WO2009054560A1 - Joint de roulement pour turbine à gaz - Google Patents

Joint de roulement pour turbine à gaz Download PDF

Info

Publication number
WO2009054560A1
WO2009054560A1 PCT/KR2007/005415 KR2007005415W WO2009054560A1 WO 2009054560 A1 WO2009054560 A1 WO 2009054560A1 KR 2007005415 W KR2007005415 W KR 2007005415W WO 2009054560 A1 WO2009054560 A1 WO 2009054560A1
Authority
WO
WIPO (PCT)
Prior art keywords
foil
porous
rotating shaft
porous foil
bearing
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.)
Ceased
Application number
PCT/KR2007/005415
Other languages
English (en)
Inventor
Dong Jin Park
Yong Bok Lee
Chang Ho Kim
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Korea Institute of Science and Technology KIST
Original Assignee
Korea Institute of Science and Technology KIST
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Korea Institute of Science and Technology KIST filed Critical Korea Institute of Science and Technology KIST
Publication of WO2009054560A1 publication Critical patent/WO2009054560A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F16C17/024—Sliding-contact bearings for exclusively rotary movement for radial load only with flexible leaves to create hydrodynamic wedge, e.g. radial foil 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/74—Sealings of sliding-contact 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines

Definitions

  • the present invention relates to a bearing seal for a gas turbine.
  • the present invention can reduce axial leakage of a working gas of a turbine and can support the vertical loads and shear forces efficiently.
  • a gas turbine rotational device has an in-line gas flow through a gas inlet, a compressor, a combustor, a turbine and outlet. Leakage of the working gas between a rotating shaft of the turbine (or the compressor) and a housing surrounding the rotating shaft deteriorates efficiency of the rotational device.
  • a bearing seal reduces axial leakage of the working gas in the rotational device.
  • a brush seal is used for reducing such axial leakage.
  • FIG. 1 is a sectional view showing a prior art brush seal of a bearing.
  • Fig. 2 is a perspective view partially showing the brush seal of Fig. 1.
  • a brush seal (3) is mounted to the inner surface of a tubular housing (1) at which a rotating shaft (2) is positioned.
  • the brush seal (3) is made of many setae, one end being fixed to the housing (1) and the other end being free.
  • One end of the brush seal (3) is fixed to a brush holder (4) mounted to the housing (1). The other end, which is free, contacts an outer surface of the rotating shaft (2).
  • the brush seal (3) can prevent the working gas from leaking.
  • the brush seal (3) can be easily worn out by contact with the rotating shaft (2).
  • leakage prevention may be deteriorated very rapidly.
  • the rotational device may have low efficiency because the rotation may be resisted by the frictional force between the brush seal (3) and the rotating shaft (1) when they contact each other. Disclosure of Invention
  • the present invention is conceived to solve the above problems.
  • the present invention may be used in a dynamic pressure bearing that has less friction loss than a bearing having a brush seal.
  • a porous foil with a density ratio varying in an axial direction is disposed on the bearing for adjusting a gap between a surface of a bearing seal and a rotating shaft changeable in proportion to the rotating speed.
  • the present invention may provide a dynamic pressure bearing seal of a gas turbine that seals the axial leakage of the working gas efficiently.
  • a bearing seal for a gas turbine of the present invention disposed on the inner surface of a bearing housing wherein a rotating shaft is positioned at the center of the bearing housing.
  • the bearing seal comprises an elastic porous foil for adjusting leakage of a working gas through the space between the rotating shaft and the bearing housing with a density ratio of the porous foil increasing in a direction of gas inflow.
  • the porous foil is deformed elastically by the dynamic pressure of the working gas leaked around the rotating shaft during rotation of the rotating shaft for making a gap between the porous foil and the rotating shaft.
  • the porous foil may include a single porous foil element having a density varying continuously.
  • the porous foil may include a plurality of porous foil elements having different density ratios to each other, the porous foil elements being disposed along the rotating shaft.
  • the bearing seal further comprises bump foils disposed at both sides of the porous foil element (or elements).
