WO2015125246A1 - 回転機械システム - Google Patents
回転機械システム Download PDFInfo
- Publication number
- WO2015125246A1 WO2015125246A1 PCT/JP2014/054001 JP2014054001W WO2015125246A1 WO 2015125246 A1 WO2015125246 A1 WO 2015125246A1 JP 2014054001 W JP2014054001 W JP 2014054001W WO 2015125246 A1 WO2015125246 A1 WO 2015125246A1
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- WO
- WIPO (PCT)
- Prior art keywords
- shaft
- compressor
- coupling
- baffle plate
- bearing
- Prior art date
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Classifications
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- 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
- F01D25/18—Lubricating arrangements
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/029—Gearboxes; Mounting gearing therein characterised by means for sealing the gearboxes, e.g. to improve airtightness
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- 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
- F01D13/00—Combinations of two or more machines or engines
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- 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
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
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- 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
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
- F16D3/56—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic metal lamellae, elastic rods, or the like, e.g. arranged radially or parallel to the axis, the members being shear-loaded collectively by the total load
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
- F16H57/0423—Lubricant guiding means mounted or supported on the casing, e.g. shields or baffles for collecting lubricant, tubes or pipes
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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
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0469—Bearings or seals
- F16H57/0471—Bearing
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2300/00—Special features for couplings or clutches
- F16D2300/06—Lubrication details not provided for in group F16D13/74
Definitions
- the present invention relates to a rotary machine system in which a plurality of rotary machines are connected to each other.
- a compressor applied to a plant facility or the like is driven by a drive source such as a steam turbine, for example.
- the rotating shaft of the steam turbine serving as the drive shaft and the rotating shaft of the compressor serving as the driven shaft are connected via a coupling such as a flange-type flexible shaft joint, for example, to transmit the torque of the steam turbine.
- a coupling such as a flange-type flexible shaft joint, for example, to transmit the torque of the steam turbine.
- a bearing device that performs lubrication by oil bath lubrication (forced lubrication) as a bearing device provided at the end of the rotating shaft.
- lubricating oil that is ejected from the bearing device during operation may be applied to the coupling. Since the coupling rotates at a high speed, when the lubricating oil is applied to the coupling, the temperature of the lubricating oil rises due to friction. When the temperature of the lubricating oil rises, the deterioration of the lubricating oil is accelerated, and it is not preferable when the lubricating oil is recovered and reused.
- An object of the present invention is to provide a rotating machine system that can suppress an increase in temperature of the lubricating oil in a rotating machine system having a bearing device to which the lubricating oil is supplied.
- a rotary machine system includes a first rotary machine having a drive shaft that can be driven around an axis, a driven shaft that is rotatable around the axis, and an end of the driven shaft that is driven by the shaft end.
- Rotating the drive shaft by connecting the drive shaft and the driven shaft to a second rotary machine having a bearing device that is slidably supported by the pad surface on the part side and supplied with lubricating oil to the pad surface
- a baffle that is provided between the bearing device and the coupling portion of the second rotary machine and separates the space on the bearing device side and the space on the coupling portion side.
- the baffle plate prevents the lubricating oil ejected from the bearing device from coming into contact with the rotating coupling portion, and no frictional heat is generated in the coupling portion, thereby suppressing the temperature rise of the lubricating oil. be able to.
- the coupling portion may include a disk-shaped disk portion protruding in a radial direction of the drive shaft and the driven shaft. According to such a configuration, a higher driving force can be transmitted to the driven shaft.
- the baffle plate has a plurality of support portions provided at intervals in the circumferential direction, and the baffle plate is an inner circumference of the casing of the first rotary machine or the second rotary machine. It is good also as a structure supported on the surface via the said support part.
- a gap can be provided between the baffle plate and the casing. Thereby, it can prevent that the pressure of the space between a baffle plate and a casing rises too much. Further, the pressure can be released from the upper gap, and the lubricating oil can be discharged from the lower gap.
- the lubricating oil ejected from the bearing device by the baffle plate does not come into contact with the rotating coupling portion, and frictional heat is not generated in the coupling portion, so that the temperature rise of the lubricating oil can be suppressed. it can.
