JP3769757B2 - Turbo rotating machine bearing device - Google Patents
Turbo rotating machine bearing device Download PDFInfo
- Publication number
- JP3769757B2 JP3769757B2 JP13852693A JP13852693A JP3769757B2 JP 3769757 B2 JP3769757 B2 JP 3769757B2 JP 13852693 A JP13852693 A JP 13852693A JP 13852693 A JP13852693 A JP 13852693A JP 3769757 B2 JP3769757 B2 JP 3769757B2
- Authority
- JP
- Japan
- Prior art keywords
- receiving surface
- side receiving
- bearing
- rotating
- rotating shaft
- 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.)
- Expired - Fee Related
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- Sliding-Contact Bearings (AREA)
Description
【０００１】
【産業上の利用分野】
この発明は、ターボ回転機の軸受装置に関する。
【０００２】
【従来の技術】
この種の回転機では、インペラが取り付けられた回転軸を高速回転させるために軸受装置を動圧気体軸受で構成するのが一般的であり、一例としては、例えば特開平１−２４９９９６号公報で知られているものがある。このものでは、図２に示すように、インペラ（ａ）が取り付けられた端部を有する回転軸（ｂ）と、該回転軸（ｂ）を回転可能に半径方向において支持するジャーナル軸受（ｃ）と、固定側に設けられた固定側受け面（ｄ）と上記回転軸（ｂ）の端部に設けられた回転側受け面（ｅ）とを有しかつ該両受け面（ｄ），（ｅ）間で回転軸（ｂ）を回転可能に軸心方向において支持するスラスト軸受（ｆ）とを備えている。そして、例えばスラスト軸受（ｆ）では、上記固定側受け面（ｄ）及び回転側受け面（ｅ）の一方に動圧発生用のスパイラルグルーブが設けられており、回転軸（ｂ）の高速回転に伴って両受け面（ｄ），（ｅ）間に動圧が発生するようになされている。
【０００３】
【発明が解決しようとする課題】
しかしながら、上記のようにスラスト軸受（ｆ）の回転側受け面（ｅ）が回転軸の端部に設けられている場合には、図２に仮想線で誇張して示すように高速回転時に回転軸（ｂ）が撓むと回転側受け面（ｅ）が固定側受け面（ｄ）に対し傾斜することになるが、動圧気体軸受では両受け面（ｄ），（ｅ）間のクリアランスが数μｍしかなく、したがって、上記撓みが大きいときには回転側受け面（ｅ）が固定側受け面（ｄ）に接触する虞れがある。
【０００４】
この発明は斯かる点に鑑みてなされたものであり、その主な目的は、高速回転時に回転軸が撓んだときにでも、スラスト軸受の回転側受け面が固定側受け面に接触するのを回避して両受け面間に適正な動圧の発生を確保できるようにすることにある。
【０００５】
【課題を解決するための手段】
上記の目的を達成するために、請求項１の発明では、スラスト軸受の回転側受け面及び固定側受け面を、ジャーナル軸受からの距離を曲率半径とする球面状とし、回転軸が高速回転時に撓んだときに回転側受け面が固定側受け面に対し所定クリアランスを確保した状態で曲率中心周りにスライド移動できるようにした。
【０００６】
具体的には、この発明では、図１に示すように、インペラ（１ａ）が取り付けられた端部を有する回転軸（１）と、該回転軸（１）を回転可能に半径方向において支持するジャーナル軸受（２）と、固定側に設けられた固定側受け面（３ａ）及び上記回転軸（１）の端部に設けられた回転側受け面（１ｂ）を有しかつ該固定側受け面（３ａ）及び回転側受け面（１ｂ）の間で回転軸（１）を回転可能に軸心方向において支持するスラスト軸受（３）とを備え、上記ジャーナル軸受（２）及びスラスト軸受（３）が動圧気体軸受により構成されたターボ回転機の軸受装置が前提である。
【０００７】
そして、上記スラスト軸受（３）の固定側受け面（３ａ）及び回転軸（１）の回転側受け面（１ｂ）を、上記ジャーナル軸受（２）からの距離（Ｌ）を曲率半径とする球面状に構成する。
【０００８】
【作用】
以上の構成により、請求項１の発明では、回転軸（１）は高速回転時にその端部がジャーナル軸受（２）の部分を中心としかつ該ジャーナル軸受（２）からの距離（Ｌ）を曲率半径とする球面に沿って変位する状態に撓む。これに伴い、回転軸（１）の回転側受け面（１ｂ）は上記端部と同様にジャーナル軸受（２）からの距離（Ｌ）を曲率半径とする球面に沿ってスライド移動する。このとき、固定側の受け面（３ａ）及び回転側受け面（１ｂ）は、ジャーナル軸受（２）からの距離（Ｌ）を曲率半径とする球面状になされているので、回転側受け面（１ｂ）のスライド移動に拘らず、該回転側受け面（１ｂ）と固定側受け面（３ａ）との間のクリアランスは一定に保持される。したがって、高速回転時の回転軸（１）が撓んでも、回転側受け面（１ｂ）は固定側受け面（３ａ）に接触せず、かつ両者間のクリアランスが一定に保持されることにより、該両者間に適正な動圧を発生させて回転軸（１）を回転可能にスラスト方向において支持することができる。
【０００９】
【実施例】
以下、この発明の実施例を図面に基づいて説明する。
【００１０】
