JP2009168205A - Tilting pad bearing - Google Patents

Tilting pad bearing Download PDF

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Publication number
JP2009168205A
JP2009168205A JP2008008953A JP2008008953A JP2009168205A JP 2009168205 A JP2009168205 A JP 2009168205A JP 2008008953 A JP2008008953 A JP 2008008953A JP 2008008953 A JP2008008953 A JP 2008008953A JP 2009168205 A JP2009168205 A JP 2009168205A
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bearing
pad
peripheral surface
tilting pad
curvature
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Inventor
Isao Saito
勲 斉藤
Tadasuke Nishioka
忠相 西岡
Kyoichi Ikeno
恭一 池野
Sadamu Takahashi
定 高橋
Naoyuki Nagai
直之 長井
Yuzo Tsurusaki
有三 津留崎
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Priority to JP2008008953A priority Critical patent/JP2009168205A/en
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    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/02—Sliding-contact bearings
    • F16C23/04—Sliding-contact bearings self-adjusting

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tilting pad bearing equalizing the axial temperature of a bearing pad by uniformly adjusting and maintaining the thickness of an oil film in an axial direction in addition to a peripheral direction even under a misalignment condition. <P>SOLUTION: In this tilting pad bearing 11 rotatably supporting a rotor 10, each back surface of a plurality of bearing pads 12 arranged along the outer peripheral surface of the rotor 10 is formed into a projecting shape, thereby the bearing pad has a curvature in the axial direction in addition to the peripheral surface; meanwhile, the inner peripheral surface of a bearing housing 13, opposed to the back surface of the bearing pad, is formed into a recessed shape, thereby the bearing housing has a curvature at least in the peripheral direction. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、蒸気タービン等のロータ（回転軸）を回転自在に支持するティルティングパッド（ジャーナル）軸受に関するものである。   The present invention relates to a tilting pad (journal) bearing that rotatably supports a rotor (rotating shaft) such as a steam turbine.

例えば蒸気タービン等においては、図６に示すように、ロータ（回転軸）１００は図示しないタービンケーシングに対してティルティングパッド軸受１０１を介して回転自在に支持される（図６Ａの断面図参照）。   For example, in a steam turbine or the like, as shown in FIG. 6, the rotor (rotating shaft) 100 is rotatably supported by a turbine casing (not shown) via a tilting pad bearing 101 (see the cross-sectional view of FIG. 6A). .

このティルティングパッド軸受１０１は、ロータ１００の外周面に沿って複数個（図６Ｂの断面図では五つ）配設された軸受パッド１０２が軸受ハウジング１０３に収装されてなり、軸受パッド背面のピボット点（図６Ｂ中白抜き三角形で示した支持点参照）を中心に各軸受パッド１０３が周方向に揺動することで、ロータ外周面と軸受パッド潤滑面との間に形成される油膜の厚さを周方向に均一に調整・保持し得るようになっている。   The tilting pad bearing 101 includes a plurality of bearing pads 102 (five in the cross-sectional view of FIG. 6B) arranged along the outer peripheral surface of the rotor 100. Each bearing pad 103 swings in the circumferential direction around the pivot point (see the support point indicated by the white triangle in FIG. 6B), so that the oil film formed between the rotor outer peripheral surface and the bearing pad lubricating surface The thickness can be adjusted and maintained uniformly in the circumferential direction.

特開２００２−２２７８２２号公報（第３頁，図１〜図３）Japanese Patent Laid-Open No. 2002-227822 (page 3, FIGS. 1 to 3)

ところで、図６に示したようなティルティングパッド軸受１０１において、ロータ１００とティルティングパッド軸受１０１との間にミスアライメント（ロータ外周面と軸受パッド内周面との軸方向隙間が不均一になる）が発生した場合には、軸受パッド１０２がロータ１００に追従する（上記軸方向隙間を均一にする）ことができず、軸方向に対し油膜厚さが不均一となるという不具合を生じる。   Incidentally, in the tilting pad bearing 101 as shown in FIG. 6, misalignment between the rotor 100 and the tilting pad bearing 101 (the axial clearance between the rotor outer peripheral surface and the bearing pad inner peripheral surface becomes non-uniform). ) Occurs, the bearing pad 102 cannot follow the rotor 100 (the axial clearance is made uniform), and the oil film thickness becomes nonuniform in the axial direction.

