connected to the left oil supply port 36a.
【００４１】しかして、例えば図のように回転軸１が右
に傾いた場合には、軸方向の油膜圧力分布は非対称にな
り、右の油供給口３６ｂ付近の圧力が左の油供給口３６
ａ付近の圧力よりも高くなる。その結果、右の油供給口
３６ｂに接続されている左の油圧アクチュエータ２７ａ
の発生する力が右の油圧アクチュエータ２７ｂよりも大
きくなり、軸受の内輪２は油圧アクチュエータにより右
回りに滑り、回転軸１の傾きに追随される。そして、回
転軸１と内輪２が平行になると、油膜圧力分布は対称に
なり、２つの油供給口３６ａ，３６ｂ付近の圧力が同じ
になるため、２つの油圧アクチュエータ２７ａ，２７ｂ
で発生する力も同じになって均合うため、球面座を滑ら
せようとする力は作用しなくなる。左側に傾いた場合も
同様である。If, for example, the rotary shaft 1 is tilted to the right as shown in the figure, the oil film pressure distribution in the axial direction becomes asymmetric, and the pressure near the right oil supply port 36b is reduced.
It becomes higher than the pressure near a. As a result, the left hydraulic actuator 27a connected to the right oil supply port 36b
Is greater than the right hydraulic actuator 27b, the inner ring 2 of the bearing slides clockwise by the hydraulic actuator, and follows the inclination of the rotating shaft 1. When the rotating shaft 1 and the inner ring 2 are parallel to each other, the oil film pressure distribution becomes symmetric and the pressures near the two oil supply ports 36a and 36b become the same, so that the two hydraulic actuators 27a and 27b
Since the forces generated in the steps are equal and equal, the force for sliding the spherical seat does not work. The same applies to the case where the vehicle is tilted to the left.
【００４２】ところで、ジャーナル軸受においては運転
中内輪２の温度が外輪３の温度より高くなり、内輪２の
熱膨張によって内輪２の外径が大きくなり、その結果、
内輪と外輪の間隙が小さくなって内輪２と外輪３が滑り
にくくなる。In the journal bearing, the temperature of the inner ring 2 becomes higher than the temperature of the outer ring 3 during operation, and the outer diameter of the inner ring 2 increases due to the thermal expansion of the inner ring 2.
The gap between the inner ring and the outer ring is reduced, and the inner ring 2 and the outer ring 3 are less likely to slip.
【００４３】そこで、内輪２の線膨張係数が外輪の線膨
張係数よりも小さくなるように、内輪２と外輪３の材料
を選ぶこともできる。しかして、この場合内輪２の温度
が外輪３より高くなっても、両者の熱膨張量の差を小さ
くすることができ、内輪２と外輪３が滑りにくくなるこ
とを防止することができる。Therefore, the materials of the inner ring 2 and the outer ring 3 can be selected so that the coefficient of linear expansion of the inner ring 2 is smaller than the coefficient of linear expansion of the outer ring. Thus, in this case, even if the temperature of the inner ring 2 becomes higher than that of the outer ring 3, the difference in the amount of thermal expansion between the two can be reduced, and the inner ring 2 and the outer ring 3 can be prevented from becoming slippery.
【００４４】図１２は、内輪２と外輪３の熱膨張量の差
を小さくするために、内輪２を冷却するようにしたもの
を示す図であり、内輪２には軸方向に延びる複数の冷却
用孔３７が穿設してあり、その冷却用孔３７に供給管３
８から冷却水または冷却空気を流し、排出管３９から排
出するようにしてある。しかして、上記冷却水或は冷却
空気の流通によって内輪２の温度が低減され、内輪２お
よび外輪３間の熱膨張量の差が小さくされる。FIG. 12 is a view showing a structure in which the inner ring 2 is cooled in order to reduce the difference in the amount of thermal expansion between the inner ring 2 and the outer ring 3. The cooling pipe 37 is provided in the cooling hole 37.
