JPH10205527A - Thrust bearing - Google Patents
Thrust bearingInfo
- Publication number
- JPH10205527A JPH10205527A JP9009191A JP919197A JPH10205527A JP H10205527 A JPH10205527 A JP H10205527A JP 9009191 A JP9009191 A JP 9009191A JP 919197 A JP919197 A JP 919197A JP H10205527 A JPH10205527 A JP H10205527A
- Authority
- JP
- Japan
- Prior art keywords
- pressure oil
- oil supply
- supply port
- runner
- bearing pad
- 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.)
- Pending
Links
Landscapes
- Sliding-Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明はスラスト軸受装置に
関する。[0001] The present invention relates to a thrust bearing device.
【０００２】[0002]
【従来の技術】高荷重を支えるスラスト軸受には、圧油
を強制的に供給することによりスラストランナと軸受パ
ッドの間に油膜を形成するための圧油供給口が軸受パッ
ド摺動面に設けられている。このようなスラスト軸受
は、「機械設計便覧」１１０８頁に記載の動圧型ティル
ティングパッドスラスト軸受と、同じく「機械設計便
覧」１１０８頁に記載の静圧型スラスト軸受の双方の特
徴を併せもつ。定格回転時には軸受パッドがスラストラ
ンナとの間に回転方向に先細のくさび形状の隙間ができ
るように傾き、くさび効果により発生する動圧によりス
ラストランナと軸受パッドの間に油膜を形成するように
設計されている。つまり、動圧型ティルティングパッド
軸受である。一方、定格回転数以下では十分な動圧が発
生しないため、圧油供給口より圧油を供給し、静圧によ
りスラストランナと軸受パッドの間に油膜を形成するの
で、静圧軸受である。2. Description of the Related Art In a thrust bearing supporting a high load, a pressure oil supply port for forming an oil film between a thrust runner and a bearing pad by forcibly supplying pressure oil is provided on a sliding surface of the bearing pad. Have been. Such a thrust bearing has both features of a dynamic pressure type tilting pad thrust bearing described on page 1108 of “Machine Design Handbook” and a hydrostatic type thrust bearing described on page 1108 of “Mechanical Design Handbook”. At rated rotation, the bearing pad is tilted so that there is a tapered wedge-shaped gap in the rotational direction between the thrust runner and the thrust runner, and the dynamic pressure generated by the wedge effect forms an oil film between the thrust runner and the bearing pad Have been. That is, it is a dynamic pressure type tilting pad bearing. On the other hand, since sufficient dynamic pressure is not generated below the rated rotation speed, pressure oil is supplied from the pressure oil supply port, and an oil film is formed between the thrust runner and the bearing pad by static pressure.
【０００３】従来、可逆回転をする回転軸を支えるスラ
スト軸受では、軸受パッドの支持中心点及び圧油供給口
は、どちらも軸受パッドの円周方向中心線上に設けられ
ていた。これは、軸受の性能が回転軸の方向に依存する
ことをさけるために有効な配置であるとされている。Conventionally, in a thrust bearing that supports a rotating shaft that rotates reversibly, both a support center point of a bearing pad and a pressure oil supply port are provided on a center line in a circumferential direction of the bearing pad. This is said to be an effective arrangement for avoiding that the performance of the bearing depends on the direction of the rotating shaft.
【０００４】[0004]
【発明が解決しようとする課題】しかし、この構造では
圧油供給中に軸受パッドの円周方向傾斜のバランスが悪
くなることがあった。However, in this structure, the balance of the inclination of the bearing pad in the circumferential direction may be deteriorated during the supply of the pressure oil.
