JP2000310342A - Floating seal for rotating machine - Google Patents
Floating seal for rotating machineInfo
- Publication number
- JP2000310342A JP2000310342A JP11119938A JP11993899A JP2000310342A JP 2000310342 A JP2000310342 A JP 2000310342A JP 11119938 A JP11119938 A JP 11119938A JP 11993899 A JP11993899 A JP 11993899A JP 2000310342 A JP2000310342 A JP 2000310342A
- Authority
- JP
- Japan
- Prior art keywords
- seal member
- seal
- annular
- floating
- floating seal
- 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.)
- Granted
Links
Landscapes
- Turbine Rotor Nozzle Sealing (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
- Sealing Of Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、回転圧縮機、送風
機、タービン等の回転機械に関し、特にそこに用いられ
るフローティングシールに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary machine such as a rotary compressor, a blower, and a turbine, and more particularly to a floating seal used therein.
【０００２】[0002]
【従来の技術】圧縮機等の回転流体機械においては、取
り扱う流体をシールするため、フローティングシールが
使用されている。これをタービンを例にして説明する
と、図５において、回転体としてのタービンロータ１
が、ラジアル軸受３，５により半径方向に支持され、ス
ラスト軸受７によって軸方向に支持されている。タービ
ンロータ１の外面には、多段の動翼９が円周方向に並ん
で配設されている。そして、動翼９を駆動する作動流体
をシールするフローティングシール１１がタービンロー
タ１の両端側の適所に設けられている。フローティング
シール１１の詳細構造が図６に示されているが、タービ
ンロータ１のシール面を取り囲んで円環状のシール部材
１３が設けられ、更にシール部材１３の外側部を受け入
れる環状溝が形成された保持部材１５が固定側に設けら
れている。そして、タービンロータ１とシール部材１３
の内周面との間に隙間ｈが設けられ、この隙間ｈによっ
て発生する流体圧による浮上力Ｐ（図７参照）によっ
て、求心作用が発生し、タービンロータ１に対しシール
部材１３が同軸的に位置される。更に、シール部材１３
には、車室内の高圧ＰIと外部の低圧ＰOとの流体差圧
（ＰI−ＰO）が作用し、保持部材１５の環状端面１７に
シール部材１３の一方の側面が押し付けられる。このよ
うにして、シール部材１３と保持部材１５との間には隙
間が無く、更に隙間ｈは所定の最小隙間に維持されてシ
ールが為される。2. Description of the Related Art In a rotary fluid machine such as a compressor, a floating seal is used to seal a fluid to be handled. This will be described by taking a turbine as an example. In FIG. 5, a turbine rotor 1 as a rotating body is shown.
Are supported in the radial direction by the radial bearings 3 and 5 and are supported in the axial direction by the thrust bearing 7. On the outer surface of the turbine rotor 1, multi-stage moving blades 9 are arranged in a circumferential direction. Floating seals 11 for sealing a working fluid for driving the moving blades 9 are provided at appropriate positions on both ends of the turbine rotor 1. The detailed structure of the floating seal 11 is shown in FIG. 6. An annular seal member 13 is provided around the seal surface of the turbine rotor 1, and an annular groove for receiving the outer portion of the seal member 13 is formed. The holding member 15 is provided on the fixed side. Then, the turbine rotor 1 and the seal member 13
A clearance h is provided between the seal member 13 and the inner peripheral surface of the turbine rotor 1, and a floating force P (see FIG. 7) generated by the fluid pressure generated by the clearance h generates a centripetal action. Is located. Further, the sealing member 13
, A fluid pressure difference (P I -P O ) between the high pressure P I in the vehicle compartment and the low pressure P O outside acts on one side of the seal member 13 against the annular end face 17 of the holding member 15. In this way, there is no gap between the seal member 13 and the holding member 15, and the gap h is maintained at a predetermined minimum gap to perform sealing.
