JPH05296236A - Tilting pad type thrust bearing device - Google Patents
Tilting pad type thrust bearing deviceInfo
- Publication number
- JPH05296236A JPH05296236A JP4091398A JP9139892A JPH05296236A JP H05296236 A JPH05296236 A JP H05296236A JP 4091398 A JP4091398 A JP 4091398A JP 9139892 A JP9139892 A JP 9139892A JP H05296236 A JPH05296236 A JP H05296236A
- Authority
- JP
- Japan
- Prior art keywords
- stationary plate
- pivot
- thrust bearing
- bearing device
- rotating body
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2380/00—Electrical apparatus
- F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
Landscapes
- Sliding-Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は可逆回転機械の回転体の
スラスト荷重を支えるティルティングパッド式スラスト
軸受装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a tilting pad type thrust bearing device for supporting a thrust load of a rotating body of a reversible rotating machine.
【０００２】[0002]
【従来の技術】揚水形水車発電機や電動機等のような可
逆回転機械の回転体のスラスト荷重を支えるスラスト軸
受は、正逆両方の回転に対して膜圧力が発生し、荷重を
支えられる構造を持っていなければならない。2. Description of the Related Art Thrust bearings, which support the thrust load of a rotating body of a reversible rotating machine such as a pumped-wheel turbine generator or an electric motor, have a structure in which a membrane pressure is generated in both forward and reverse rotations to support the load. Must have
【０００３】また、逆転を防止する機構を持っていない
ポンプ機械等においても、流体力による反転方向の力を
受け、逆回転する可能性があるため、可逆回転を許容す
る軸受構造が必要となる。特に、負荷容量が高く安定性
・組立性（周方向のレベル）に優れるティルティングパ
ッド式スラスト軸受の可逆構造はニーズが高い。Further, even in a pump machine or the like which does not have a mechanism for preventing reverse rotation, there is a possibility of reverse rotation due to the force in the reverse direction due to the fluid force, so that a bearing structure which allows reversible rotation is required. .. In particular, there is a great need for a reversible structure of a tilting pad type thrust bearing that has high load capacity and excellent stability and assembling (level in the circumferential direction).
【０００４】次に、従来技術の代表例を引用しながら、
従来技術の問題について説明する。図４は一方向回転機
に用いられるティルティングパッドであり、１は回転
体、２はこの回転体１のスラスト荷重を支える静止板を
示している。Next, referring to typical examples of the prior art,
The problems of the prior art will be described. FIG. 4 shows a tilting pad used in a one-way rotating machine, where 1 is a rotating body and 2 is a stationary plate which supports the thrust load of the rotating body 1.
【０００５】前記静止板２の摺動面２ａが図示の如き平
面の場合、良く知られている（例えば、「軸受」：岩波
全書）ように、支持中心Ｘ1 ／（Ｘ1 ＋Ｘ2 ）を０．５
５〜０．６０にとれば最大負荷容量が得られる。When the sliding surface 2a of the stationary plate 2 is a flat surface as shown in the drawing, the supporting center X1 / (X1 + X2) is set to 0.5 as well known (for example, "bearing": Iwanami Zensho).
The maximum load capacity can be obtained by setting it to 5 to 0.60.
【０００６】しかしながら、支持中心を何れにとって
も、静止板２の摺動面２ａが平面で、且つ軸受隙間内潤
滑剤の密度低下による、いわゆる「熱くさび効果」が著
しく大きくなければ、正逆両方向（正両方向ω，逆両方
向−ω）の回転は許容されない。However, if the sliding surface 2a of the stationary plate 2 is flat and the so-called "wedge effect" due to the decrease in the density of the lubricant in the bearing gap is not significantly large regardless of the supporting center, both the forward and reverse directions are possible. Rotation in (both normal direction ω and reverse both directions −ω) is not allowed.
【０００７】図５は従来技術の可逆構造で、（ａ）
（ｂ）共に中央支持構造である。図５の（ａ）は、回転
体１を支える静止板２が運転中に厚さ方向の温度差で凸
型に熱変形するか、静止板２を予め凸型に加工するもの
で、前記静止板２の適度な湾曲が得られれば、正逆回転
時ともに十分な圧力が発生することが知られている（日
本機械学会論文集：３１巻２３１号、ｐｐ．１７３１．
「ミッチェル形スラスト軸受の変形について」、田原久
祺）。FIG. 5 shows a reversible structure of the prior art.