即ち、油膜厚さの不均一化により、軸受パッド１０２の軸方向に温度差が生じ、油膜が薄く、温度が高い方（図６Ａ中の破線で示した潤滑面の軸方向温度プロファイル参照）は軸受パッド１０２が熱膨張し、油膜の薄膜化が助長されるのである。また、油膜厚さの不均一化により軸受剛性・減衰性の低下も招来される。   That is, due to the non-uniformity of the oil film thickness, a temperature difference occurs in the axial direction of the bearing pad 102, the oil film is thinner, and the temperature is higher (see the axial temperature profile of the lubricated surface indicated by the broken line in FIG. 6A). The bearing pad 102 is thermally expanded, and the thinning of the oil film is promoted. Further, the non-uniformity of the oil film thickness causes a decrease in bearing rigidity and damping.

尚、特許文献１では、すべり軸受の軸受面が端縁に向かいテーパが取られ、相手面は端縁に向って小径化することで、クラウニングと同様に機能して、負荷状態においても軸受メタルの端部近傍における油膜厚さを確保して強当たりによる障害を回避するようにした技術が開示されているが、このすべり軸受の軸受メタルはティルティングパッド軸受の軸受パッドとは構造が異なり、周方向における油膜厚さの調整機能は全く有していない。   In Patent Document 1, the bearing surface of the slide bearing is tapered toward the end edge, and the mating surface is reduced in diameter toward the end edge so that it functions in the same way as crowning, and even in a loaded state, the bearing metal Although the technology that secures the oil film thickness in the vicinity of the end of the belt and avoids the obstacle due to the strong hit is disclosed, the bearing metal of this sliding bearing is different in structure from the bearing pad of the tilting pad bearing, It does not have any function of adjusting the oil film thickness in the circumferential direction.

そこで、本発明の目的は、ミスアライメント状態下にあっても、周方向に加えて軸方向にも油膜厚さを均一に調整・保持して軸受パッドの軸方向温度を均一にすることができるティルティングパッド軸受を提供することにある。   Accordingly, an object of the present invention is to uniformly adjust and maintain the oil film thickness in the axial direction in addition to the circumferential direction even in a misaligned state, so that the axial temperature of the bearing pad can be made uniform. It is to provide a tilting pad bearing.

上記の課題を解決するための本発明に係るティルティングパッド軸受は、
回転軸を回転自在に支持するティルティングパッド軸受において、
前記回転軸の外周面に沿って複数個配設される軸受パッドの背面を凸状形状として周方向に加えて軸方向にも曲率を持たせる一方、該軸受パッド背面に対向する軸受ハウジングの内周面を凹状形状として少なくとも周方向に曲率を持たせたことを特徴とする。 The tilting pad bearing according to the present invention for solving the above-described problems is
In the tilting pad bearing that rotatably supports the rotating shaft,
A plurality of bearing pads arranged along the outer peripheral surface of the rotating shaft have a convex rear surface, and have a curvature in the axial direction in addition to the circumferential direction. The circumferential surface has a concave shape and has a curvature in at least the circumferential direction.

また、
前記軸受パッド背面の曲率半径Ｒｂと前記軸受ハウジング内周面の曲率半径Ｒｈとの間には、Ｒｂ＜Ｒｈの関係が設定されることを特徴とする。 Also,
A relationship of Rb <Rh is set between a curvature radius Rb of the back surface of the bearing pad and a curvature radius Rh of the inner peripheral surface of the bearing housing.

また、
前記軸受パッド背面と前記軸受ハウジング内周面との少なくとも何れか一方の接触部分を本体部分と異なった低摩耗摺動材料で形成したことを特徴とする。 Also,
The contact portion of at least one of the back surface of the bearing pad and the inner peripheral surface of the bearing housing is formed of a low wear sliding material different from the main body portion.

また、
前記接触部分は前記本体部分に交換可能に埋設されることを特徴とする。 Also,
The contact portion is embedded in the main body portion in a replaceable manner.

本発明に係るティルティングパッド軸受によれば、軸受パッドの背面を凸状形状として周方向に加えて軸方向にも曲率を持たせる一方、該軸受パッド背面に対向する軸受ハウジングの内周面を凹状形状として少なくとも周方向に曲率を持たせたので、軸受パッドはピボット点回りに周方向に加えて軸方向にも揺動可能となる。   According to the tilting pad bearing of the present invention, the back surface of the bearing pad is formed in a convex shape so as to have a curvature in the axial direction in addition to the circumferential direction, while the inner peripheral surface of the bearing housing facing the back surface of the bearing pad is provided. Since the concave shape has a curvature in at least the circumferential direction, the bearing pad can swing in the axial direction in addition to the circumferential direction around the pivot point.