Cooling water or cooling air flows from 8 and is discharged from a discharge pipe 39. Thus, the temperature of the inner race 2 is reduced by the flow of the cooling water or the cooling air, and the difference in the amount of thermal expansion between the inner race 2 and the outer race 3 is reduced.
【００４５】また、図１３（ａ），（ｂ）は内輪２の温
度を低下させる他の手段を示す図であり、内輪２の両側
面に冷却フイン４０が設けられている。低圧タービンの
軸受付近における雰囲気の温度は３０〜４０℃で内輪よ
りも低いので、冷却フイン４０により内輪２を冷却する
ことができる。したがって、上記冷却フイン４０による
冷却によって内輪２が冷却され内輪２の熱膨張が抑えら
れ、内輪２と外輪３との滑りがよくされる。FIGS. 13A and 13B are views showing another means for lowering the temperature of the inner race 2, and cooling fins 40 are provided on both side surfaces of the inner race 2. FIG. Since the temperature of the atmosphere near the bearing of the low-pressure turbine is 30 to 40 ° C. lower than that of the inner ring, the inner ring 2 can be cooled by the cooling fins 40. Therefore, the inner ring 2 is cooled by the cooling by the cooling fins 40, and the thermal expansion of the inner ring 2 is suppressed, so that the slip between the inner ring 2 and the outer ring 3 is improved.
【００４６】図１４は逆に外輪３を加熱するようにした
ものであって、外輪３には軸線方向に延びる加熱用孔４
１が穿設してあり、供給管４２から上記加熱用孔４１に
蒸気また油を供給し、排出管４３から排出するようにし
てある。しかして、これにより外輪３が加熱され外輪３
の温度が内輪２と同等にされ、内輪と外輪３の熱膨張力
が同等にされる。したがって、内輪２と外輪３の間隙が
確保され、内輪と外輪間が滑りにくくなることが防止さ
れる。FIG. 14 shows an arrangement in which the outer ring 3 is heated in reverse. The outer ring 3 has a heating hole 4 extending in the axial direction.
A steam or oil is supplied from the supply pipe 42 to the heating hole 41 and discharged from the discharge pipe 43. Thus, this causes the outer ring 3 to be heated,
Is made equal to that of the inner ring 2, and the thermal expansion forces of the inner ring and the outer ring 3 are made equal. Therefore, a gap between the inner race 2 and the outer race 3 is ensured, and the slip between the inner race and the outer race is prevented from becoming difficult.
【００４７】図１５は本発明のさらに他の実施の態様を
示す図であり、外輪３の内周面に加工されている球面の
曲率半径が内輪２の外周面の径よりも大きくしてある。
これにより、内輪２が外輪３の内面を滑るというより転
がることができる。しかして、転がり摩擦力が滑り摩擦
力より小さいことから、内輪は従来のものと比べて小さ
い力で動くことができ、回転軸に容易に追随することが
できる。FIG. 15 is a view showing still another embodiment of the present invention. The radius of curvature of the spherical surface formed on the inner peripheral surface of the outer ring 3 is larger than the diameter of the outer peripheral surface of the inner ring 2. .
This allows the inner race 2 to roll rather than slide on the inner surface of the outer race 3. Since the rolling frictional force is smaller than the sliding frictional force, the inner ring can move with a smaller force than the conventional one, and can easily follow the rotating shaft.
【００４８】図１６は本発明の他の実施の態様を示す図
であり、軸受４４の外周部には同じ高さの相対する位置
に外方に突出する腕４５が設けらてれおり、この腕４５
が球体４６を介して軸受台４７に支持されている。しか
して、回転軸１の傾動に応じて軸受４４が球体４６と軸
受台４７との接触点を中心に回動し、軸受４４が回転軸
１に追随することができる。FIG. 16 is a view showing another embodiment of the present invention. The outer periphery of a bearing 44 is provided with arms 45 projecting outward at opposite positions of the same height. Arm 45
Are supported by a bearing base 47 via a sphere 46. Thus, the bearing 44 rotates around the contact point between the sphere 46 and the bearing base 47 in accordance with the tilt of the rotating shaft 1, and the bearing 44 can follow the rotating shaft 1.