【０００３】[0003]
【発明が解決しようとする課題】しかしながら、シール
部材と保持部材の接触端面において、シール部材のフロ
ーティング作用に際し摩擦力が発生する。そして、機械
の長期間使用などによってその接触端面が荒れ、摩擦係
数が増大すると、図７に示すような摩擦力Ｆが浮上力Ｐ
より大きくなり、シール部材が保持部材の端面に固定さ
れた状態となる。このような状態では、タービンロータ
とシール部材が接触して損傷したり、隙間ｈの量が最適
値より大きくなって適正なシール作用が得られないこと
になる。本発明は、このような問題を解決するために為
されたものであり、長期に亙ってフローティングシール
部材のフローティング作用が得られて、シール性能が低
下しない回転機械のフローティングシールを提供するこ
とを課題とする。However, a frictional force is generated at the contact end face between the seal member and the holding member when the seal member floats. When the contact end face becomes rough due to long-term use of the machine and the friction coefficient increases, the frictional force F as shown in FIG.
As a result, the seal member is fixed to the end face of the holding member. In such a state, the turbine rotor and the sealing member come into contact with each other and are damaged, or the amount of the gap h becomes larger than the optimum value, so that an appropriate sealing action cannot be obtained. The present invention has been made in order to solve such a problem, and it is an object of the present invention to provide a floating seal for a rotating machine in which a floating action of a floating seal member is obtained for a long period of time and the sealing performance is not reduced. As an issue.
【０００４】[0004]
【課題を解決するための手段】如上の課題を解決するた
め、本発明によれば、回転機械のフローティングシール
は、回転機械のロータなどの回転体の外周面に所定の隙
間を有して遊嵌された円環状シール部材と、そのシール
部材を外側から取り囲む環状保持部材と、前記シール部
材の一方の半径方向面に接する支持手段を有し、その支
持手段が該シール部材の低圧側側面に正面が当接して密
封摺動面を形成する環状ホルダーと、一端が該ホルダー
の背面に連接され他端が前記環状保持部材に固定された
円筒状弾性スリーブとから形成されていることを特徴と
する。なお、前述の円筒状弾性スリーブがベローズ形状
に形成されると、円環状のシール部材の半径方向移動を
更に容易に許容して有利である。According to the present invention, there is provided a floating seal for a rotary machine having a predetermined clearance on an outer peripheral surface of a rotating body such as a rotor of the rotary machine. An annular seal member fitted, an annular holding member surrounding the seal member from the outside, and support means for contacting one radial surface of the seal member, the support means being provided on the low-pressure side surface of the seal member An annular holder having a front surface abutting to form a sealed sliding surface, and a cylindrical elastic sleeve having one end connected to the back surface of the holder and the other end fixed to the annular holding member. I do. In addition, it is advantageous that the above-mentioned cylindrical elastic sleeve is formed in a bellows shape, because the radial movement of the annular seal member can be more easily permitted.