【０００５】回転軸停止中に圧油を供給したとき軸受パ
ッドは円周方向にはほとんど傾斜しておらず水平であ
る。圧油を供給したまま回転軸の回転を開始すると、油
膜に発生するせん断力等によりランナの回転方向に対し
て前端部が持ち上がるように軸受パッドは傾く。一般
に、このような方向に傾いたまま回転数が上昇していく
と、くさび効果の逆の効果により油膜の圧力は減少す
る。円周方向支持中心線上の圧油供給口付近及びその下
流の油膜の圧力は圧油の供給があるために、ある程度は
保たれる。ところが、その上流にあたる軸受パッドの前
半部では圧力の減少を補償するだけの圧油の流入はない
ので、圧力は減少する。軸受パッドの後半部での圧力は
保たれ前半部の圧力は減少するので、相対的に後半部の
圧力が前半部よりも高くなる。従って、軸受パッドには
後端を押し下げる力がかかり、軸受パッドの傾きはより
大きくなる。When pressure oil is supplied while the rotating shaft is stopped, the bearing pad is horizontal with little inclination in the circumferential direction. When the rotation of the rotating shaft is started while the pressurized oil is supplied, the bearing pad is inclined so that the front end is lifted in the rotation direction of the runner due to a shearing force or the like generated in the oil film. In general, when the rotational speed increases while tilting in such a direction, the pressure of the oil film decreases due to the opposite effect of the wedge effect. The pressure of the oil film near the pressure oil supply port on the circumferential support center line and at the downstream thereof is maintained to some extent because of the supply of the pressure oil. However, the pressure decreases in the first half of the bearing pad, which is upstream of the bearing pad, since there is no inflow of pressure oil to compensate for the decrease in pressure. Since the pressure in the second half of the bearing pad is maintained and the pressure in the first half decreases, the pressure in the second half is relatively higher than that in the first half. Therefore, a force for pushing down the rear end is applied to the bearing pad, and the inclination of the bearing pad becomes larger.
【０００６】このように、従来の圧油供給口が軸受パッ
ドの円周方向支持中心線上にのみある従来の構造では、
圧油供給中に回転軸を回転させたときに軸受パッドがそ
の円周方向の前縁部を持ち上げる方向に大きく傾いてし
まうのである。このときの軸受パッドの前縁部とスラス
トランナとの間隔は数十μｍと狭くなり、場合によって
は接触し双方の破損を招く可能性がある。As described above, in the conventional structure in which the conventional pressure oil supply port is located only on the circumferential support center line of the bearing pad,
When the rotating shaft is rotated during the supply of the pressurized oil, the bearing pad is greatly inclined in a direction to lift the front edge in the circumferential direction. At this time, the distance between the leading edge of the bearing pad and the thrust runner becomes as small as several tens of μm, and depending on the case, there is a possibility that both may be damaged.
【０００７】このような、軸受パッドがその前縁部を持
ち上げるように大きく傾く現象は、水力発電機の大型化
に伴い大型化したスラスト軸受装置において顕著にあら
われることが確認されている。水力発電機で軸受の損傷
事故が発生するとその修理中は発電を停止することにな
り、甚大な経済的損害を引き起こす。[0007] It has been confirmed that such a phenomenon that the bearing pad is greatly inclined so as to lift the front edge thereof is remarkable in a thrust bearing device which is increased in size as the hydroelectric generator is increased in size. If a bearing damage occurs in a hydroelectric generator, power generation will be stopped during the repair, causing enormous economic damage.
【０００８】本発明の目的は、圧油供給中の軸受パッド
がスラストランナの回転方向に対し前端部を持ち上げる
ように円周方向に大きく傾斜することを防止し、スラス
トランナとの接触による損傷が起きないスラスト軸受を
提供することにある。An object of the present invention is to prevent a bearing pad being supplied with pressurized oil from being greatly inclined in a circumferential direction so as to lift a front end portion with respect to a rotation direction of a thrust runner, thereby preventing damage due to contact with the thrust runner. It is to provide a thrust bearing that does not occur.