(B) Both are central support structures. 5A shows that the stationary plate 2 supporting the rotating body 1 is thermally deformed into a convex shape due to the temperature difference in the thickness direction during operation, or the stationary plate 2 is processed into a convex shape in advance. It is known that when the plate 2 is appropriately curved, sufficient pressure is generated during both forward and reverse rotations (Proceedings of the Japan Society of Mechanical Engineers: Vol. 31, No. 231, pp. 1731.
"Deformation of Mitchell-type thrust bearing", Hisagu Tahara).
【０００８】しかしながら、このような適度な湾曲（最
小膜厚さ程度の湾曲）を変形で与えるには、十分な実験
データと解析が必要であり、構造や大きさの異なる機械
などへ適用する度に多大な労力を必要とし、且つ困難で
ある。However, sufficient experimental data and analysis are required to give such an appropriate curvature (bent of about the minimum film thickness) by deformation, and the degree of application to machines with different structures and sizes is large. It requires a lot of labor and is difficult.
【０００９】図５（ｂ）は、回転体１と静止板２との間
の軸受隙間内の潤滑剤の温度が静止板２の出口側へ向か
って上昇し、潤滑剤の密度が低下することによって生じ
る、いわゆる「熱くさび効果」を利用するものである
が、実際上大きな圧力発生は期待できず、特に低粘度剤
料や小型機では皆無に等しい。FIG. 5B shows that the temperature of the lubricant in the bearing gap between the rotating body 1 and the stationary plate 2 rises toward the outlet side of the stationary plate 2 and the density of the lubricant decreases. Although it utilizes the so-called "heat wedge effect" that is caused by, it is not possible to expect a large pressure generation in practice, and especially with a low-viscosity agent and a small machine, it is virtually nonexistent.
【００１０】[0010]
【発明が解決しようとする課題】前述したように、従来
技術による可逆回転機用のティルティングパッド式スラ
スト軸受の設計は、非常に困難であり、場合によっては
流体潤滑が不可能となり、焼付きなどの事故になる可能
性がある。As described above, the design of the tilting pad type thrust bearing for a reversible rotating machine according to the prior art is extremely difficult, and in some cases fluid lubrication becomes impossible, and seizure occurs. There is a possibility of such an accident.
【００１１】本発明は前記従来技術の問題を解消するた
めになされたもので、逆方向に回転可能なティルティン
グパッド構造を提供し、設計・製作が容易で且つ長期に
わたって安定した軸受性能を発揮する可逆回転機用のテ
ィルティングパッド式スラスト軸受装置を提供すること
を目的とする。The present invention has been made to solve the above-mentioned problems of the prior art, and provides a tilting pad structure capable of rotating in the opposite direction, which is easy to design and manufacture and exhibits stable bearing performance for a long period of time. It is an object of the present invention to provide a tilting pad type thrust bearing device for a reversible rotating machine.
【００１２】[0012]
【課題を解決するための手段】前記の目的を達成するた
めに、静止板の摺動部を傾斜平面とし、且つこの静止板
を支持するピボットを備え、このピボットの高さを調整
する調整溝を静止板受台に設けたことを特徴とする。In order to achieve the above-mentioned object, the sliding portion of the stationary plate is an inclined plane, and a pivot for supporting the stationary plate is provided, and an adjusting groove for adjusting the height of the pivot is provided. Is provided on the stationary plate pedestal.
【００１３】[0013]
【作用】回転体の正方向回転時に、前記ピボットは調整
溝の浅い方の溝部に位置し、偏心支持のティルティング
パッド軸受構造となり、軸受隙間内に圧力が発生する。
一方、回転体の逆方向回転時には、前記ピボットは調整
溝の深い方の溝部に位置し、ピボットの効果を失って静
止板底面が静止板受台に密着し、傾斜平面軸受を構成し
て圧力が発生する。これにより、逆方向回転を許容する
ことができる。When the rotating body rotates in the forward direction, the pivot is located in the shallower groove portion of the adjusting groove, and has a tilting pad bearing structure of eccentric support, so that pressure is generated in the bearing gap.