【００４９】また、図１７（ａ），（ｂ）は他の例を示
す図であり、軸受４４を支持する腕４８が円柱状に形成
してあり、その円柱状の腕４８が軸受台４７上に支持さ
れている。しかして、この場合も回転軸１の傾動に対応
して腕４８と軸受台４７との接触点を中心として腕４８
が回動し、軸受４４が回転軸に追随することができる。FIGS. 17A and 17B are views showing another example, in which an arm 48 for supporting a bearing 44 is formed in a columnar shape, and the columnar arm 48 is used as a bearing base 47. Supported above. In this case, too, the arm 48 is moved around the contact point between the arm 48 and the bearing base 47 in accordance with the tilt of the rotary shaft 1.
Are rotated, and the bearing 44 can follow the rotating shaft.
【００５０】図１８は、軸受が軸受中心を中心として回
転するようにした例を示したものである。この例では球
体４６と軸受台４７とが接する点が軸受４４の中心と同
じ高さになっている。したがって、軸受中心と軸受の回
転中心が一致し、軸受４４が回転軸１に追随して転がっ
た場合でも軸受中心の高さを一定に保つことができ、ア
ライメントを変化させずに軸受を回転軸１に追随させる
ことができる。FIG. 18 shows an example in which the bearing rotates around the center of the bearing. In this example, the point where the sphere 46 and the bearing base 47 are in contact with each other is at the same height as the center of the bearing 44. Therefore, even when the bearing center coincides with the rotation center of the bearing and the bearing 44 rolls following the rotating shaft 1, the height of the bearing center can be kept constant, and the bearing can be rotated without changing the alignment. 1 can follow.
【００５１】図１９は本発明のさらに他の実施の態様を
示す図であり、内輪２を支持する外輪３の外周部にさら
に第２の外輪４８が設けられており、外輪３と第２の外
輪４８との間にも球面座４８ａが形成されている。しか
して、２つの球面座のうちいずれか一方の球面座で固着
が発生し摩擦力が大きくなって滑りが悪くなり、球面座
として機能しなくなった場合でも、他方の球面座で滑り
が生じる。したがって、軸受が回転軸に対して容易に追
随することができる。FIG. 19 is a view showing still another embodiment of the present invention, wherein a second outer ring 48 is further provided on the outer peripheral portion of the outer ring 3 supporting the inner ring 2, and the outer ring 3 and the second A spherical seat 48a is also formed between the outer ring 48 and the outer ring 48. Thus, even if one of the two spherical seats is stuck and the frictional force is increased to make the slip worse, and the spherical seat no longer functions, slip occurs at the other spherical seat. Therefore, the bearing can easily follow the rotating shaft.
【００５２】[0052]
【発明の効果】本発明は上述のように構成したので、回
転軸に追随して軸受を容易に傾動させることができ、回
転軸の傾きによる片当り現象や軸受損傷を防ぐことがで
き、また回転軸と軸受面との平行を維持することができ
るので適正な油膜が形成され、十分な油膜減衰効果が得
られ、軸振動も低く抑えることができ、大型回転機械に
おいても長期の安定した運転が可能となる。Since the present invention is constructed as described above, it is possible to easily tilt the bearing following the rotating shaft, thereby preventing the one-side contact phenomenon and bearing damage due to the tilting of the rotating shaft. Since the rotating shaft and the bearing surface can be kept parallel, an appropriate oil film is formed, a sufficient oil film damping effect can be obtained, shaft vibration can be suppressed low, and long-term stable operation can be performed even for large rotating machines. Becomes possible.
【図１】第１の発明の一実施の形態の側面断面図。FIG. 1 is a side sectional view of an embodiment of the first invention.
【図２】第２の発明の実施の形態を示す側面断面図。FIG. 2 is a side sectional view showing an embodiment of the second invention.
