JP2000046042A - Thrust bearing device - Google Patents
Thrust bearing deviceInfo
- Publication number
- JP2000046042A JP2000046042A JP10214153A JP21415398A JP2000046042A JP 2000046042 A JP2000046042 A JP 2000046042A JP 10214153 A JP10214153 A JP 10214153A JP 21415398 A JP21415398 A JP 21415398A JP 2000046042 A JP2000046042 A JP 2000046042A
- Authority
- JP
- Japan
- Prior art keywords
- stationary plate
- thrust bearing
- bearing device
- stationary
- 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- Withdrawn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
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
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/30—Application independent of particular apparatuses related to direction with respect to gravity
- F16C2300/34—Vertical, e.g. bearings for supporting a vertical shaft
Landscapes
- Sliding-Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、縦軸回転電機等に
用いられるスラスト軸受装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a thrust bearing device used for a vertical rotating electric machine or the like.
【０００２】[0002]
【従来の技術】図２０は、水力発電機に用いられる一般
的なスラスト軸受装置の縦断面図であって、回転軸１に
はスラストカラー２が取り付けられており、そのスラス
トカラー２の下面に回転板３が装着されている。一方、
上記回転軸１の外周には潤滑油が満たされた環状の油槽
４が配設されており、その油槽４内に設けられた支持板
５上に、回転軸１の周りに放射状に配設された複数の扇
形状の静止板６が弾性体７を介して支持されている。そ
して、上記静止板６上に回転板３が摺動可能に支持され
ている。また、スラストカラー２の側面にはガイド軸受
８が取り付けられ、このガイド軸受８の外周には潤滑油
が満たされている第２の油槽９が設けられている。2. Description of the Related Art FIG. 20 is a longitudinal sectional view of a general thrust bearing device used in a hydroelectric generator. A thrust collar 2 is attached to a rotating shaft 1 and a lower surface of the thrust collar 2 is attached to the thrust collar 2. The rotating plate 3 is mounted. on the other hand,
An annular oil tank 4 filled with lubricating oil is provided on the outer periphery of the rotary shaft 1, and is disposed radially around the rotary shaft 1 on a support plate 5 provided in the oil tank 4. A plurality of fan-shaped stationary plates 6 are supported via elastic bodies 7. The rotating plate 3 is slidably supported on the stationary plate 6. A guide bearing 8 is attached to a side surface of the thrust collar 2, and a second oil tank 9 filled with lubricating oil is provided on an outer periphery of the guide bearing 8.
【０００３】上記扇形状の各静止板６は、図２１に示す
ように鋼製の静止板台金１０の上面にホワイトメタルか
ら形成された軸受すべり面材１１を層着することにより
形成されている。Each of the fan-shaped stationary plates 6 is formed by layering a bearing sliding surface material 11 made of white metal on the upper surface of a steel stationary plate base 10 as shown in FIG. I have.
【０００４】ところで、スラスト軸受の摩擦損失、潤滑
油の撹拌損失等からなる機械損失を低減し、水力発電機
の高効率を図る方策として、軸受すべり面の平均面圧を
高めて軸受を小型化する方法があるが、図２１に示すよ
うなホワイトメタルから形成された軸受すべり面材１１
を備えた静止板６は、すべり面材自体の温度強度限界、
高面圧下でのクリープ開始時点の温度限界が存在するこ
とに加えて、すべり面で発生する熱が静止板台金１０に
伝わり、静止板６の著しい熱変形を招き、軸受性能を低
下させるとともに、過酷な運転状況下で軸受の焼損を発
生させる恐れがある。Meanwhile, as a measure to reduce the mechanical loss such as the friction loss of the thrust bearing and the agitation loss of the lubricating oil, and to increase the efficiency of the hydraulic power generator, the bearing is reduced in size by increasing the average surface pressure of the sliding surface of the bearing. The sliding surface material 11 made of white metal as shown in FIG.
The stationary plate 6 provided with the temperature limit of the sliding surface material itself,
In addition to the existence of a temperature limit at the start of creep under a high surface pressure, heat generated on the slip surface is transmitted to the stationary platen 10, causing significant thermal deformation of the stationary plate 6, degrading bearing performance and Under severe operating conditions, the bearing may be burned out.
【０００５】そこで、軸受すべり面材に、グラスファイ
バー、二硫化モリブデン等を充填したテトラフルオロエ
チレン材料を適用することで、従来の軸受合金材料では
得られないほどの耐摩耗性に優れ、軸受すべり面摩擦係
数も小さく、軸受平均面圧も従来軸受より高めることが
でき、軸受損失を減少させることができるようになっ
た。[0005] Therefore, by applying a tetrafluoroethylene material filled with glass fiber, molybdenum disulfide, or the like to the bearing sliding surface material, the bearing sliding material has excellent wear resistance that cannot be obtained with conventional bearing alloy materials. The surface friction coefficient is small, the bearing average surface pressure can be increased as compared with conventional bearings, and bearing loss can be reduced.
