JPS62237111A - Journal bearing - Google Patents
Journal bearingInfo
- Publication number
- JPS62237111A JPS62237111A JP7810886A JP7810886A JPS62237111A JP S62237111 A JPS62237111 A JP S62237111A JP 7810886 A JP7810886 A JP 7810886A JP 7810886 A JP7810886 A JP 7810886A JP S62237111 A JPS62237111 A JP S62237111A
- Authority
- JP
- Japan
- Prior art keywords
- pad
- rotor
- oil film
- pads
- film pressure
- 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
- 239000002184 metal Substances 0.000 claims abstract 2
- 239000003921 oil Substances 0.000 abstract description 29
- 239000010687 lubricating oil Substances 0.000 abstract description 5
- 238000007790 scraping Methods 0.000 abstract description 3
- 230000000694 effects Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000013016 damping Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
Landscapes
- Sliding-Contact Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、ガスタービン、蒸気タービン、圧縮機1発電
機等の高速回転機器に主に利用される。DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention is mainly used in high-speed rotating equipment such as gas turbines, steam turbines, and compressor/generators.
パッドの内径面は、大同メタル工業、K、に型録に示さ
れるように、一つの円弧で出来ており、上半側に位置す
るパッドに発生する油膜圧力は下半側に位置するパッド
に発生する油膜圧力より極端に小さく、ロータの自励微
小振動が発生した場合、これを抑える効果が小さかった
。The inner diameter surface of the pad is made of a single arc, as shown in the mold list by Daido Metal Kogyo K., and the oil film pressure generated on the pad located on the upper half side is transferred to the pad located on the lower half side. When the self-excited micro-vibration of the rotor occurs, which is extremely lower than the oil film pressure that occurs, the effect of suppressing this is small.
テイルテイングパッド型ジャーナル軸受は、高速域で安
定性と制振側に優れており、特に、オイルウイツプの防
止に有効である事は周知であり。It is well known that tailing pad type journal bearings are excellent in stability and vibration damping at high speeds, and are particularly effective in preventing oil whip.
高速低荷重の条件下で広く利用されている。しかし、低
荷重ロータなどに見られるジャーナルの平衡位置の不安
定性によって発生する自励微小振動がパッドの安定性に
及ぼす影響は少なくない。特に、テイルテイングパッド
型ジャーナル軸受の場合、下半側に位置するパッドに発
生する油膜圧力に比べ、上半側に位置するパッドに発生
する油膜圧力は極端に小さく、ジャーナルの微小振動に
よる影響により、上半側に位置するパッドは傾斜角が安
定せず微小振動を繰返えし、パッドの支点を中心とする
パッドのシーソー運動が引き起こされ。Widely used under high speed and low load conditions. However, the self-excited micro-vibrations generated by the instability of the equilibrium position of the journal, which is found in low-load rotors, have a considerable effect on the stability of the pad. In particular, in the case of tailing pad type journal bearings, the oil film pressure generated on the pads located on the upper half side is extremely small compared to the oil film pressure generated on the pads located on the lower half side, and this is due to the influence of minute vibrations of the journal. The pad located in the upper half has an unstable inclination angle and repeats minute vibrations, causing a see-saw movement of the pad around the pad's fulcrum.
ひいてはパッド端面がジャーナルと接触する程になり、
機械全体に多大な損傷を与え兼ねない事態に至る。Eventually, the pad end surface will come into contact with the journal,
This could lead to a situation that could cause significant damage to the entire machine.
本発明の目的は、低荷重ロータなどに見られるジャーナ
ルの平衡位置の不安定性による自励微小振動にパッドが
励起されないか、また万一パッドが励起されシーソー運
動を始めたとしても、ジャーナルと接触しないジャーナ
ル軸受を提供することにある。The purpose of the present invention is to prevent the pad from being excited by self-excited minute vibrations caused by the instability of the equilibrium position of the journal, which is seen in low-load rotors, and to prevent the pad from coming into contact with the journal even if the pad is excited and begins a see-saw movement. Our goal is to provide journal bearings that do not.