図１はこの実施例に係るターボ回転機を示し、該ターボ回転機は、両端が開口された円筒状のケーシング（４）内に、インペラ（１ａ）がそれぞれ取り付けられた両端部を有する回転軸（１）を備えている。上記ケーシング（４）内には、回転軸（１）の軸心方向中間部に対応するジャーナル軸受用フレーム（５）と、端部に対応するスラスト軸受用フレーム（６）とが配設固定されている。そして、ジャーナル軸受用フレーム（５）と回転軸（１）との間には、回転軸（１）を回転可能に半径方向において支持するジャーナル軸受（２）が軸心方向の２箇所にそれぞれ設けられている。また、スラスト軸受用フレーム（６）とインペラ（１ａ）との間には、回転軸（１）を回転可能に軸心方向において支持するスラスト軸受（３）がそれぞれ設けられている。上記ジャーナル軸受（２）及びスラスト軸受（３）は共に動圧気体軸受により構成されている。
【００１１】
上記スラスト軸受（３）は、スラスト軸受用フレーム（６）に設けられた固定側受け面（３ａ）と、インペラ（１ａ）背面に設けられた回転側受け面（１ｂ）とからなり、これら受け面（３ａ），（１ｂ）の一方には動圧発生用のスパイラルグルーブが設けられている。そして、上記固定側受け面（３ａ）及び回転側受け面（１ｂ）は、各々のスラスト軸受（３）に近い側の上記ジャーナル軸受（２）からの距離（Ｌ）を曲率半径とする球面状になされている。すなわち、固定側受け面（３ａ）は凸面状に、また回転側受け面（１ｂ）は凹面状にそれぞれなされている。
【００１２】
したがって、この実施例では、図１に仮想線で誇張して示すように、回転軸（１）は高速回転時にインペラ（１ａ）がジャーナル軸受（２）の部分を中心としかつ該ジャーナル軸受（２）からの距離（Ｌ）を曲率半径とする球面に沿って変位する状態に撓む。これに伴い、インペラ（１ａ）背面の回転側受け面（１ｂ）はジャーナル軸受（２）からの距離（Ｌ）を曲率半径とする球面に沿ってスライド移動する。このとき、固定側の受け面（３ａ）及び回転側受け面（１ｂ）は、ジャーナル軸受（２）からの距離（Ｌ）を曲率半径とする球面状になされているので、回転側受け面（１ｂ）のスライド移動に拘らず、該回転側受け面（１ｂ）と固定側受け面（３ａ）との間のクリアランスは一定に保持される。したがって、高速回転時の回転軸（１）が撓んでも、回転側受け面（１ｂ）が固定側受け面（３ａ）に接触するのを回避でき、その上、両受け面（１ｂ），（３ａ）間のクリアランスを一定に保持できるので、回転軸（１）の撓みにも拘らず該両受け面（１ｂ），（３ａ）間に適正な動圧を発生させることができ、回転軸（１）を回転可能にスラスト方向において支持することができる。
【００１３】
【発明の効果】
以上説明したように、請求項１の発明によれば、インペラが取り付けられた端部を有する回転軸が動圧気体軸受からなるジャーナル軸受及びスラスト軸受により回転可能に支持されている場合に、上記スラスト軸受の回転側受け面及び固定側受け面を、ジャーナル軸受からの距離を曲率半径とする曲面状としたことにより、回転軸が高速回転時に撓んで上記回転側受け面が揺動しても、該回転側受け面が固定側受け面に接触するのを回避でき、かつ両受け面間のクリアランスを一定に保持して適正な動圧を発生させるようにすることができる。
【図面の簡単な説明】
【図１】 この発明の実施例に係るターボ回転機を示す縱断面図である。
【図２】 従来のターボ回転機の要部を示す縱断面図である。
【符号の説明】
（１） 回転軸
（１ａ） インペラ
（１ｂ） 回転側受け面
（２） ジャーナル軸受
（３） スラスト軸受
（３ａ） 固定側受け面
（Ｌ） ジャーナル軸受からの距離 [0001]
[Industrial application fields]
The present invention relates to a bearing device for a turbo rotating machine.
[0002]
[Prior art]
In this type of rotating machine, in order to rotate a rotating shaft to which an impeller is attached at a high speed, the bearing device is generally constituted by a dynamic pressure gas bearing. As an example, for example, in JP-A-1-249996 There is something known. In this structure, as shown in FIG. 2 , a rotating shaft (b) having an end portion to which an impeller (a) is attached, and a journal bearing (c) that rotatably supports the rotating shaft (b) in the radial direction. And a fixed side receiving surface (d) provided on the fixed side and a rotating side receiving surface (e) provided at the end of the rotating shaft (b), and both the receiving surfaces (d), ( and a thrust bearing (f) that rotatably supports the rotating shaft (b) in the axial direction. For example, in the thrust bearing (f), a spiral groove for generating dynamic pressure is provided on one of the fixed side receiving surface (d) and the rotating side receiving surface (e), and the rotating shaft (b) rotates at high speed. As a result, dynamic pressure is generated between the receiving surfaces (d) and (e).