【０００６】[0006]
【発明が解決しようとする課題】ところが、従来のスラ
スト軸受装置の静止板においては、静止板の形状が扇形
であるため、回転方向遅れ側の静止板端部で、潤滑油の
衝突、流れ方向の急変等があり、軸受すべり面材にグラ
スファイバー、二硫化モリブデン等を充填したテトラフ
ルオロエチレン材を適用し、軸受を小型化しても潤滑油
の撹拌損失はあまり低減させることができないという問
題がある。また、軸受すべり面表面に発生する油膜圧力
は、静止板の支持点とスラスト力が釣り合った荷重支持
点を中心に、ほぼ同心円状に分布しており、扇形の角部
の軸受能力はほとんど無視できる。However, in the conventional stationary plate of the thrust bearing device, since the stationary plate has a fan shape, collision and flow direction of the lubricating oil occur at the end of the stationary plate on the rotation direction delay side. The use of tetrafluoroethylene material filled with glass fiber, molybdenum disulfide, etc. as the sliding surface material of the bearing has the problem that even if the bearing is downsized, the stirring loss of the lubricating oil cannot be reduced much. is there. In addition, the oil film pressure generated on the sliding surface of the bearing is distributed almost concentrically around the load supporting point where the thrust force is balanced with the supporting point of the stationary plate, and the bearing capacity at the corner of the sector is almost ignored. it can.
【０００７】本発明は、このような点に鑑み、静止板の
形状を扇形から丸形にして、殆ど軸受能力を発生してい
ない部分を省くことにより小型化を図るとともに、回転
方向遅れ側の静止板端部での潤滑油の衝突、流れ方向の
急変等による撹拌損失を低減させ高い効率化を図ったス
ラスト軸受を得ることを目的とする。[0007] In view of the above, the present invention aims at reducing the size of the stationary plate by changing the shape of the stationary plate from a sector shape to a round shape and omitting a portion where little bearing capacity is generated, and at the same time reducing the rotational direction. It is an object of the present invention to obtain a thrust bearing that achieves high efficiency by reducing stirring loss due to collision of lubricating oil at the end of a stationary plate, sudden change in flow direction, and the like.
【０００８】[0008]
【課題を解決するための手段】第１の発明は、回転軸の
回りに放射状に配設され、上記回転軸に取り付けられた
スラストカラーの下端面に設けた回転板を摺動可能に支
持する複数の静止板を有するスラスト軸受装置におい
て、上記静止板の平面形状を丸形としたことを特徴とす
る。According to a first aspect of the present invention, a rotary plate radially disposed around a rotary shaft and provided on a lower end surface of a thrust collar attached to the rotary shaft is slidably supported. In a thrust bearing device having a plurality of stationary plates, the planar shape of the stationary plate is round.
【０００９】第２の発明は、第１の発明において、上記
静止板における軸受すべり面が、ポリエーテルエーテル
ケトン材料、ポリイミド材料等の高分子材料で形成され
ていることを特徴とする。According to a second aspect of the present invention, in the first aspect, the bearing sliding surface of the stationary plate is formed of a polymer material such as a polyetheretherketone material or a polyimide material.
【００１０】第３の発明は、第１の発明または第２の発
明において、上記静止板における回転遅れ側の表面およ
び回転進み側の表面の少なくとも一方に、静止板の外周
側に向かって静止板の厚さが薄くなるような所定幅の傾
斜部が設けられていることを特徴とする。[0010] In a third aspect based on the first or second aspect, at least one of the surface on the rotation delay side and the surface on the rotation advance side of the stationary plate is provided with the stationary plate facing the outer peripheral side of the stationary plate. Is characterized in that an inclined portion having a predetermined width is provided so as to reduce the thickness.
【００１１】第４の発明は、第１乃至第３の発明のいず
れかにおいて、静止板が、グラススファイバー等を充填
して形成した高分子材料からなる支持体によって支持さ
れていることを特徴とする。A fourth invention is characterized in that, in any one of the first to third inventions, the stationary plate is supported by a support made of a polymer material formed by filling glass fibers or the like. And
【００１２】第５の発明は、第１乃至第３の発明のいず
れかにおいて、静止板が、径が大きくなるにつれバネ強
さが弱くなる円筒状バネを複数組み合わせた多重円筒バ
ネ構造体によって支持されていることを特徴とする。According to a fifth aspect of the present invention, in any one of the first to third aspects, the stationary plate is supported by a multi-cylindrical spring structure in which a plurality of cylindrical springs whose spring strengths decrease as the diameter increases. It is characterized by having been done.
【００１３】第６の発明は、第１乃至第３の発明のいず
れかにおいて、静止板が、径が大きくなるにつれバネ強
さが弱くなるようグラスファイバー等を充填して形成し
た高分子材料からなる円筒状の積層体を複数組み合わせ
た多重円筒の積層体により支持されていることを特徴と
する。According to a sixth aspect of the present invention, in any one of the first to third aspects, the stationary plate is made of a polymer material formed by filling glass fiber or the like so that the spring strength becomes weaker as the diameter increases. Characterized by being supported by a multi-cylindrical laminate obtained by combining a plurality of such cylindrical laminates.
【００１４】第７の発明は、第１乃至第３の発明のいず
れかにおいて、静止板が、球殻状の支持構造体で支持さ
れていることを特徴とする。According to a seventh aspect, in any one of the first to third aspects, the stationary plate is supported by a spherical shell-shaped support structure.