本発明によるテイルテイングパッド型ジャーナル軸受の
パッド部分のみを第1図に示す、第2図にはパッドの組
立状態を、第3図に本発明の詳細部分を示す。Only the pad portion of the tailing pad type journal bearing according to the present invention is shown in FIG. 1, FIG. 2 shows the assembled state of the pad, and FIG. 3 shows the detailed portion of the present invention.
第1図において、パッド2a〜2eは第2図に示すよう
な構造に組立られテイルテイングパッド型ジャーナル軸
受として軸受ハウジングに組み込まれる。すなわち、第
2図でパッド2bの軸方向両端面で支持ピン5によりパ
ツドリテナ3の中に保持される。更に、ピボット4によ
りその先端部6でパッド2bはピボット支持されており
、ピボットピン先端部6を支持とし、半径方向にシーソ
ー運動が出来る構造となっている。第2図において、左
側から見てパッド2a〜2eの部分を取り、出した図が
第1図である。すなわち、パッド2a〜2eはロータ
1の回りにセグメント状に分割されて配置されており、
パッドリテナ3を通過した油膜油7はパッド2a〜2e
の隙間8を通り、図示のように、パッド2a〜2eとロ
ータ1との隙間に入って行き、くさび状の油膜を形成し
、ロータ1を保持している。この時、ロータ1の回転方
向は反時計方向となっている。これらパッド28〜2e
のうち上半側に位置するパッド2a〜2Cの円滑油7の
入口側端面ぶ内径側を削り取る。In FIG. 1, pads 2a to 2e are assembled into a structure as shown in FIG. 2 and incorporated into a bearing housing as a tailing pad type journal bearing. That is, in FIG. 2, the pad 2b is held in the pad retainer 3 by the support pins 5 at both axial end faces thereof. Furthermore, the pad 2b is pivotally supported by the pivot 4 at its tip 6, and is structured to be able to see-saw in the radial direction by supporting the pivot pin tip 6. FIG. 1 is a view of the pads 2a to 2e taken out when viewed from the left in FIG. 2. That is, the pads 2a to 2e are arranged around the rotor 1 in segments,
The oil film 7 that has passed through the pad retainer 3 is transferred to the pads 2a to 2e.
As shown in the figure, the oil passes through the gap 8 and enters the gap between the pads 2a to 2e and the rotor 1, forming a wedge-shaped oil film and holding the rotor 1. At this time, the rotation direction of the rotor 1 is counterclockwise. These pads 28-2e
The inner diameter side of the end face on the inlet side of the lubricating oil 7 of the pads 2a to 2C located on the upper half side is scraped off.
ff13図に示す一点鎖線で囲んだテーパ状の斜線部9
が削り取り部分の詳細図である。Tapered diagonal area 9 surrounded by a dashed-dotted line shown in Figure ff13
is a detailed view of the scraped part.
第3図において、円滑油7はパッド2bの右側端面から
流入し、ロータ1の回転に引かれパッド2bの内面とロ
ータ1の間隙に入って行き、パッド2bとロータ1の間
隙を流れる時にこの間隙内にパッド2bの支点6を頂点
とし、パッド2bの端面部を底辺とするクサビ形状の油
膜を形成する。In FIG. 3, lubricating oil 7 flows in from the right end surface of pad 2b, is drawn by the rotation of rotor 1, and enters the gap between the inner surface of pad 2b and rotor 1, and as it flows through the gap between pad 2b and rotor 1, this A wedge-shaped oil film is formed in the gap, with the fulcrum 6 of the pad 2b as the apex and the end face of the pad 2b as the base.