【０００９】[0009]
【課題を解決するための手段】上記課題は、回転軸と、
この回転軸に固定されたランナと、このランナを摺動支
持し、かつランナの周方向に沿って設けられた複数の軸
受パッドと、この軸受パッドを支持する支持部材と、前
記軸受パッドの摺動面に設けられた圧油供給口と、この
圧油供給口に圧油を供給する圧油供給手段からなるスラ
スト軸受において、前記圧油供給口を軸受パッドの円周
方向支持中心線をはさんで対応するように複数個設け、
それぞれに圧油供給装置から圧油を供給し、油膜を形成
することにより解決される。The above object is achieved by a rotating shaft,
A runner fixed to the rotating shaft; a plurality of bearing pads slidably supporting the runner and provided along a circumferential direction of the runner; a support member for supporting the bearing pad; In a thrust bearing composed of a pressure oil supply port provided on a moving surface and pressure oil supply means for supplying pressure oil to the pressure oil supply port, the pressure oil supply port is separated from a circumferential support center line of a bearing pad. , Set up multiple to correspond,
The problem is solved by supplying pressure oil from each pressure oil supply device to form an oil film.
【００１０】圧油供給口は軸受パッドとスラストランナ
の間に設けられたばねのような作用をするので、上記の
ように圧油供給口を設けることは支持中心線をはさんで
対応するように複数個ばねを設けたことと同じ効果をも
たらす。円周方向に傾斜させるような外力が軸受パッド
にかかったとしても、これらのばねがパッドをほぼ水平
に保とうとする。また、スラストランナの回転方向に対
する前端部を持ち上げるように軸受パッドが傾斜したと
き、圧油供給口が円周方向支持中心線上にのみある場合
は、軸受パッドの前半部では圧油が行き届きにくかった
ために圧力が減少していた。これに対し、上記のように
圧油供給口を設けると、軸受パッドの前半部にも圧油が
供給されるので、この部分での圧力はあまり減少しなく
なり、軸受パッドの傾きを小さく押さえることが出来
る。このように、軸受パッドはほぼ水平に保たれ、ラン
ナとの接触による損傷を防ぐことができるようになる。[0010] Since the pressure oil supply port acts like a spring provided between the bearing pad and the thrust runner, providing the pressure oil supply port as described above corresponds to the support center line. This has the same effect as providing a plurality of springs. These springs try to keep the pad substantially horizontal, even if an external force is applied to the bearing pad that causes it to tilt in the circumferential direction. Also, when the bearing pad was inclined to lift the front end in the rotation direction of the thrust runner, if the pressure oil supply port was only on the circumferential support center line, the pressure oil was difficult to reach in the first half of the bearing pad. The pressure was decreasing. On the other hand, if the pressure oil supply port is provided as described above, the pressure oil is also supplied to the first half of the bearing pad, so that the pressure at this portion does not decrease so much and the inclination of the bearing pad is suppressed to a small extent. Can be done. In this way, the bearing pad is kept substantially horizontal, and damage due to contact with the runner can be prevented.
【００１１】[0011]
【発明の実施の形態】以下、本発明の実施例を図面を参
照して説明する。図１は本発明の一実施例であり、軸受
パッド３の平面図と軸受パッドにつながる圧油供給装置
を示す。この例では、軸受パッド３には二つの圧油供給
口１２ａ，１２ｂがあり、これらは円周方向支持中心線
をはさんで対応するように配置されている。対応する圧
油供給口と円周方向支持中心線との距離は相等しくなっ
ており、それぞれの圧油供給口のまわりには圧油みぞが
設けられている。Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows an embodiment of the present invention, and shows a plan view of a bearing pad 3 and a pressure oil supply device connected to the bearing pad. In this example, the bearing pad 3 has two pressure oil supply ports 12a and 12b, which are arranged so as to correspond to each other with a circumferential support center line interposed therebetween. The distance between the corresponding pressure oil supply port and the circumferential support center line is equal, and a pressure oil groove is provided around each pressure oil supply port.