【００１５】第８の発明は、第１乃至第３の発明のいず
れかにおいて、静止板の静止板台金部側面の少なくとも
回転方向遅れ側および進み側に所定幅のスリット溝が形
成されていることを特徴とする。According to an eighth aspect of the present invention, in any one of the first to third aspects, a slit groove having a predetermined width is formed on at least a rotationally delayed side and an advanced side of a side surface of the stationary plate base of the stationary plate. It is characterized by the following.
【００１６】第９の発明は、第１乃至第８の発明のいず
れかにおいて、静止板における静止板台金の径が軸受す
べり面材の径より大きくしてあることを特徴とする。According to a ninth aspect of the present invention, in any one of the first to eighth aspects, the diameter of the stationary base plate in the stationary plate is larger than the diameter of the bearing sliding surface material.
【００１７】第１０の発明は、第１乃至第９の発明のい
ずれかにおいて、静止板における軸受すべり面に、外部
から強制的に潤滑油を供給する油留まりが設けられてい
ることを特徴とする。According to a tenth aspect, in any one of the first to ninth aspects, an oil sump for forcibly supplying lubricating oil from the outside is provided on a bearing slip surface of the stationary plate. I do.
【００１８】第１１の発明は、第１乃至第１０の発明の
いずれかにおいて、静止板が回転軸を中心とする同心円
上に複数列配列されていることを特徴とする。According to an eleventh aspect, in any one of the first to tenth aspects, the stationary plates are arranged in a plurality of rows on a concentric circle centered on the rotation axis.
【００１９】[0019]
【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。図１は、本発明の一実
施の形態におけるスラスト軸受の静止板２０の鳥瞰図で
あって、静止板２０は、静止板台金２１の上面に中間層
２２を強固に一体化させ、グラスファイバー、二硫化モ
リブデン等を充填したテトラフルオロエチレン材からな
る軸受すべり面材２３を中間層２２の上面に接合するこ
とによって構成されている。そして図に示すように、従
来の扇形の静止板で軸受性能が十分に満足される有効面
積と等価の面積が得られる等価径を直径とした丸形状と
してある。Embodiments of the present invention will be described below with reference to the accompanying drawings. FIG. 1 is a bird's-eye view of a stationary plate 20 of a thrust bearing according to an embodiment of the present invention, and the stationary plate 20 has a middle layer 22 firmly integrated on the upper surface of a stationary plate base 21, The bearing sliding surface member 23 made of a tetrafluoroethylene material filled with molybdenum disulfide or the like is configured to be joined to the upper surface of the intermediate layer 22. Then, as shown in the figure, the conventional fan-shaped stationary plate has a circular shape having a diameter equivalent to an effective area capable of providing an area equivalent to an effective area sufficient for bearing performance.
【００２０】このように、静止板２０を従来の扇形から
丸形にすることにより軸受能力を発生していない角部を
省くことにより小型化を図ることができるとともに、軸
受摺動面積が少なくなり、軸受損失を低減でき、また軸
受静止板端部での潤滑油の流れをスムーズにし、静止板
端部での潤滑油の衝突、流れ方向の急変による撹拌損失
を低減させ高効率化を図ることができる。As described above, by making the stationary plate 20 round from the conventional sector shape, it is possible to reduce the size by eliminating corners where no bearing capacity is generated, and to reduce the bearing sliding area. To reduce the bearing loss, smooth the lubricating oil flow at the end of the stationary plate of the bearing, and reduce the agitation loss due to the collision of the lubricating oil at the end of the stationary plate and the sudden change in the flow direction to achieve higher efficiency. Can be.
【００２１】また、上記実施の形態においては、軸受す
べり面材２３として従来と同様にグラスファイバー、二
硫化モリブデン等を充填したテトラフルオロエチレン材
を使用したものを示したが、ポリエーテルエーテルケト
ン材料、ポリイミド材料等の高分子材料によって軸受す
べり面を形成してもよい。Further, in the above-described embodiment, the bearing sliding surface material 23 is made of a material such as a glass fiber or a tetrafluoroethylene material filled with molybdenum disulfide or the like, as in the prior art. The bearing slip surface may be formed of a polymer material such as a polyimide material.
【００２２】図２は、本発明のスラスト軸受装置におけ
る静止板の他の実施の形態を示す平面図であって、静止
板２０の回転遅れ側の表面に、所定幅で静止板２０の外
周側に向かって静止板２０の厚さが薄くなるように傾斜
部２０ａが形成されている（図３）。そして軸受すべり
面２３ａと傾斜部２０ａの境界線２４が、回転軸１の中
心と静止板２０の中心を結ぶ線２５と平行になるように
形成してある。FIG. 2 is a plan view showing another embodiment of the stationary plate in the thrust bearing device according to the present invention. The inclined portion 20a is formed so that the thickness of the stationary plate 20 becomes thinner toward (FIG. 3). A boundary line 24 between the bearing slide surface 23a and the inclined portion 20a is formed so as to be parallel to a line 25 connecting the center of the rotating shaft 1 and the center of the stationary plate 20.