【図３】第２の発明の他の実施例を示す側面断面図。FIG. 3 is a side sectional view showing another embodiment of the second invention.
【図４】（ａ），（ｂ）は第３の発明の実施の形態を示
す正面断面図および軸受外輪下半の立面図。FIGS. 4 (a) and (b) are a front sectional view and an elevation view of a lower half of a bearing outer ring showing an embodiment of a third invention.
【図５】第４の発明の実施の形態を示す正面断面図。FIG. 5 is a front sectional view showing an embodiment of the fourth invention.
【図６】第４の発明のさらに他の実施の態様を示す正面
断面図。FIG. 6 is a front sectional view showing still another embodiment of the fourth invention.
【図７】第５の発明の一実施の態様を示す側面断面図。FIG. 7 is a side sectional view showing an embodiment of the fifth invention.
【図８】第５の発明の他の実施の態様を示す側面断面
図。FIG. 8 is a side sectional view showing another embodiment of the fifth invention.
【図９】第５の発明のさらに他の実施の態様を示す側面
断面図。FIG. 9 is a side sectional view showing still another embodiment of the fifth invention.
【図１０】第５の発明の他の実施の態様を示す図。FIG. 10 is a diagram showing another embodiment of the fifth invention.
【図１１】第６の発明の実施の態様を示す側面断面図。FIG. 11 is a side sectional view showing an embodiment of the sixth invention.
【図１２】第７の発明の一実施の態様を示す側面断面
図。FIG. 12 is a side sectional view showing an embodiment of the seventh invention.
【図１３】（ａ），（ｂ）はそれぞれ第７の発明の他の
実施の態様を示す正面図および側面断面図。FIGS. 13 (a) and 13 (b) are a front view and a side sectional view, respectively, showing another embodiment of the seventh invention.
【図１４】第７の発明の他の実施の態様を示す側面断面
図。FIG. 14 is a side sectional view showing another embodiment of the seventh invention.
【図１５】第８の発明の実施の態様を示す側面断面図。FIG. 15 is a side sectional view showing an embodiment of the eighth invention.
【図１６】第９の発明の実施の態様を示す正面断面図。FIG. 16 is a front sectional view showing an embodiment of the ninth invention;
【図１７】（ａ），（ｂ）はそれぞれ第９の発明の他の
実施の態様を示す正面断面図および側面図。17A and 17B are a front sectional view and a side view, respectively, showing another embodiment of the ninth invention.
【図１８】第９の発明のさらに他の実施の態様を示す正
面断面図。FIG. 18 is a front sectional view showing still another embodiment of the ninth invention.
【図１９】第１０の発明の実施の態様を示す側面断面
図。FIG. 19 is a side sectional view showing an embodiment of the tenth invention.
【図２０】（ａ），（ｂ）はそれぞれ一般的なジャーナ
ル軸受の正面断面図および側面断面図。20A and 20B are a front sectional view and a side sectional view of a general journal bearing, respectively.
【図２１】球面座の自動調心メカニズムを模式的に示す
図。FIG. 21 is a diagram schematically showing a self-aligning mechanism of a spherical seat.
【図２２】回転軸と軸受が平行な状態のときと、傾いて
いるときの振動応答の違いを示す図。FIG. 22 is a diagram illustrating a difference in vibration response between a state where the rotating shaft and the bearing are parallel and a state where the bearing is inclined.
【図２３】従来のジャーナル軸受の正面断面図。FIG. 23 is a front sectional view of a conventional journal bearing.
