WO2000025035A1 - Hydrodynamic journal bearing, particularly for steam turbines - Google Patents
Hydrodynamic journal bearing, particularly for steam turbines Download PDFInfo
- Publication number
- WO2000025035A1 WO2000025035A1 PCT/PL1999/000035 PL9900035W WO0025035A1 WO 2000025035 A1 WO2000025035 A1 WO 2000025035A1 PL 9900035 W PL9900035 W PL 9900035W WO 0025035 A1 WO0025035 A1 WO 0025035A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- bearing
- sliding
- radii
- sliding surfaces
- extent
- Prior art date
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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/108—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid with a plurality of elements forming the bearing surfaces, e.g. bearing pads
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
- F01D25/166—Sliding contact bearing
-
- 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
- F16C17/028—Sliding-contact bearings for exclusively rotary movement for radial load only with fixed wedges to generate hydrodynamic pressure, e.g. multi-lobe 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
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/1075—Wedges, e.g. ramps or lobes, for generating pressure
Definitions
- This invention relates to hydrodynamic journal bearings suitable especially for supporting steam turbine shafts.
- the elliptic bearing called also "lemon bearing” is also well known as a stabilising one. It comprises a bipartite bearing bush bisected by a horizontal plane. Each of bush parts has a cylindrical sliding lobe. The lobes have sliding surfaces shaped cylindrically and with axes lying on opposite sides of the horizontal plane dividing the bearing bush. While operating, two oil film wedges at opposite sides are formed maintaining shafts stability and preventing its vibration. However, the features of this bearing worsen significantly when the load direction varies from the direction perpendicular to the dividing plane.
- Hydrodynamic bearing having three sliding surfaces taking each 120° in extent is theoretically a more advantageous one.
- manufacturing and assembly difficulties cause that this bearing type has found no technical application so far.
- Hydrodynamic bearing known from the U.S. Patent No. 3,680,932 for supporting shafts of large machines like turbines and generators has a bipartite bearing bush divided by a horizontal plane.
- the bottom bush part has its sliding lobe extended through an arc of about 180° and the top bush part has two sliding lobes, each of about 90° in extent.
- the sliding lobes are separated by axial grooves lying along the width of the sliding surface. Lubricating oil is supplied under pressure to each of these grooves.
- Each lobe has on its sliding surface a circumferentially extended recess, tapered along the arc.
- the width of the recess is less than the width of the sliding surface. It is placed in the middle of the surface.
- the recess begins from the adjacent axial groove and there is its deepest part.
- the recess' depth decreases in the direction of shaft rotation.
- the recesses have their inner surfaces shaped cylindrically and their axes do not coincide with the bearing bush central axis. But typically they are still placed either on the horizontal or on the vertical middle plane of the bearing.
- Different alternative designs of the bearing have also circumferential grooves on its sliding lobes enabling oil flow from one axial groove to another.
- the bearing has improved stabilising features when compared with the "lemon bearing".
- its start up features become worse when the bearing is heavy loaded.
- large recess area causes decrease of the hydrostatic oil lifting efficiency (using oil under high pressure) and increases risk of seizure when the machine is starting up or coasting.
- the design of the bearing consisting of two bearing bush parts and the present manufacturing technology status one may imply that in reality only a bearing having two sliding lobes can be produced. It would have features similar to those of the "lemon bearing". All this caused that the bearing known from the U.S. Patent No. 3,680,932 did not widespread.
- the presented invention relates to the hydrodynamic journal bearing having three sliding lobes with improved stabilising features when operating under high sliding speed.
- the bearing can be heavy loaded in start up and in coasting processes and may commonly be used to substitute the "lemon bearing" in existing ma- chines. Especially in steam turbines.
- the bearing has three sliding lobes covering three separate parts of the bearing bush.
- the bottom bush part takes 180° in extent and the two other parts take each 90° in extent.
- Sliding surfaces of the lobes are shaped cylindrically. To the advantage they all have equal radii. But at least in two of them the radii have their origins not lying on the bearing axis and they have different eccentricity amounts.