【００２３】しかして、このように形成された静止板２
０の表面に沿って回転板３（図２０）が回転すると、そ
の回転板３とともに移動する潤滑油がこの回転板３の下
面と静止板２０の傾斜部２０ａとで形成される楔状の空
間に圧入され、その潤滑油が軸受すべり面２３ａと回転
板３間にスムースに導入される。したがって、上記軸受
すべり面２３ａ上に油膜圧力が適正に発生され、軸受損
失を減少させることができる。Thus, the stationary plate 2 thus formed is
When the rotary plate 3 (FIG. 20) rotates along the surface of the rotary plate 3, the lubricating oil that moves with the rotary plate 3 enters a wedge-shaped space formed by the lower surface of the rotary plate 3 and the inclined portion 20a of the stationary plate 20. The lubricating oil is press-fitted and smoothly introduced between the bearing slide surface 23a and the rotating plate 3. Therefore, the oil film pressure is appropriately generated on the bearing slide surface 23a, and the bearing loss can be reduced.
【００２４】ところで、図２においては静止板２０の回
転遅れ側の表面に傾斜部２０ａを設けたものを示した
が、図４に示すように、静止板２０の回転進み側及び回
転遅れ側の両表面に傾斜部２０ａを形成してもよい。ま
た、静止板２０の回転進み側の表面のみに傾斜部２０ａ
を形成してもよい。FIG. 2 shows the stationary plate 20 provided with the inclined portion 20a on the surface on the rotation delay side, but as shown in FIG. 4, the stationary plate 20 on the rotation advance side and the rotation delay side is provided. The inclined portions 20a may be formed on both surfaces. Also, only the inclined portion 20a is provided only on the surface on the rotation advance side of the stationary plate 20.
May be formed.
【００２５】さらに、図２においては、軸受すべり面２
３ａと傾斜部２０ａの境界線２４が回転軸の中心と静止
板２０の中心を結ぶ線２５と平行になるようにしたもの
を示したが、図５に示すように、上記境界線２４を回転
軸の中心を通る放射線上に位置するようにしてもよい。Further, in FIG. 2, the bearing sliding surface 2
Although the boundary line 24 between 3a and the inclined portion 20a is shown to be parallel to the line 25 connecting the center of the rotation axis and the center of the stationary plate 20, the boundary line 24 is rotated as shown in FIG. It may be located on a ray passing through the center of the axis.
【００２６】図６は、本発明の他の実施の形態を示す図
であって静止板２０における軸受すべり面材２３を支持
する静止板台金２１が支持体２６によって支持されてい
る。上記支持体２６はグラスファイバー等を充填し形成
した高分子材料からなる多層構造を有する積層体からな
り、その支持体２６上に、静止板台金２１が接触面で微
少な所定範囲の摺動が許容され、その回転が制限される
ように支持されている。すなわち、静止板台金２１の底
面には中央凹部２１ａが形成され、その中央凹部２１ａ
の内周面と支持体２６の外周面との間に微少間隙を有す
るように中央凹部２１ａが支持体２６の上部に嵌合支持
せしめられている。FIG. 6 is a view showing another embodiment of the present invention. A stationary plate base 21 for supporting a bearing sliding surface member 23 of a stationary plate 20 is supported by a support 26. The support 26 is a laminate having a multi-layer structure made of a polymer material formed by filling glass fiber or the like. On the support 26, the stationary metal plate 21 is slid within a small predetermined range on the contact surface. Are allowed, and the rotation thereof is limited. That is, a central concave portion 21a is formed on the bottom surface of the stationary sheet metal 21 and the central concave portion 21a is formed.
The central concave portion 21a is fitted and supported on the upper portion of the support 26 so as to have a minute gap between the inner peripheral surface of the support 26 and the outer peripheral surface of the support 26.
【００２７】高分子材料からなる積層体を用いることに
より、従来の金属バネに比べ高いバネ支持剛性が得られ
る。By using a laminate made of a polymer material, a higher spring supporting rigidity can be obtained as compared with a conventional metal spring.
【００２８】図７は、上記支持体２６の他の変形例を示
す図であって、支持体２６が円筒状のバネ２７を複数組
み合わせた多重円筒状のバネ構造体によって形成され、
外周側になる程その円筒状のバネのバネ強さが弱くなる
ようにしてある。FIG. 7 is a view showing another modification of the above-mentioned support member 26. The support member 26 is formed by a multi-cylindrical spring structure in which a plurality of cylindrical springs 27 are combined.
The spring strength of the cylindrical spring becomes weaker toward the outer peripheral side.
【００２９】また、支持体２６は、図８に示すようにグ
ラスファイバー等を充填して形成した高分子材料からな
る円筒状の積層体２８を複数組み合わせた多重円筒状の
積層体によって構成され、外周側になるにつれその積層
体２８のバネ強さが弱くなるようにしてもよい。Further, as shown in FIG. 8, the support 26 is constituted by a multi-cylindrical laminate obtained by combining a plurality of cylindrical laminates 28 made of a polymer material formed by filling a glass fiber or the like. The spring strength of the laminated body 28 may become weaker toward the outer peripheral side.
【００３０】さらに、上記支持体２６は、図９に示すよ
うに、球殻状の支持構造体２９としてもよい。Further, the support 26 may be a spherical shell-like support structure 29 as shown in FIG.