これにより、軸受パッドの潤滑面と回転軸の外周面との間に形成される油膜が周方向に加えて軸方向にも均一となり、ミスアライメント状態下にあっても周方向に加えて軸方向にも回転軸外周面と軸受パッド潤滑面との間に形成される油膜厚さを均一に調整・保持して軸受パッドの軸方向温度を均一にすることができる。   As a result, the oil film formed between the lubrication surface of the bearing pad and the outer peripheral surface of the rotating shaft becomes uniform in the axial direction in addition to the circumferential direction, and even in the misaligned state, in addition to the circumferential direction, the axial direction In addition, the oil film thickness formed between the outer peripheral surface of the rotating shaft and the bearing pad lubrication surface can be adjusted and maintained uniformly to make the axial temperature of the bearing pad uniform.

以下、本発明に係るティルティングパッド軸受を実施例により図面を用いて詳細に説明する。   Hereinafter, a tilting pad bearing according to the present invention will be described in detail with reference to the accompanying drawings.

図１は本発明の実施例１を示すティルティングパッド軸受の要部断面図、図２は軸受パッドと軸受ハウジングの斜視図、図３は軸受パッドの組み付け状態の説明図で、図３Ａは軸方向断面図，図３Ｂは軸受パッド中央位置周方向断面図、図４はミスアライメントの説明図で、図４Ａは軸受ハウジングのミスアライメント無しの軸方向断面図，図４Ｂは軸受ハウジングのミスアライメント有りの軸方向断面図である。   1 is a sectional view of a principal part of a tilting pad bearing showing Embodiment 1 of the present invention, FIG. 2 is a perspective view of a bearing pad and a bearing housing, FIG. 3 is an explanatory view of an assembled state of the bearing pad, and FIG. Cross-sectional view, FIG. 3B is a circumferential cross-sectional view of the bearing pad center position, FIG. 4 is an explanatory diagram of misalignment, FIG. 4A is an axial cross-sectional view of the bearing housing without misalignment, and FIG. FIG.

図１に示すように、蒸気タービン等のロータ（回転軸）１０は図示しないタービンケーシングに対しティルティングパッド軸受１１を介して回転自在に支持される。   As shown in FIG. 1, a rotor (rotary shaft) 10 such as a steam turbine is rotatably supported by a turbine casing (not shown) via a tilting pad bearing 11.

前記ティルティングパッド軸受１１は、前記ロータ１０の外周面に沿って複数個配設される軸受パッド１２が軸受ハウジング１３に収装されてなる（図６Ｂ参照）と共に、図２及び図３に示すように、軸受パッド１２の背面を凸状形状として周方向に加えて軸方向にも曲率を持たせる一方、該軸受パッド背面に対向する軸受ハウジング１３の内周面を凹状形状として周方向に加えて軸方向にも曲率を持たせている。   The tilting pad bearing 11 includes a plurality of bearing pads 12 arranged along the outer peripheral surface of the rotor 10 and is housed in a bearing housing 13 (see FIG. 6B), and is shown in FIGS. As described above, the back surface of the bearing pad 12 is formed in a convex shape so as to have a curvature in the axial direction in addition to the circumferential direction, while the inner peripheral surface of the bearing housing 13 facing the back surface of the bearing pad is formed in a concave shape in the circumferential direction. The curvature is also given in the axial direction.

即ち、軸受パッド１２の背面と軸受ハウジング１３の内周面には、周方向クラウニング加工と軸方向クラウニング加工が施されるのである。尚、軸受ハウジング１３の内周面においては、周方向にのみ曲率を持たせても良い。   That is, circumferential crowning and axial crowning are performed on the back surface of the bearing pad 12 and the inner circumferential surface of the bearing housing 13. The inner peripheral surface of the bearing housing 13 may have a curvature only in the circumferential direction.

また、前記軸受パッド背面の曲率半径Ｒｂと前記軸受ハウジング内周面の曲率半径Ｒｈとの間には、Ｒｂ＜Ｒｈの関係が設定される。   Further, a relationship of Rb <Rh is set between the curvature radius Rb of the back surface of the bearing pad and the curvature radius Rh of the inner peripheral surface of the bearing housing.

