JPH0886268A - Water lubricated type water turbine main bearing - Google Patents
Water lubricated type water turbine main bearingInfo
- Publication number
- JPH0886268A JPH0886268A JP6246825A JP24682594A JPH0886268A JP H0886268 A JPH0886268 A JP H0886268A JP 6246825 A JP6246825 A JP 6246825A JP 24682594 A JP24682594 A JP 24682594A JP H0886268 A JPH0886268 A JP H0886268A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- water
- pad
- water turbine
- main 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.)
- Pending
Links
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
Landscapes
- Hydraulic Turbines (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は水潤滑式水車主軸受に関
し、水車及びポンプ水車主軸受の潤滑を水で行う場合の
主軸受構造に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a water-lubricated water turbine main bearing, and more particularly to a main bearing structure for lubricating a water turbine and a pump turbine main bearing with water.
【０００２】[0002]
【従来の技術】図３は従来のセグメンタル形の油潤滑式
水車主軸受の縦断面図、図４はそのＩ−Ｉ断面図であ
る。これらの図において、主軸１のジャーナル部２は分
割されたパッド（軸受メタル）３で支えられ、パッド３
は支持板４と板ばね５とで軸方向に支持され、半径方向
にはピボット受６及び先端に球面状のピボット７を有す
る調整ボルト８を介して、軸受胴９で支持されている。
パッド３の下部には油槽１０が設けられ、油槽１０内に
は油冷却器１１が取りつけられている。2. Description of the Related Art FIG. 3 is a vertical sectional view of a conventional segmental type oil-lubricated water turbine main bearing, and FIG. In these figures, the journal portion 2 of the main shaft 1 is supported by a divided pad (bearing metal) 3 and the pad 3
Is axially supported by a support plate 4 and a leaf spring 5, and is supported in a radial direction by a bearing shell 9 via a pivot receiver 6 and an adjusting bolt 8 having a spherical pivot 7 at the tip.
An oil tank 10 is provided below the pad 3, and an oil cooler 11 is installed in the oil tank 10.
【０００３】上記の構成において、球面状のピボット７
はピボット受６の平面と点接触し、主軸ジャーナル部２
との間に適正なくさび状の油膜を自動的に形成する。軸
受隙間の調整はピボット７と一体の調整ボルト８を回
し、ピボット７の位置を調節した後ナット１２でロック
される。In the above structure, the spherical pivot 7
Comes into point contact with the plane of the pivot receiver 6, and the spindle journal 2
A proper wedge-shaped oil film is automatically formed between and. To adjust the bearing clearance, the adjusting bolt 8 integrated with the pivot 7 is turned to adjust the position of the pivot 7 and then locked by the nut 12.
【０００４】[0004]
【発明が解決しようとする課題】近時、油圧式ガバナに
替えて電気式ガバナが採用されると共に、軸受の潤滑を
油に替えて水で行い、油を必要としない水車プラントの
実用化が逐次推進されている。Recently, electric governors have been adopted in place of hydraulic governors, and bearings are lubricated with water instead of oil, so that a water turbine plant that does not require oil can be put to practical use. It is being promoted one after another.
【０００５】しかしながら、水は油に比べて粘度が低い
ため、軸受の潤滑流体を水とすると、軸受面水膜の振動
に対するダンピング特性は著しく低くなる。従って、一
度振動が発生すると、振動は減衰せず、遂には水膜が切
れて金属接触を起こし、摩耗や焼け付きの危険が生じる
という問題があった。However, since the viscosity of water is lower than that of oil, if the lubricating fluid of the bearing is water, the damping characteristic against vibration of the water film on the bearing surface becomes significantly low. Therefore, once the vibration is generated, the vibration is not attenuated, and finally the water film is broken to cause metal contact, which poses a problem that there is a risk of abrasion or burning.
【０００６】本発明は上記従来技術の課題を解決するた
めになされたもので、潤滑流体として水を用いた場合に
も摩耗や焼け付きのない水車主軸受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 an object of the present invention is to provide a water turbine main bearing that does not wear or burn even when water is used as a lubricating fluid.
【０００７】[0007]
【課題を解決するための手段】上記の課題を解決するた
めに、本発明では、主軸と軸受胴との間に複数個に分割
されたパッドを有するセグメンタル形の水車主軸受にお
いて、面積がパッド背面面積の４０％以上、厚さが軸受
径の０．０２〜０．２倍の弾性体を前記パッドの背面に
配置したものとしている。In order to solve the above problems, according to the present invention, a segmental type water turbine main bearing having a plurality of pads between a main shaft and a bearing shell has an area of An elastic body having a surface area of 40% or more of the pad back surface and a thickness of 0.02 to 0.2 times the bearing diameter is arranged on the back surface of the pad.
【０００８】[0008]
【作用】弾性体は金属性パッドと同等の調心能力を持
ち、パッドは自由に傾いて主軸との間には適正なくさび
状の水膜が形成される。The elastic body has the same centering ability as that of the metallic pad, and the pad freely tilts to form a proper wedge-shaped water film between itself and the main shaft.