【００３１】しかして、これらの実施の形態において
は、支持体２６の外周部のバネ強さが弱くなるようにし
てあることから、軸受すべり面２３ａに加わる油膜圧力
に応じて静止板台金２１が傾動し、回動板の回転方向の
軸受すべり面２３ａの形状が適正に中央で凸形状とな
り、油膜圧力を適正に発生させることができる。In these embodiments, since the spring strength of the outer peripheral portion of the support 26 is weakened, the stationary sheet metal 21 can be adjusted according to the oil film pressure applied to the bearing slide surface 23a. Is tilted, and the shape of the bearing sliding surface 23a in the rotation direction of the rotating plate becomes appropriately convex at the center, so that the oil film pressure can be appropriately generated.
【００３２】図１０は、前記静止板２０の他の実施の形
態を示す図であって、静止板台金２１の回転方向遅れ側
側面および進み側側面に弦方向に延びるスリット溝３０
が形成してある。しかして、この場合は静止板台金２１
の頂部外周面部に上記スリット溝３０によって弾性が付
与され、軸受すべり面２３ａに加わる油膜圧力に応じて
外周部が下方に湾曲し、回転板の回転方向の軸受すべり
面２３ａの形状が適正に中央で凸形状となり、油膜圧力
が適正に発生させられる。FIG. 10 is a view showing another embodiment of the stationary plate 20. A slit groove 30 extending in the chord direction is provided on the side surface of the stationary plate base 21 on the delay side and the advance side in the rotation direction.
Is formed. Thus, in this case, the stationary sheet metal 21
Elasticity is imparted to the outer peripheral surface of the top by the slit groove 30, the outer peripheral portion is curved downward according to the oil film pressure applied to the bearing sliding surface 23a, and the shape of the bearing sliding surface 23a in the rotating direction of the rotating plate is properly adjusted to the center. And the oil film pressure is appropriately generated.
【００３３】また、静止板台金の側面にスリット溝３０
を設けたものにおいて、図１１に示すように軸受すべり
面の回転進み側及び回転遅れ側の両方或はそのいずれか
一方に傾斜面２０ａを形成してもよい。さらに上記スリ
ット溝は全周にわたって延びるものとしてもよい。Further, a slit groove 30 is provided on the side of the stationary plate base.
As shown in FIG. 11, an inclined surface 20a may be formed on both or one of the rotation advance side and the rotation delay side of the bearing slide surface. Further, the slit groove may extend over the entire circumference.
【００３４】図１２は、本発明のスラスト軸受装置にお
ける静止板２０の他の実施の形態を示す図であって、静
止板台金２１の直径が軸受すべり面材２３の直径より大
きくしてある。FIG. 12 is a view showing another embodiment of the stationary plate 20 in the thrust bearing device of the present invention, wherein the diameter of the stationary plate base 21 is larger than the diameter of the bearing sliding surface member 23. .
【００３５】しかして、この場合、軸受すべり面２３ａ
の潤滑油が静止板台金２１の表面に流れ出ることによっ
て、軸受すべり面２３ａの潤滑油の熱が静止板台金２１
に直接伝わる。そのため、上記潤滑油の熱によって静止
板台金２１に適正な熱変形が起こり、回転板の回転方向
の軸受すべり面２３ａの形状が適正に中央で凸形状とな
り、油膜圧力が適正に発生される。In this case, however, the bearing sliding surface 23a
Of the lubricating oil flows out to the surface of the stationary platen 21, and the heat of the lubricating oil on the bearing slide surface 23 a is
Directly transmitted to. Therefore, the heat of the lubricating oil causes an appropriate thermal deformation of the stationary platen 21, and the shape of the bearing sliding surface 23 a in the rotating direction of the rotating plate is appropriately convex at the center, and the oil film pressure is appropriately generated. .
【００３６】図１３乃至図１６はそれぞれ軸受すべり面
２３ａに油溜まりを形成した例を示す図であり、図１３
に示すようにすべり面２３ａには回転軸１の中心と静止
板２０の中心線を結ぶ線に沿って所定長さの長溝状の油
溜まり３１が形成されており、この油溜まり３１に静止
板台金内に穿設された潤滑油供給路３２の一端が開口さ
れ、この潤滑油供給路３２の他端が油圧浮上機構３３に
接続されている。FIGS. 13 to 16 show examples in which an oil reservoir is formed on the bearing slide surface 23a.
As shown in FIG. 3, a long groove-shaped oil reservoir 31 having a predetermined length is formed on the sliding surface 23a along a line connecting the center of the rotating shaft 1 and the center line of the stationary plate 20. One end of a lubricating oil supply passage 32 formed in the base metal is opened, and the other end of the lubricating oil supply passage 32 is connected to a hydraulic levitation mechanism 33.
【００３７】しかして、上記油圧浮上機構３３によって
潤滑油が上記油溜まり３１に外部から強制的に送給さ
れ、その油溜まり３１を介して図示しない回転板と軸受
すべり面２３ａとの摺接部に潤滑油が送り出される。Thus, the lubricating oil is forcibly supplied from the outside to the oil reservoir 31 by the hydraulic levitation mechanism 33, and the sliding contact portion between the rotating plate (not shown) and the bearing sliding surface 23a via the oil reservoir 31. The lubricating oil is sent out.