- FIG. 3 is a cross-sectional view taken along the line AA in FIG. 2 and illustrates a shape of the baffle plate viewed from the axial direction.
- the rotary machine system 1 of the present embodiment is a system for compressing a gas such as air in plant equipment or the like, and a steam turbine 4 (first rotary machine) that is a drive source, steam And a compressor 2 (second rotating machine) driven by a turbine 4.
- the compressor 2 has a compressor rotation shaft 3 that is a driven shaft
- the steam turbine 4 has a turbine rotation shaft 5 that is a drive shaft.
- the compressor rotating shaft 3 and the turbine rotating shaft 5 are connected via a coupling portion 6.
- the steam turbine 4 is a rotary machine that converts the energy of steam into rotational motion via a turbine (impeller) and a shaft.
- the steam turbine 4 of the present embodiment includes a turbine casing 8 (see FIG. 2), a turbine rotating shaft 5 that is rotatably provided inside the turbine casing 8, and that transmits power to the compressor 2.
- a general configuration includes a stationary vane (not shown) that is held, a moving blade (not shown) provided on the turbine rotating shaft 5, and a bearing portion that rotatably supports the turbine rotating shaft 5 about its axis. Has been.
- the compressor 2 is a uniaxial multistage centrifugal compressor that compresses a gas such as air, for example.
- the compressor 2 includes a compressor casing 9 (see FIG. 2), a compressor rotating shaft 3 that is rotatably provided inside the compressor casing 9, and that is rotated by the driving force of the turbine.
- a compressor casing 9 see FIG. 2
- a compressor rotating shaft 3 that is rotatably provided inside the compressor casing 9, and that is rotated by the driving force of the turbine.
- impellers impellers
- FIG. 2 is a detailed cross-sectional view of the coupling unit 6, the compressor 2 in the vicinity of the coupling unit 6, and the steam turbine 4 in the vicinity of the coupling unit 6 of the rotary machine system 1 of the present embodiment.
- the compressor rotating shaft 3 of the compressor 2 is rotatably supported by a journal bearing 11 in the radial direction.
- the journal bearing 11 is a bearing which is lubricated by oil bath lubrication (forced lubrication) and supports the compressor rotating shaft 3 by a pad surface 37 so as to be slidable.
- the end of the compressor rotating shaft 3 not shown is supported by a journal bearing 13 and a thrust bearing 12.
- the turbine rotating shaft 5 of the steam turbine 4 is supported by an axial load by a thrust bearing 12 and is also rotatably supported by a journal bearing 13 in a radial direction.
- axial directions of the compressor rotating shaft 3 and the turbine rotating shaft 5 are simply referred to as axial directions.
- the coupling unit 6 includes an intermediate shaft 15, a first coupling 16 that connects the intermediate shaft 15 and the compressor rotation shaft 3, a second coupling 17 that connects the intermediate shaft 15 and the turbine rotation shaft 5, have.
- the intermediate shaft 15 has a cylindrical shape, and intermediate shaft flange portions 18 projecting in the radial direction are formed at both axial ends of the intermediate shaft 15.
- the intermediate shaft 15 is not limited to a cylindrical shape, and may be a solid structure.
- FIG. 3 is an enlarged view of the first coupling 16.
- the first coupling 16 is a joint known as a flange-type flexible shaft joint.
- the first coupling 16 is connected to the first joint member 19 attached to the compressor rotating shaft 3, and the second joint member 19 is connected to the first joint member 19 via a plurality of bolts 22 and nuts 23.
- a joint member 20 is attached to the shaft portion of the bolt 22.
- the bush 24 is formed of an elastic material such as a vibration proof rubber, for example.
- the first joint member 19 includes a cylindrical first hub part 25 and a disk-shaped first disk part 26 provided so as to protrude in the radial direction from the outer peripheral surface of the first hub part 25. .
- the inner diameter of the first hub portion 25 is formed so as to be fitted to the compressor rotation shaft 3 by fitting.