【０００５】[0005]
【発明の実施の形態】以下、添付の図面を参照して本発
明の実施形態を説明する。尚、前述の従来装置に関する
図面を含め、全図に亘り同一部材には同一の符号を付す
こととする。先ず、図１を参照するに図示しない軸受に
より回転自在に支持されたタービンロータ１の端部に
は、フローティングシール面１ａが形成され、これを囲
んで円環状のシール部材１３が設けられる。このシール
部材１３の内径は、フローティングシール面１ａとの間
に好適な隙間が形成されるように僅かに大きい値となっ
ている。図示しないケーシング側に固定された環状保持
部材２１内周端側には、環状空間２３が形成され、この
中にシール部材１３の外側部分を収容している。環状空
間２３は図示のように段付きの形状になっており、支持
手段３０の弾性円筒状スリーブ３１の一端部が、シール
部材１３から離れた内側面に固定されている。円筒状ス
リーブ３１の他端は、シール部材１３の側面に当接する
摺動面を備えた環状ホルダー３３に繋がっている。環状
ホルダー３３の構造を更に説明すると、シール部材１３
の低圧側側面に当接する摺動面３３ａ，シール部材１３
の外周面の外側に突出してシール部材１３の半径方向移
動を規制するリップ部３３ｂ及び均圧孔３３ｃを有して
いる。更に環状ホルダー３３は、摺動面３３ａの外側に
環状凹み３３ｄを有し、均圧孔３３ｃに繋がっている。Embodiments of the present invention will be described below with reference to the accompanying drawings. Note that the same members are denoted by the same reference numerals throughout the drawings including the drawings related to the above-described conventional apparatus. First, a floating seal surface 1a is formed at an end of the turbine rotor 1 rotatably supported by a bearing (not shown in FIG. 1), and an annular seal member 13 is provided so as to surround the floating seal surface 1a. The inner diameter of the seal member 13 is a slightly large value so that a suitable gap is formed between the seal member 13 and the floating seal surface 1a. An annular space 23 is formed on the inner peripheral end side of the annular holding member 21 fixed to the casing (not shown), and accommodates the outer portion of the seal member 13 therein. The annular space 23 has a stepped shape as shown in the drawing, and one end of an elastic cylindrical sleeve 31 of the support means 30 is fixed to an inner surface remote from the seal member 13. The other end of the cylindrical sleeve 31 is connected to an annular holder 33 having a sliding surface that contacts the side surface of the seal member 13. The structure of the annular holder 33 will be further described.
Sliding surface 33a contacting the low pressure side surface of
And a lip portion 33b and a pressure equalizing hole 33c that protrude outside the outer peripheral surface of the seal member 13 and restrict the radial movement of the seal member 13. Further, the annular holder 33 has an annular recess 33d outside the sliding surface 33a, and is connected to the pressure equalizing hole 33c.
【０００６】次に前述のような構成のフローティングシ
ール２０の作用を図２を参照して説明する。回転流体機
械の運転中、内側には高圧ＰI，外側には低圧ＰOが発生
する。この差圧により、シール部材１３は低圧側に押さ
れて摺動面３３ａに押し付けられ、その面間に隙間は無
くなる。環状凹み３３ｄ内の流体は均圧孔３３ｃから外
部に流出するので、シール部材１３と環状ホルダー３３
との良好な接触は妨害されない。このため、高圧の流体
がシール部材１３の内周面とフローティングシール面１
ａとの間に入り込み、シール部材１３に芯合わせ作用が
生じて、シール部材１３とタービンロータ１とが同軸状
態になる。即ち、シール部材１３の内周面とフローティ
ングシール面１ａとの間の隙間量が全円周に亙り一様と
なり、良好なシールが得られる。摺動面３３ａが円滑な
間は、シール部材１３の半径方向変位は阻止されない。
しかしながら、運転が進み、摺動面３３ａの摩擦力が大
きくなると、浮上力Ｐに対して大きな摩擦抵抗力が作用
する。然るに、本実施例によれば、円筒状スリーブ３１
が弾性を有するように形成されているので、浮上力Ｐに
より２点鎖線の位置から実線位置に移動する。このよう
な円筒状スリーブ３１の変形により、シール部材１３の
内周面とタービンロータ１のフローティングシール面１
ａとの間の隙間が全円周において一様となり、良好なフ
ローティングシール作用が得られる。Next, the operation of the floating seal 20 configured as described above will be described with reference to FIG. During operation of the rotary fluid machine, high pressure P I is generated inside and low pressure P O is generated outside. Due to this pressure difference, the seal member 13 is pushed to the low pressure side and pressed against the sliding surface 33a, and there is no gap between the surfaces. Since the fluid in the annular recess 33d flows out of the pressure equalizing hole 33c to the outside, the seal member 13 and the annular holder 33
Good contact with is not disturbed. For this reason, the high-pressure fluid flows between the inner peripheral surface of the seal member 13 and the floating seal surface 1.
a, the centering action of the seal member 13 occurs, and the seal member 13 and the turbine rotor 1 are coaxial. That is, the amount of clearance between the inner peripheral surface of the seal member 13 and the floating seal surface 1a becomes uniform over the entire circumference, and a good seal is obtained. While the sliding surface 33a is smooth, the radial displacement of the seal member 13 is not prevented.