【００３８】図１４は上記油溜まりの変形を示す図であ
り、軸受すべり面２３ａには静止板２０と同心円状の油
溜まり３４が形成されている。FIG. 14 is a view showing the deformation of the oil sump. An oil sump 34 concentric with the stationary plate 20 is formed on the bearing slide surface 23a.
【００３９】また、図１５に示すように、回転軸の中心
と静止板２０の中心を結ぶ線上に複数個の油溜まり３５
を設けてもよく、さらに図１６に示すように、軸受すべ
り面２３ａに、回転軸の中心と静止板２０の中心を結ぶ
線に対して対称位置に２系統の油溜まり３６ａ、３６ｂ
を設け、その両油溜まり３６ａ、３６ｂにそれぞれ別々
に外部から潤滑油を強制的に供給するようにしてもよ
い。As shown in FIG. 15, a plurality of oil sumps 35 are located on a line connecting the center of the rotating shaft and the center of the stationary plate 20.
Further, as shown in FIG. 16, two systems of oil sumps 36a and 36b are provided on the bearing slide surface 23a at positions symmetrical with respect to a line connecting the center of the rotating shaft and the center of the stationary plate 20.
May be provided, and the lubricating oil may be separately and forcibly supplied to the oil sumps 36a and 36b from the outside.
【００４０】しかして、このように軸受すべり面２３ａ
と回転板との間に外部から潤滑油を強制的に供給するこ
とによって両者の摺接部に油膜圧力を適正に発生せしめ
ることができ、軸受平均面圧を高め、軸受損失を減少さ
せることができる。Thus, as described above, the bearing sliding surface 23a
By forcibly supplying the lubricating oil from the outside between the rotating plate and the rotating plate, the oil film pressure can be properly generated at the sliding contact portion between them, and the bearing average surface pressure can be increased and the bearing loss can be reduced. it can.
【００４１】また、図１７乃至図１９はそれぞれ本発明
のスラスト軸受装置における静止板の配置状態を示す図
であって、図１７においては、同じ径の静止板２０が、
回転軸の中心を中心とした同心円上に複数列にわたって
配設されており、回転軸の中心と内周側の静止板の中心
と結んだ線の延長線上に外側に配置される静止板２０の
中心がくるようにしてある。FIGS. 17 to 19 are views showing the arrangement of the stationary plates in the thrust bearing device of the present invention. In FIG.
The stationary plate 20 is disposed over a plurality of rows on a concentric circle centered on the center of the rotation axis, and is disposed outside on an extension of a line connecting the center of the rotation axis and the center of the inner stationary plate. It is centered.
【００４２】図１８においては、同じ径の静止板２０が
同心状に複数列にわたって配設されるとともに、回転軸
の中心と、内周側の隣同士の静止板２０の中間点を結ん
だ線の延長線上に、外周側に配置されている静止板２０
の中心がくるように千鳥状に配設されている。In FIG. 18, stationary plates 20 of the same diameter are arranged concentrically in a plurality of rows, and a line connecting the center of the rotating shaft and the intermediate point of the adjacent stationary plates 20 on the inner peripheral side. The stationary plate 20 arranged on the outer peripheral side on the extension of
Are arranged in a zigzag pattern so that the center of the center comes.
【００４３】また、図１９に示すように、同心状に複数
列にわたって配設された静止板２０のうち、外周側の静
止板２０の直径を内周側の静止板の直径より大きくする
こともできる。そして、この場合、軸受すべり面に潤滑
油を強制的に供給する際には、内周側の特定の静止板の
みに供給するようにしてもよい。As shown in FIG. 19, among the stationary plates 20 arranged concentrically in a plurality of rows, the diameter of the stationary plate 20 on the outer peripheral side may be larger than the diameter of the stationary plate on the inner peripheral side. it can. In this case, when the lubricating oil is forcibly supplied to the bearing slip surface, the lubricating oil may be supplied only to the specific stationary plate on the inner peripheral side.
【００４４】[0044]
【発明の効果】以上説明したように、本発明はスラスト
軸受装置の静止板を丸形状としたため、従来の扇形状の
静止板における軸受性能を殆ど発生しない隅角部を取り
除いた形となり、軸受装置の小型化を実現することがで
き、さらに回転方向遅れ側の静止板端部で発生する、潤
滑油の衝突、流れ方向の急変等による攪拌喪失を低減す
ることができ、スラスト軸受の高効率化を図ることがで
きる。As described above, according to the present invention, since the stationary plate of the thrust bearing device has a round shape, the conventional fan-shaped stationary plate has a shape in which corner portions that hardly generate bearing performance are removed, and the bearing is formed. This makes it possible to reduce the size of the device and reduce loss of agitation caused by the collision of lubricating oil and sudden changes in the flow direction, etc., which occur at the end of the stationary plate on the delay side in the rotation direction. Can be achieved.
【図１】本発明のスラスト軸受装置における静止板の鳥
瞰図。FIG. 1 is a bird's-eye view of a stationary plate in a thrust bearing device of the present invention.