油膜の圧力は支点6の近傍で最大となりパッド2bの端
面部で最小となるように発生する。この油膜圧力の状況
を第4図に示す、第4図は支点6で支持されたパッド2
a〜2bの内面に発生する油膜圧力を一点lri線Pで
示している。下半側パッド2a〜2eに発生する油膜圧
力Pは、上半側パッド2a〜2cに発生する油膜圧力P
よりはるかに大きい値となっている。この現象は各種文
献に紹介されている通りである。下半側パッドの油膜圧
力に比し、小さくなっている上半側パッドの油膜圧力を
更に監察すると、ロータ回転方向に対し、入口側部分の
油膜圧力は出口端の油膜圧力よりも小さい値となってい
る事が特徴的である。この油膜圧力の小さい部分にあた
るパッドの内面をパッド全幅にわたり削り取る事により
、第4図に破線で示す油膜圧力分布P′のように、油膜
圧力は高くなり、ロータの微小振動に対してパッドは励
起されず安定性が向上する。更に、第5図に示すように
、油膜圧力分布が、従来のパッドの場合、曲線Pで示す
よう支点6の左側に頂点を持つ曲線となっており、油膜
圧力による支点6の回りのモーメントM□2M2が零と
ならず、支点6を中心とするシーソー運動の励起に非常
に敏感で、ロータの微小振動により、直ちに1反応する
ため、不安定な状態にある。しかし1本発明による圧力
分布P′を見ると、支点6の回りの油膜圧力によるモー
メントM1.M、がほぼ零となり、非常に安定な状態と
なっており、パッドのシーソー運動を抑える事ができる
。The pressure of the oil film is generated to be maximum near the fulcrum 6 and minimum at the end surface of the pad 2b. The situation of this oil film pressure is shown in Fig. 4. Fig. 4 shows the pad 2 supported by the fulcrum 6.
The oil film pressure generated on the inner surfaces of a to 2b is shown by a single point lri line P. The oil film pressure P generated on the lower half pads 2a to 2e is equal to the oil film pressure P generated on the upper half pads 2a to 2c.
It is a much larger value. This phenomenon has been introduced in various literature. Further monitoring of the oil film pressure on the upper half pad, which is smaller than the oil film pressure on the lower half pad, reveals that the oil film pressure on the inlet side is smaller than the oil film pressure on the outlet end in the direction of rotor rotation. It is characteristic that By scraping the inner surface of the pad, which corresponds to the area where the oil film pressure is low, over the entire width of the pad, the oil film pressure increases as shown by the oil film pressure distribution P' shown by the broken line in Figure 4, and the pad is excited by the minute vibrations of the rotor. stability is improved. Furthermore, as shown in FIG. 5, in the case of the conventional pad, the oil film pressure distribution is a curve with an apex on the left side of the fulcrum 6 as shown by curve P, and the moment M around the fulcrum 6 due to the oil film pressure is □2M2 does not become zero, it is very sensitive to the excitation of the see-saw motion centered on the fulcrum 6, and it is in an unstable state because it immediately reacts by 1 due to minute vibrations of the rotor. However, when looking at the pressure distribution P' according to the present invention, the moment M1. due to the oil film pressure around the fulcrum 6. M is almost zero, which is a very stable state, and the see-saw movement of the pad can be suppressed.
一方、機械の運転において起動から停止までの間、常に
、パッドの支点回りのモーメントが零となる平衡状態を
保持し続ける事は困難である。パッドの支点回りのモー
メントが零とならず、パッドのシーソー運動が始まった
場合、従来のパッド形状ではパッド端面内径部がジャー
ナルと接触を起こしジャーナル、および、パッド損傷に
至るところであるが、第3図に示すように、削り取り部
9のようにテーパ状に削り取っておく事により。On the other hand, during the operation of a machine, it is difficult to maintain an equilibrium state in which the moment around the fulcrum of the pad is always zero from start to stop. If the moment around the fulcrum of the pad does not become zero and the pad begins to see-saw, with the conventional pad shape, the inner diameter of the end surface of the pad will come into contact with the journal, leading to damage to the journal and pad. As shown in the figure, by scraping off in a tapered shape like the scraped part 9.
ある程度のパッドのシーソー運動に対してパッドとジャ
ーナルの接触を防ぐ事ができる。Contact between the pad and the journal can be prevented against a certain degree of see-saw movement of the pad.
本発明によれば、ロータの微小自励振動によるパッドの
振動を抑える事により、振動大による機械全体の停止、
あるいは、ロータ、軸受など部品の械損傷を防止できる
。According to the present invention, by suppressing the vibration of the pad due to minute self-excited vibrations of the rotor, it is possible to prevent the entire machine from stopping due to large vibrations.