【図２４】図２３のジャーナル軸受の側面断面図。FIG. 24 is a side sectional view of the journal bearing of FIG. 23;
１ 回転軸 ２ 内輪 ２ａ 軸受面 ３ 外輪 ３ａ 球面座 ４ 潤滑油供給孔 ５ 潤滑油排油孔 １０ 油溝 １１，２２ 潤滑油供給路 １２ 潤滑油排油路 １３ 多孔質体 ２５ａ，２５ｂ 変位センサ ２７ａ，２７ｂ 油圧アクチュエータ ３４ａ，３４ｂ 温度センサ ３５ａ，３５ｂ 電磁アクチュエータ ３６ａ，３６ｂ 油供給口 ３７ 冷却用孔 ３８，４２ 供給管 ３９，４３ 排出管 ４０ 冷却フイン ４１ 加熱用孔 ４４ 軸受 ４５，４８ 腕 ４６ 球体 ４７ 軸受台 ４８ 第２の外輪 REFERENCE SIGNS LIST 1 rotating shaft 2 inner ring 2a bearing surface 3 outer ring 3a spherical seat 4 lubricating oil supply hole 5 lubricating oil drain hole 10 oil groove 11,22 lubricating oil supply path 12 lubricating oil drain path 13 porous body 25a, 25b displacement sensor 27a , 27b Hydraulic actuator 34a, 34b Temperature sensor 35a, 35b Electromagnetic actuator 36a, 36b Oil supply port 37 Cooling hole 38, 42 Supply pipe 39, 43 Discharge pipe 40 Cooling fin 41 Heating hole 44 Bearing 45, 48 Arm 46 Sphere 47 Bearing stand 48 Second outer ring
───────────────────────────────────────────────────── フロントページの続き (72)発明者 山 下 達 雄 神奈川県横浜市鶴見区末広町２丁目４番地 株式会社東芝京浜事業所内 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Tatsuo Yamashita 2-4 Suehirocho, Tsurumi-ku, Yokohama-shi, Kanagawa Pref.
Claims (21)
内輪とその内輪の外周に設けられた外輪との間に球面座
を具えたジャーナル軸受において、上記外輪の内周面ま
たは内輪の外周面に潤滑油用の少なくとも１個の油溝を
設けるとともに、その油溝内に多孔質体を装着したこと
を特徴とするジャーナル軸受。1. A journal bearing having a spherical seat between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on an outer periphery of the inner ring. A journal bearing, wherein at least one oil groove for lubricating oil is provided on an outer peripheral surface of an inner ring, and a porous body is mounted in the oil groove.
内輪とその内輪の外周に設けられた外輪との間に球面座
を設けるとともに、その内輪と外輪との間に潤滑油を供
給する潤滑油供給機構を設けたジャーナル軸受におい
て、内輪を支持する外輪全体またはその一部、或は内輪
外周面が多孔質材によって形成されていることを特徴と
するジャーナル軸受。2. A spherical seat is provided between an inner ring having a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on an outer periphery of the inner ring, and lubricating oil is provided between the inner ring and the outer ring. A journal bearing provided with a lubricating oil supply mechanism for supplying the inner ring, wherein the whole or a part of the outer ring supporting the inner ring or the outer peripheral surface of the inner ring is formed of a porous material.
内輪とその内輪の外周に設けられた外輪との間に球面座
を設けるとともに、その内輪と外輪との間に潤滑油を供
給する潤滑油供給機構を設けたジャーナル軸受におい
て、球面座へ供給される潤滑油は、軸受外輪外周部から
内輪内周面に向って穿設された軸受用潤滑油供給孔から
分岐導出されることを特徴とするジャーナル軸受。3. A spherical seat is provided between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on the outer periphery of the inner ring, and lubricating oil is provided between the inner ring and the outer ring. In the journal bearing provided with a lubricating oil supply mechanism for supplying lubricating oil, lubricating oil supplied to the spherical seat is branched and led out from a lubricating oil supply hole for a bearing drilled from the outer peripheral portion of the bearing outer ring toward the inner peripheral surface of the inner ring. A journal bearing characterized in that:
内輪とその内輪の外周に設けられた外輪との間に球面座
を設けるとともに、その内輪と外輪との間に潤滑油を供
給する潤滑油供給機構を設けたジャーナル軸受におい
て、内輪と外輪間の球面座に潤滑油を供給するための潤
滑油供給路を、定格運転時に油膜の圧力が高圧となる軸
受面に連通したことを特徴とするジャーナル軸受。4. A spherical seat is provided between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on an outer periphery of the inner ring, and lubricating oil is provided between the inner ring and the outer ring. The lubricating oil supply path for supplying lubricating oil to the spherical seat between the inner ring and the outer ring is connected to the bearing surface where the pressure of the oil film becomes high during rated operation in a journal bearing provided with a lubricating oil supply mechanism that supplies oil A journal bearing characterized in that:
内輪とその内輪の外周に設けられた外輪との間に球面座
を設けるとともに、その内輪と外輪との間に潤滑油を供
給する潤滑油供給機構を設けたジャーナル軸受におい
て、内輪と外輪間の球面座から潤滑油を排出する潤滑油
排油路を、定格運転時に油膜の圧力が負となる軸受面に
連通したことを特徴とするジャーナル軸受。5. A spherical seat is provided between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on an outer periphery of the inner ring, and lubricating oil is provided between the inner ring and the outer ring. In a journal bearing with a lubricating oil supply mechanism that supplies oil, the lubricating oil drainage path that discharges lubricating oil from the spherical seat between the inner ring and the outer ring communicates with the bearing surface where the oil film pressure becomes negative during rated operation. Characterized by a journal bearing.