【図２】本発明のスラスト軸受装置における静止板の他
の実施の形態を示す平面図。FIG. 2 is a plan view showing another embodiment of the stationary plate in the thrust bearing device of the present invention.
【図３】図２のＡ−Ａ線拡大断面図。FIG. 3 is an enlarged sectional view taken along line AA of FIG. 2;
【図４】図２に示す静止板の変形例を示す平面図。FIG. 4 is a plan view showing a modification of the stationary plate shown in FIG. 2;
【図５】図２に示す静止板の他の変形例を示す平面図。FIG. 5 is a plan view showing another modification of the stationary plate shown in FIG. 2;
【図６】本発明のスラスト軸受装置における静止板の支
持構造部を示す断面図。FIG. 6 is a sectional view showing a support structure of a stationary plate in the thrust bearing device of the present invention.
【図７】図６の静止板の支持構造部の他の変形例を示す
図。FIG. 7 is a view showing another modification of the support structure of the stationary plate of FIG. 6;
【図８】図６の静止板の支持構造部の他の変形例を示す
図。FIG. 8 is a view showing another modification of the support structure of the stationary plate of FIG. 6;
【図９】図６の静止板の支持構造部のさらに他の変形例
を示す図。FIG. 9 is a view showing still another modification of the support structure of the stationary plate of FIG. 6;
【図１０】本発明のスラスト軸受装置における静止板の
さらに他の実施の形態を示す断面図。FIG. 10 is a sectional view showing still another embodiment of the stationary plate in the thrust bearing device of the present invention.
【図１１】図１０の静止板の変形を示す断面図。FIG. 11 is a sectional view showing a modification of the stationary plate of FIG. 10;
【図１２】本発明のスラスト軸受装置における静止板の
他の実施の形態を示す断面図。FIG. 12 is a sectional view showing another embodiment of the stationary plate in the thrust bearing device of the present invention.
【図１３】本発明のスラスト軸受装置における静止板の
さらに他の実施の形態を示す平面図。FIG. 13 is a plan view showing still another embodiment of the stationary plate in the thrust bearing device of the present invention.
【図１４】図１３の静止板の変形例を示す平面図。FIG. 14 is a plan view showing a modification of the stationary plate of FIG. 13;
【図１５】図１３の静止板の他の変形例を示す平面図。FIG. 15 is a plan view showing another modification of the stationary plate of FIG. 13;
【図１６】図１３の静止板のさらに他の変形例を示す平
面図。FIG. 16 is a plan view showing still another modification of the stationary plate of FIG. 13;
【図１７】本発明のスラスト軸受装置における静止板の
配列状態を示す平面図。FIG. 17 is a plan view showing an arrangement of stationary plates in the thrust bearing device of the present invention.
【図１８】図１７の変形例を示す平面図。FIG. 18 is a plan view showing a modification of FIG. 17;
【図１９】図１７の他の変形例を示す平面図。FIG. 19 is a plan view showing another modification of FIG. 17;
【図２０】水力発電機に用いられるスラスト軸受の構造
を示す断面図。FIG. 20 is a cross-sectional view showing the structure of a thrust bearing used in a hydroelectric generator.
【図２１】従来のスラスト軸受装置の静止板の斜視図。FIG. 21 is a perspective view of a stationary plate of a conventional thrust bearing device.
１ 回転軸 ２ スラストカラー ３ 回転板 ５ 支持板 ６ 静止板 ２０ 静止板 ２０ａ 傾斜部 ２１ 静止板台金 ２３ 軸受すべり面材 ２３ａ 軸受すべり面 ２４ 境界線 ２６ 支持体 ２７ 円筒状のバネ ２８ 円筒状の積層体 ２９ 球殻状の支持構造体 ３０ スリット溝 ３１、３４、３５、３６ａ、３６ｂ 油溜まり ３３ 油圧浮上機構 DESCRIPTION OF SYMBOLS 1 Rotating shaft 2 Thrust collar 3 Rotating plate 5 Support plate 6 Stationary plate 20 Stationary plate 20a Inclined part 21 Stationary plate base metal 23 Bearing sliding surface material 23a Bearing sliding surface 24 Boundary line 26 Support body 27 Cylindrical spring 28 Cylindrical spring 28 Laminated body 29 Spherical shell-shaped support structure 30 Slit groove 31, 34, 35, 36a, 36b Oil reservoir 33 Hydraulic levitation mechanism
───────────────────────────────────────────────────── フロントページの続き (72)発明者 宇 野 修 悦 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 (72)発明者 安 藤 雅 敏 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 Ｆターム(参考） 3J011 AA03 AA04 BA15 BA17 JA02 KA03 LA06 MA02 NA02 QA04 SC14 SC20 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor, Shuetsu Uno 2-4, Suehirocho, Tsurumi-ku, Yokohama-shi, Kanagawa Prefecture Inside the Toshiba Keihin Plant (72) Inventor, Masatoshi Ando Suehiro, Tsurumi-ku, Yokohama-shi, Kanagawa 2-4 cho-cho F-term in Toshiba Keihin Works (reference) 3J011 AA03 AA04 BA15 BA17 JA02 KA03 LA06 MA02 NA02 QA04 SC14 SC20
Claims (11)
転軸に取り付けられたスラストカラーの下端面に設けた
回転板を摺動可能に支持する複数の静止板を有するスラ
スト軸受装置において、上記静止板の平面形状を丸型と
したことを特徴とするスラスト軸受装置。1. A thrust bearing device having a plurality of stationary plates radially disposed around a rotating shaft and slidably supporting a rotating plate provided on a lower end surface of a thrust collar attached to the rotating shaft. A thrust bearing device, wherein the planar shape of the stationary plate is round.