Alternatively, mechanical damage to parts such as rotors and bearings can be prevented.
もし、パッドに振動が励起されシーソー運動がある程度
大きくなった場合にも、パッドとロータが接触する事な
く、パッドおよびロータの損傷を防止できる。Even if vibrations are excited in the pad and the see-saw movement becomes large to some extent, the pad and rotor will not come into contact with each other, and damage to the pad and rotor can be prevented.
第1図は本発明の一実施例のテイルテイングパッド型ジ
ャーナル軸受のパッド部分がロータの回りに配置されて
いるところを軸方向に見た図、第2図は第1図の■−■
矢視断面図、第3図は第1図の■部の断面図、第4図は
従来の軸受と本発明による軸受に発生する油膜圧力分布
図、第5図は第4図に示す油膜圧力分布のパッド1ケに
ついての詳細図である。
第1 回
菖2固
薯30
裏lf口Fig. 1 is an axial view of the pad portion of a tailing pad type journal bearing according to an embodiment of the present invention arranged around the rotor, and Fig. 2 is an axial view of Fig. 1.
3 is a sectional view of part ■ in FIG. 1, FIG. 4 is an oil film pressure distribution diagram generated in the conventional bearing and the bearing according to the present invention, and FIG. 5 is the oil film pressure shown in FIG. 4. It is a detailed diagram of one pad of distribution. 1st iris 2 hard 薯 30 back LF entrance
Claims (1)
成るジャーナル軸受において、上半側に位置するパッド
のメタル部分を前記パッドの端面から適当な長さだけ前
記パッドの全幅にわたつて削り取つたことを特徴とする
ジャーナル軸受。 2、特許請求の範囲第1項において、前記削り取り部分
の形状がテーパ状である事を特徴とするジャーナル軸受
。[Claims] 1. In a journal bearing consisting of a pad divided into several segments on the inner circumference, the metal part of the pad located on the upper half side is extended from the end surface of the pad by an appropriate length. A journal bearing characterized by having its entire width cut out. 2. The journal bearing according to claim 1, wherein the shaved portion has a tapered shape.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP7810886A JPS62237111A (en) | 1986-04-07 | 1986-04-07 | Journal bearing |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP7810886A JPS62237111A (en) | 1986-04-07 | 1986-04-07 | Journal bearing |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS62237111A true JPS62237111A (en) | 1987-10-17 |
Family
ID=13652690
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP7810886A Pending JPS62237111A (en) | 1986-04-07 | 1986-04-07 | Journal bearing |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS62237111A (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0368558A2 (en) * | 1988-11-07 | 1990-05-16 | Westinghouse Electric Corporation | Hydrodynamic pivoted pad bearing assembly for a reactor coolant pump |
JP2011256773A (en) * | 2010-06-09 | 2011-12-22 | Hitachi Ltd | Tilting pad journal bearing device, and steam turbine using the same |
CN103026086A (en) * | 2010-07-27 | 2013-04-03 | 大丰工业株式会社 | Sliding member and method for producing same |
JP2017072173A (en) * | 2015-10-06 | 2017-04-13 | 株式会社東芝 | Tilting-pad journal bearing and turbo machine |
KR101984545B1 (en) * | 2019-01-02 | 2019-09-03 | 주식회사 우진지엠씨 | Spindle |
-
1986
- 1986-04-07 JP JP7810886A patent/JPS62237111A/en active Pending
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0368558A2 (en) * | 1988-11-07 | 1990-05-16 | Westinghouse Electric Corporation | Hydrodynamic pivoted pad bearing assembly for a reactor coolant pump |
JP2011256773A (en) * | 2010-06-09 | 2011-12-22 | Hitachi Ltd | Tilting pad journal bearing device, and steam turbine using the same |
CN103026086A (en) * | 2010-07-27 | 2013-04-03 | 大丰工业株式会社 | Sliding member and method for producing same |
JP2017072173A (en) * | 2015-10-06 | 2017-04-13 | 株式会社東芝 | Tilting-pad journal bearing and turbo machine |
KR101984545B1 (en) * | 2019-01-02 | 2019-09-03 | 주식회사 우진지엠씨 | Spindle |
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