  • a top foil can be arranged on the surfaces of the porous foil and the bump foil facing the rotating shaft.
  • a gas film formed by the leaked working gas is disposed between the top foil and the rotating shaft during the rotation of the shaft.
  • a receiving groove for receiving the porous foil and the bump foil may be formed on the bearing housing.
  • the porous foil and the bump foil are received in the receiving groove and a shim foil is disposed between the porous and bump foils collectively, and the bearing housing during rotation of the shaft.
  • the bearing seal of a gas turbine according to the present invention can improve seal's performance of a dynamic pressure bearing while the porous foil, which has a density ratio varying along the rotating shaft, is positioned around a rotating shaft.
  • the bump foil is used with the porous foil.
  • seal performance, vibration damping performance, and shear force supporting performance may be improved.
  • FIG. 1 is a sectional view illustrating a brush seal of a bearing of the prior art.
  • FIG. 2 is a perspective view partially illustrating a brush seal of Fig. 1.
  • FIG. 3 is a perspective view illustrating a bearing housing having a bearing seal according to the present invention, the bearing housing being partially removed.
  • FIG. 4 is a front sectional view illustrating an embodiment of a bearing seal according to the present invention.
  • Fig. 5 is a graph illustrating the relationship between density ratio and hardness of a porous foil.
  • Fig. 6 is a side-sectional view illustrating the bearing seal of Fig. 4, a shear force being applied to the bearing seal.
  • Fig. 7 is a side-sectional view illustrating the bearing seal of Fig. 4, a load and a shear force being applied to the bearing seal.
  • FIG. 8 is a side-sectional view illustrating an embodiment having a plurality of porous foils, each having different a density ratio, bump foils being coupled at both ends of the porous foils respectively.
  • FIG. 3 is a perspective view illustrating a bearing housing having a bearing seal according to the present invention, the bearing housing being partially removed.
  • the present invention relates to a seal of dynamic pressure bearing as illustrated in the drawing.
  • the bearing seal can adjust the amount of a working gas leaked in an axial direction between a rotating shaft (10) and a bearing housing (20).
  • Two porous foil elements (30a, 30b) form a porous foil (30).
  • the elements (30a, 30b) are positioned on an inner surface of the bearing housing (20) around the rotating shaft (10).
  • Each of the elements (30a, 30b) has a different density ratio in an axial direction. Density ratio of the porous foil (30) increases along working gas inflow direction.
  • the porous elements (30a, 30b) are manufactured of metal chips pressure-molded under a predetermined heat and pressure in a hot plate.
  • the present invention is not limited to forming the porous foil (30) by two porous foil elements (30a, 30b) as described in the above embodiment. It is understood that the porous foil (30) may be formed by an arrangement of more than two porous foil elements, or by a porous foil element having a density ratio varying continuously.
  • Fig. 4 is a front sectional view illustrating an embodiment of a bearing seal according to the present invention.
  • the bearing seal (30) comprises a porous foil (30) positioned on the inner surface of the bearing housing (20), a bump foil (40) disposed on each of the axial front end and rear end of the porous foil (30), and a top foil (50) forming a gas film of working gas leaked between the top foil (50) and the rotating shaft (10).
  • a shim foil (60) is positioned on the lower surface of the porous foil (30) and the bump foil (40). The shim foil (60) protects the bearing housing (20) surface and produces friction between the porous foil (30) and the bump foil (40).
  • Fig. 4 illustrates a sectional view of the bearing and the rotating shaft in a radial direction (density ratio of the porous foil (30) not shown). The density ratio of the porous foil
  • the porous foil (30), the bump foil (40), the top foil (50) and the shim foil (60) may be manufactured from a beryllium copper, stainless steel, Inconel series steal material, or the like.
  • one end of each foil is fixed to the bearing housing (20) and the other end is free.
  • the bearing housing (20) has a receiving groove (21) for receiving the porous foil (30) and the bump foil (40).
  • the shim foil (60) can be received in the receiving groove (21).