内輪とその内輪の外周に設けられた外輪との間に球面座
を具えたジャーナル軸受において、回転軸と軸受面との
相対的な傾きを検出する検出装置と、その検出装置と同
じ円周方向位置もしくはそれと径方向に対向する位置或
はその両位置に設けられ、外輪と内輪の間に軸受幅方向
の力を発生し、内輪を外輪に対して傾動させるアクチュ
エータと、上記検出装置で検出された傾きが許容値以内
になるように上記アクチュエータを制御する信号を出力
する制御装置とを有することを特徴とするジャーナル軸
受。6. A journal bearing having a spherical seat between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on the outer periphery of the inner ring. A detecting device for detecting the relative inclination, and a detecting device which is provided at the same circumferential position as the detecting device or at a position radially opposed to the detecting device or at both positions thereof, and generates a force in a bearing width direction between the outer ring and the inner ring. A journal bearing, comprising: an actuator for tilting the inner ring with respect to the outer ring; and a control device for outputting a signal for controlling the actuator so that the tilt detected by the detection device is within an allowable value. .
検出装置が、内輪の両側面の同じ円周方向位置に設けら
れた２つの非接触変位センサーと、その変位の差から回
転軸と軸受の傾きを算出する演算器とからなることを特
徴とする、請求項６記載のジャーナル軸受。7. A detecting device for detecting a relative inclination between a rotating shaft and a bearing surface comprises two non-contact displacement sensors provided at the same circumferential position on both side surfaces of an inner ring, and a rotation sensor based on a difference between the displacements. 7. The journal bearing according to claim 6, comprising a shaft and a calculator for calculating the inclination of the bearing.
検出装置が、同じ周方向位置の両側面付近の軸受潤滑油
温度または軸受温度を検出する２つの温度センサーと、
測定された温度から回転軸と軸受の傾きを算出する演算
器とからなることを特徴とする、請求項６記載のジャー
ナル軸受。8. A temperature sensor for detecting a bearing lubricating oil temperature or a bearing temperature near both side surfaces at the same circumferential position, comprising: a temperature sensor for detecting a relative inclination between the rotating shaft and the bearing surface;
7. The journal bearing according to claim 6, comprising a rotation shaft and a calculator for calculating a tilt of the bearing from the measured temperature.
