JPS58156718A - Pad type journal bearing - Google Patents
Pad type journal bearingInfo
- Publication number
- JPS58156718A JPS58156718A JP57038172A JP3817282A JPS58156718A JP S58156718 A JPS58156718 A JP S58156718A JP 57038172 A JP57038172 A JP 57038172A JP 3817282 A JP3817282 A JP 3817282A JP S58156718 A JPS58156718 A JP S58156718A
- Authority
- JP
- Japan
- Prior art keywords
- pad
- rotating shaft
- pads
- directly below
- hydraulic
- 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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
- F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
-
- 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
- F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
- F16C41/02—Arrangements for equalising the load on a plurality of bearings or their elements
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
（発明の技術分野〕
本発明はタービン発電機のような高速かつ高荷重の回転
軸を支承する改良したパッド形ジャーナル軸受に関する
。DETAILED DESCRIPTION OF THE INVENTION TECHNICAL FIELD OF THE INVENTION The present invention relates to an improved pad-type journal bearing for supporting a high-speed, high-load rotating shaft such as a turbine generator.
パッド形ジャーナル軸受は、回転子の振動抑制効果が大
きく、オイルホイップ等軸受の不安定現象が発生しにく
い丸め、タービン発電機のようＣ＝高速回転機の軸受と
して広く使用されている。すなわち、第１図は従来使用
されているパッド形ジャーナル軸受゛で、回転軸１はそ
の外周６：配設され九複数個（図において６個）のパッ
ド２−１．２−２．−２−３．２−４．２−５および２
−６により回転自在に支承されている。眩パッド２−１
ないし２−６はその内周面が軸受中心Ｏ１より半径ｒ、
の円周上に位置するように配設され、それ（れ軸受外輪
３１：設けられえピボット４−１．４−２．４−３．４
−４．４−５ Ｔｈよび４−６ニょ）点ないし球面接触
によって揺動可能なように支承されている。Pad-type journal bearings are widely used as bearings for high-speed rotating machines, such as round and turbine generators, because they have a large rotor vibration suppression effect and are less likely to cause instability phenomena such as oil whip. That is, FIG. 1 shows a conventionally used pad-type journal bearing, in which a rotating shaft 1 has nine pads 2-1, 2-2. -2-3.2-4.2-5 and 2
It is rotatably supported by -6. Dazzling pad 2-1
to 2-6, the inner peripheral surface thereof has a radius r from the bearing center O1,
The bearing outer ring 31 is provided with a pivot 4-1.4-2.4-3.4.
-4.4-5 Th and 4-6 Nyo) Supported so as to be swingable by point or spherical contact.
このようなパッド形ジャーナル軸受で支持された回転軸
１が実＄に回転速度ωで回転する場合、回転軸１は回転
軸１とパッド２−１ないし２−６との間隙内に形成され
る油膜圧力と回転軸の自重とが平衡する位置まで下降し
、その回転軸ｌの中心はへよ）ｅだけ偏心し九〇ａｔで
移動し、回転軸ｌは符号ｌ′で示す状態となる。この時
回転輪ｌと各パッド２−１ないし２−６との間に形成さ
れる間隙ｈ１（ｈｓ ＋ ｌｉｔ −ｔｌｍ）は次式で
表わされる。When the rotating shaft 1 supported by such a pad-type journal bearing rotates at a rotational speed ω, the rotating shaft 1 is formed in the gap between the rotating shaft 1 and the pads 2-1 to 2-6. It descends to a position where the oil film pressure and the weight of the rotating shaft are in equilibrium, and the center of the rotating shaft l is eccentric by an amount of e) and moves at 90 at, and the rotating shaft l is in the state indicated by the symbol l'. At this time, the gap h1 (hs+lit-tlm) formed between the rotating wheel l and each pad 2-1 to 2-6 is expressed by the following equation.