【０００９】[0009]
【実施例】図１は本発明の一実施例を示す断面図であ
る。図１において、主軸１３は８個のパッド１４を介し
て、軸受胴１５で支えられ、各パッド１４の背面には弾
性体１６が接着等により固定されている。弾性体１６に
は一般に圧縮強さ、吸水率、耐老化性、軟化温度に優れ
た特性を持つゴム、例えば硬質ゴム等を用いる。1 is a sectional view showing an embodiment of the present invention. In FIG. 1, the main shaft 13 is supported by a bearing shell 15 via eight pads 14, and an elastic body 16 is fixed to the back surface of each pad 14 by adhesion or the like. The elastic body 16 is generally made of rubber having excellent properties such as compressive strength, water absorption, aging resistance and softening temperature, such as hard rubber.
【００１０】本発明では、弾性体１６はその面積をパッ
ド背面面積の４０％以上、厚さｈを軸受径Ｄの０．０２
〜０．２倍としている。以下その根拠について説明す
る。In the present invention, the elastic member 16 has an area of 40% or more of the pad back surface area and a thickness h of 0.02 of the bearing diameter D.
~ 0.2 times. The basis will be described below.
【００１１】通常、弾性体である硬質ゴムのばね定数Ｋ
は、図２に示したように、ａを弾性体の幅（cm）、ｂを
弾性体の長さ（cm）、ｈを弾性体の厚さ（cm）とすると
き、Usually, the spring constant K of hard rubber, which is an elastic body,
As shown in FIG. 2, where a is the width (cm) of the elastic body, b is the length (cm) of the elastic body, and h is the thickness (cm) of the elastic body,
【数１】Ｋ＝Ｅａｂ／ｈ により表わすことができる。ここで、Ｅは弾性体の弾性
率（kgf/cm2）であり、特に、角柱のゴムの場合は、 Ｅ＝（３＋６．５８Ｓ2）Ｇ Ｇ：ゴムせん断弾性率 Ｓ＝ａｂ／｛（２ａ＋ｂ）ｈ｝ となる。なお、Ｅは一般的に、Ｅ≒１５００kgf/cm2の
レベルとなる。## EQU1 ## It can be expressed by K = Eab / h. Here, E is the elastic modulus (kgf / cm 2 ) of the elastic body, and particularly in the case of a prismatic rubber, E = (3 + 6.58S 2 ) G G: rubber shear elastic modulus S = ab / {(2a + b ) H}. Note that E is generally at a level of E≈1500 kgf / cm 2 .
【００１２】また、パッド１４の背面面積Ａは、Ｄを軸
受径、Ｌを軸受長さ、Ｚをパッド数（通常４〜１０枚程
度）とするとき、Ａ＝πＤＬ／Ｚと表わすことができ
る。The back surface area A of the pad 14 can be expressed as A = πDL / Z, where D is the bearing diameter, L is the bearing length, and Z is the number of pads (usually about 4 to 10). .
【００１３】従って、数１のばね定数Ｋは、Therefore, the spring constant K of Equation 1 is
【数２】Ｋ＝Ｅ｛（β1Ａ）／（β2Ｄ）｝ ＝Ｅ｛β1（πＤＬ／Ｚ）／（β2Ｄ）｝ ＝πＥ（β1／β2）（Ｌ／Ｚ） のように書き直すことができる。ここで、β1はパッド
背面面積に対する弾性体面積の比率であり、β2は軸受
径に対する弾性体厚さの比率である。## EQU2 ## K = E {(β 1 A) / (β 2 D)} = E {β 1 (πDL / Z) / (β 2 D)} = πE (β 1 / β 2 ) (L / Z ) Can be rewritten as Here, β 1 is the ratio of the elastic body area to the pad back surface area, and β 2 is the ratio of the elastic body thickness to the bearing diameter.
【００１４】ところで、水車の要求するばね定数Ｋは、By the way, the spring constant K required by the water turbine is
【数３】Ｋ＝α｛（ＰＤＬ）／Ｃ｝ で表わすことができる。ここで、Ｐは軸受面圧（kgf/cm
2）、Ｄは軸受径（cm）、Ｌは軸受長さ（cm）、Ｃは軸
受隙間（cm）、αは係数（１．５〜１０）であり、この
中で、一般に、Ｐは５kgf/cm2程度、ＣはＤ／１０００
が使われている。## EQU3 ## It can be expressed by K = α {(PDL) / C}. Where P is the bearing surface pressure (kgf / cm
2 ), D is the bearing diameter (cm), L is the bearing length (cm), C is the bearing clearance (cm), α is the coefficient (1.5 to 10), and in general, P is 5 kgf. / cm 2 , C is D / 1000
Is used.
【００１５】さて、この水車の要求するばね定数はパッ
ド１４のばね定数を表した数２と等しくなる必要があ
る。すなわち、 Ｋ＝πＥ｛（β1／β2）（Ｌ／Ｚ）｝＝α｛（ＰＤＬ）
／Ｃ｝ ＝α｛（ＰＤＬ）／（Ｄ／１０００）｝＝１０００α・
ＰＬ ゆえに、 β1／β2＝（１０００α／π）（Ｐ／Ｅ）Ｚ となる。Now, the spring constant required by the water turbine must be equal to the expression 2 representing the spring constant of the pad 14. That is, K = πE {(β 1 / β 2 ) (L / Z)} = α {(PDL)
/ C} = α {(PDL) / (D / 1000)} = 1000α
Because of PL, β 1 / β 2 = (1000α / π) (P / E) Z.