る検出装置およびアクチュエータが、それぞれ互いに円
周方向に９０度だけ偏位した位置に設けられた２組から
なることを特徴とする、請求項６乃至８のいずれかに記
載のジャーナル軸受。9. The apparatus according to claim 1, wherein the detecting device and the actuator for detecting the relative inclination between the rotating shaft and the bearing surface comprise two sets provided at positions deviated from each other by 90 degrees in the circumferential direction. The journal bearing according to any one of claims 6 to 8, wherein:
た内輪とその内輪の外周に設けられた外輪との間に球面
座を具えたジャーナル軸受において、軸受幅方向中央を
通る鉛直面に対して対称の位置に、内輪に対してそれぞ
れ逆の方向の力を作用させる２つの油圧アクチュエータ
を設けるとともに、その油圧アクチュエータと同じ周方
向位置で軸受両側面付近の軸受面上に２つの開口を設
け、各開口を対応する油圧アクチュエータに連通させ、
上記開口付近の軸受潤滑油を用い、回転軸が傾いた時の
非対称油膜圧力分布により内輪を回転軸の傾きに追随さ
せるようにしたことを特徴とするジャーナル軸受。10. A journal bearing having a spherical seat between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface thereof and an outer ring provided on an outer periphery of the inner ring. Two hydraulic actuators that apply forces in opposite directions to the inner ring are provided at symmetrical positions with respect to the surface, and two hydraulic actuators are provided on the bearing surface near both sides of the bearing at the same circumferential position as the hydraulic actuator. Openings are provided, and each opening communicates with the corresponding hydraulic actuator,
A journal bearing wherein the inner ring follows the inclination of the rotating shaft by using an asymmetric oil film pressure distribution when the rotating shaft is inclined using the bearing lubricating oil near the opening.
た内輪とその内輪の外周に設けられた外輪との間に球面
座を具えたジャーナル軸受において、内輪と外輪との熱
膨張量の差を小さくしたことを特徴とするジャーナル軸
受。11. A thermal expansion of an inner ring and an outer ring in a journal bearing having a spherical seat between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on an outer periphery of the inner ring. A journal bearing characterized in that the difference in the amount is reduced.
を形成する材料の線膨張係数より小さくしたことを特徴
とする、請求項１１記載のジャーナル軸受。12. The journal bearing according to claim 11, wherein the coefficient of linear expansion of the material forming the inner ring is smaller than the coefficient of linear expansion of the material forming the outer ring.
内輪を冷却するようにしたことを特徴とする、請求項１
１記載のジャーナル軸受。13. The temperature of the inner ring and that of the outer ring are equalized.
2. The inner ring is cooled.
The journal bearing according to 1.
したことを特徴とする、請求項１３記載のジャーナル軸
受。14. The journal bearing according to claim 13, wherein a cooling fluid is circulated inside the inner ring.
徴とする、請求項１３記載のジャーナル軸受。15. The journal bearing according to claim 13, wherein a cooling fin is provided on a side surface of the inner ring.
輪を加熱することを特徴とする、請求項１１記載のジャ
ーナル軸受。16. The journal bearing according to claim 11, wherein the outer ring is heated so that the temperatures of the inner ring and the outer ring become equal.
特徴とする、請求項１６記載のジャーナル軸受。17. The journal bearing according to claim 16, wherein a heating fluid is circulated inside the outer ring.
た内輪とその内輪の外周に設けられた外輪との間に球面
座を具えたジャーナル軸受において、外輪内側球面の曲
率半径を内輪外側球面の曲率半径より大きくしたことを
特徴とするジャーナル軸受。18. A journal bearing having a spherical seat between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on an outer periphery of the inner ring. A journal bearing having a radius of curvature larger than the radius of curvature of the inner ring outer spherical surface.
た内輪とその内輪の外周に設けられた外輪との間に球面
座を具えたジャーナル軸受において、軸受外周部に同じ
高さで互いに相反する方向に突出する２本の腕を設け、
その各腕と軸受台間に介装された球体を介して軸受を軸
受台上に支持するようにしたことを特徴とする、ジャー
ナル軸受。19. A journal bearing having a spherical seat between an inner ring having a bearing surface for supporting a rotating shaft on an inner peripheral surface thereof and an outer ring provided on the outer periphery of the inner ring. To provide two arms protruding in opposite directions,
A journal bearing, wherein a bearing is supported on a bearing base via a sphere interposed between each arm and the bearing base.