- At least one sliding surface axis is lying eccentrically on a plane including the bearing axis. But the plane is turned around the bearing axis by amount of ⁇ in the shaft direction of rotation.
- the bearing having its bush divided in segments of 180° and twice of 90° is characterised by simplified manufacturing and assembly technology when compared with known bearings having three sliding surfaces.
- the bearing design with a bottom bush part of 180° in extent allows its application in existing bearing nests of present operating turbines where "lemon bearings" have been used.
- Fig. 1 shows bearing's longitidunal section
- fig. 3 shows schematically the geometry of three sliding lobes and of their sliding surfaces.
- the bearing bush consists of three segments 1 , 2 and 3.
- the bottom segment 1 takes 180° in extent and the upper segment 2 on the right and the upper segment 3 on the left take each 90° in extent.
- Segments 1 , 2 and 3 are joined together by fitted bolts 4.
- the segments of the bearing bush are covered by sliding lobes 5, 6, 7 with specially shaped sliding surfaces 8, 9, 10.
- Sliding surfaces 8, 9, 10 are shaped by radii R having equal lengths and having origins at points 11 , 12, 13 which lie eccentrically to the geometrical centre of the bearing bush and have different eccentricities ⁇ and are placed on lines 15, 16 and 17.
- Lines 15, 16 and 17 go through centre point 14 of the bearing and are created by rotation of symmetry axes 18, 19, 20 of sliding surfaces arcs 8, 9, 10 by angle ⁇ in the rotation direction of the shaft 21.
- the origin 11 of radius R1 of sliding surface 8 is placed at the distance ⁇ 1 from centre 14 of the bearing bush and is rotated by angle ⁇ 1 starting from symmetry axis 18 of sliding lobe 8 in the rotation direction of the shaft 21.
- Origin 12 of radius R2 of sliding surface 9 is placed at the distance ⁇ 2 from centre 14 and is rotated by angle ⁇ 2 in the rotation direction of the shaft 21.
- origin 13 of radius R3 of sliding surface 10 is placed at the distance ⁇ 3 from centre 14 and rotated.
- Lubricating oil is supplied to sliding surfaces through hole 22, through three oil pockets 23 and through circumferential groove 24, which connects pockets 23.
- Amounts of sliding surface angular extension may vary in wide range from 30° to 180° for segment 1 and from 25° to 90° for segments 2 and 3 and depend on requirements to the bearing and the operating conditions.
- the set of geometrical quantities - radii R and polar coordinates ⁇ , ⁇ - depends on requirements posed on bearing features like high critical turning speed, high damping abilities for vibrations and loading capabilities during starting up and coasting processes. They also depend on the length to width ratio of the bearing, bearing clearance, oil viscosity and the shafts turning speed.
- the optimum bearing design for specified applications may be found by calculations made using computational programs based on hydrodynamic lubrication theory.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Sliding-Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Abstract
The bearing has three sliding surfaces (8, 9, 10) in form of three sliding lobes (5, 6, 7), covering separate bearing bush segments of which one takes 180° in extent and the other two take each 90° in extent. The sliding surfaces (8, 9, 10) are shaped by radii (R). At least two of the radii (R) have their origins displaced from the bearing bush center (14) by different amounts (ε). At least one of the radii (R) has its origin on lines (15, 16, 17). Lines (15, 16, 17) are going through the bearing bush centre (14) and are rotated by angles (α) measured from symmetry axes (18, 19, 20) of sliding lobes (8, 9, 10) in the rotation direction of shaft (21).
Description
HYDRODYNAMIC JOURNAL BEARING, PARTICULARLY FOR STEAM TURBINES
FIELD OF THE INVENTION
This invention relates to hydrodynamic journal bearings suitable especially for supporting steam turbine shafts.
BACKGROUND OF THE INVENTION
Typically, symptoms of unstable shaft operation occur in the bearings in case of high sliding velocity and low bearing load. As a result anti-vibration bearings find their application in steam turbines and other rotating machines.
