JPS61236916A - Sliding pad bearing - Google Patents
Sliding pad bearingInfo
- Publication number
- JPS61236916A JPS61236916A JP7529585A JP7529585A JPS61236916A JP S61236916 A JPS61236916 A JP S61236916A JP 7529585 A JP7529585 A JP 7529585A JP 7529585 A JP7529585 A JP 7529585A JP S61236916 A JPS61236916 A JP S61236916A
- Authority
- JP
- Japan
- Prior art keywords
- pad
- bearing
- sliding
- shaft
- sliding pad
- 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
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、軸を回転自在に支持する軸受パッドがハウジ
ング内で摺動し得るようにしたスライディングパッド軸
受に関する。DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to a sliding pad bearing in which a bearing pad rotatably supporting a shaft can slide within a housing.
〈従来の技術〉
圧縮機やタービン等の高速回転機械のロータを支承する
軸受としてテイルテイングパツド軸受が一般に用いられ
ている。<Prior Art> Tailing pad bearings are generally used as bearings that support the rotors of high-speed rotating machines such as compressors and turbines.
このテイルテイングパッド軸受の断面構造を表す第7図
及びその■−■矢視断面形状を表す第8図に示すように
、下部ハウジング03′の内周部に二個のテイルテイン
グパツド02が収納され、各テイルテイングパツド02
は支持座Xを支点として傾動自在に構成されている。又
、上部ハウジング03には給油孔04が穿設されている
。As shown in FIG. 7, which shows the cross-sectional structure of this tailing pad bearing, and FIG. 8, which shows its cross-sectional shape as seen from the Stored and each tailing pad 02
is configured to be tiltable about the support seat X as a fulcrum. Further, an oil supply hole 04 is bored in the upper housing 03.
+11101の回転中に給油孔04?介して供給され゛
る油は軸01とテイルテイングパツド02との間に油膜
Yt−形取し、核油8!!Y内には楔作用によって軸0
1を支持するに必要な油圧が発生する。Oil supply hole 04 during rotation of +11101? The oil supplied through the shaft 01 forms an oil film Yt- between the shaft 01 and the tailing pad 02, and the kernel oil 8! ! Axis 0 in Y due to wedge action
Hydraulic pressure necessary to support 1 is generated.
かかるテ゛イルティングパッド軸受は、胃速軸受に見ら
れるオイルホワールや一オイルホイップ等の不安定現象
を生ずることがなく、安定した作動特性を示す利点があ
る。即ち、各テイルテイングパツド02はその支持座X
を中心に傾動自在であるため、モーメントを負担するこ
とができずに支持座Xの左右の油膜Y中の圧力分布の合
力の該支持座Xまわシのそ一メントが釣合うように傾く
。従って、各テイルテイングパツド02には軸01の中
心と支持座Xとを結ぶ方向の合力のみが作用し、両テイ
ルテイングパツド02からの支持反力は常に軸01の中
心に向くのである。この結果、軸01に加わる動的荷重
に対して該軸01の偏心量が変化しても、振れ回るよう
な方向の力が発生せず、当該テイルテイングパッド軸受
は極めて安定した特性を示す。Such a tilting pad bearing has the advantage of exhibiting stable operating characteristics without producing unstable phenomena such as oil whirl or oil whip that are seen in gastrointestinal bearings. That is, each tailing pad 02 has its support seat
Since it is freely tiltable about the support seat X, it cannot bear a moment and tilts so that the resultant force of the pressure distribution in the oil films Y on the left and right sides of the support seat X balances the rotation of the support seat X. Therefore, only the resultant force in the direction connecting the center of the shaft 01 and the support seat X acts on each tailing pad 02, and the supporting reaction force from both tailing pads 02 is always directed toward the center of the shaft 01. . As a result, even if the eccentricity of the shaft 01 changes with respect to the dynamic load applied to the shaft 01, no force in a direction that causes it to swing around is generated, and the tailing pad bearing exhibits extremely stable characteristics.