ｈｉ＝ｚｃ−ｅ ｃｏｓｐ＝ｃ（１−εｃｏｓｗｔ）
曲−・（１）と＼で６はｅ／ｃを表わし、偏心率を意味
する。ψは偏心方向０１Ｏ−を基準とし対象とするパッ
ドの関Ｆ ｓｔでの円周方向角度を示す。なお
Ｊｉｃｏｓψ１は各パッドの相当偏心率を意味する・
このよりなノリド形ジャーナル軸受において、発生する
油膜圧力分布は、第２図に示すように真下位置のパッド
２−２で最大となり、他のパッドと比較して分担負荷も
大きい。これは回転時真下位置のパッド２−２の相当偏
心率が他のパッドより大きいためである。このよう−二
従来のパッド形ジャーナル軸受１：おいては、回転軸の
真下位置のパッド２−２の分担負荷が大きく、負荷分担
の不均一、真下メタル温度が他のパッドに比較して高く
なるなどの欠点があり九。hi=zc-e cosp=c(1-εcoswt)
In the song (1) and \, 6 represents e/c, which means eccentricity. ψ indicates an angle in the circumferential direction at the target pad Fst with reference to the eccentric direction 01O-. Note that Jicos ψ1 means the equivalent eccentricity of each pad. In this rigid Norid type journal bearing, the oil film pressure distribution that occurs is maximum at pad 2-2 located directly below, as shown in Figure 2, and other pads The shared load is also large compared to the above. This is because the equivalent eccentricity of the pad 2-2 located directly below during rotation is greater than that of the other pads. In this type of conventional pad type journal bearing 1, the load shared by the pad 2-2 located directly below the rotating shaft is large, the load is unevenly distributed, and the temperature of the metal directly below is higher than that of other pads. There are nine drawbacks such as:
［発明の目的〕
本発明の目的は、各パッドの負荷分担を均一化し、負荷
能力および安定性（＝優れたパッド形ジャーナル軸受を
提供するにある。[Object of the Invention] An object of the present invention is to provide a pad-type journal bearing that equalizes the load sharing among each pad and has excellent load capacity and stability.
本発明は回転軸を支承する豪数個のパッドの内、回転軸
の真下位置およびこの前後のピボット支持部に油圧装置
を設けて連通し、各パッドの平均油膜圧力を均一化する
ように構成し九パッド形ジャーナル軸受に関するもので
ある。The present invention is configured such that among the several pads that support the rotating shaft, a hydraulic device is installed and communicated with the position directly below the rotating shaft and the pivot support portions before and after this, so as to equalize the average oil film pressure of each pad. This invention relates to a nine-pad type journal bearing.
以下本発明を第３図に示す実施例について説明する。第
３図（＝おいて第１図と同一符号は同一部分を示すもの
であるから、その説明を省略する。The present invention will be described below with reference to an embodiment shown in FIG. In FIG. 3 (=), the same reference numerals as in FIG. 1 indicate the same parts, so the explanation thereof will be omitted.
本発明においては、各パッド２−１ないし２−６の内、
回転軸１の真下のパッド２−２とその前後のパッド２−
１および２−３のピボット支持部１；油圧装置５−１゜
５−２および５−３を設ける。そして回転軸ｌの真下前
後の油圧装置５−１および５−３は、連通管６によって
連通されている。またパッド２−３の油膜面圧中心≦二
は、開口部７が設けられてお抄、パッド２−３の摺動面
に発生する油膜圧力を持つ九油は、開口部７よりフレキ
シブルパイプ８および油圧倍力（減力）装置９を介して
真下のピボット支持部の油圧装置５−２と連通している
。In the present invention, among each pad 2-1 to 2-6,
Pad 2-2 directly below rotation axis 1 and pad 2-2 before and after it
Pivot supports 1 and 2-3; hydraulic devices 5-1 and 5-2 and 5-3 are provided. The hydraulic devices 5-1 and 5-3 located directly below the rotation axis 1 are communicated with each other through a communication pipe 6. In addition, if the oil film surface pressure center of the pad 2-3 is ≦2, the opening 7 is provided, and if the oil film pressure generated on the sliding surface of the pad 2-3 is 9, the flexible pipe 8 is moved from the opening 7. It also communicates with the hydraulic device 5-2 of the pivot support section directly below via the hydraulic booster (force reduction) device 9.