The elliptic bearing called also "lemon bearing" is also well known as a stabilising one. It comprises a bipartite bearing bush bisected by a horizontal plane. Each of bush parts has a cylindrical sliding lobe. The lobes have sliding surfaces shaped cylindrically and with axes lying on opposite sides of the horizontal plane dividing the bearing bush. While operating, two oil film wedges at opposite sides are formed maintaining shafts stability and preventing its vibration. However, the features of this bearing worsen significantly when the load direction varies from the direction perpendicular to the dividing plane.
Hydrodynamic bearing having three sliding surfaces taking each 120° in extent is theoretically a more advantageous one. However, manufacturing and assembly difficulties cause that this bearing type has found no technical application so far.
Hydrodynamic bearing known from the U.S. Patent No. 3,680,932 for supporting shafts of large machines like turbines and generators has a bipartite bearing bush divided by a horizontal plane. In one of alternative bearing design versions the bottom bush part has its sliding lobe extended through an arc of about 180° and the top bush part has two sliding lobes, each of about 90° in extent. The sliding lobes are separated by axial grooves lying along the width of the sliding surface. Lubricating oil is supplied under pressure to each of these grooves. Each lobe has on its sliding surface a circumferentially extended recess, tapered along the arc. The width of the recess is less than the width of the sliding surface. It is placed in the middle of the surface. The recess begins from the adjacent axial groove and there is its deepest part. The recess' depth decreases in the direction of shaft rotation. The recesses have their inner surfaces shaped cylindrically and their axes do not coincide with the bearing bush central axis. But typically they are still placed either on the horizontal or on the vertical middle plane of the bearing. Different alternative designs of the bearing have also circumferential grooves on its sliding lobes enabling oil flow from one axial groove to another. Having three sliding lobes with tapered recesses the bearing has improved stabilising features when compared with the "lemon bearing". However, its start up features become worse when the bearing is heavy loaded. Especially when the tapered recess covers a big part of the lobe surface, large recess area causes decrease of the hydrostatic oil lifting efficiency (using oil under high pressure) and increases risk of seizure when the machine is starting up or coasting. Taking into consideration the design of the bearing consisting of two bearing bush parts and the present manufacturing technology status one may imply that in reality only a bearing having two sliding lobes can be produced. It would have features similar to those of the "lemon bearing". All this caused that the bearing known from the U.S. Patent No. 3,680,932 did not widespread.
DESCRIPTION OF THE INVENTION
The presented invention relates to the hydrodynamic journal bearing having three sliding lobes with improved stabilising features when operating under high sliding speed. The bearing can be heavy loaded in start up and in coasting processes and may commonly be used to substitute the "lemon bearing" in existing ma- chines. Especially in steam turbines.
The bearing has three sliding lobes covering three separate parts of the bearing bush. The bottom bush part takes 180° in extent and the two other parts take each 90° in extent. Sliding surfaces of the lobes are shaped cylindrically. To the advantage they all have equal radii. But at least in two of them the radii have their origins not lying on the bearing axis and they have different eccentricity amounts. At least one sliding surface axis is lying eccentrically on a plane including the bearing axis. But the plane is turned around the bearing axis by amount ofα in the shaft direction of rotation.
Eccentricities of sliding surface axes form tapered slots between the sliding surfaces and the shaft surface, taking all together more than a half of the total sliding surface circumference in extent. As a result hydrodynamic pressure appears in the slots and this increases the bearing load capability in the gravity direction and in perpendicular directions, too. Computational simulations have shown that also the vibration damping ability improves and that the critical turning speed value increase to the advantage.
The bearing having its bush divided in segments of 180° and twice of 90° is characterised by simplified manufacturing and assembly technology when compared with known bearings having three sliding surfaces. The bearing design with a bottom bush part of 180° in extent allows its application in existing bearing nests of present operating turbines where "lemon bearings" have been used.