【００１２】図７はスラスト軸受装置の全体の断面図で
ある。圧油供給装置作動時には、ポンプ７により圧油は
流量調整バルブ６，チェックバルブ８を通り、この圧油
給油口１２からパッド３とランナ２の摺動面に流れ込み
油膜１５を形成する。流量調整バルブを設けることによ
り、荷重の変動による油膜厚さの変化の少ない油膜を形
成することが出来る。チェックバルブは、ポンプの異常
停止など圧油の供給側の圧力が低下した場合に、油膜か
ら潤滑油が圧油供給装置を逆流することを避けるために
設けられている。図１に示した例では、ポンプから伸び
る１本の管は二つの圧油供給口につながるために途中で
２本に分岐しており、この分岐点と圧油供給口との間に
流量調整バルブ及びチェックバルブが設けられている。
これら２種類のバルブは分岐点よりもポンプ側に設けら
れてもよい。FIG. 7 is a sectional view of the entire thrust bearing device. When the pressure oil supply device is operated, the pressure oil flows from the pressure oil supply port 12 to the sliding surface of the pad 3 and the runner 2 from the pressure oil supply port 12 to form an oil film 15 by the pump 7. By providing the flow control valve, it is possible to form an oil film in which a change in oil film thickness due to a change in load is small. The check valve is provided to prevent the lubricating oil from flowing back through the oil pressure supply device from the oil film when the pressure on the pressure oil supply side drops due to an abnormal stop of the pump or the like. In the example shown in FIG. 1, one pipe extending from the pump is branched into two pipes on the way to connect to two pressure oil supply ports, and the flow rate is adjusted between the branch point and the pressure oil supply port. A valve and a check valve are provided.
These two types of valves may be provided on the pump side of the branch point.
【００１３】回転軸１の停止時に圧油供給口１２から圧
油を供給すると、図１中Ｅ−Ｅ′線上の油膜に発生する
圧力の分布は図２のようになる。このとき、Ｆ側から見
た軸受パッド３の傾きは、図３のようにスラストランナ
２に対し平行になっている。ここで、回転軸１がＤ方向
に回転をはじめると、潤滑油のせん断力等は軸受パッド
を前端部が持ち上がるようなＧ′方向に傾けようとす
る。When pressure oil is supplied from the pressure oil supply port 12 when the rotary shaft 1 is stopped, the distribution of pressure generated in the oil film on the line EE 'in FIG. 1 is as shown in FIG. At this time, the inclination of the bearing pad 3 as viewed from the F side is parallel to the thrust runner 2 as shown in FIG. Here, when the rotating shaft 1 starts rotating in the D direction, the shearing force of the lubricating oil and the like tends to tilt the bearing pad in the G 'direction such that the front end is lifted.
【００１４】圧油供給口部分においてスラストランナと
軸受パッドとの間隔が狭くなると、圧油供給口での油膜
圧力は高くなり、逆に圧油供給口部分においてスラスト
ランナと軸受パッドとの間隔が広くなると、圧油供給口
での油膜圧力は低くなる。つまり、圧油供給口はばねの
ような働きをする訳である。本発明のように圧油供給口
を設けることは、図４に示すように軸受パッドとスラス
トランナの間にばねを設けたことと同じ効果がある。軸
受パッドを円周方向に傾斜させようとする力が働いて
も、支点の両側のばねにより軸受パッドはほぼ水平に保
たれる。When the distance between the thrust runner and the bearing pad is reduced at the pressure oil supply port, the oil film pressure at the pressure oil supply port is increased, and conversely, the distance between the thrust runner and the bearing pad at the pressure oil supply port is reduced. As the pressure increases, the oil film pressure at the pressure oil supply port decreases. That is, the pressure oil supply port acts like a spring. Providing the pressure oil supply port as in the present invention has the same effect as providing a spring between the bearing pad and the thrust runner as shown in FIG. Even when a force is exerted to tilt the bearing pad in the circumferential direction, the bearing pad is kept substantially horizontal by the springs on both sides of the fulcrum.