このよう−二構成し九本発明のパッド形ジャーナル軸受
の作用を説明する。回転軸１が回転している時１：回転
軸ｌと各パッドの関ＩＩ区二発生する油膜圧力分布は、
従来のパッド形ジャーナル軸受Ｃ；おいて第２図に示す
ようロー真下の位置のパッド２−８が高く、その前後の
パッド２−１．２−３で低い。いｔ第３図のパッド２−
Ｉ Ｉ ２−２１２−３の符号に合せて各パッドの平均
圧力をＰ、、Ｐ、、Ｐ、とする。すなわち真下位置のパ
ッド２−２４：発生する平均油膜圧力Ｐ、。The operation of the pad type journal bearing of the present invention having two configurations as described above will be explained. When the rotating shaft 1 is rotating, the oil film pressure distribution generated between the rotating shaft 1 and each pad is as follows:
In a conventional pad type journal bearing C, as shown in FIG. 2, the pad 2-8 located directly below the row is high, and the pads 2-1, 2-3 in front and behind it are low. Pad 2 in Figure 3
Let the average pressure of each pad be P, , P, , P, according to the code of I I 2-212-3. That is, the pad 2-24 located directly below: the generated average oil film pressure P.
真下前後のパッド２−１．２−３１ニ一発生する平均油
膜圧力Ｐ、、Ｐ、とする。各パッドの平均圧力は、一般
的Ｃ二第３図に示す矢示Ｙ、を回転軸ｌの回転方向とし
てＰ、）Ｐ、≧Ｐ、（Ｐ、中ｐｔ）の関係がある。いま
圧力Ｐ、。Assume that the average oil film pressure generated between the pads 2-1, 2-31 directly below and behind is P, , P. The average pressure of each pad has a general relationship of P, )P, ≧P, (P, medium pt), with arrow Y shown in FIG. Now the pressure is P.
Ｐｌの大きさＣ；差があ抄、僅かＣ二圧力Ｐ、ｉ１大き
いとする。つｔａパッド２−３の相当偏心率がパッド２
−１に比べて大きくなっている場合である。Assume that the difference between the magnitude of Pl and the pressure P is slightly larger than that of C and i1. The equivalent eccentricity of pad 2-3 is pad 2.
This is a case where it is larger than -1.
この時パッド２−１とパッド２−３を支持するピポッド
支持部の油圧袋［５−１と５−３は、連通しているので
、パッド２−３は相当偏心率がはソ等しくなるまで外径
側へ押し下げられ、パッド２−１は内径側へ押し上げら
れ、平均油膜圧力Ｐ１＃Ｐｌが婢しくなるところでつり
あう。また真下のパッド２−２を支持するピボット支持
部の油圧装置５−２には、パッド面積を８．油圧装置の
シリンダボア面積を１としてｐ＝ｅ＋ ｐ、 ×Ｂ／＠
なる油圧が加わる。パッド２−３の油圧面圧中心の開口
部７と真下のピボット支持部油圧装置５−２を連通する
連通管１Ｇの中間に設けられ九倍力（減力）装置９は、
パッド２−３から油圧装置５−２へ流れる油の圧力をに
８／ｓ倍Ｉ油圧装置５−２からパッド２−３へ流れる油
の圧力をｓ／ｋｌ１倍する装置である。At this time, since the hydraulic bags [5-1 and 5-3 of the pivot support part that support pads 2-1 and 2-3 are in communication with each other, pads 2-3 will be closed until the equivalent eccentricity becomes equal to The pad 2-1 is pushed down to the outer diameter side, and the pad 2-1 is pushed up to the inner diameter side, and the average oil film pressure P1#Pl is balanced at the point where it becomes dirty. In addition, the hydraulic device 5-2 of the pivot support part that supports the pad 2-2 directly below has a pad area of 8. Assuming the cylinder bore area of the hydraulic system to be 1, p=e+p, ×B/@
A certain amount of hydraulic pressure is added. A nine force (force reduction) device 9 is provided in the middle of the communication pipe 1G that communicates the opening 7 at the center of the hydraulic surface pressure of the pad 2-3 with the pivot support hydraulic device 5-2 directly below.