[0003]
[Problems to be solved by the invention]
However, when the rotation-side receiving surface of the thrust bearing (f) as described above (e) is provided at an end portion of the rotary shaft is rotated during high-speed rotation as shown in exaggerated in phantom in FIG. 2 When the shaft (b) is bent, the rotating side receiving surface (e) is inclined with respect to the fixed side receiving surface (d). However, in the hydrodynamic gas bearing, the clearance between the receiving surfaces (d) and (e) is small. several μm only without Accordingly, when the deflection is large, there is a possibility rotating side receiving surface (e) is in contact with the receiving surface fixed side (d).
[0004]
The present invention has been made in view of such a point, and its main object is that the rotating side receiving surface of the thrust bearing comes into contact with the fixed side receiving surface even when the rotating shaft is bent during high speed rotation. This is to prevent generation of an appropriate dynamic pressure between both receiving surfaces.
[0005]
[Means for Solving the Problems]
In order to achieve the above object, according to the first aspect of the present invention, the rotation-side receiving surface and the stationary-side receiving surface of the thrust bearing have a spherical shape with a radius of curvature as the distance from the journal bearing, and the rotating shaft is at high speed rotation. The rotating side receiving surface can be slid around the center of curvature with a predetermined clearance with respect to the fixed side receiving surface when bent.
[0006]
Specifically, in the present invention, as shown in FIG. 1, a rotary shaft (1) having an end portion to which an impeller (1a) is attached, and the rotary shaft (1) are rotatably supported in a radial direction. A journal bearing (2), a fixed side receiving surface (3a) provided on the fixed side, and a rotating side receiving surface (1b) provided on the end of the rotating shaft (1), and the fixed side receiving surface (3a) and a thrust bearing (3) for rotatably supporting the rotating shaft (1) in the axial direction between the rotating side receiving surface (1b), the journal bearing (2) and the thrust bearing (3) The premise is a bearing device for a turbo rotating machine that is constituted by a dynamic pressure gas bearing.