【００１５】軸受パッドの前端部が持ち上がるように傾
いてしまった場合、このような方向に傾いたまま回転数
が上昇していくと、くさび効果の逆の効果により油膜の
圧力は減少する。軸受パッドの圧油供給口の上流にあた
る部分では圧力の減少を補償するだけの圧油の流入はな
いので圧力は減少するが、本発明のように圧油供給口を
設けた場合にはそれに該当する部分は、従来のものに比
べ狭い。従って、軸受パッドの前半部の圧力が後半部の
圧力に比べ小さくなるとしても、その差は余り大きくな
く、軸受パッドの傾斜は小さいままに押さえることが出
来る。In the case where the front end of the bearing pad is tilted so as to rise, if the rotation speed increases while tilting in such a direction, the pressure of the oil film decreases due to the opposite effect of the wedge effect. In the portion of the bearing pad upstream of the pressure oil supply port, the pressure decreases because the pressure oil does not flow in just to compensate for the decrease in pressure, but this corresponds to the case where the pressure oil supply port is provided as in the present invention. The part to be formed is narrower than the conventional one. Therefore, even if the pressure in the first half of the bearing pad is smaller than the pressure in the second half, the difference is not so large, and the inclination of the bearing pad can be kept small.
【００１６】また、対応する圧油供給口と円周方向支持
中心線との距離を相等しいとすると、対応する圧油供給
口から供給される圧油の流量が相等しくなるように流量
調節バルブを設置するだけで軸受パッドはより水平に近
い傾きでバランスするようになる。さらに、このように
厚油供給口を配置することにより、回転軸の回転方向の
違いによる特性の違いも無くすことが出来る。Further, assuming that the distance between the corresponding pressure oil supply port and the center line in the circumferential direction is equal, the flow rate adjusting valve is controlled so that the flow rate of the pressure oil supplied from the corresponding pressure oil supply port becomes equal. By simply installing the bearing pad, the bearing pads will be balanced with a more horizontal inclination. Further, by disposing the thick oil supply port in this manner, it is possible to eliminate a difference in characteristics due to a difference in the rotation direction of the rotating shaft.
【００１７】また、圧油供給口のまわりに圧油みぞを設
けると、圧油供給口付近の広い範囲に同一の圧力が分布
するようになり、パッドがより安定しやすくなる。Further, when a pressure oil groove is provided around the pressure oil supply port, the same pressure is distributed over a wide range near the pressure oil supply port, and the pad is more easily stabilized.
【００１８】図４に本発明の別の実施例を示す。この例
では、軸受パッドの半径方向支持中心線１８の外側に二
つ、内側に一つの圧油供給口をもうけてある。外側の二
つは、軸受パッドの円周方向支持中心線に関し対称とな
っている。この図の例では半径方向支持中心線の内側に
は円周方向支持中心線上に一つ圧油供給口が設けられた
だけであるが、外側の二つと同様に円周方向支持中心線
をはさみ対応するように複数の圧油供給口を設けても良
い。図５に、図４中Ｈ−Ｈ′線での軸受パッドの断面図
を示す。この図からわかるように、軸受パッドの摺動面
の円周方向の両端はテーパが付けられている。FIG. 4 shows another embodiment of the present invention. In this example, two pressure oil supply ports are provided outside the radial support center line 18 of the bearing pad and one pressure oil supply port is provided inside. The outer two are symmetrical about the circumferential support centerline of the bearing pad. In the example of this figure, only one pressure oil supply port is provided on the circumferential support center line inside the radial support center line, but the circumferential support center line is sandwiched like the two outside. A plurality of pressure oil supply ports may be provided correspondingly. FIG. 5 is a sectional view of the bearing pad taken along line HH 'in FIG. As can be seen from this figure, both ends in the circumferential direction of the sliding surface of the bearing pad are tapered.
【００１９】このように圧油供給口を配置すると、軸受
パッド支持中心線の両側に静圧が発生するので、軸受パ
ッドの半径方向傾斜も安定する。When the pressure oil supply port is arranged in this manner, a static pressure is generated on both sides of the bearing pad support center line, so that the radial inclination of the bearing pad is also stabilized.