On the other hand, when the rotating body rotates in the reverse direction, the pivot is located in the deeper groove of the adjustment groove, loses the effect of the pivot, and the bottom surface of the stationary plate comes into close contact with the stationary plate pedestal, forming a tilted plane bearing and pressure. Occurs. This allows the reverse rotation.
【００１４】[0014]
【実施例】以下、本発明の一実施例を図１及び図２に従
い具体的に説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be specifically described below with reference to FIGS.
【００１５】図１及び図２は本発明の一実施例を示す構
造図であり、回転体１は数枚乃至十数枚からなる静止板
２によって、軸受隙間８（回転体１と静止板２との間に
確保される隙間）内の潤滑剤を介して支えられている。
前記静止板２の摺動面２ａは、回転体１の正回転方向に
向かって下り坂の傾斜面として形成されている。FIGS. 1 and 2 are structural views showing an embodiment of the present invention, in which a rotating body 1 comprises a stationary plate 2 consisting of several to a dozen sheets, and a bearing gap 8 (rotating body 1 and stationary plate 2). It is supported via the lubricant in the gap secured between () and.
The sliding surface 2a of the stationary plate 2 is formed as an inclined surface that descends downward in the forward rotation direction of the rotating body 1.
【００１６】前記静止板２と静止板受台３との間には、
静止板２を支持するボール或いは円筒体からなるピボッ
ト７（図示例はボールのピボットを示している）が静止
板２及び静止板受台３のどちらにも固定されない状態で
介在される。Between the stationary plate 2 and the stationary plate pedestal 3,
A pivot 7 (a ball pivot is shown in the drawing) which supports the stationary plate 2 and which is a ball or a cylindrical body is interposed in neither the stationary plate 2 nor the stationary plate pedestal 3 in a fixed state.
【００１７】このピボット７を静止板２と静止板受台３
との間の特定位置に転動可能に保持するため、前記静止
板２にピボット７が係合する凹状のピボット受５を設
け、且つ前記静止板受台３にピボット７の高さ（静止板
受台３上への突出高さ）を調整する深溝部及び浅溝部の
連設溝からなる調整溝６を回転体１の逆回転方向へ向け
て図示の如く凹設している。The pivot 7 is attached to the stationary plate 2 and the stationary plate support 3
In order to hold the stationary plate 2 at a specific position between the stationary plate 2 and the stationary plate 2 so that the pivot 7 is engaged, a concave pivot receiver 5 is provided, and the stationary plate pedestal 3 has a height of the pivot 7 (static plate). An adjusting groove 6 which is a continuous groove of a deep groove portion and a shallow groove portion for adjusting the protruding height of the pedestal 3) is provided as shown in the drawing in the reverse rotation direction of the rotating body 1.
【００１８】また、前記静止板２の静止板受台３に対す
る接離移動を可能とするため、前記静止板２と静止板受
台３の周方向には、静止板移動許容隙間Ｘ4 が設けられ
ている。なお、静止板受台３はベース４上に固着され
る。次に、前記構成のティルティングパッド式スラスト
軸受装置がどのように作用するかについて説明する。In order to allow the stationary plate 2 to move toward and away from the stationary plate receiving base 3, a stationary plate moving allowance gap X4 is provided in the circumferential direction between the stationary plate 2 and the stationary plate receiving base 3. ing. The stationary plate support 3 is fixed on the base 4. Next, how the tilting pad type thrust bearing device having the above-described structure works will be described.
【００１９】仮に前記回転体１の停止時において、移動
可能なピボット７が調整溝６の深溝部に位置していると
する。この時、前記ピボット７と静止板のピボット受５
との間に隙間を有するように前記調整溝６の深溝部の溝
深さを決める。It is assumed that the movable pivot 7 is located in the deep groove portion of the adjusting groove 6 when the rotating body 1 is stopped. At this time, the pivot 7 and the pivot receiver 5 of the stationary plate
The groove depth of the deep groove portion of the adjusting groove 6 is determined so that there is a gap between the groove and the groove.