- the end portion of the compressor rotating shaft 3 connected to the first hub portion 25 is formed to be fitted by fitting with the inner diameter of the first hub portion 25.
- the end portion of the compressor rotating shaft 3 is fitted with the first hub portion 25 by hydraulic fitting.
- a plurality of first through holes 27 penetrating in the axial direction are formed in the first disk portion 26.
- the first through holes 27 are formed at equal intervals in the circumferential direction.
- the first through hole 27 is a hole for inserting the bolt 22.
- the inner diameter of the first through hole 27 is formed to be slightly larger than the shaft portion of the bolt 22.
- the second joint member 20 protrudes in the radial direction from the cylindrical second hub portion 29 formed so as to cover the first hub portion 25 of the first joint member 19 and the outer peripheral surface of the second hub portion 29. And a disk-shaped second disk portion 30 provided on the disk.
- the second disk part 30 is provided at one end of the second hub part 29. Specifically, the second disk portion 30 is disposed at an end portion that is closer to the center of gravity of the compressor rotation shaft 3.
- the inner diameter of the second hub portion 29 is formed so that the inner peripheral surface of the second hub portion 29 is in contact with the outer peripheral surface of the first hub portion 25 when the first joint member 19 and the second joint member 20 are connected.
- the outer diameter of the second disk portion 30 is formed to be substantially the same as the outer diameter of the first disk portion 26.
- a plurality of second through holes 31 penetrating in the axial direction are formed in the first disk portion 26.
- the second through holes 31 are formed at equal intervals in the circumferential direction.
- the second through hole 31 is a hole through which the bolt 22 and the bush 24 are inserted.
- the inner diameter of the second through hole 31 is formed to be substantially the same as the outer diameter of the bush 24 attached to the bolt 22.
- a joint flange portion 32 protruding in the radial direction is formed at the end portion of the second hub portion 29 opposite to the one end portion where the second disk portion 30 is provided.
- a spacer 33 is sandwiched between the first disk portion 26 of the first joint member 19 and the second disk portion 30 of the second joint member 20.
- the first disk part 26 of the first joint member 19 and the second disk part 30 of the second joint member 20 are connected via the spacer 33 and are not in direct contact with each other.
- the spacer 33 has a disk shape having a through hole for inserting the bolt 22 in the center.
- the center axis of the compressor rotating shaft 3 and the center axis of the intermediate shaft 15 do not coincide with each other. Even that madness can be tolerated.
- the intermediate shaft 15 and the first coupling 16 are connected by fastening the intermediate shaft flange portion 18 of the intermediate shaft 15 and the joint flange portion 32 of the first coupling 16 using a fastening member such as a bolt and a nut. Has been.
- the first journal bearing 11 includes an annular bearing casing 34, pivots 35 provided at equal angular intervals on the inner peripheral surface of the bearing casing 34, and swingable support on each pivot 35.
- Bearing pad 36 is provided.
- the pivot 35 is interposed between the bearing pad 36 and the bearing casing 34.
- the bearing pad 36 is divided in the circumferential direction. In the present embodiment, the bearing pad 36 is divided into four parts, and each bearing pad 36 is supported by a pivot 35.
- Each bearing pad 36 has an arc shape when viewed in a line of sight parallel to the axis of the compressor rotary shaft 3 and has a wide curved plate shape.
- the radius of curvature of the pad surface 37 of the bearing pad 36 is formed slightly larger than the radius of curvature of the outer peripheral surface of the compressor rotating shaft 3. That is, the entire pad surface 37 of the bearing pad 36 does not come into contact with the compressor rotating shaft 3.
- the pad surface 37 of the bearing pad 36 is formed of a soft metal such as white metal (babbit metal).
- the pivot 35 is formed to protrude from the bearing casing 34 in the radial direction of the compressor rotating shaft 3, and supports the bearing pad 36 at the center of the back surface of the bearing pad 36.
- the bearing pad 36 can swing in any direction. That is, the pivot 35 and the bearing pad 36 are in a contact state by point contact, and misalignment between the compressor rotating shaft 3 and the bearing device (the outer peripheral surface of the compressor rotating shaft 3 and the pad surface 37 of the bearing pad 36).