【００２０】また、軸受パッドの摺動面のスラストラン
ナの回転方向に対し前端部に付けられたテーパにより、
パッドの前端部で動圧が発生するために、軸受パッドを
その前端部が持ち上がるように傾けようとする力は弱め
られる。この例では、パッドの円周方向の両端の摺動面
にテーパが付けられているので、回転軸がどちらに回転
してもこの効果が得られる。Also, the taper attached to the front end of the sliding surface of the bearing pad with respect to the rotation direction of the thrust runner,
Due to the generation of dynamic pressure at the front end of the pad, the force for tilting the bearing pad so that the front end is lifted is reduced. In this example, since the sliding surfaces at both ends in the circumferential direction of the pad are tapered, this effect can be obtained irrespective of the rotation of the rotating shaft.
【００２１】[0021]
【発明の効果】本発明のティルティングパッドスラスト
軸受によれば、軸受パッドの支持中心の両側に圧油供給
口を設けたことにより軸受パッドを水平に保つことが出
来るので、圧油供給中に軸受パッドのスラストランナと
の接触で損傷することを防ぐことができる。According to the tilting pad thrust bearing of the present invention, since the pressure oil supply ports are provided on both sides of the support center of the bearing pad, the bearing pad can be kept horizontal. The bearing pad can be prevented from being damaged by contact with the thrust runner.
【図１】本発明によるスラスト軸受パッドの平面図。FIG. 1 is a plan view of a thrust bearing pad according to the present invention.
【図２】回転軸静止時に本発明によるスラスト軸受に発
生する油膜圧力の円周方向分布の特性図。FIG. 2 is a characteristic diagram of a circumferential distribution of an oil film pressure generated in a thrust bearing according to the present invention when the rotating shaft is stationary.
【図３】回転軸静止時の本発明によるスラスト軸受パッ
ドの円周方向の傾きの説明図。FIG. 3 is an explanatory view of a circumferential inclination of a thrust bearing pad according to the present invention when the rotating shaft is stationary.
【図４】本発明のスラスト軸受の原理の説明図。FIG. 4 is an explanatory view of the principle of the thrust bearing of the present invention.
【図５】本発明によるスラスト軸受パッドの平面図。FIG. 5 is a plan view of a thrust bearing pad according to the present invention.
【図６】テーパのついたスラスト軸受パッドの断面図。FIG. 6 is a cross-sectional view of a tapered thrust bearing pad.
【図７】一般的なスラスト軸受の全体の断面図。FIG. 7 is an overall sectional view of a general thrust bearing.
１…回転軸、６…流量調節バルブ、７…ポンプ、８…チ
ェックバルブ、９…潤滑油、１２…圧油供給口、１３…
圧油みぞ、１７…半径方向支持中心線。DESCRIPTION OF SYMBOLS 1 ... Rotating shaft, 6 ... Flow control valve, 7 ... Pump, 8 ... Check valve, 9 ... Lubricating oil, 12 ... Pressure oil supply port, 13 ...
Pressure oil groove, 17 ... radial support center line.
Claims (5)
と、前記ランナを摺動支持し、前記ランナの円周方向に
沿って設けられた複数の軸受パッドと、前記軸受パッド
を支持する支持部材と、前記軸受パッドの摺動面に設け
られた圧油供給口と、前記圧油供給口に圧油を供給する
圧油供給手段からなるスラスト軸受において、前記圧油
供給口を前記軸受パッドの円周方向支持中心線をはさん
で対応するように複数個設け、それぞれに前記圧油供給
手段から圧油を供給し、油膜を形成することを特徴とす
るスラスト軸受装置。1. A rotating shaft, a runner fixed to the rotating shaft, a plurality of bearing pads slidably supporting the runner, and provided along a circumferential direction of the runner, and supporting the bearing pad. A supporting member, a pressure oil supply port provided on the sliding surface of the bearing pad, and a pressure oil supply means for supplying pressure oil to the pressure oil supply port. A thrust bearing device, wherein a plurality of bearing pads are provided so as to correspond to each other in a circumferential direction of a support center line, and pressurized oil is supplied from each of the pressurized oil supply means to form an oil film.