BRIEF DESCRIPTION OF THE DRAWINGS
The design of the bearing can be explained on the example shown in fig. 1 with its cross section. Fig. 2 shows bearing's longitidunal section and fig. 3 shows schematically the geometry of three sliding lobes and of their sliding surfaces.
The bearing bush consists of three segments 1 , 2 and 3. The bottom segment 1 takes 180° in extent and the upper segment 2 on the right and the upper segment 3 on the left take each 90° in extent. Segments 1 , 2 and 3 are joined together by fitted bolts 4. The segments of the bearing bush are covered by sliding lobes 5, 6, 7 with specially shaped sliding surfaces 8, 9, 10. Sliding surfaces 8, 9, 10 are shaped by radii R having equal lengths and having origins at points 11 , 12, 13
which lie eccentrically to the geometrical centre of the bearing bush and have different eccentricities ε and are placed on lines 15, 16 and 17. Lines 15, 16 and 17 go through centre point 14 of the bearing and are created by rotation of symmetry axes 18, 19, 20 of sliding surfaces arcs 8, 9, 10 by angle α in the rotation direction of the shaft 21. Thus the origin 11 of radius R1 of sliding surface 8 is placed at the distance ε1 from centre 14 of the bearing bush and is rotated by angle α1 starting from symmetry axis 18 of sliding lobe 8 in the rotation direction of the shaft 21. Origin 12 of radius R2 of sliding surface 9 is placed at the distance ε2 from centre 14 and is rotated by angle α2 in the rotation direction of the shaft 21. Similarly, origin 13 of radius R3 of sliding surface 10 is placed at the distance ε3 from centre 14 and rotated. Lubricating oil is supplied to sliding surfaces through hole 22, through three oil pockets 23 and through circumferential groove 24, which connects pockets 23.
Amounts of sliding surface angular extension may vary in wide range from 30° to 180° for segment 1 and from 25° to 90° for segments 2 and 3 and depend on requirements to the bearing and the operating conditions.
The set of geometrical quantities - radii R and polar coordinates ε, α - depends on requirements posed on bearing features like high critical turning speed, high damping abilities for vibrations and loading capabilities during starting up and coasting processes. They also depend on the length to width ratio of the bearing, bearing clearance, oil viscosity and the shafts turning speed. The optimum bearing design for specified applications may be found by calculations made using computational programs based on hydrodynamic lubrication theory.
Claims
1. Journal bearing suitable especially for supporting steam turbine shafts, enabling appearance of hydrodynamic oil wedges and having three sliding surfaces, characterised in that: the sliding surfaces /8/, 191, /10/ are in form of three sliding lobes 151, 161, 111 covering three separate segments IM, 121, 13/ of the bearing bush, where the bottom segment IM take 180° in extent and the other two take each 90° in extent and where the sliding surfaces 181, 191, /10/ are shaped by radii IRl, at least two radii IRl have their origins displaced from the bearing bush centre /14/ by different amounts Id, at least one radii IRl has its origin on lines /15/, /16/, /17/ going through bearing bush centre /14/ and turned around it by angles /α/ measured from symmetry axes /18/, /19/, /20/ of sliding lobe arcs 181, 191, /10/ in the rotation direction of the shaft /21/.