- the bearing pad 36 can follow the rotating shaft.
- an oil supply nozzle 38 which is a lubricating oil supply section, is provided toward the compressor rotating shaft 3, and a lubricating oil supply pump 39 is connected to these oil supply nozzles 38. ing. Accordingly, the lubrication oil supply pump 39 is driven to lubricate from the oil supply nozzle 38 toward the pad surface 37 of the bearing pad 36 adjacent to the oil supply nozzle 38 on the downstream side in the rotational direction R of the compressor rotation shaft 3. Oil will be supplied.
- a guard member 41 is attached to the compressor casing 9 and the turbine casing 8.
- the guard member 41 has a cylindrical shape, and is attached so as to cover the space between the compressor casing 9 and the turbine casing 8.
- a predetermined gap G ⁇ b> 1 is provided between the pair of guard members 41.
- the gap G1 between the guard members 41 has two functions.
- One function is a function of suppressing an excessive increase in the pressure of the space formed by the casings 8 and 9 and the guard member 41. That is, the upper gap G1 functions as an exhaust port (ventilation port, vent).
- the function as the exhaust port is not limited to that by the gap G1.
- exhaust ports may be formed in the casings 8 and 9.
- Another function of the gap G1 between the guard members 41 is to discharge the lubricating oil discharged from the journal bearings 11 and 13. That is, the lower gap G1 functions as a lubricant outlet.
- the function as a discharge port is not restricted to the thing by the gap G1.
- a discharge port may be formed in the casings 8 and 9.
- a baffle plate 7 is provided between the journal bearing 11 and the coupling portion 6 to separate the space on the journal bearing 11 side and the space on the coupling portion 6 side. (Shield plate) is attached.
- the baffle plate 7 is a disk-shaped member having a circular hole 42 at the center.
- the baffle plate 7 is disposed between the first journal bearing 11 and the first coupling 16 of the compressor 2 in the axial direction.
- the baffle plate 7 is attached to the inner peripheral surface of the compressor casing 9 via a plurality of support members 43.
- the support member 43 is attached to the inner peripheral surface of the compressor casing 9 by a fastening member such as a bolt, for example.
- the outer diameter of the baffle plate 7 is formed to be slightly larger than the outer diameter of the first disk portion 26 of the first coupling 16. Further, the outer diameter of the baffle plate 7 is dimensioned so as to form a gap G ⁇ b> 3 (see FIG. 5) with the inner peripheral surface of the compressor casing 9. Since the gap G3 is formed between the inner peripheral surface of the compressor casing 9 and the lubricant ejected from the first journal bearing 11 hits the baffle plate 7, the inner periphery of the compressor casing 9 is It flows on the surface, and is discharged through the lower gap G3 and the gap G1 between the guard members 41. The discharged lubricating oil is reused for lubricating the bearing device. The collected lubricating oil does not need to be reused and may be discarded.
- the gap G3 is formed between the baffle plate 7 and the inner peripheral surface of the compressor casing 9, air can be discharged from the upper gap G3, and the compressor casing 9 and the baffle plate 7 It can suppress that the pressure of the space formed by increases too much.
- the support member 43 is formed integrally with the baffle plate 7.
- the baffle plate 7 and the support member 43 are integrally formed by sheet metal processing.
- the support members 43 are formed at intervals in the circumferential direction.
- Four support members 43 of the present embodiment are formed at intervals (about 90 °) in the circumferential direction.
- the inner diameter of the hole 42 of the baffle plate 7 is slightly larger than the outer diameter of the compressor rotating shaft 3.
- a minute gap G4 is formed between the compressor rotating shaft 3 and the baffle plate 7. The minute gap G4 is preferably as small as possible if the contact between the baffle plate 7 and the compressor rotating shaft 3 can be avoided.
- the baffle plate 7 prevents the lubricating oil ejected from the first journal bearing 11 from coming into contact with the first coupling 16 of the rotating coupling portion 6. Thereby, when the compressor rotating shaft 3 rotates at a high speed, the frictional heat due to the lubricating oil adhering to the first coupling 16 is not generated, so that the temperature rise of the lubricating oil can be suppressed. Thereby, deterioration of the lubricating oil to be reused is suppressed.