距離が、対応する前記圧油供給口と円周方向支持中心線
との距離と相等しい請求項１に記載のスラスト軸受装
置。2. The thrust bearing according to claim 1, wherein the distance between the pressure oil supply port and the circumferential support center line is equal to the distance between the corresponding pressure oil supply port and the circumferential support center line. apparatus.
た請求項１または２に記載のスラスト軸受装置。3. The thrust bearing device according to claim 1, wherein a pressure oil groove is provided around the pressure oil supply port.
向支持中心線をはさんで対応するように一つ以上の圧油
供給口を設けた請求項１，２または３に記載のスラスト
軸受装置。4. The pressure oil supply port according to claim 1, wherein one or more pressure oil supply ports are provided so as to correspond to the corresponding plurality of pressure oil supply ports with a radial support center line interposed therebetween. Thrust bearing device.
向に対する前端部にテーパを付けた請求項１，２，３ま
たは４に記載のスラスト軸受装置。5. The thrust bearing device according to claim 1, wherein a front end portion of the sliding surface of the bearing pad in the rotation direction of the runner is tapered.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9009191A JPH10205527A (en) | 1997-01-22 | 1997-01-22 | Thrust bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9009191A JPH10205527A (en) | 1997-01-22 | 1997-01-22 | Thrust bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH10205527A true JPH10205527A (en) | 1998-08-04 |
Family
ID=11713642
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9009191A Pending JPH10205527A (en) | 1997-01-22 | 1997-01-22 | Thrust bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH10205527A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008095703A (en) * | 2006-10-05 | 2008-04-24 | Hitachi Ltd | Thrust bearing device |
-
1997
- 1997-01-22 JP JP9009191A patent/JPH10205527A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008095703A (en) * | 2006-10-05 | 2008-04-24 | Hitachi Ltd | Thrust bearing device |
| JP4554583B2 (en) * | 2006-10-05 | 2010-09-29 | 株式会社日立製作所 | Thrust bearing device |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US3930691A (en) | Swing pad bearing | |
| JP4249822B2 (en) | Disk support method and compliant foil fluid film thrust bearing | |
| US4082375A (en) | Dual wedge fluid thrust bearing including wave spring | |
| US20150362012A1 (en) | Foil bearing assembly | |
| JP4554583B2 (en) | Thrust bearing device | |
| US6158892A (en) | Fluid film thrust bearing having integral compliant foils | |
| US9366287B2 (en) | Tilting pad bearing device | |
| US5772335A (en) | Self-stabilizing, true-tilting pad with abruptly-stepped pocket for journal bearing | |
| JP2014533342A (en) | Fluid dynamic pressure thrust bearing | |
| US5634725A (en) | Bearing assembly | |
| US10077802B2 (en) | Tilting pad journal bearing assembly | |
| JP2010151292A (en) | Tilting-pad bearing | |
| CN113669363A (en) | Thrust dynamic pressure gas bearing of fillet elastic foil piece supporting structure | |
| JP6332919B2 (en) | Tilting pad bearing device | |
| JPH01320316A (en) | Roller bearing device | |
| JPH10205527A (en) | Thrust bearing | |
| EP0191674A1 (en) | Pressurized-fluid mechanism for a rotor | |
| JP7482000B2 (en) | Tilting pad journal bearing and rotating machine equipped with same | |
| JPH09126228A (en) | Pressure dam type journal bearing | |
| JP5812973B2 (en) | Journal bearing and steam turbine | |
| JPH0893769A (en) | Journal bearing device | |
| RU2677435C2 (en) | Bearing assembly (versions) | |
| JP2005315113A (en) | Turbocharger | |
| KR20200109088A (en) | Foil thrust bearing | |
| JPH07180721A (en) | Tilting pad journal bearing device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080731 Year of fee payment: 13 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Year of fee payment: 13 Free format text: PAYMENT UNTIL: 20080731 |
|
| FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090731 Year of fee payment: 14 |
|
| LAPS | Cancellation because of no payment of annual fees |