た内輪とその内輪の外周に設けられた外輪との間に球面
座を具えたジャーナル軸受において、軸受外周部に同じ
高さで互いに相反する方向に突出する２本の円柱状の腕
を設け、その２本の円柱状の腕を介して軸受を軸受台上
に支持するようにしたことを特徴とする、ジャーナル軸
受。20. A journal bearing having a spherical seat between an inner ring having a bearing surface for supporting a rotating shaft on an inner peripheral surface thereof and an outer ring provided on the outer periphery of the inner ring, wherein the journal bearing has the same height on the outer peripheral portion of the bearing. 2. A journal bearing comprising: two cylindrical arms protruding in mutually opposite directions; and a bearing supported on a bearing base via the two cylindrical arms.
た内輪とその内輪の外周に設けられた外輪との間に球面
座を具えたジャーナル軸受において、内輪を支持する外
輪部の外側にさらに第２の外輪を設け、両外輪間にも球
面座を設けたことを特徴とする、ジャーナル軸受。21. A journal bearing having a spherical seat between an inner ring provided with a bearing surface for supporting a rotating shaft on an inner peripheral surface and an outer ring provided on the outer periphery of the inner ring. A journal bearing, further comprising a second outer ring provided on an outer side, and a spherical seat provided between both outer rings.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1446598A JPH11210747A (en) | 1998-01-27 | 1998-01-27 | Journal bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1446598A JPH11210747A (en) | 1998-01-27 | 1998-01-27 | Journal bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH11210747A true JPH11210747A (en) | 1999-08-03 |
Family
ID=11861816
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1446598A Withdrawn JPH11210747A (en) | 1998-01-27 | 1998-01-27 | Journal bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH11210747A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002327739A (en) * | 2001-05-08 | 2002-11-15 | Koyo Seiko Co Ltd | Method and unit for measuring preload of double row rolling bearing |
| JP2012007718A (en) * | 2010-06-28 | 2012-01-12 | Mitsubishi Heavy Ind Ltd | Journal bearing |
| KR101173768B1 (en) | 2010-08-26 | 2012-08-13 | 한전케이피에스 주식회사 | A bolt structure for temperature sensor fixing |
| JP2016089753A (en) * | 2014-11-06 | 2016-05-23 | 三菱日立パワーシステムズ株式会社 | Shaft center position control device, rotary machine system, shaft center position control method and program |
| JP2017009122A (en) * | 2016-10-05 | 2017-01-12 | 株式会社クボタ | Bearing device, method for assembling pump and bearing device and method for adjusting drain oil groove position |
| JP2019105287A (en) * | 2017-12-11 | 2019-06-27 | 株式会社酉島製作所 | bearing |
-
1998
- 1998-01-27 JP JP1446598A patent/JPH11210747A/en not_active Withdrawn
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002327739A (en) * | 2001-05-08 | 2002-11-15 | Koyo Seiko Co Ltd | Method and unit for measuring preload of double row rolling bearing |
| JP4506028B2 (en) * | 2001-05-08 | 2010-07-21 | 株式会社ジェイテクト | Preload measuring method and preload measuring device for double row rolling bearing |
| JP2012007718A (en) * | 2010-06-28 | 2012-01-12 | Mitsubishi Heavy Ind Ltd | Journal bearing |
| KR101173768B1 (en) | 2010-08-26 | 2012-08-13 | 한전케이피에스 주식회사 | A bolt structure for temperature sensor fixing |
| JP2016089753A (en) * | 2014-11-06 | 2016-05-23 | 三菱日立パワーシステムズ株式会社 | Shaft center position control device, rotary machine system, shaft center position control method and program |
| JP2017009122A (en) * | 2016-10-05 | 2017-01-12 | 株式会社クボタ | Bearing device, method for assembling pump and bearing device and method for adjusting drain oil groove position |
| JP2019105287A (en) * | 2017-12-11 | 2019-06-27 | 株式会社酉島製作所 | bearing |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A300 | Withdrawal of application because of no request for examination |
Free format text: JAPANESE INTERMEDIATE CODE: A300 Effective date: 20050405 |