- the first coupling 16 has the disk portions 26 and 30, a higher driving force can be transmitted to the driven shaft. Further, by providing the gap G3 between the baffle plate 7 and the compressor casing 9, it is possible to prevent the pressure in the space between the baffle plate 7 and the compressor casing 9 from rising excessively. it can. In addition, the pressure can be released from the upper gap G3, and the lubricating oil can be discharged from the lower gap G3.
- the first disk portion 26 is disposed at a position close to the center of gravity of the compressor rotating shaft 3, the weight distribution on the shaft end portion side from the first journal bearing 11 as the support portion can be improved.
- the steam turbine 4 is employed as a drive source.
- an electric motor such as an electric motor may be employed.
- the coupling part 6 becomes a structure which has the intermediate shaft 15, without providing the intermediate shaft 15, the 2nd coupling member 20 of the 1st coupling 16, and the 2nd coupling 17
- the second joint member 20 may be integrated.
- the turbine rotating shaft 5 of the steam turbine 4 and the compressor rotating shaft 3 of the compressor 2 may be directly connected by a coupling.
- baffle plate 7 may be installed on the steam turbine 4 side, or may be installed on both the compressor 2 side and the steam turbine 4 side.
- Rotating machine system Compressor (second rotating machine) 3 Compressor rotating shaft (driven shaft) 4 Steam turbine (first rotating machine) 5 Turbine rotating shaft (drive shaft) 6 Coupling part 7 Baffle plate 8 Turbine casing 9 Compressor casing (casing) 11 First journal bearing 12 Thrust bearing 13 Second journal bearing 15 Intermediate shaft 16 First coupling 17 Second coupling 18 Intermediate shaft flange portion 19 First joint member 20 Second joint member 22 Bolt 23 Nut 24 Bush 25 First Hub part 26 First disk part 27 First through hole 29 Second hub part 30 Second disk part 31 Second through hole 32 Joint flange part 33 Spacer 34 Bearing casing 35 Pivot 36 Bearing pad 37 Pad surface 38 Lubrication nozzle 39 Lubricating oil Supply pump 41 Guard member 42 Hole 43 Support member
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- Engineering & Computer Science (AREA)
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- Mechanical Engineering (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Sliding-Contact Bearings (AREA)
- General Details Of Gearings (AREA)