However, when the operation proceeds and the frictional force of the sliding surface 33a increases, a large frictional resistance acts on the floating force P. However, according to the present embodiment, the cylindrical sleeve 31
Is moved from the position indicated by the two-dot chain line to the position indicated by the solid line due to the levitation force P. Due to such deformation of the cylindrical sleeve 31, the inner peripheral surface of the seal member 13 and the floating seal surface 1 of the turbine rotor 1 are formed.
a becomes uniform over the entire circumference, and a good floating sealing action can be obtained.
【０００７】尚、前述の実施形態においては、シール部
材に当接する環状ホルダーを支持する支持手段に弾性円
筒状スリーブを用いたが、図３及び図４に示すように、
ベローズ部材５１を使用しても良い。この場合、支持手
段５０は、環状ホルダー５３と薄い金属板から形成され
たベローズ部材５１とから形成され、ベローズ部材５１
の右端（図において）は前述の円筒状スリーブ３１と同
様に保持部材４１に固定される。保持部材４１の環状空
間４３と摺動面５３ａ，リップ５３ｂ，均圧孔５３ｃ及
び環状凹み５３ｄを持つ環状ホルダー５３は、前述の実
施形態の環状空間２３と環状ホルダー３３にそれぞれ対
応するものであり、細部の形状寸法は異なるものの同様
の機能を有する。そして、ベローズ部材５１は、右側の
固定端を基端として半径方向に曲げ変形（撓み変形）を
生じ易いばかりでなく軸方向にも凹み易いので、シール
部材１３の半径方向及び軸方向の変位を徒に拘束せずに
環状ホルダー５３をこれに追従させる。このため、前述
の実施形態の場合と同様に、摺動面５３ａの摩擦抵抗力
が大きくなっても、適切に変形してシール部材１３の芯
合わせ作用を確実に行わしめると共に、摺動面５３ａと
シール部材１３の低圧側側面との密着を確実にし、良好
なシール性能を確保できる。In the above-described embodiment, the elastic cylindrical sleeve is used as the support means for supporting the annular holder abutting on the seal member. However, as shown in FIGS.
The bellows member 51 may be used. In this case, the support means 50 is formed by an annular holder 53 and a bellows member 51 formed of a thin metal plate,
Is fixed to the holding member 41 in the same manner as the cylindrical sleeve 31 described above. The annular space 43 of the holding member 41 and the annular holder 53 having the sliding surface 53a, the lip 53b, the equalizing hole 53c, and the annular recess 53d correspond to the annular space 23 and the annular holder 33 of the above-described embodiment, respectively. , And have similar functions, although the details and dimensions are different. The bellows member 51 not only tends to be bent in the radial direction with the fixed end on the right side as a base end but also easily dented in the axial direction, so that the displacement of the seal member 13 in the radial and axial directions is reduced. The annular holder 53 is made to follow this without being restrained. Therefore, as in the case of the above-described embodiment, even if the frictional resistance of the sliding surface 53a becomes large, the sliding surface 53a is appropriately deformed to ensure the centering action of the seal member 13, and the sliding surface 53a And the low-pressure side surface of the seal member 13 can be surely adhered to ensure good sealing performance.