〈発明が解決しようとする問題点〉
テイルテイングパッド軸受は動特性が他の軸受よシ優れ
ている反面、そのテイルテイングパツド02の支持座X
の円周方向の幅b(第7図参照)が小さく、この幅b″
ft:大きくすると自由に傾動できずにモーメント負荷
を受け、本来の特性を発揮することができない。<Problem to be solved by the invention> Although the tailing pad bearing has better dynamic characteristics than other bearings, the support seat X of the tailing pad 02
has a small circumferential width b (see Fig. 7), and this width b''
ft: If it is too large, it will not be able to tilt freely and will be subject to a moment load, making it impossible to exhibit its original characteristics.
テイルテイングパツド02の支持座Xの@bが小さいと
、支持座Xt−受ける下部ハウジング03’の部分の面
圧が高くなシ、特に動特性を改善するために支持座Xの
当シ面に丸味を付けて軸がシ接触させると、面圧が過大
となって接触部に弾性変形を生じてしまい、結果的には
接触面積が増大してテイルテイングバツド02の傾動が
制限され、テイルテイングバツド軸受本来の機能を十分
発揮させることができなくなる。又、テイルテイングパ
ツド02は中央部で支持されるため、特に大荷重を支え
る場合にはこれが曲げによって変形し。If @b of the support seat X of the tailing pad 02 is small, the surface pressure of the lower housing 03' that receives the support seat Xt will be high. If the shafts are rounded and brought into contact with each other, the surface pressure will be excessive and elastic deformation will occur in the contact area.As a result, the contact area will increase and the tilting movement of the tailing butt 02 will be restricted. The tailing butt bearing will not be able to fully demonstrate its original function. Furthermore, since the tailing pad 02 is supported at the center, it may deform due to bending, especially when supporting a large load.
′@01との摺動面の曲率が変化する等の問題も生ずる
。Problems such as changes in the curvature of the sliding surface with '@01 also occur.
本発明は、かかる従来のテイルテイングパッド軸受に関
する上述し7I?、程々の不具合に鑑み、人荷11Lt
−受けても安定した性能を維持することができるスライ
ディングパッド軸受を提供することを目的とする。The present invention relates to such conventional tailing pad bearings as described above. , due to some minor problems, the passenger load was reduced to 11Lt.
- It is an object of the present invention to provide a sliding pad bearing that can maintain stable performance even when subjected to shocks.
く問題点を解決するための手段〉
本発明は、軸受ハウジング内に@を回転自在に保持する
複数の軸受パッドを設けて成る軸受においで、上記軸受
ハウジングの内側と前記軸受パッドの背面との対向面を
この軸受パッドの略中心線に対して垂直な平面とし。Means for Solving the Problems> The present invention provides a bearing comprising a plurality of bearing pads for rotatably holding an @ in a bearing housing, in which a contact between the inside of the bearing housing and the back surface of the bearing pad is provided. The opposing surface is a plane perpendicular to the approximate center line of this bearing pad.
該平面に対して前記軸受パッドを摺動可能に設けたもの
である。The bearing pad is slidably provided on the plane.
く作 用〉
軸受パッドの背面はその全域に亘って略均−に軸受ハウ
ジングに接し、面圧が略均−に分布する結果、大荷重を
安定して支えることと表る。又、軸受パッドは軸の振れ
回シヲ起こす力を解消する方向に摺動し、極めて安定し
た作動特性となる。Function: The back surface of the bearing pad is in contact with the bearing housing approximately evenly over its entire area, and as a result of the surface pressure being distributed approximately evenly, it is possible to stably support a large load. Furthermore, the bearing pad slides in a direction that eliminates the force that causes the shaft to swing, resulting in extremely stable operating characteristics.