このように構成されるため、本ティルティングパッド軸受１１において、軸受パッド１２はピボット点（図１〜図３中白抜き三角形で示した支持点参照）回りに周方向に加えて軸方向にも揺動可能となる。   Because of this configuration, in the tilting pad bearing 11, the bearing pad 12 is arranged in the axial direction in addition to the circumferential direction around the pivot point (see the support point indicated by the white triangle in FIGS. 1 to 3). It can swing.

これにより、軸受パッド１２の潤滑面とロータ１０の外周面との間に形成される油膜厚さが周方向に加えて軸方向にも均一となり、ミスアライメント状態下にあっても周方向に加えて軸方向にもロータ外周面と軸受パッド潤滑面との間に形成される油膜厚さを均一に調整・保持して軸受パッド１２の軸方向温度を均一にすることができる（図１中の破線で示す潤滑面の軸方向温度プロファイル参照）。   As a result, the oil film thickness formed between the lubrication surface of the bearing pad 12 and the outer peripheral surface of the rotor 10 becomes uniform in the axial direction in addition to the circumferential direction. In the axial direction as well, the oil film thickness formed between the outer peripheral surface of the rotor and the bearing pad lubrication surface can be adjusted and maintained uniformly to make the axial temperature of the bearing pad 12 uniform (see FIG. 1). (Refer to the axial temperature profile of the lubricated surface indicated by the broken line).

ところで、軸受パッド１２と軸受ハウジング１３の接触圧力をHertz（ヘルツ）の接触圧力で評価する場合、
（１）軸受パッド１２と軸受ハウジング１３が共に周方向・軸方向に曲率を有する（本実施例のように内接する球対球）、
（２）軸受パッド１２に周方向・軸方向に曲率を有し、軸受ハウジング１３に周方向に曲率を有する（内接する球対円筒）、
（３）軸受パッド１２に周方向に曲率を有し、軸受ハウジング１３に周方向・軸方向に曲率を有する（外接する円筒対球）、
三つの構造が考えられるが、前記（１）の構造が最も圧力を低く抑える曲率半径の設計が容易であると言える。 By the way, when evaluating the contact pressure between the bearing pad 12 and the bearing housing 13 with the Hertz contact pressure,
(1) Both the bearing pad 12 and the bearing housing 13 have curvatures in the circumferential direction and the axial direction (inscribed ball-to-ball as in this embodiment),
(2) The bearing pad 12 has a curvature in the circumferential direction and the axial direction, and the bearing housing 13 has a curvature in the circumferential direction (inscribed ball-to-cylinder).
(3) The bearing pad 12 has a curvature in the circumferential direction, and the bearing housing 13 has a curvature in the circumferential direction and the axial direction (a circumscribed cylindrical ball),
Although three structures are conceivable, it can be said that the structure of (1) is easy to design a curvature radius that suppresses the pressure to the lowest level.

因みに、図４に示すように、前記（３）の構造において、軸受ハウジング１３自体にミスアライメントが生じた場合（図４Ｂ参照）、ピボット点（図４中白抜き三角形で示した支持点参照）の位置が軸方向に中心から移動する（図４Ａの軸受ハウジング１３にミスアライメントが生じてない場合を比較参照）。ピボット点の位置が偏心すれば、軸方向圧力分布が非対称になることで、油膜厚さ分布も非対称になり、軸受パッド１２に軸方向温度差が生じる。これに対して、前記（１）の構造のように軸受パッド１２と軸受ハウジング１３の両方にクラウニングを設けた場合、ピボット点の位置は軸方向にずれることはない。   Incidentally, as shown in FIG. 4, in the structure of (3) above, when misalignment occurs in the bearing housing 13 itself (see FIG. 4B), the pivot point (see the support point indicated by the white triangle in FIG. 4). Is moved from the center in the axial direction (see the case where no misalignment occurs in the bearing housing 13 in FIG. 4A). If the position of the pivot point is decentered, the axial pressure distribution is asymmetrical, the oil film thickness distribution is also asymmetrical, and an axial temperature difference occurs in the bearing pad 12. On the other hand, when the crowning is provided on both the bearing pad 12 and the bearing housing 13 as in the structure (1), the position of the pivot point does not shift in the axial direction.

図５は本発明の実施例２を示すティルティングパッド軸受の説明図で、図４Ａは組み付け状態要部断面図，図４Ｂは図４ＡのＡ−Ａ矢視断面図である。   FIG. 5 is an explanatory view of a tilting pad bearing showing Embodiment 2 of the present invention, FIG. 4A is a cross-sectional view of the main part in the assembled state, and FIG. 4B is a cross-sectional view taken along arrow AA in FIG.