2. Journal bearing characterised in claim 1 and characterised by sliding surfaces 181, 191, /10/ that are shaped by radii IRl of equal lengths.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PLP.329361 | 1998-10-23 | ||
PL98329361A PL329361A1 (en) | 1998-10-23 | 1998-10-23 | Radial plain bearing in particular that for steam turbine shafts |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2000025035A1 true WO2000025035A1 (en) | 2000-05-04 |
Family
ID=20073050
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/PL1999/000035 WO2000025035A1 (en) | 1998-10-23 | 1999-10-20 | Hydrodynamic journal bearing, particularly for steam turbines |
Country Status (2)
Country | Link |
---|---|
PL (1) | PL329361A1 (en) |
WO (1) | WO2000025035A1 (en) |
Cited By (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006007549A3 (en) * | 2004-07-01 | 2006-05-04 | Elliott Co | Four-bearing rotor system |
FR2916498A1 (en) * | 2007-05-24 | 2008-11-28 | Flender Graffenstaden | HYDRODYNAMIC CUSHION WITH ASYMMETRIC LOBES. |
EP2679842A1 (en) * | 2012-05-02 | 2014-01-01 | A&O Expert Olgierd Olszewski | Hydrodynamic journal bearing - especially for the use in steam turbine and other rotary equipment |
EP2362080A3 (en) * | 2010-02-18 | 2014-09-10 | Honeywell International Inc. | Multi-lobe semi-floating journal bearing |
ITMI20132181A1 (en) * | 2013-12-20 | 2015-06-21 | Ansaldo Energia Spa | SUPPORT EQUIPMENT FOR A ROTATING MACHINE TREE AND METHOD OF REPAIRING A ROTATING MACHINE USING SUCH A EQUIPMENT |
CN107906125A (en) * | 2017-12-22 | 2018-04-13 | 上海理工大学 | A kind of sound compression column body revolute pair |
CN107939836A (en) * | 2017-12-22 | 2018-04-20 | 上海理工大学 | A kind of dynamic pressure cone bearing |
CN107989900A (en) * | 2017-12-22 | 2018-05-04 | 上海理工大学 | A kind of dynamic pressure cylinder revolute pair |
CN108105258A (en) * | 2017-12-22 | 2018-06-01 | 上海理工大学 | A kind of dynamic and static pressure hemisphere revolute pair |
CN108105259A (en) * | 2017-12-22 | 2018-06-01 | 上海理工大学 | A kind of dynamic and static pressure cone bearing shafting and precision machine tool |
CN108119547A (en) * | 2017-12-22 | 2018-06-05 | 上海理工大学 | A kind of dynamic and static pressure cylinder bearing shafting and precision machine tool |
CN108131386A (en) * | 2017-12-22 | 2018-06-08 | 上海理工大学 | A kind of dynamic and static pressure cone revolute pair |
CN108131392A (en) * | 2017-12-22 | 2018-06-08 | 上海理工大学 | A kind of dynamic and static pressure hemisphere bearing shafting and precision machine tool |
CN108167332A (en) * | 2017-12-22 | 2018-06-15 | 上海理工大学 | A kind of high-precision motor device and precision equipment |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1048534A (en) * | 1963-03-15 | 1966-11-16 | Schmidt Gmbh Karl | Improvements in or relating to plain bearings |
US3680932A (en) | 1970-09-10 | 1972-08-01 | Westinghouse Electric Corp | Stable journal bearing |
US3738717A (en) * | 1971-09-27 | 1973-06-12 | Waukesha Bearings Corp | Flexible pad journal bearing |
JPS61236922A (en) * | 1985-04-12 | 1986-10-22 | Mitsubishi Heavy Ind Ltd | Static pressure bearing |
FR2651845A1 (en) * | 1989-09-08 | 1991-03-15 | Electricite De France | Multi-lobe bearing bush with no feed grooves for a hydrodynamic bearing |
-
1998
- 1998-10-23 PL PL98329361A patent/PL329361A1/en unknown
-
1999
- 1999-10-20 WO PCT/PL1999/000035 patent/WO2000025035A1/en active Application Filing
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1048534A (en) * | 1963-03-15 | 1966-11-16 | Schmidt Gmbh Karl | Improvements in or relating to plain bearings |
US3680932A (en) | 1970-09-10 | 1972-08-01 | Westinghouse Electric Corp | Stable journal bearing |