Abstract
Description
また、例えば、一軸多段遠心圧縮機などの大型回転機械においては、回転軸の端部に設けられる軸受装置として、油浴潤滑(強制潤滑)により潤滑を行う軸受装置を用いることが一般的である。
このような構成によれば、より高い駆動力を従動軸に伝達することができる。
図1に示すように、本実施形態の回転機械システム1は、プラント設備などにおいて空気などの気体を圧縮するためのシステムであり、駆動源である蒸気タービン4(第一回転機械)と、蒸気タービン4によって駆動される圧縮機2(第二回転機械)とを有している。圧縮機2は、従動軸である圧縮機回転軸3を有しており、蒸気タービン4は、駆動軸であるタービン回転軸5を有している。圧縮機回転軸3とタービン回転軸5とは、カップリング部6を介して連結されている。
本実施形態の蒸気タービン4は、タービンケーシング8(図2参照)と、タービンケーシング8の内方に回転自在に設けられ、動力を圧縮機2に伝達するタービン回転軸5と、タービンケーシング8に保持された静翼(図示せず)と、タービン回転軸5に設けられた動翼(図示せず)と、タービン回転軸5を軸回りに回転可能に支持する軸受部とを備えて大略構成されている。
圧縮機2は、圧縮機ケーシング9(図2参照)と、圧縮機ケーシング9の内方に回転自在に設けられ、タービンの駆動力によって回転する圧縮機回転軸3と、圧縮機回転軸3に圧縮機回転軸3とともに回転するように一体に取り付けられた複数のインペラ(羽根車、図示せず)と、圧縮機回転軸3を軸回りに回転可能に支持する軸受部とを備えて大略構成されている。
図2に示すように、圧縮機2の圧縮機回転軸3は、ジャーナル軸受11によって径方向の荷重を回転支持されている。ジャーナル軸受11は、油浴潤滑(強制潤滑)により潤滑され、パッド面37によって圧縮機回転軸3を摺動可能に支持する軸受である。図示しないが、圧縮機回転軸3の図示されていない方の端部は、ジャーナル軸受13、及びスラスト軸受12によって支持されている。
中間軸15は、円筒状をなし、中間軸15の軸方向両端部には、径方向に突出する中間軸フランジ部18が形成されている。なお、中間軸15は円筒状に限らず、中実構造としてもよい。
第一カップリング16は、フランジ形たわみ軸継手として知られる継手である。図3に示すように、第一カップリング16は、圧縮機回転軸3に取り付けられる第一継手部材19と、第一継手部材19と複数のボルト22・ナット23を介して接続される第二継手部材20とを有している。
ボルト22の軸部には、円筒状のブッシュ24が取り付けられている。ブッシュ24は、例えば、防振ゴムのような弾性を有する材料によって形成されている。
第一円盤部26は、第一継手部材19を圧縮機回転軸3に取り付けた際に、圧縮機回転軸3の軸方向の中心部側にオフセットして配置されている。換言すれば、第一円盤部26は、圧縮機回転軸3の重心により近い位置に配置されている。
第二ハブ部29の第二円盤部30が設けられている一方の端部とは反対側の端部には、径方向に突出する継手フランジ部32が形成されている。
中間軸15と第一カップリング16とは、中間軸15の中間軸フランジ部18と第一カップリング16の継手フランジ部32とがボルト・ナットなどの締結部材を用いて締結されることにより連結されている。
ピボット35は、軸受パッド36と軸受ケーシング34との間に介在している。軸受パッド36は、周方向に分割されている。本実施形態では、軸受パッド36は四個に分割されており、各々の軸受パッド36がそれぞれピボット35によって支持されている。
上述した構成により、軸受パッド36は、任意の方向に揺動可能とされている。即ち、ピボット35と軸受パッド36とは、点接触による接触状態であり、圧縮機回転軸3と軸受装置との間にミスアライメント(圧縮機回転軸3の外周面と軸受パッド36のパッド面37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36が回転軸に追従することができる。
ガード部材41間の隙間G1のもう一つの機能は、ジャーナル軸受11,13から排出される潤滑油の排出である。即ち、下方の隙間G1は、潤滑油の排出口として機能する。なお、排出口としての機能は、隙間G1によるものに限ることはない。例えば、ケーシング8,9に排出口を形成してもよい。
バッフルプレート7は、複数の支持部材43を介して圧縮機ケーシング9の内周面に取り付けられている。支持部材43は、例えば、ボルトのような締結部材によって、圧縮機ケーシング9の内周面に取り付けられている。
また、バッフルプレート7の外径は、圧縮機ケーシング9の内周面との間に隙間G3(図5参照)を形成するような寸法とされている。圧縮機ケーシング9の内周面との間に隙間G3が形成されていることによって、第一ジャーナル軸受11から噴き出た潤滑油は、バッフルプレート7に当たった後、圧縮機ケーシング9の内周面上を流れ、下方の隙間G3、ガード部材41間の隙間G1を介して排出される。排出された潤滑油は、軸受装置の潤滑に再利用される。なお、回収された潤滑油は再利用する必要はなく、廃棄してもよい。
バッフルプレート7の孔42の内径は、圧縮機回転軸3の外径よりも僅かに大きな寸法とされている。圧縮機回転軸3とバッフルプレート7との間には、微小隙間G4が形成されている。微小隙間G4は、バッフルプレート7と圧縮機回転軸3との接触を回避できれば、可能な限り小さくすることが好ましい。
また、バッフルプレート7と圧縮機ケーシング9との間に隙間G3が設けられていることによって、バッフルプレート7と圧縮機ケーシング9との間の空間の圧力が過度に上昇することを防止することができる。また、上方の隙間G3から圧力を逃がすとともに、下方の隙間G3から潤滑油を排出することができる。