【００１６】ここで、先に示した数値例のＰ＝５kgf/cm
2、Ｚ＝８枚、Ｅ＝１５００kgf/cm2を代入すると、 β1／β2＝８．５α≒１０〜６０ となる。Here, P = 5 kgf / cm in the numerical example shown above.
2 , Z = 8 sheets and E = 1500 kgf / cm 2 are substituted, then β 1 / β 2 = 8.5α≈10-60.
【００１７】従って、ほぼこの関係が成り立つように、
β1は、β1＝１〜０．４、β2は、β2＝０．０２〜０．
２としている。すなわち、弾性体１６はその面積がパッ
ド１４の面積の４０〜１００％、厚さが軸受径の０．０
２〜０．２倍のものが用いられ、これによって、弾性体
１６の弾性変形によるパッド１４の変位を可能とし、水
潤滑式水車主軸受に必要な性能、つまり、軸受面水膜の
振動に対するダンピング特性が確保される。Therefore, so that this relationship is almost satisfied,
β 1 is β 1 = 1 to 0.4, β 2 is β 2 = 0.02 to 0.
2 That is, the area of the elastic body 16 is 40 to 100% of the area of the pad 14, and the thickness is 0.0 of the bearing diameter.
2 to 0.2 times that is used, which enables the displacement of the pad 14 due to elastic deformation of the elastic body 16 and the performance required for the water-lubricated water turbine main bearing, that is, the vibration of the bearing surface water film. Damping characteristics are secured.
【００１８】[0018]
【発明の効果】以上述べたように、本発明によれば、セ
グメンタル形水車主軸受の潤滑を水で行うことが可能と
なり、油を必要としない水車プラントの実用化を計るこ
とができる。また、水車の使用流体である河川水を潤滑
水に使用すれば、油潤滑のときに必要であった油冷却装
置等を省略することができ、しかも、河川の油汚染の問
題を解消することができる。As described above, according to the present invention, it is possible to lubricate the main bearing of the segmental type water turbine with water, and it is possible to put into practical use a water turbine plant that does not require oil. Also, by using river water, which is the fluid used in the water turbine, as lubricating water, it is possible to omit the oil cooling device, etc., which was necessary for oil lubrication, and solve the problem of oil pollution in the river. You can
【図１】本発明の一実施例に係る水潤滑式水車主軸受の
断面図である。FIG. 1 is a sectional view of a water-lubricated water turbine main bearing according to an embodiment of the present invention.
【図２】パッド及び弾性体を示す斜視図である。FIG. 2 is a perspective view showing a pad and an elastic body.
【図３】従来の油潤滑式水車主軸受の縦断面図である。FIG. 3 is a vertical sectional view of a conventional oil-lubricated turbine main bearing.
【図４】図３のＩ−Ｉ断面図である。4 is a cross-sectional view taken along the line I-I of FIG.
１３ 主軸 １４ パッド １５ 軸受胴 １６ 弾性体 13 main shaft 14 pad 15 bearing shell 16 elastic body
フロントページの続き (72)発明者 小室 隆信 兵庫県高砂市荒井町新浜二丁目１番１号 三菱重工業株式会社高砂製作所内 (72)発明者 石橋 進 兵庫県高砂市荒井町新浜二丁目１番１号 三菱重工業株式会社高砂研究所内Front page continuation (72) Inventor Takanobu Takamuro 2-1-1, Niihama, Arai-cho, Takasago-shi, Hyogo Mitsubishi Heavy Industries, Ltd. Takasago Plant (72) Susumu Ishibashi 2-1-1, Niihama, Arai-cho, Takasago-shi, Hyogo Heavy industry Takasago Research Institute
Claims (1)
パッドを有するセグメンタル形の水車主軸受において、
面積がパッド背面面積の４０％以上、厚さが軸受径の
０．０２〜０．２倍の弾性体を前記パッドの背面に配置
したことを特徴とする水潤滑式水車主軸受。1. A segmental type turbine main bearing having a plurality of divided pads between a main shaft and a bearing shell,
A water-lubricated water turbine main bearing, characterized in that an elastic body having an area of 40% or more of the pad back surface area and a thickness of 0.02 to 0.2 times the bearing diameter is arranged on the back surface of the pad.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6246825A JPH0886268A (en) | 1994-09-16 | 1994-09-16 | Water lubricated type water turbine main bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6246825A JPH0886268A (en) | 1994-09-16 | 1994-09-16 | Water lubricated type water turbine main bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0886268A true JPH0886268A (en) | 1996-04-02 |
Family
ID=17154259
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6246825A Pending JPH0886268A (en) | 1994-09-16 | 1994-09-16 | Water lubricated type water turbine main bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0886268A (en) |
-
1994
- 1994-09-16 JP JP6246825A patent/JPH0886268A/en active Pending
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