[0007]
Then, the fixed side receiving surface (3a) of the thrust bearing (3) and the rotating side receiving surface (1b) of the rotating shaft (1) are spherical surfaces whose radius of curvature is the distance (L) from the journal bearing (2). Construct in a shape.
[0008]
[Action]
With the above configuration, according to the first aspect of the present invention, when the rotary shaft (1) rotates at a high speed, its end is centered on the journal bearing (2) and the distance (L) from the journal bearing (2) is the curvature. It bends so as to be displaced along a spherical surface having a radius. Along with this, the rotation-side receiving surface (1b) of the rotating shaft (1) slides along a spherical surface having a radius of curvature of the distance (L) from the journal bearing (2) in the same manner as the end portion. At this time, the fixed-side receiving surface (3a) and the rotating-side receiving surface (1b) are formed in a spherical shape having a radius of curvature of the distance (L) from the journal bearing (2). Regardless of the sliding movement of 1b), the clearance between the rotating side receiving surface (1b) and the fixed side receiving surface (3a) is kept constant. Therefore, even if the rotating shaft (1) at the time of high-speed rotation is bent, the rotating side receiving surface (1b) does not contact the fixed side receiving surface (3a), and the clearance between the two is kept constant. An appropriate dynamic pressure can be generated between the two so that the rotating shaft (1) can be rotatably supported in the thrust direction.
[0009]
【Example】
Embodiments of the present invention will be described below with reference to the drawings.
[0010]
Figure 1 shows a turbo rotating machine according to this embodiment, the turbo rotation machine, the both ends apertured cylindrical casing (4) in the rotating shaft having opposite ends impeller (1a) is attached respectively (1) is provided. In the casing (4), a journal bearing frame (5) corresponding to an intermediate portion in the axial direction of the rotating shaft (1) and a thrust bearing frame (6) corresponding to an end portion are disposed and fixed. ing. Between the journal bearing frame (5) and the rotary shaft (1), journal bearings (2) for rotatably supporting the rotary shaft (1) in the radial direction are provided at two locations in the axial direction. It has been. Further, between the thrust bearing frame (6) and the impeller (1a), there are provided thrust bearings (3) for rotatably supporting the rotating shaft (1) in the axial direction. Both the journal bearing (2) and the thrust bearing (3) are constituted by dynamic pressure gas bearings.
[0011]
The thrust bearing (3) includes a fixed side receiving surface (3a) provided on the thrust bearing frame (6) and a rotating side receiving surface (1b) provided on the back surface of the impeller (1a). One of the surfaces (3a) and (1b) is provided with a spiral groove for generating dynamic pressure. The fixed-side receiving surface (3a) and the rotating-side receiving surface (1b) are spherical surfaces having a radius of curvature that is a distance (L) from the journal bearing (2) on the side close to each thrust bearing (3). Has been made. That is, the fixed side receiving surface (3a) is formed in a convex shape, and the rotating side receiving surface (1b) is formed in a concave shape.
[0012]
Thus, in this embodiment, as shown in exaggerated in phantom in FIG. 1, the rotation shaft (1) is part of the central Toshikatsu the journal bearing of the impeller (1a) is a journal bearing (2) at the time of high-speed rotation ( 2) It bends in a state of being displaced along a spherical surface with a radius of curvature (L) from the curvature radius. Along with this, the rotation-side receiving surface (1b) on the back surface of the impeller (1a) slides along a spherical surface whose radius of curvature is the distance (L) from the journal bearing (2). At this time, the fixed-side receiving surface (3a) and the rotating-side receiving surface (1b) are formed in a spherical shape having a radius of curvature of the distance (L) from the journal bearing (2). Regardless of the sliding movement of 1b), the clearance between the rotating side receiving surface (1b) and the fixed side receiving surface (3a) is kept constant. Therefore, even if the rotating shaft (1) at the time of high-speed rotation is bent, it is possible to prevent the rotating side receiving surface (1b) from coming into contact with the fixed side receiving surface (3a). In addition, both receiving surfaces (1b), ( 3a) can be kept constant, so that an appropriate dynamic pressure can be generated between the receiving surfaces (1b) and (3a) regardless of the bending of the rotating shaft (1). 1) can be rotatably supported in the thrust direction.