This is a device that multiplies the pressure of oil flowing from the pad 2-3 to the hydraulic device 5-2 by 8/s/1 and the pressure of the oil flowing from the hydraulic device 5-2 to the pad 2-3 by 1 s/kl.
この丸め、真下の油圧装置５−２１．発生する油圧Ｐ−
Ｐ會８／魯は、倍力（減力）装置９によりＰｚ Ｐ。This round, the hydraulic system 5-21 directly below. Hydraulic pressure generated P-
P Kai 8/Lu is Pz P by the booster (reduction) device 9.
８／ｓ ｘ ｓ／に８ ｚ Ｐ、／にとなる。なおｋは
パッド２−３の平均面圧Ｐａ＆開口部７の圧力Ｐａ（７
）比に；Ｐ、／Ｐ６で倍力（減力）補正係数を示す。Ｐ
、）Ｐ、であるから真下のパッド２−２は、相轟偏心率
がパツドト３とａソ等しくなる壕で外径側へ押し下げら
れ、平均油膜圧力Ｐ、とＰｌが等しくなり九ところでつ
９あう。8/s x s/ becomes 8 z P, /. Note that k is the average surface pressure Pa of the pad 2-3 & pressure Pa of the opening 7 (7
) to the ratio ;P, /P6 indicates the boost (reduction) correction coefficient. P
, )P, so the pad 2-2 directly below is pushed down to the outer diameter side by the trench where the phase eccentricity becomes equal to pad 3 and a, and the average oil film pressure P and Pl become equal and at 9 match.
以上の作用によって本発明のパツ゛ド形ジャーナル軸受
ζ二おいては、各パッドの油膜圧力分布は９４図Ｃり示
すように均一化される。As a result of the above action, in the pad-type journal bearing ζ2 of the present invention, the oil film pressure distribution on each pad is made uniform as shown in Figure 94C.
θ
以上のように本発明においては、回転軸の真下前後のパ
ッドを支持するピボット支持部の油圧装置が連通され、
かつ真下前後のパッドζ二発生する油膜圧力を倍力（減
力）装置を介して真下のピボット支持部の油圧装置１：
連通させているため、各パッドは間隙方向（半径方向）
の移動が可能であゆ、各パッドの平均油膜圧力を均一化
することができる。このため従来形のパッド形ジャーナ
ル軸受Ｉ：比べて負荷能力の向上および真下メタル温度
の低下をもたらすことができ、回転軸真下パッドの油膜
切れなどを防止することができる。θ As described above, in the present invention, the hydraulic system of the pivot support part that supports the front and rear pads directly below the rotating shaft is communicated with each other,
The oil film pressure generated by the pads ζ2 directly below is transferred to the hydraulic system 1 of the pivot support directly below via a booster (force reduction) device:
Because they are connected, each pad is aligned in the gap direction (radial direction)
The average oil film pressure of each pad can be made uniform. Therefore, compared to the conventional pad type journal bearing I, it is possible to improve the load capacity and lower the temperature of the metal directly below, and it is possible to prevent the oil film from running out on the pad directly below the rotating shaft.