エーテルエーテルケトン材料、ポリイミド材料等の高分
子材料で形成されていることを特徴とする、請求項１記
載のスラスト軸受装置。2. The thrust bearing device according to claim 1, wherein a bearing sliding surface of said stationary plate is formed of a polymer material such as a polyetheretherketone material or a polyimide material.
び回転進み側の表面の少なくとも一方に、静止板の外周
側に向かって静止板の厚さが薄くなるような所定幅の傾
斜部が設けられていることを特徴とする、請求項１また
は２記載のスラスト軸受装置。3. An inclined portion having a predetermined width so that the thickness of the stationary plate decreases toward the outer peripheral side of the stationary plate on at least one of the surface on the rotation delay side and the surface on the rotation advance side of the stationary plate. The thrust bearing device according to claim 1, wherein the thrust bearing device is provided.
形成した高分子材料からなる支持体によって支持されて
いることを特徴とする、請求項１乃至３のいずれかに記
載のスラスト軸受装置。4. The thrust bearing device according to claim 1, wherein the stationary plate is supported by a support made of a polymer material formed by filling a glass fiber or the like. .
が弱くなる円筒状バネを複数組み合わせた多重円筒バネ
構造体によって支持されていることを特徴とする、請求
項１乃至３のいずれかに記載のスラスト軸受装置。5. The stationary plate is supported by a multi-cylindrical spring structure in which a plurality of cylindrical springs whose strength decreases as the diameter increases are combined. A thrust bearing device according to any one of the claims.
が弱くなるようグラスファイバー等を充填して形成した
高分子材料からなる円筒状の積層体を複数組み合わせた
多重円筒の積層体により支持されていることを特徴とす
る、請求項１乃至３のいずれかに記載のスラスト軸受装
置。6. A multi-cylinder laminate formed by combining a plurality of cylindrical laminates made of a polymer material formed by filling a glass fiber or the like so that the spring strength decreases as the diameter increases. The thrust bearing device according to any one of claims 1 to 3, wherein the thrust bearing device is supported.
ていることを特徴とする、請求項１乃至３のいずれかに
記載のスラスト軸受装置。7. The thrust bearing device according to claim 1, wherein the stationary plate is supported by a spherical shell-shaped support structure.
転方向遅れ側および進み側に所定幅のスリット溝が形成
されていることを特徴とする、請求項１乃至３のいずれ
かに記載のスラスト軸受装置。8. The stationary plate according to claim 1, wherein a slit groove having a predetermined width is formed on at least a side of the stationary plate base portion on the side of the stationary plate base that is delayed and advanced in the rotational direction. Thrust bearing device.
り面材の径より大きくしてあることを特徴とする、請求
項１乃至８のいずれかに記載のスラスト軸受装置。9. The thrust bearing device according to claim 1, wherein the diameter of the stationary plate base of the stationary plate is larger than the diameter of the bearing sliding surface material.
ら強制的に潤滑油を供給する油留まりが設けられている
ことを特徴とする、請求項１乃至９のいずれかに記載の
スラスト軸受装置。10. The thrust bearing device according to claim 1, wherein an oil reservoir for forcibly supplying lubricating oil from the outside is provided on the bearing slide surface of the stationary plate. .
複数列配列されていることを特徴とする、請求項１乃至
１０のいずれかに記載のスラスト軸受装置。11. The thrust bearing device according to claim 1, wherein a plurality of stationary plates are arranged on a concentric circle centered on a rotation axis.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10214153A JP2000046042A (en) | 1998-07-29 | 1998-07-29 | Thrust bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10214153A JP2000046042A (en) | 1998-07-29 | 1998-07-29 | Thrust bearing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2000046042A true JP2000046042A (en) | 2000-02-15 |
Family
ID=16651109
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10214153A Withdrawn JP2000046042A (en) | 1998-07-29 | 1998-07-29 | Thrust bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2000046042A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009185843A (en) * | 2008-02-04 | 2009-08-20 | Mitsubishi Heavy Ind Ltd | Bearing device and rotary machine |
| JP2021055677A (en) * | 2019-09-26 | 2021-04-08 | 株式会社東芝 | Thrust bearing device |
-
1998
- 1998-07-29 JP JP10214153A patent/JP2000046042A/en not_active Withdrawn
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009185843A (en) * | 2008-02-04 | 2009-08-20 | Mitsubishi Heavy Ind Ltd | Bearing device and rotary machine |
| US8292507B2 (en) | 2008-02-04 | 2012-10-23 | Mitsubishi Heavy Industries, Ltd. | Bearing device and rotary machine |
| JP2021055677A (en) * | 2019-09-26 | 2021-04-08 | 株式会社東芝 | Thrust bearing device |
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