〈実施例〉
本発明によるスライディングパッド軸受の一実施例の断
面構造を表す第1図及びその■−n矢視断面構造を表す
第2図に示すように、下部ハウジング3′円には二個の
スライディングパッド2が収納されておシ、上部ハウジ
ング3に紘従来と同様に給油孔4が穿設されている。上
記各スライディングパッド2の背面は平面で構成され、
又、下部ハウジング3′の摺動面7も平面で構成される
が、との摺動面7はスライディングパッド2の中心軸O
Mに対して垂直を成している。各スライディングパッド
2は、その背面と摺動面7との間に介設された複数のこ
る5を介して摺動面7に沿って摺動し得るよう構成され
、これらの自重を支える強さのばね8によって下部ハウ
ジング3′内に位置決め保持されている。なお、ζる5
は保持器6によってその位置関係が正常に保たれている
。<Embodiment> As shown in FIG. 1 showing the cross-sectional structure of an embodiment of the sliding pad bearing according to the present invention, and FIG. 2 showing the cross-sectional structure in the direction of the A sliding pad 2 is housed therein, and an oil supply hole 4 is bored in the upper housing 3 as in the conventional model. The back surface of each of the sliding pads 2 is made of a flat surface,
The sliding surface 7 of the lower housing 3' is also formed of a flat surface, and the sliding surface 7 of the lower housing 3' is parallel to the central axis O of the sliding pad 2.
It is perpendicular to M. Each sliding pad 2 is configured to be able to slide along the sliding surface 7 via a plurality of levers 5 interposed between its back surface and the sliding surface 7, and has the strength to support its own weight. It is held in position within the lower housing 3' by a spring 8. In addition, ζru5
Their positional relationship is maintained normally by the retainer 6.
軸1の回転中に給油孔4全介して供給される油は、軸1
とスライディングパッド2との間に油膜21−形成し、
核油@2には楔作用によって軸1を支持するに必要な油
圧が発生する。The oil supplied through all the oil supply holes 4 while the shaft 1 is rotating is
an oil film 21 is formed between the sliding pad 2 and the sliding pad 2;
Hydraulic pressure necessary to support the shaft 1 is generated in the kernel oil@2 by a wedge action.
ところで、スライディングパッド2は下部ハウジング3
′の摺動面7に沿って摺動自在であるため、該摺動面、
7と平行な方向の荷重を受は持つことができず、従って
軸1に対しても同方向の反力が及ぶことがなく、油膜2
の圧力の合力は常に軸1の中心0に向かう。このように
%4111のスライディングパッド2に対する相対変位
がどのようであっても、スライディングパッド2はその
略中心線OMに対して垂直な方向の反力を軸1に及ぼさ
ないため、軸1の振れ回シは抑制され、轟該スライディ
ングパッド軸受は極めて安定した特性を示す。By the way, the sliding pad 2 is attached to the lower housing 3.
Since it can freely slide along the sliding surface 7 of
The bearing cannot carry a load in the direction parallel to shaft 1, so no reaction force is applied in the same direction to shaft 1, and the oil film 2
The resultant force of pressure is always directed toward the center 0 of axis 1. In this way, no matter what the relative displacement of %4111 with respect to the sliding pad 2 is, the sliding pad 2 does not exert a reaction force on the axis 1 in the direction perpendicular to its approximate center line OM, so the deflection of the axis 1 is reduced. Rotation is suppressed, and the sliding pad bearing exhibits extremely stable characteristics.
又、スライディングパッド2はその背面が全面に亙って
摺動面7に略均−に支持されるため、従来のテイルテイ
ングパツド軸受の支持座に発生してい九局部的に高い面
圧を形成することがなく、高荷重を支えることができる
と共にスライディングパッド2が曲げによって変形する
こともなく、油膜2の形成が安定化する。In addition, since the sliding pad 2 is supported almost uniformly on the sliding surface 7 over its entire back surface, it is not subject to the locally high surface pressure that occurs on the support seat of conventional tailing pad bearings. The oil film 2 is not formed and can support a high load, and the sliding pad 2 is not deformed by bending, and the formation of the oil film 2 is stabilized.
本発明の他の一実施例の断面構造を表す第3図に示すよ
うに、スライディングパッド102の背面にボケツ)
105t−設け、ここに給油孔107及び絞り 106
1に介して高圧油を供給し、流体静力学的にスライディ
ングパッド102を下部ハウジング103′から浮き上
がらせ、これと下部ハウジング103′との間の摩擦抵
抗を小さく抑えるようにするととも可能である。As shown in FIG. 3, which shows the cross-sectional structure of another embodiment of the present invention, there is a hole on the back surface of the sliding pad 102.
105t- provided, oil supply hole 107 and throttle 106 here
This is also possible by supplying high-pressure oil through the pad 1 to hydrostatically lift the sliding pad 102 from the lower housing 103', thereby minimizing the frictional resistance between the sliding pad 102 and the lower housing 103'.