【００２０】前記回転体１が正方向（図１矢印ωで示す
方向）に回転すると、この回転体１と静止板２との間の
軸受隙間８には圧力が発生しない。このため、回転体１
は静止板２に対し片当り或いは全面が接触した状態で静
止板２を回転方向に引きずって行く。この時、ピボット
７は転がり或いは滑りながら、静止板２と回転体１を押
し上げつつ溝表面を移動し、最終的に前記調整溝６の浅
溝部に位置する。When the rotating body 1 rotates in the forward direction (the direction indicated by the arrow ω in FIG. 1), no pressure is generated in the bearing gap 8 between the rotating body 1 and the stationary plate 2. Therefore, the rotating body 1
Moves the stationary plate 2 in the direction of rotation with the stationary plate 2 contacting one side or the entire surface. At this time, the pivot 7 moves on the groove surface while pushing up the stationary plate 2 and the rotating body 1 while rolling or sliding, and finally positioned at the shallow groove portion of the adjusting groove 6.
【００２１】ここで、前記の静止板移動許容隙間Ｘ4 は
静止板２が傾斜できるように深溝部と浅溝部の間隔寸法
Ｘ3 より若干大きくし、また支持率はＸ1 ／（Ｘ1 ＋Ｘ
2 ）＝０．５５〜０．６程度とする。前記深溝部と浅溝
部の段差は、後述するように軸受平均隙間の十倍程度と
れば良く、従って１〜３mm程度とする。以上のようにし
て静止板２は、ピボット７で支持された図１に示すティ
ルティングパッド構造となる。次に、前記回転体１が何
等かの原因で逆方向（図２矢印−ωで示す方向）に回転
する場合の作用について説明する。Here, the stationary plate movement allowance gap X4 is set to be slightly larger than the space dimension X3 between the deep groove portion and the shallow groove portion so that the stationary plate 2 can be tilted, and the supporting rate is X1 / (X1 + X).
2) = 0.55 to 0.6. The step difference between the deep groove portion and the shallow groove portion may be about ten times the average bearing clearance as described later, and is therefore about 1 to 3 mm. As described above, the stationary plate 2 has the tilting pad structure shown in FIG. 1 supported by the pivot 7. Next, the operation when the rotating body 1 rotates in the reverse direction (direction shown by arrow -ω in FIG. 2) for some reason will be described.
【００２２】前記回転体１が一旦停止すると、ピボット
７上の静止板２は回転体１と接触する。この状態から前
記回転体１が逆方向に回転し始めると、正回転の時と同
様に回転体１は静止板２を引きずって行く。これにより
ピボット７は前記調整溝６の深溝部の方向へ移動してピ
ボットの効果を失い、このため静止板２と静止板受台３
が図２の如く接触する。従って、静止板２はティルティ
ングパッドの機能を失い、傾斜平面パッド構造を形成し
て軸受隙間８内に圧力を発生する。図３（ａ），（ｂ）
に傾斜平面軸受９を圧力分布１０との関係で示す。Once the rotating body 1 stops, the stationary plate 2 on the pivot 7 comes into contact with the rotating body 1. When the rotating body 1 starts to rotate in the opposite direction from this state, the rotating body 1 drags the stationary plate 2 as in the case of normal rotation. As a result, the pivot 7 moves toward the deep groove portion of the adjusting groove 6 and loses the effect of the pivot, so that the stationary plate 2 and the stationary plate support 3
Contact as shown in FIG. Therefore, the stationary plate 2 loses the function of the tilting pad, forms an inclined flat pad structure, and generates pressure in the bearing gap 8. 3 (a), 3 (b)
The inclined plane bearing 9 is shown in relation to the pressure distribution 10.
【００２３】負荷容量は隙間比；ｈi ／ｈo が２．０〜
２．５程度（例えば、「軸受」：岩波全書）で最大とな
るため、傾斜平面パッドの高さの差；ｈi −ｈo ＝（１
−ｈo／ｈi ）×ｈi は、０．４〜０．５・ｈi とすれ
ば良い。従って、前述の溝段差Ｙは１〜３mmで十分とな
る。以上の作用により、正逆両回転時ともに十分な負荷
容量が得られる。The load capacity is a clearance ratio; hi / ho is 2.0 to
Since the maximum is about 2.5 (for example, "bearing": Iwanami Zensho), the difference in height of the inclined flat pads; hi-ho = (1
-Ho / hi) * hi may be 0.4 to 0.5.hi. Therefore, the above-mentioned groove step Y of 1 to 3 mm is sufficient. With the above operation, sufficient load capacity can be obtained in both forward and reverse rotations.