【０００８】[0008]
【発明の効果】以上説明したように、本発明によれば、
タービンロータ等の回転体に浮動状態で設けられるシー
ル部材を、半径方向に撓み易い円筒状スリーブ又はベロ
ーズ部材を有する支持手段により半径方向に支持したの
で、支持手段とシール部材との間に働く摩擦抵抗力が大
きくなってもシール部材の芯合わせ作用を妨げないか
ら、長期に亙って良好なフローティングシール性能を維
持することができる。As described above, according to the present invention,
Since the seal member provided in a floating state on a rotating body such as a turbine rotor is supported in the radial direction by the support means having a cylindrical sleeve or a bellows member which is easily bent in the radial direction, friction acting between the support means and the seal member is provided. Even if the resistance increases, the centering action of the seal member is not hindered, so that good floating seal performance can be maintained for a long period of time.
【図１】本発明の実施形態を示す部分断面図である。FIG. 1 is a partial sectional view showing an embodiment of the present invention.
【図２】前記実施形態の作用状態を示す作用説明図であ
る。FIG. 2 is an operation explanatory view showing an operation state of the embodiment.
【図３】前記実施形態の一部を改変した改変実施形態を
示す部分断面図である。FIG. 3 is a partial sectional view showing a modified embodiment in which a part of the embodiment is modified.
【図４】前記改変実施形態の作用状態を示す作用説明図
である。FIG. 4 is an operation explanatory view showing an operation state of the modified embodiment.
【図５】回転機械の一例であるタービンのタービンロー
タの概念図である。FIG. 5 is a conceptual diagram of a turbine rotor of a turbine as an example of a rotating machine.
【図６】前記タービンに使用されている従来構造のフロ
ーティングシールを示す部分断面図である。FIG. 6 is a partial cross-sectional view showing a floating seal having a conventional structure used in the turbine.
【図７】従来構造のフローティングシールの不具合状況
を説明する作用説明図である。FIG. 7 is an operation explanatory view for explaining a problem state of a floating seal having a conventional structure.
１ タービンロータ １３ シール部材 ２０ フローティングシール ２１ 保持部材 ２３ 環状空間 ３０ 支持手段 ３１ 円筒状スリーブ ３３ 環状ホルダー ３３ａ 摺動面 ３３ｂ リップ部 ３３ｃ 均圧孔 ３３ｄ 環状凹み ４０ フローティングシール ４１ 保持部材 ４３ 環状空間 ５０ 支持手段 ５１ ベローズ部材 ５３ 環状ホルダー ５３ａ 摺動面 ５３ｂ リップ部 ５３ｃ 均圧孔 ５３ｄ 環状凹み DESCRIPTION OF SYMBOLS 1 Turbine rotor 13 Seal member 20 Floating seal 21 Holding member 23 Annular space 30 Supporting means 31 Cylindrical sleeve 33 Annular holder 33a Sliding surface 33b Lip portion 33c Equalizing hole 33d Annular recess 40 Floating seal 41 Holding member 43 Annular space 50 Support Means 51 Bellows member 53 Annular holder 53a Sliding surface 53b Lip portion 53c Equalizing hole 53d Annular dent
Claims (2)
嵌された円環状シール部材と、該シール部材を外側から
取り囲む環状保持部材と、前記シール部材の一方の半径
方向面に接する支持手段を有する回転機械のフローティ
ングシールであって、 前記シール部材の低圧側側面に正面が当接して密封摺動
面を形成する環状ホルダーと、一端が該ホルダーの背面
に連接され他端が前記環状保持部材に固定された円筒状
弾性スリーブとから前記支持手段が形成されていること
を特徴とする回転機械のフローティングシール。An annular seal member loosely fitted with a predetermined gap to an outer peripheral surface of a rotating body, an annular holding member surrounding the seal member from outside, and one radial surface of the seal member. A floating seal of a rotary machine having a supporting means that is in contact therewith, an annular holder having a front surface abutting against a low-pressure side surface of the seal member to form a sealing sliding surface, one end connected to the back surface of the holder, and the other end connected. A floating seal for a rotary machine, wherein the support means is formed from a cylindrical elastic sleeve fixed to the annular holding member.