例えば、上記実施形態では、駆動源として蒸気タービン4を採用しているがこれに限らず、電動モーターなどの電動機の採用も可能である。
2 圧縮機(第二回転機械)
3 圧縮機回転軸(従動軸)
4 蒸気タービン(第一回転機械)
5 タービン回転軸(駆動軸)
6 カップリング部
7 バッフルプレート
8 タービンケーシング
9 圧縮機ケーシング(ケーシング)
11 第一ジャーナル軸受
12 スラスト軸受
13 第二ジャーナル軸受
15 中間軸
16 第一カップリング
17 第二カップリング
18 中間軸フランジ部
19 第一継手部材
20 第二継手部材
22 ボルト
23 ナット
24 ブッシュ
25 第一ハブ部
26 第一円盤部
27 第一貫通孔
29 第二ハブ部
30 第二円盤部
31 第二貫通孔
32 継手フランジ部
33 スペーサ
34 軸受ケーシング
35 ピボット
36 軸受パッド
37 パッド面
38 給油ノズル
39 潤滑油供給用ポンプ
41 ガード部材
42 孔
43 支持部材
Claims (3)
- 軸線回りに駆動可能な駆動軸を有する第一回転機械と、
前記軸線回りに回転可能な従動軸、及び、前記従動軸を軸端部側でパッド面によって摺動可能に支持して前記パッド面に潤滑油が供給される軸受装置を有する第二回転機械と、
前記駆動軸と前記従動軸とを連結して、駆動軸の回転を従動軸に伝達するカップリング部と、
前記軸受装置と前記カップリング部との間に設けられて、前記軸受装置側の空間と前記カップリング部側の空間を隔てるバッフルプレートと、を備える回転機械システム。 - 前記カップリング部は、前記駆動軸及び前記従動軸の径方向に突出する円盤状の円盤部を有する請求項1に記載の回転機械システム。
- 前記バッフルプレートは周方向に間隔を開けて設けられた複数の支持部を有し、
前記バッフルプレートは、前記前記第一回転機械又は前記第二回転機械のケーシングの内周面に、前記支持部を介して支持されている請求項1又は請求項2に記載の回転機械システム。
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US14/894,252 US10113446B2 (en) | 2014-02-20 | 2014-02-20 | Rotary machine system |
PCT/JP2014/054001 WO2015125246A1 (ja) | 2014-02-20 | 2014-02-20 | 回転機械システム |
EP14883072.2A EP2990693B1 (en) | 2014-02-20 | 2014-02-20 | Rotating machine system |
JP2015542883A JP6101816B2 (ja) | 2014-02-20 | 2014-02-20 | 回転機械システム |
CN201480030148.8A CN105247248B (zh) | 2014-02-20 | 2014-02-20 | 旋转机械*** |
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PCT/JP2014/054001 WO2015125246A1 (ja) | 2014-02-20 | 2014-02-20 | 回転機械システム |
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US (1) | US10113446B2 (ja) |
EP (1) | EP2990693B1 (ja) |
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US10400883B2 (en) * | 2017-01-04 | 2019-09-03 | United Technologies Corporation | Gear with fluid control dam and apertures |
DE102017216701A1 (de) * | 2017-09-21 | 2019-03-21 | Robert Bosch Gmbh | Kippsegmentlager und Maschine mit wenigstens einem Kippsegmentlager |
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JP7333247B2 (ja) * | 2019-11-01 | 2023-08-24 | 三菱重工コンプレッサ株式会社 | アンモニアプラント合成ガス圧縮機トレイン |
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CN105247248A (zh) | 2016-01-13 |
EP2990693A4 (en) | 2017-02-15 |
CN105247248B (zh) | 2017-12-22 |
US20160123149A1 (en) | 2016-05-05 |
JPWO2015125246A1 (ja) | 2017-03-30 |
EP2990693B1 (en) | 2018-01-31 |
JP6101816B2 (ja) | 2017-03-22 |
US10113446B2 (en) | 2018-10-30 |
EP2990693A1 (en) | 2016-03-02 |
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