【００２４】[0024]
【発明の効果】本発明のティルティングパッド式スラス
ト軸受装置によれば、回転体の正方向回転時にはティル
ティングパッド構造を、また回転体の逆方向回転時には
傾斜平面パッド構造を形成して、各々最適な潤滑膜形状
を与え、十分な負荷容量が得られる。これにより、可逆
回転機用のティルティングパッド式スラスト軸受装置を
容易に設計・製作することができ、高性能で長期信頼性
に優れた回転機械を提供することができる。According to the tilting pad type thrust bearing device of the present invention, the tilting pad structure is formed when the rotating body rotates in the forward direction, and the inclined plane pad structure is formed when the rotating body rotates in the reverse direction. The optimum lubricating film shape is given and sufficient load capacity is obtained. As a result, a tilting pad type thrust bearing device for a reversible rotating machine can be easily designed and manufactured, and a rotating machine having high performance and excellent long-term reliability can be provided.
【図１】本発明の一実施例によるティルティングパッド
式スラスト軸受装置を回転体正回転時の状態で示した構
造図。FIG. 1 is a structural diagram showing a tilting pad type thrust bearing device according to an embodiment of the present invention in a state of normal rotation of a rotating body.
【図２】前記スラスト軸受装置を回転体逆回転時の状態
で示した構造図。FIG. 2 is a structural diagram showing the thrust bearing device in a state in which a rotating body is reversely rotated.
【図３】（ａ），（ｂ）は傾斜平面軸受の説明図。3 (a) and 3 (b) are explanatory views of a tilted plane bearing.
【図４】従来のスラスト軸受装置を示した構造図。FIG. 4 is a structural diagram showing a conventional thrust bearing device.
【図５】（ａ），（ｂ）は従来技術による可逆回転用の
ティルティングパッド軸受の原理図。5A and 5B are principle diagrams of a tilting pad bearing for reversible rotation according to a conventional technique.
１ 回転体 ２ 静止板 ３ 静止板受台 ４ ベース ５ ピボット受 ６ 調整溝 ７ ピボット ８ 軸受隙間 1 rotating body 2 stationary plate 3 stationary plate pedestal 4 base 5 pivot receiver 6 adjustment groove 7 pivot 8 bearing gap
Claims (1)
る静止板と静止板受台を有したスラスト軸受装置におい
て、前記静止板の摺動部を傾斜平面とし、且つこの静止
板を支持するピボットを備え、このピボットの高さを調
整する調整溝を静止板受台に設けたことを特徴とするテ
ィルティングパッド式スラスト軸受装置。1. A thrust bearing device having a stationary plate for supporting a thrust load of a rotating body of a rotating machine and a stationary plate pedestal, wherein a sliding portion of the stationary plate is an inclined plane and a pivot for supporting the stationary plate. And a tilting pad type thrust bearing device characterized in that an adjustment groove for adjusting the height of the pivot is provided in the stationary plate pedestal.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4091398A JPH05296236A (en) | 1992-04-13 | 1992-04-13 | Tilting pad type thrust bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4091398A JPH05296236A (en) | 1992-04-13 | 1992-04-13 | Tilting pad type thrust bearing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH05296236A true JPH05296236A (en) | 1993-11-09 |
Family
ID=14025280
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4091398A Pending JPH05296236A (en) | 1992-04-13 | 1992-04-13 | Tilting pad type thrust bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH05296236A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012529611A (en) * | 2009-06-08 | 2012-11-22 | ウォーキシャー ベアリングス コーポレイション | Bidirectional rotating offset pivot thrust bearing |
| KR20200012719A (en) | 2018-07-27 | 2020-02-05 | 다이도 메탈 고교 가부시키가이샤 | Bearing device and rotating machine using the same |
-
1992
- 1992-04-13 JP JP4091398A patent/JPH05296236A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012529611A (en) * | 2009-06-08 | 2012-11-22 | ウォーキシャー ベアリングス コーポレイション | Bidirectional rotating offset pivot thrust bearing |
| KR20200012719A (en) | 2018-07-27 | 2020-02-05 | 다이도 메탈 고교 가부시키가이샤 | Bearing device and rotating machine using the same |
| US10948010B2 (en) | 2018-07-27 | 2021-03-16 | Daido Metal Company Ltd. | Bearing device and rotating machine using the same |
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