ーズ形状に形成されていることを特徴とする請求項１記
載の回転機械のフローティングシール。2. The floating seal according to claim 1, wherein said cylindrical elastic sleeve of said support means is formed in a bellows shape.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11993899A JP3912926B2 (en) | 1999-04-27 | 1999-04-27 | Floating machine floating seal |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11993899A JP3912926B2 (en) | 1999-04-27 | 1999-04-27 | Floating machine floating seal |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2000310342A true JP2000310342A (en) | 2000-11-07 |
| JP3912926B2 JP3912926B2 (en) | 2007-05-09 |
Family
ID=14773892
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11993899A Expired - Fee Related JP3912926B2 (en) | 1999-04-27 | 1999-04-27 | Floating machine floating seal |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3912926B2 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2017014316A1 (en) * | 2015-07-23 | 2017-01-26 | 株式会社 豊田自動織機 | Centrifugal compressor |
| WO2018155315A1 (en) | 2017-02-22 | 2018-08-30 | イーグル工業株式会社 | Seal device |
| WO2018155318A1 (en) | 2017-02-22 | 2018-08-30 | イーグル工業株式会社 | Seal device |
| CN112012954A (en) * | 2020-09-08 | 2020-12-01 | 北京星际荣耀空间科技有限公司 | Turbo pump sealing mechanism and turbo pump |
| JP2021510796A (en) * | 2018-01-26 | 2021-04-30 | ターボデン・ソチエタ・ペル・アツィオーニＴｕｒｂｏｄｅｎ Ｓ．Ｐ．Ａ． | Turbo machine with fluid seal device |
| US11549589B2 (en) | 2018-02-21 | 2023-01-10 | Eagle Industry Co., Ltd. | Mechanical seal |
| US11739844B2 (en) | 2016-09-14 | 2023-08-29 | Eagle Industry Co., Ltd. | Mechanical seal |
-
1999
- 1999-04-27 JP JP11993899A patent/JP3912926B2/en not_active Expired - Fee Related
Cited By (12)
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|---|---|---|---|---|
| WO2017014316A1 (en) * | 2015-07-23 | 2017-01-26 | 株式会社 豊田自動織機 | Centrifugal compressor |
| JP2017025822A (en) * | 2015-07-23 | 2017-02-02 | 株式会社豊田自動織機 | Centrifugal compressor |
| US10514041B2 (en) | 2015-07-23 | 2019-12-24 | Kabushiki Kaisha Toyota Jidoshokki | Centrifugal compressor |
| US11739844B2 (en) | 2016-09-14 | 2023-08-29 | Eagle Industry Co., Ltd. | Mechanical seal |
| WO2018155315A1 (en) | 2017-02-22 | 2018-08-30 | イーグル工業株式会社 | Seal device |
| WO2018155318A1 (en) | 2017-02-22 | 2018-08-30 | イーグル工業株式会社 | Seal device |
| US11085539B2 (en) | 2017-02-22 | 2021-08-10 | Eagle Industry Co., Ltd. | Seal device |
| JP2021510796A (en) * | 2018-01-26 | 2021-04-30 | ターボデン・ソチエタ・ペル・アツィオーニＴｕｒｂｏｄｅｎ Ｓ．Ｐ．Ａ． | Turbo machine with fluid seal device |
| JP7308840B2 (en) | 2018-01-26 | 2023-07-14 | ターボデン・ソチエタ・ペル・アツィオーニ | Turbomachine with fluid sealing device |
| US11549589B2 (en) | 2018-02-21 | 2023-01-10 | Eagle Industry Co., Ltd. | Mechanical seal |
| CN112012954A (en) * | 2020-09-08 | 2020-12-01 | 北京星际荣耀空间科技有限公司 | Turbo pump sealing mechanism and turbo pump |
| CN112012954B (en) * | 2020-09-08 | 2022-04-12 | 北京星际荣耀空间科技股份有限公司 | Turbo pump sealing mechanism and turbo pump |
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| JP3912926B2 (en) | 2007-05-09 |
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