[0013]
【The invention's effect】
As described above, according to the first aspect of the present invention, when the rotating shaft having the end portion to which the impeller is attached is rotatably supported by the journal bearing and the thrust bearing made of a dynamic pressure gas bearing, By making the rotational bearing surface and the stationary bearing surface of the thrust bearing into a curved surface with the radius of curvature as the distance from the journal bearing, even if the rotational shaft bends at high speed and the rotational side bearing surface swings, The rotation-side receiving surface can be prevented from coming into contact with the fixed-side receiving surface, and an appropriate dynamic pressure can be generated by maintaining a constant clearance between the both receiving surfaces.
[Brief description of the drawings]
1 is a縱断sectional view showing a turbo rotating machine according to an embodiment of the present invention.
FIG. 2 is a cross-sectional view showing a main part of a conventional turbo rotating machine.
[Explanation of symbols]
(1 ) Rotating shaft (1a ) Impeller (1b ) Rotating side bearing surface (2 ) Journal bearing (3 ) Thrust bearing (3a) Fixed side bearing surface
(L) distance from the journal bearing
Claims (1)
上記スラスト軸受（３）の固定側受け面（３ａ）及び回転軸（１）の回転側受け面（１ｂ）は、上記ジャーナル軸受（２）からの距離（Ｌ）を曲率半径とする球面状に構成されている
ことを特徴とするターボ回転機の軸受装置。A rotating shaft (1) having an end portion to which an impeller (1a) is attached, a journal bearing (2) that rotatably supports the rotating shaft (1) in the radial direction, and a fixed side receiver provided on the fixed side A rotating side receiving surface (1b) provided at the end of the surface (3a) and the rotating shaft (1), and the rotating shaft between the fixed side receiving surface (3a) and the rotating side receiving surface (1b); And a thrust bearing (3) that rotatably supports (1) in the axial direction, wherein the journal bearing (2) and the thrust bearing (3) are constituted by a dynamic pressure gas bearing. ,
The fixed side receiving surface (3a) of the thrust bearing (3) and the rotating side receiving surface (1b) of the rotating shaft (1) have a spherical shape with a radius of curvature as the distance (L) from the journal bearing (2). A bearing device for a turbo rotating machine, characterized in that it is configured.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13852693A JP3769757B2 (en) | 1993-06-10 | 1993-06-10 | Turbo rotating machine bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13852693A JP3769757B2 (en) | 1993-06-10 | 1993-06-10 | Turbo rotating machine bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH06346896A JPH06346896A (en) | 1994-12-20 |
| JP3769757B2 true JP3769757B2 (en) | 2006-04-26 |
Family
ID=15224218
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13852693A Expired - Fee Related JP3769757B2 (en) | 1993-06-10 | 1993-06-10 | Turbo rotating machine bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3769757B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08312582A (en) * | 1995-05-23 | 1996-11-26 | Daikin Ind Ltd | Reversal preventing device for compressor |
| CN103742201B (en) * | 2013-01-10 | 2016-08-24 | 摩尔动力(北京)技术股份有限公司 | Vertical and high-speed bearing impeller mechanism |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4617842Y1 (en) * | 1970-08-01 | 1971-06-22 | ||
| JPS5441063B2 (en) * | 1973-07-13 | 1979-12-06 | ||
| JPS5846255Y2 (en) * | 1978-10-12 | 1983-10-21 | 日本精工株式会社 | Support device for hydrodynamic bearings |
| JPS60121308A (en) * | 1984-08-21 | 1985-06-28 | Nippon Seiko Kk | Dynamic pressure type composite bearing device |
| JPH01249996A (en) * | 1988-03-31 | 1989-10-05 | Ebara Corp | Blower for high temperature gas |
-
1993
- 1993-06-10 JP JP13852693A patent/JP3769757B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH06346896A (en) | 1994-12-20 |
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