これは、実施例１における軸受パッド１２の背面と軸受ハウジング１３の内周面との両方の接触部分１２ｂ，１３ｂを本体部分１２ａ，１３ａと異なった低摩耗摺動材料（例えば窒化珪素等のセラミックス）で形成すると共に、前記接触部分１２ｂ，１３ｂを矩形断面のキー状に形成して前記本体部分１２ａ，１３ａに形成した矩形断面の溝部に交換可能に埋設した例である。   This is because the contact portions 12b, 13b of the back surface of the bearing pad 12 and the inner peripheral surface of the bearing housing 13 in Example 1 are different from the main body portions 12a, 13a in a low wear sliding material (for example, ceramics such as silicon nitride). ), And the contact portions 12b and 13b are formed in a key shape having a rectangular cross section and embedded in the groove portions having a rectangular cross section formed in the main body portions 12a and 13a in an exchangeable manner.

これによれば、実施例１と同様の作用・効果に加えて、ピボット点近傍にフレッチング等の損傷が発生した場合、軸受パッド１２・軸受ハウジング１３ごと交換せずに各々の接触部分１２ｂ，１３ｂのみ交換すれば良く、容易に交換可能となると共に、軸受パッド１２・軸受ハウジング１３全体を高価な低摩耗摺動材料で形成するより低コストを実現できる利点が得られる。   According to this, in addition to the same actions and effects as in the first embodiment, when damage such as fretting occurs near the pivot point, the contact portions 12b and 13b are not replaced without replacing the bearing pad 12 and the bearing housing 13 together. The bearing pad 12 and the bearing housing 13 as a whole are made of an expensive low-wear sliding material, and the cost can be reduced.

尚、上記実施例において、軸受パッド１２の背面と軸受ハウジング１３の内周面との何れか一方の接触部分１２ｂ又は１３ｂを本体部分１２ａ又は１３ａと異なった低摩耗摺動材料で形成しても良い。   In the above embodiment, either the contact portion 12b or 13b of the back surface of the bearing pad 12 and the inner peripheral surface of the bearing housing 13 may be formed of a low wear sliding material different from the main body portion 12a or 13a. good.

また、本願発明は上記各実施例に限定されず、軸受パッド１２や軸受ハウジング１３の形状・寸法変更等各種変更が可能であることは言うまでもない。   Further, the present invention is not limited to the above embodiments, and it goes without saying that various changes such as changes in the shape and dimensions of the bearing pad 12 and the bearing housing 13 are possible.

本発明の実施例１を示すティルティングパッド軸受の要部断面図である。It is principal part sectional drawing of the tilting pad bearing which shows Example 1 of this invention. 軸受パッドと軸受ハウジングの斜視図である。It is a perspective view of a bearing pad and a bearing housing. 軸受パッドの組み付け状態の説明図で、図３Ａは軸方向断面図，図３Ｂは軸受パッド中央位置周方向断面図である。FIG. 3A is a sectional view in the axial direction, and FIG. 3B is a sectional view in the circumferential direction of the center position of the bearing pad. ミスアライメントの説明図で、図４Ａは軸受ハウジングのミスアライメント無しの軸方向断面図，図４Ｂは軸受ハウジングのミスアライメント有りの軸方向断面図である。FIG. 4A is an axial sectional view of the bearing housing without misalignment, and FIG. 4B is an axial sectional view of the bearing housing with misalignment. 本発明の実施例２を示すティルティングパッド軸受の説明図で、図４Ａは組み付け状態要部断面図，図４Ｂは図４ＡのＡ−Ａ矢視断面図である。4A and 4B are explanatory views of a tilting pad bearing showing Embodiment 2 of the present invention, in which FIG. 4A is a cross-sectional view of the main part in the assembled state, and FIG. 4B is a cross-sectional view taken along line AA in FIG. 従来のティルティングパッド軸受の説明図で、図６Ａは軸方向断面図，図６Ｂは周方向断面図である。FIG. 6A is an axial sectional view and FIG. 6B is a circumferential sectional view of a conventional tilting pad bearing.