  • the porous foil (30) has a principal function to reduce axial leakage of the working gas of the gas turbine.
  • the amount of working gas leakage can be controlled by adjusting the density ratio of the porous foil (30).
  • Fig. 5 is a graph illustrating a relationship between a density ratio and hardness of a porous foil. As shown in Fig. 5, the hardness can be changed in proportion to the density ratio of the porous material. It is desired that hardness of the porous foil (30) and the bump foil (40) are the same.
  • the porous foil (30) is made from Inconel or stainless steel in this illustrative embodiment.
  • the hardness of the bump foil (40) should be in the range from 8 x 10 10 [N/m 3 ] to 1.1 x 10 n [N/m 3 ].
  • the preferred density ratio of the porous foil (30) is about 0.7.
  • the porous foil (30) contacts the rotating shaft (10) when the rotating shaft (10) is in a stationary state.
  • the rotation of the rotating shaft (10) generates dynamic pressure of the gas, which pushes the porous foil (30) toward the bearing housing (20).
  • the porous foil (30) and the rotating shaft (10) have a gap therebetween without contact. That is, the dynamic pressure applied around the rotating shaft (10) acts as a plain seal while the porous foil (30) acts as a brush seal.
  • the porous foil can reduce axial leakage of the working gas efficiently.
  • the density ratio of the porous foil (30) varies along the axial direction for adjusting the gap between the top foil (50) and the rotating shaft (10) in proportion to the rotating speed of the rotating shaft (10).
  • the density ratio increases along the working gas inflow direction.
  • the gap between the top foil (50) and rotating shaft (10) may be narrower at high speeds than in low speeds. Consequently, friction between the rotating shaft (10) and the seal can be considerably reduced by the wider gap in an initial rotating state, and the leakage of working gas of a gas turbine can be considerably reduced by the narrower gap in proportion to increasing rotation speed. Further, less friction results in improved durability
  • Fig. 6 is a side-sectional view illustrating the bearing seal of Fig. 4, a shear force being applied thereto.
  • working gas is leaked between the top foil (50) of the bearing seal and the rotating shaft and a shear force is produced like the arrow.
  • the porous foil (30) There are several vesicles in the porous foil (30), making it difficult to mount the fastener for fastening the porous foil (40) to the bearing housing (20). Further, it may be fragile to shear force since its deformation direction is irregular.
  • the bump foil (40) mounted on the front end and the rear end of the porous foil (30) can support the shear force efficiently.
  • Fig. 7 is a side-sectional view illustrating the bearing seal of Fig. 4, a load and a shear force being applied thereto.
  • the hardness of the bump foil (40) is close to that of the porous foil (30) for supporting the vertical load efficiently.
  • vertical loads and shear forces act simultaneously during the rotation of the rotating shaft.
  • the bearing seal can considerably reduce axial leakage of working gas and the seal performance can be improved when it uses the porous foil (30).
  • One end of the bump foil (40) can be pin jointed or welded to the inner surface of the bearing housing (20).
  • the bump foil (40) can be mounted on the bearing housing (20) strongly and can support the axial shear force.
  • the density ratio of the porous foil varies along the axial direction for maximizing sealing function.
  • the bump foil (40) is positioned at both ends of the porous foil (30) for maximizing vibration damping effects and supporting axial shear force well.
  • Fig. 8 is a lateral sectional view illustrating an embodiment having a plurality of porous foils, each having a different density ratio with respect to each other. Bump foils are coupled at both ends of the porous foils respectively.
  • the bump foils (140a, 140b) are positioned at both ends of the porous foil elements (130a, 130b) respectively, and density ratios of the porous foil elements are different to each other.
  • the characteristics of each bump foil may match those of the corresponding porous foil.
  • the multiple porous foil elements having density ratios different to each other are arranged.
  • the present invention is not limited to these embodiments.
  • the present invention may have a porous foil having a density ratio continuously varying along an axial direction.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Support Of The Bearing (AREA)