又1本実施例ではスライディングパッド102の側面と
下部ハウジング103′との間に第4図に示す如き小さ
な波状を成す薄板ばね108t”複数枚介装し、これら
薄板ばね108自身の剛性とこれら薄板ばね108間に
介在する油のスクイズ効果によってダンピング効果を持
たせている。なお1図中の符号で101は軸、103は
上部ハウジング、104は給油孔である。Furthermore, in this embodiment, a plurality of thin plate springs 108t'' having a small wave shape as shown in FIG. A damping effect is provided by the squeezing effect of the oil interposed between the springs 108. In FIG. 1, 101 is a shaft, 103 is an upper housing, and 104 is an oil supply hole.
又1本発明の別な一実施例の断面構造を表す第5図及び
その■−■矢視断面構造を表す第6図に示すように、ス
ライディングパッド202の背面にポケット205を設
け、給油孔207及び絞D 2061介してポケット2
05に供給される高圧油によってスライディングパッド
202fcフローテイング支持するように、更に、スラ
イディングパッド202の背面をこれと平行な軸を中心
とする円筒状に設定し、自動調心効果を持たせることも
可能である。なお、図中の符号で201は軸、203は
上部ハウジング、203′は下部ハウジング、204は
給油孔であシ、これらの機能は前述の実施例と同様であ
る。Furthermore, as shown in FIG. 5 showing the cross-sectional structure of another embodiment of the present invention and FIG. 6 showing the cross-sectional structure taken along the arrows 1--2, a pocket 205 is provided on the back surface of the sliding pad 202, and a pocket 205 is provided on the back surface of the sliding pad 202, and a pocket 205 is provided on the back surface of the sliding pad 202. Pocket 2 through 207 and diaphragm D 2061
In order to floatingly support the sliding pad 202fc by the high-pressure oil supplied to the sliding pad 202f, the back surface of the sliding pad 202 may be set in a cylindrical shape centered on an axis parallel to this to provide a self-aligning effect. It is possible. In the figure, 201 is a shaft, 203 is an upper housing, 203' is a lower housing, and 204 is an oil supply hole, and these functions are the same as in the previous embodiment.
〈発明の効果〉
本発明によれば、軸受ハウジングと軸受パッドの背面と
の対向面を、軸受パッドの略中心線に対して垂直な平面
とし、該平面に対して軸受パッドを摺動可能とした沈め
、軸の振れ回りを誘起する力の発生を防いで安蝋した軸
受特性が得られる。又、局部的な面圧過大°箇所が存在
しないために負荷容tを高めることができる。<Effects of the Invention> According to the present invention, the facing surfaces of the bearing housing and the back surface of the bearing pad are made into a plane perpendicular to the approximate center line of the bearing pad, and the bearing pad can be slid on the plane. This prevents the generation of forces that would cause the shaft to sink and whirl, resulting in stable bearing characteristics. Furthermore, since there are no localized excessive surface pressure points, the load capacity t can be increased.
第1図は本発明に係るスライディングパッド軸受の一実
施例の断面図、第2図はその■−■矢視断面図、第3図
は本発明の他の一実施例に係るスライディングパッド軸
受の断面図、第4図はその薄板ばねの斜視図、第5図は
本発明の別な一実施例に係るスライディングパッド軸受
の断面図、第6図はその■−■矢視断面図、第7図は従
来のテイルティングパッド軸受の断面図、第8図はその
■−■矢視断面図である。
図 面 中、
1.101,201は軸、2,102,202はスライ
ディングパッドTh 31103.203は上部ハウ
ジング、3’、 103’、 203’は下部ハウジン
グ、5はころ、°7は摺動面、8,108はばねである
。FIG. 1 is a cross-sectional view of one embodiment of a sliding pad bearing according to the present invention, FIG. 2 is a cross-sectional view taken along arrows -■, and FIG. 4 is a perspective view of the thin plate spring, FIG. 5 is a sectional view of a sliding pad bearing according to another embodiment of the present invention, FIG. The figure is a cross-sectional view of a conventional tailing pad bearing, and FIG. In the figure, 1.101, 201 are shafts, 2, 102, 202 are sliding pads Th, 31103.203 are upper housings, 3', 103', 203' are lower housings, 5 is rollers, °7 is sliding surface , 8,108 are springs.