US3738717A (en) * | 1971-09-27 | 1973-06-12 | Waukesha Bearings Corp | Flexible pad journal bearing |
JPS61236922A (en) * | 1985-04-12 | 1986-10-22 | Mitsubishi Heavy Ind Ltd | Static pressure bearing |
FR2651845A1 (en) * | 1989-09-08 | 1991-03-15 | Electricite De France | Multi-lobe bearing bush with no feed grooves for a hydrodynamic bearing |
Non-Patent Citations (1)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 11, no. 82 (M - 571) 12 March 1987 (1987-03-12) * |
Cited By (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006007549A3 (en) * | 2004-07-01 | 2006-05-04 | Elliott Co | Four-bearing rotor system |
CN1981135B (en) * | 2004-07-01 | 2010-04-14 | 艾略特公司 | Four-bearing rotor system |
US7726883B2 (en) | 2004-07-01 | 2010-06-01 | Elliott Company | Four-bearing rotor system |
KR101173443B1 (en) | 2004-07-01 | 2012-08-16 | 엘리오트 컴퍼니 | A bearing apparatus for reducing vibrations in a compressor and Method for reducing vibrations in a shaft |
FR2916498A1 (en) * | 2007-05-24 | 2008-11-28 | Flender Graffenstaden | HYDRODYNAMIC CUSHION WITH ASYMMETRIC LOBES. |
WO2008149038A2 (en) * | 2007-05-24 | 2008-12-11 | Flender Graffenstaden S.A.S. | Hydrodynamic bearing with asymmetrical lobes |
WO2008149038A3 (en) * | 2007-05-24 | 2009-02-12 | Flender Graffenstaden S A S | Hydrodynamic bearing with asymmetrical lobes |
EP2362080A3 (en) * | 2010-02-18 | 2014-09-10 | Honeywell International Inc. | Multi-lobe semi-floating journal bearing |
EP2679842A1 (en) * | 2012-05-02 | 2014-01-01 | A&O Expert Olgierd Olszewski | Hydrodynamic journal bearing - especially for the use in steam turbine and other rotary equipment |
WO2015092764A1 (en) * | 2013-12-20 | 2015-06-25 | Ansaldo Energia S.P.A. | Supporting equipment for a shaft of a rotating machine, and method of repairing a rotating machine using such a supporting equipment |
ITMI20132181A1 (en) * | 2013-12-20 | 2015-06-21 | Ansaldo Energia Spa | SUPPORT EQUIPMENT FOR A ROTATING MACHINE TREE AND METHOD OF REPAIRING A ROTATING MACHINE USING SUCH A EQUIPMENT |
CN107906125A (en) * | 2017-12-22 | 2018-04-13 | 上海理工大学 | A kind of sound compression column body revolute pair |
CN107939836A (en) * | 2017-12-22 | 2018-04-20 | 上海理工大学 | A kind of dynamic pressure cone bearing |
CN107989900A (en) * | 2017-12-22 | 2018-05-04 | 上海理工大学 | A kind of dynamic pressure cylinder revolute pair |
CN108105258A (en) * | 2017-12-22 | 2018-06-01 | 上海理工大学 | A kind of dynamic and static pressure hemisphere revolute pair |
CN108105259A (en) * | 2017-12-22 | 2018-06-01 | 上海理工大学 | A kind of dynamic and static pressure cone bearing shafting and precision machine tool |
CN108119547A (en) * | 2017-12-22 | 2018-06-05 | 上海理工大学 | A kind of dynamic and static pressure cylinder bearing shafting and precision machine tool |
CN108131386A (en) * | 2017-12-22 | 2018-06-08 | 上海理工大学 | A kind of dynamic and static pressure cone revolute pair |
CN108131392A (en) * | 2017-12-22 | 2018-06-08 | 上海理工大学 | A kind of dynamic and static pressure hemisphere bearing shafting and precision machine tool |
CN108167332A (en) * | 2017-12-22 | 2018-06-15 | 上海理工大学 | A kind of high-precision motor device and precision equipment |
CN108167332B (en) * | 2017-12-22 | 2020-05-05 | 上海理工大学 | High-precision motor device and precision equipment |
CN108131392B (en) * | 2017-12-22 | 2020-05-29 | 上海理工大学 | Dynamic and static pressure hemispherical bearing shaft system and precision machine tool |
Also Published As
Publication number | Publication date |
---|---|
PL329361A1 (en) | 2000-04-25 |
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