Abstract

La présente invention concerne un joint de roulement pour turbine à gaz permettant de réduire la fuite axiale d'un gaz de travail d'une turbine et le support efficace de charges verticales et de forces de cisaillement. Le joint est disposé sur une face intérieure d'un logement de roulement où est positionné un arbre rotatif au centre du logement de roulement. Le joint de roulement comporte un film poreux élastique pour ajuster la fuite d'un gaz de travail à travers l'espace entre l'arbre rotatif et le logement de roulement, un rapport de densité du film poreux s'accroissant selon la direction du débit entrant de gaz. Le film poreux subit une déformation élastique par la pression dynamique du gaz de travail en fuite autour de l'arbre rotatif lors de la rotation de l'arbre rotatif pour créer un espace entre le film poreux et l'arbre rotatif.
PCT/KR2007/005415 2007-10-23 2007-10-31 Joint de roulement pour turbine à gaz Ceased WO2009054560A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR20070106396A KR20090040956A (ko) 2007-10-23 2007-10-23 가스터빈용 베어링 시일
KR10-2007-0106396 2007-10-23

Publications (1)

Publication Number Publication Date
WO2009054560A1 true WO2009054560A1 (fr) 2009-04-30

Family

ID=40579652

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2007/005415 Ceased WO2009054560A1 (fr) 2007-10-23 2007-10-31 Joint de roulement pour turbine à gaz

Country Status (2)

Country Link
KR (1) KR20090040956A (fr)
WO (1) WO2009054560A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103438091A (zh) * 2013-08-02 2013-12-11 湖南大学 具有金属橡胶和弹性箔片复合支承结构的空气动压轴承
JP2018028387A (ja) * 2016-08-16 2018-02-22 ハミルトン・サンドストランド・コーポレイションＨａｍｉｌｔｏｎ Ｓｕｎｄｓｔｒａｎｄ Ｃｏｒｐｏｒａｔｉｏｎ 軸受および回転機
EP3201439A4 (fr) * 2014-09-29 2018-05-30 New Way Machine Components, Inc. Palier de butée sous la forme d'un joint d'étanchéité
CN113513594A (zh) * 2021-05-20 2021-10-19 中国计量大学 具有动压浮动密封坝的箔片端面气膜密封结构

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5993515A (ja) * 1982-11-17 1984-05-30 Aisin Seiki Co Ltd タ−ボチヤ−ジヤ用軸受装置
JPS6174910A (ja) * 1984-09-18 1986-04-17 Ishikawajima Harima Heavy Ind Co Ltd 流体軸受構造
JPH02173416A (ja) * 1988-12-27 1990-07-04 Hitachi Chem Co Ltd 静圧空気軸受
JPH09151941A (ja) * 1995-11-30 1997-06-10 Hitachi Powdered Metals Co Ltd 複合型多孔質軸受及びその製造方法
JPH09251252A (ja) * 1996-03-15 1997-09-22 Ricoh Co Ltd 加圧ローラ
JP2002023541A (ja) * 2000-07-03 2002-01-23 Minolta Co Ltd 離型剤塗布ローラ
JP2005221002A (ja) * 2004-02-05 2005-08-18 Nsk Ltd 気体絞り層の形成方法

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5993515A (ja) * 1982-11-17 1984-05-30 Aisin Seiki Co Ltd タ−ボチヤ−ジヤ用軸受装置
JPS6174910A (ja) * 1984-09-18 1986-04-17 Ishikawajima Harima Heavy Ind Co Ltd 流体軸受構造
JPH02173416A (ja) * 1988-12-27 1990-07-04 Hitachi Chem Co Ltd 静圧空気軸受
JPH09151941A (ja) * 1995-11-30 1997-06-10 Hitachi Powdered Metals Co Ltd 複合型多孔質軸受及びその製造方法
JPH09251252A (ja) * 1996-03-15 1997-09-22 Ricoh Co Ltd 加圧ローラ
JP2002023541A (ja) * 2000-07-03 2002-01-23 Minolta Co Ltd 離型剤塗布ローラ
JP2005221002A (ja) * 2004-02-05 2005-08-18 Nsk Ltd 気体絞り層の形成方法

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103438091A (zh) * 2013-08-02 2013-12-11 湖南大学 具有金属橡胶和弹性箔片复合支承结构的空气动压轴承
EP3201439A4 (fr) * 2014-09-29 2018-05-30 New Way Machine Components, Inc. Palier de butée sous la forme d'un joint d'étanchéité
US10100932B2 (en) 2014-09-29 2018-10-16 New Way Machine Components, Inc. Thrust bearing as a seal
JP2018028387A (ja) * 2016-08-16 2018-02-22 ハミルトン・サンドストランド・コーポレイションＨａｍｉｌｔｏｎ Ｓｕｎｄｓｔｒａｎｄ Ｃｏｒｐｏｒａｔｉｏｎ 軸受および回転機
JP7000058B2 (ja) 2016-08-16 2022-02-10 ハミルトン・サンドストランド・コーポレイション 軸受および回転機
JP2022036127A (ja) * 2016-08-16 2022-03-04 ハミルトン・サンドストランド・コーポレイション 軸受および回転機
JP7350833B2 (ja) 2016-08-16 2023-09-26 ハミルトン・サンドストランド・コーポレイション 軸受および回転機
CN113513594A (zh) * 2021-05-20 2021-10-19 中国计量大学 具有动压浮动密封坝的箔片端面气膜密封结构
CN113513594B (zh) * 2021-05-20 2024-03-19 中国计量大学 具有动压浮动密封坝的箔片端面气膜密封结构

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