第１図は従来のパッド形ジャーナル軸受を示す断面図、
第２図はその発生油膜圧力分布図、第３図は本発明によ
るパッド形ジャーナル軸受の一実施例を示す断面図、第
４図はその発生油膜圧力分布図である。
ｌ・・・回転軸 ２−１〜２−６・・・パッド
３・・・軸受外輪 ４−１〜４−６・・・ピボッ
ト５−１〜５−３・・・油圧装置 ６１１０・・・連通
管７・・・パッド開口部 ８・・・フレキシブルパ
イプ９・・・倍力（減力）装置
第１図
一一円用方内角度
第 ３１１Ａ
−一円川方ｔｆｒＰ４濱Figure 1 is a sectional view showing a conventional pad type journal bearing.
FIG. 2 is a diagram showing the pressure distribution of the generated oil film, FIG. 3 is a sectional view showing an embodiment of the pad type journal bearing according to the present invention, and FIG. 4 is a diagram showing the distribution of the pressure of the generated oil film. l... Rotating shaft 2-1 to 2-6... Pad 3... Bearing outer ring 4-1 to 4-6... Pivot 5-1 to 5-3... Hydraulic device 6110... Communication pipe 7...Pad opening 8...Flexible pipe 9...Boosting (force reduction) device
Claims (2)
支承する複数個のパッドと、このパッドを支承するピボ
ットおよびとのピボットを支承する軸受外輪を具備し、
前記複数個のパッドの内前記回転軸の真下位置−二ある
パッドを支承するピボット支持部Ｃ；油圧装置を設け、
この油圧装置Ｃ；前前回回転軸真下位置前後のバッド摺
動面６二発生する油膜圧力を持つ九油を倍力（減力）装
置を介して供給することを特徴とするパッド形ジャーナ
ル軸受。(1) comprising a plurality of pads disposed in the circumferential direction of a rotating shaft and supporting the same, a pivot supporting the pads, and a bearing outer ring supporting the pivot;
A pivot support part C that supports one of the plurality of pads at a position directly below the rotation axis; a hydraulic device is provided;
This hydraulic system C is a pad type journal bearing characterized in that oil having an oil film pressure generated on the pad sliding surfaces 62 at the front and rear positions directly below the rotation axis is supplied via a booster (force reduction) device.
を支承する複数個のパッドと、このパッドを支承するピ
ボットおよびこのピボットを支承する軸受外輪を具備し
、前記豪数個のパッドの内前記回転軸の真下位置−一あ
るパッドを支承するピボット支持部礪；油圧ｉｉ装置を
設け、この油圧装置−：前記回転軸の真下位置前後のバ
ッド摺動面Ｃ二発生する油膜圧力を持った油を倍力（減
力）装置を介して供給し、さらに回転軸の真下位置前後
のピボット支持部に相互に油圧系を連通する油圧装置を
設けたことを特徴とする特許請求の範囲第１項記載のパ
ッド形ジャーナル軸受◎(2) A plurality of pads arranged in the circumferential direction of the rotating shaft to support the pads, a pivot to support the pads, and a bearing outer ring to support the pivot; A position directly below the rotating shaft - A pivot support part supporting a certain pad; A hydraulic system is provided, and this hydraulic system controls the pressure of the oil film generated on the sliding surface of the pad before and after the position directly below the rotating shaft. The claimed invention is characterized in that the oil is supplied via a booster (force reduction) device, and furthermore, hydraulic devices are provided at the pivot support portions before and after the position directly below the rotating shaft to communicate the hydraulic systems with each other. Pad type journal bearing described in item 1◎
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57038172A JPS58156718A (en) | 1982-03-12 | 1982-03-12 | Pad type journal bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57038172A JPS58156718A (en) | 1982-03-12 | 1982-03-12 | Pad type journal bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS58156718A true JPS58156718A (en) | 1983-09-17 |
Family
ID=12517966
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57038172A Pending JPS58156718A (en) | 1982-03-12 | 1982-03-12 | Pad type journal bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58156718A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11655851B2 (en) | 2019-03-22 | 2023-05-23 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Bearing device and rotating device |
-
1982
- 1982-03-12 JP JP57038172A patent/JPS58156718A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11655851B2 (en) | 2019-03-22 | 2023-05-23 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Bearing device and rotating device |
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