符号の説明Explanation of symbols

１０ ロータ
１１ ティルティングパッド軸受
１２ 軸受パッド
１２ａ 本体部分
１２ｂ 接触部分
１３ 軸受ハウジング
１３ａ 本体部分
１３ｂ 接触部分 DESCRIPTION OF SYMBOLS 10 Rotor 11 Tilting pad bearing 12 Bearing pad 12a Body part 12b Contact part 13 Bearing housing 13a Body part 13b Contact part

Claims (4)

回転軸を回転自在に支持するティルティングパッド軸受において、
前記回転軸の外周面に沿って複数個配設される軸受パッドの背面を凸状形状として周方向に加えて軸方向にも曲率を持たせる一方、該軸受パッド背面に対向する軸受ハウジングの内周面を凹状形状として少なくとも周方向に曲率を持たせたことを特徴とするティルティングパッド軸受。 In the tilting pad bearing that rotatably supports the rotating shaft,
A plurality of bearing pads arranged along the outer peripheral surface of the rotating shaft have a convex rear surface, and have a curvature in the axial direction in addition to the circumferential direction. A tilting pad bearing characterized in that the circumferential surface has a concave shape and has a curvature in at least the circumferential direction. 前記軸受パッド背面の曲率半径Ｒｂと前記軸受ハウジング内周面の曲率半径Ｒｈとの間には、Ｒｂ＜Ｒｈの関係が設定されることを特徴とする請求項１に記載のティルティングパッド軸受。   2. The tilting pad bearing according to claim 1, wherein a relationship of Rb <Rh is set between a curvature radius Rb of the back surface of the bearing pad and a curvature radius Rh of the inner peripheral surface of the bearing housing. 前記軸受パッド背面と前記軸受ハウジング内周面との少なくとも何れか一方の接触部分を本体部分と異なった低摩耗摺動材料で形成したことを特徴とする請求項１又は２に記載のティルティングパッド軸受。   3. The tilting pad according to claim 1, wherein a contact portion of at least one of the back surface of the bearing pad and the inner peripheral surface of the bearing housing is formed of a low wear sliding material different from the main body portion. bearing. 前記接触部分は前記本体部分に交換可能に埋設されることを特徴とする請求項３に記載のティルティングパッド軸受。   The tilting pad bearing according to claim 3, wherein the contact portion is embedded in the main body portion in a replaceable manner.
JP2008008953A 2008-01-18 2008-01-18 Tilting pad bearing Pending JP2009168205A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103541995A (en) * 2013-10-31 2014-01-29 湖南崇德工业科技有限公司 Tilting pad supporting structure
WO2016080000A1 (en) 2014-11-20 2016-05-26 三菱重工業株式会社 Tilting pad bearing
KR20190129467A (en) * 2018-05-11 2019-11-20 한화파워시스템 주식회사 Tilting pad bearing

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58102819A (en) * 1981-12-11 1983-06-18 Toshiba Corp Tilting pad bearing
JPH05223121A (en) * 1992-02-12 1993-08-31 Toshiba Corp Submerged bearing device
JP2005226832A (en) * 2004-02-12 2005-08-25 Laing Oliver Spherical bearing, electric motor and circulating pump
JP2006118552A (en) * 2004-10-20 2006-05-11 Mitsubishi Heavy Ind Ltd Bearing device
WO2009099094A1 (en) * 2008-02-04 2009-08-13 Mitsubishi Heavy Industries, Ltd. Bearing device and rotary machine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58102819A (en) * 1981-12-11 1983-06-18 Toshiba Corp Tilting pad bearing
JPH05223121A (en) * 1992-02-12 1993-08-31 Toshiba Corp Submerged bearing device
JP2005226832A (en) * 2004-02-12 2005-08-25 Laing Oliver Spherical bearing, electric motor and circulating pump
JP2006118552A (en) * 2004-10-20 2006-05-11 Mitsubishi Heavy Ind Ltd Bearing device
WO2009099094A1 (en) * 2008-02-04 2009-08-13 Mitsubishi Heavy Industries, Ltd. Bearing device and rotary machine

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103541995A (en) * 2013-10-31 2014-01-29 湖南崇德工业科技有限公司 Tilting pad supporting structure
WO2016080000A1 (en) 2014-11-20 2016-05-26 三菱重工業株式会社 Tilting pad bearing
US9618036B2 (en) 2014-11-20 2017-04-11 Mitsubishi Heavy Industries, Ltd. Tilting-pad bearing
KR20190129467A (en) * 2018-05-11 2019-11-20 한화파워시스템 주식회사 Tilting pad bearing
KR102575236B1 (en) * 2018-05-11 2023-09-05 한화파워시스템 주식회사 Tilting pad bearing

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