Claims (1)
パッドを設けて成る軸受であつて、上記軸受ハウジング
の内側と前記軸受パッドの背面との対向面をこの軸受パ
ッドの略中心線に対して垂直な平面とし、該平面に対し
て前記軸受パッドを摺動可能に設けたことを特徴とする
スライディングパッド軸受。A bearing comprising a plurality of bearing pads for rotatably holding a shaft within a bearing housing, wherein the opposing surfaces of the inside of the bearing housing and the back surface of the bearing pads are aligned with respect to the approximate center line of the bearing pads. A sliding pad bearing, characterized in that the bearing pad is slidably provided on a perpendicular plane.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP7529585A JPS61236916A (en) | 1985-04-11 | 1985-04-11 | Sliding pad bearing |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP7529585A JPS61236916A (en) | 1985-04-11 | 1985-04-11 | Sliding pad bearing |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS61236916A true JPS61236916A (en) | 1986-10-22 |
Family
ID=13572109
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP7529585A Pending JPS61236916A (en) | 1985-04-11 | 1985-04-11 | Sliding pad bearing |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS61236916A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100322542A1 (en) * | 2009-06-18 | 2010-12-23 | Argo-Tech Corporation | Self-aligning journal bearing |
CN112228452A (en) * | 2020-09-25 | 2021-01-15 | 青岛海尔空调器有限总公司 | Axle sleeve and air conditioner |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4868943A (en) * | 1971-12-23 | 1973-09-19 | ||
JPS52101342A (en) * | 1976-02-19 | 1977-08-25 | Mitsubishi Electric Corp | Bearing system with type of eccentrically supported pad |
-
1985
- 1985-04-11 JP JP7529585A patent/JPS61236916A/en active Pending
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4868943A (en) * | 1971-12-23 | 1973-09-19 | ||
JPS52101342A (en) * | 1976-02-19 | 1977-08-25 | Mitsubishi Electric Corp | Bearing system with type of eccentrically supported pad |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100322542A1 (en) * | 2009-06-18 | 2010-12-23 | Argo-Tech Corporation | Self-aligning journal bearing |
US8308366B2 (en) * | 2009-06-18 | 2012-11-13 | Eaton Industrial Corporation | Self-aligning journal bearing |
CN112228452A (en) * | 2020-09-25 | 2021-01-15 | 青岛海尔空调器有限总公司 | Axle sleeve and air conditioner |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US6767133B2 (en) | Tilting pad bearing arrangement | |
US3930691A (en) | Swing pad bearing | |
US5911511A (en) | Tilting pad foil thrust and journal bearings | |
US4208076A (en) | Compliant hydrodynamic bearing with improved support element | |
US4243274A (en) | Hydrodynamic bearing with radial, thrust and moment load capacity | |
US4296976A (en) | Cross-plies support element for compliant bearings | |
US4153315A (en) | Foil bearing stiffener | |
US5634725A (en) | Bearing assembly | |
US5549392A (en) | Resilient mount pad journal bearing | |
US4348066A (en) | Foil bearing mounting | |
US4502795A (en) | Foil bearing alignment | |
JPH0742978B2 (en) | Automatic load type deflection control roll | |
US4103979A (en) | Thrust bearing assembly | |
JPS61236916A (en) | Sliding pad bearing | |
JPS6052329B2 (en) | Rotor support device | |
US3738717A (en) | Flexible pad journal bearing | |
US4286828A (en) | Offset-pad bearing | |
JPH0211615Y2 (en) | ||
JPS6272919A (en) | Hydromechanical fluid film bearing | |
JP3337296B2 (en) | Hydrodynamic bearing | |
US4555187A (en) | Foil bearing alignment | |
JPS5846255Y2 (en) | Support device for hydrodynamic bearings | |
JPS609459Y2 (en) | Inclined pad type gas bearing | |
JPH0311457Y2 (en) | ||
WO2022249627A1 (en) | Bearing device |